DE102004018317A1 - Heat exchanger for motor vehicles - Google Patents

Abstract

The invention relates to a heat exchanger for motor vehicles with a plurality of manifolds (22, 24, 26, 28) forming two spaced header pipe means (10, 12) and a plurality of connecting pipes (14a, 14b, 16a) disposed between these header pipes (10, 12) , 16b), which for the fluidic connection of the two header pipe means (10, 12) respectively open at one end into the one header pipe means (10) and at the other end into the other header pipe means (12), these tie pipes (14a, 14b, 16a, 16b) are arranged to form two adjacent rows of tubes (30a, 30b) through which the first medium can flow, each of a plurality of connecting tubes (5, 10b) in the longitudinal direction (10a, 10b) of the collecting tube means (10, 12). 14 a, 14 b, 16 a, 16 b) are formed, between each of which intermediate spaces (36 a, 38 a, 40 a, 36 b, 38 b, 40 b) are formed for an air flow (42), wherein i at least one of the manifold means (10, 12) acts as a deflection device, that in each of the rows of tubes (30a, 30b), the flow direction of the first medium between the two header pipe means (10, 12) is deflected at least once, and wherein the number of changes the flow directions between the header pipe means (10, 12) in the pipe rows (30a, 30b) is identical.

Description

The The invention relates to a heat exchanger or exchanger for Motor vehicles, and in particular a radiator for cooling refrigerant for a heating or air conditioning of motor vehicles, as well as a device for heating and / or air conditioning the passenger compartment of a motor vehicle with such a heat exchanger and a motor vehicle with such a heat exchanger.

Air conditioning systems of motor vehicles usually have a refrigerant circuit. The refrigerant used is increasingly carbon dioxide (CO ₂ ) in recent times. The cooling capacity of a CO ₂ cycle is largely determined by the gas cooler. In the design of such gas cooler is generally taken to ensure that they are pressure-stable even at high temperatures, have a low internal volume and exploit the space, taking into account low weight. In order to minimize power-reducing heat return flows, a sensible interconnection in areas through which the refrigerant flows can be a criterion in the design or arrangement of such gas coolers in motor vehicles.

The German patent application 102 29 973.0 of the applicant discloses a Gas cooler, in which a cross-countercurrent connection is given. At this Design two headers are provided, which are parallel and adjacent are arranged to each other. The two headers are over one Variety U-shaped curved flat tubes connected to each other with their free ends open into one of the headers. These flat tubes follow in the longitudinal direction the headers, wherein between two neigh disclosed flat tubes in each case a gap is formed through which air can flow, allowing a heat transfer between the guided in the flat tubes refrigerant and the flowing air allows becomes. The arranged on the same side of the flat tube package Both headers are each subdivided so that in these two Hoppers are each formed two chambers. A lower chamber of a manifold is fluidically connected to an upper chamber of the other manifold via a transition piece connected. This transition piece can be in of any height of the gas cooler be attached and allows a passage of the refrigerant flowing through from the air-remote area in the air-facing area, or also vice versa. An objective of this embodiment is through skillful refrigerant guide reheating of the already cooled refrigerant to prevent by warm engine return currents.

From the German patent application 102 52 263.4 of the applicant, an embodiment of the gas cooler with four manifolds is known, of which two are arranged in pairs adjacent to form a header pipe device. The two header pipe means formed thereby are spaced apart from each other and fluidly connected via a plurality of connecting pipes or gas cooler pipes. These gas cooler tubes run in two spaced planes, or form two rows of tubes. They are each designed substantially straight and open with their distal ends in each case in one of the two manifolds devices, or in separate manifolds. In this design, so instead of from the DE 102 29 973.0 known pipe forks or U-shaped flat tubes used two equal length tubes. In the headers two axially spaced chambers are formed in each case. On a gas cooler side, a lower chamber of one header pipe is fluidly connected to an upper chamber of the other header via a transition piece. The connecting tubes are connected so that the refrigerant first flows through the entire end face plane and passes through the transition piece in the front or behind lying end face plane at closing.

at the aforementioned designs a transition piece is necessary, the surface quadrant with each other combines. Both the production and the installation of such a transition piece is costly and can cause leaks, especially if different Temperatures of the quadrants claim the solder joints in addition. moreover can the transfer forming a bottleneck, which is the refrigerant side Pressure drop may adversely affect, allowing a lower refrigerant flow The result is. Furthermore go in the crossing area one to two Pipe rows for the cooling capacity lost. A parallel flow solution is not achievable with this type.

From the EP 0 414 433 B1 a heat exchanger is known in which two parallel arranged flat tube rows are formed, each of which fluidly connect two spaced manifolds. Between in the longitudinal direction of the manifolds adjacent flat tubes each ribs are provided in the respective rows through which air can flow through the heat exchanger transversely to the longitudinal extent of the flat tubes. The inflow is connected on the same side of the heat exchanger with two rows of flat tubes. In the row of pipes facing the fresh air, the flow direction changes once and in the row of pipes facing away from the fresh air, the flow direction changes three times.

The invention is based on the object, a heat exchanger for motor vehicles, in particular to provide cooler for cooling refrigerant for a heating or air conditioning system of a motor vehicle, which shows a good transmission behavior, and can be produced inexpensively and manufacturing technology.

According to the invention is a Heat exchanger according to claim 1 or according to claim 2 or according to claim 4 proposed. An inventive device for heating and / or air conditioning the Fahrzastzel le of a motor vehicle Subject of claim 13. A motor vehicle according to the invention is the subject of claim 14. Preferred embodiments are subject of the dependent claims.

Preferably each header pipe device has at least two header pipes. Particularly preferably, each header pipe device for each row of connecting pipes or for every partial heat exchanger each separate headers. In particular, it is provided that the longitudinal axes this collecting pipes of each same header pipe device spaced are, and for example parallel to each other. A manifold can also of several separate, and in particular concentric, header pipe sections are formed, which are spaced in the axial direction, namely forming a gap or without forming such gaps.

In Particularly preferred embodiment are two manifold rows or two partial heat exchangers provided, wherein the two manifold rows each two parallel and offset from one another arranged collecting pipes. there flow in the respective one manifold connecting pipes of a connecting pipe row or of a partial heat exchanger and in the respective other manifold connecting tubes of the other row of tubes or the other part heat exchanger. It So in particular four headers are provided in this case.

Preferably are the partial heat exchangers respectively essentially identical. It can be provided that they differ by the position of their inlet and / or outlet, and otherwise identically designed. However, it is preferred provided that different layers of inlet and / or outlet opening are so, that they still - in Regarding the different partial heat exchangers - in each other corresponding areas or chambers open.

The Connecting pipes are preferably each flat tubes. It is provided in a particularly preferred embodiment, that their respective - two - end across from the intermediate area are twisted or twisted. Of the Twist angle is preferably between 10 ° and 110 °, in particular preferably between 80 ° and 100 °. He is for example, substantially 90 °.

In Particularly preferred design, the flat tubes open with their twisted or twisted end portions each so in headers, that their cross sections - perpendicular to the longitudinal axis of Flat tubes seen - in Essentially in the direction of the longitudinal axes extend the headers. Most preferably, they extend - apart from the twisted or twisted transition areas - between the end areas with their longer ones Sides of cross-sectional areas perpendicular to the longitudinal axes the headers.

The Connecting pipes, in particular flat pipes, can be designed such that they form exactly one channel in their interior, or so that in theirs Inside each train several, in particular each parallel, channels. All Connecting pipes are preferably designed to be straight throughout. Especially all are preferred Connecting pipes parallel to each other. In an advantageous design are all Connecting pipes the same length. It is further preferred that all Collecting tubes are the same length. The headers preferably have each a circular Inner cross section on. The headers can, for example, each essentially rotationally symmetrical with respect to its respective longitudinal axis be designed.

The Connecting pipes of a respective connecting pipe row or a respective partial heat exchanger are preferably arranged in a respective plane. Especially to be preferred embodiment, the levels determined thereby various connecting pipe rows or partial heat exchanger parallel and offset from each other.

The different connecting pipe rows or partial heat exchangers are in a preferred embodiment arranged to each other, that transversely to the connecting pipes flowing air successively formed by the between the connecting pipes interspaces the various connecting pipe rows or partial heat exchanger flows. It is in particular provided that air, in particular a second heat transfer medium forms, successively or in series through the various connecting pipe rows or partial heat exchanger flows, outside the connecting pipes. It is therefore provided in particular that the second heat exchange medium, in particular air, in cross-flow on the first heat exchange medium, in particular Refrigerant past is going to heat transfer to effect.

Preferably, in a respective connecting pipe row or a respective part-Wärmeü Bertrager each connected a plurality of connecting pipes in parallel. This can in particular be such that in each case a plurality of such connecting tubes are flowed through in parallel in a respective connecting tube row, and then - in particular in the opposite flow direction - other connecting tubes of the same connecting tube row or the same partial heat exchanger are also flowed through in parallel. This can be such that each pair of connecting tubes or partial heat exchangers several groups of parallel flowed through connecting tubes are connected by means of associated manifolds in series such that the connecting tubes of successive groups each in opposite directions of flow of the first medium, in particular refrigerant, are flowed through. It can be provided, in particular, that the first medium is conducted in a serpentine manner in each of the partial heat exchangers or connecting tube rows.

The Number of diversions or the respective consecutive, opposite flow directions is preferably in the partial heat exchangers or connecting pipe rows identical. It can be provided that the number of connecting pipes, each one group of in the flow direction flowed through in parallel Connecting pipes forms, in a respective connecting pipe row or a respective partial heat exchanger downstream increases or decreases or is identical.

there are two or more of such groups in the respective partial heat exchanger or the respective Connecting tube row connected in series. Also other designs are preferred.

In at least one header pipe device partition walls are preferably introduced. Particularly preferred is in different headers of the same Collecting tube means each provided at least one partition. Such partitions are in particular such that they separate areas or chambers, the longitudinal of the respective manifold follow each other. It can also be provided be that in both header pipe facilities or the corresponding Hoppers each provided at least one partition. It can also in the headers of the same header pipe device each be provided a plurality of axially spaced partitions, wherein particularly preferred is the number of partitions in different headers the same header pipe device is identical.

Preferably a thermal separation is provided between connecting pipe groups, which are successively flowed through in opposite directions. For this purpose, for example, the pitch or the distance adjacent Connecting pipes between these groups should be larger than inside the respective groups.

The two or adjacent partial heat exchanger can be arranged relative to each other so that they contact each other. You can for example soldered together be. Inside the formed from the headers and the connecting pipes System flows preferably only one medium, the first medium, such as refrigerant. The second heat exchange medium, like air, flows preferably outside during operation past the connecting pipes, in particular transversely to the longitudinal extent the connecting pipes. The heat exchanger or heat exchanger according to the invention is preferably a gas cooler or capacitor for a motor vehicle. The heat exchanger is preferably aluminum.

According to the invention is further a device according to claim 13 proposed.

According to the invention is further a motor vehicle according to claim 14 proposed. The heat exchanger according to the invention is preferred installed in the motor vehicle that through the partial heat exchanger or the rows of tubes respectively spanned planes across, in particular perpendicular, are located to the direction of travel. It is further preferred that a fan for the Heat exchanger according to the invention is provided, which in operation air through the between the connecting pipes formed spaces drives. The heat exchanger is preferred arranged with respect to the internal combustion engine of the motor vehicle that the area of the refrigerant inlet warmer by a return flow Air from the internal combustion engine is heated more than the range of Refrigerant leakage.

in the Below are embodiments of the Invention explained with reference to FIG .. It shows:

1 an exemplary heat exchanger according to the invention in a schematic representation;

2 a flow guide of the refrigerant in the design according to 1 prizipmäßig performing scheme;

3a a first exemplary design and arrangement of rows of tubes and corrugated fins;

3b a second exemplary design and arrangement of rows of tubes and corrugated fins; and

3c a third exemplary design and arrangement of rows of tubes and corrugated fins.

1 shows an exemplary heat exchanger or heat exchanger according to the invention 1 with a first header pipe device 10 , a second header pipe device 12 , a variety of connecting pipes 14a . 14b . 16a . 16b as well as with an entrance opening 18 and an exit opening 20 for a first medium, such as in particular carbon dioxide (CO ₂ ).

The heat exchanger 1 can be used in an advantageous manner as a gas cooler or condenser for an air conditioning or heating of a motor vehicle. It can be provided that this gas cooler or condenser is flowed through by a refrigerant, which is CO ₂ in a particularly advantageous design.

The header pipe facilities 10 . 12 each have two manifolds 22 . 24 respectively. 26 . 28 on. The headers 22 . 24 the first header pipe device 10 as well as the headers 26 . 28 the second manifold device 12 are each arranged adjacent in pairs, in particular so that their longitudinal axes 22a . 24a respectively. 26a . 28a extend parallel and spaced. Furthermore, the longitudinal axes 22a . 24a parallel to the longitudinal axes 26a . 28a arranged or is the longitudinal axis 10a the first header pipe device 10 parallel to the longitudinal axis 12a the second manifold device 12 arranged.

The heat exchanger 1 has two rows of tubes 30a . 30b on. These rows of pipes 30a . 30b each of a variety of connecting pipes 14a . 16a respectively. 14b . 16b formed, which - in the longitudinal direction 10a . 10b the headers facilities 10 . 12 seen - follow one another, with the longitudinal axes of these connecting pipes 14a . 16a respectively. 14b . 16b are aligned parallel to each other.

The row of pipes 30a is adjacent to the row of pipes 30b arranged, wherein the or all connecting pipes 14a . 16a the first row of pipes 30a each the first manifold 22 the first header pipe device 10 with the first manifold 26 the second manifold device 12 connect, and wherein the or all connecting pipes 14b . 16b the second row of pipes 30b in each case the second manifold 24 the first header pipe device 10 with the second manifold 28 the second manifold device 12 connect. The to a row of pipes 30a respectively. 30b belonging connecting pipes lie in one plane. The longitudinal axes of the or all connecting pipes 14a . 14b . 16a . 16b each perpendicular to the longitudinal axes 10a . 12a the headers facilities 10 . 12 ,

The connecting pipes 14a . 14b . 16a . 16b or the rows of pipes 30a . 30b are in the design according to 1 arranged essentially according to the way it is based on the 3a is explained or shown. In particular, ribs or corrugated ribs are 70 intended. But it can also be provided that this design is in another way, for example, as it is based on the 3b or on the basis of 3c is explained or shown. It can thus be provided in particular that the tube rows 30a . 30b to each other by the amount t / 2 (half pitch) are arranged offset, in particular in the longitudinal direction of the header pipe means 10 . 12 seen. It can be provided that instead of each continuous common corrugated fins 70 (see. 3a ) in each case two separate corrugated ribs 70a . 70b are provided (see. 3b ). But it can also be provided that in each case a common, stepped corrugated fin 70 is provided (cf. 3c ).

The connecting pipes 14a . 14b . 16a . 16b are straight between their opposite ends and designed as flat tubes. The planes which are spanned by the main extension direction of the respective flat tubes lie in each case perpendicular to the longitudinal axes 10a . 12a the headers facilities 10 . 12 ,

However, the respective opposite end portions of the flat tubes are twisted in a preferred design to the longitudinal axis of the respective flat tube, and preferably by 90 °, but it can also be given different angles of rotation. In designs in which the twist angle is 90 ° is preferably provided that the main extension direction of these ends - viewed in cross-section perpendicular to the longitudinal axis of the respective flat tube - in the direction of the longitudinal axes 10a . 12a is located. Between these ends, the corresponding main extension direction of the or of all flat tubes - as already mentioned - substantially perpendicular to the longitudinal axes 10a . 12a the headers facilities 10 . 12 , This has the advantage that smaller (inside) cross sections of the headers 10 . 12 can be realized. For example, in the design after 14 and 15 of the EP 0 814 433 B1 the inner diameter of the headers down through the flat tube width limited, which according to the invention does not necessarily have to be. But it can also be larger than the flat tube width according to the invention, the respective inner diameter of the manifolds.

The or all headers 22 . 24 . 26 . 28 have in an advantageous design a circular inner cross-section, in particular continuously. Particularly preferably, its outer sheath can be designed circular or cylindrical.

With their respective opposite ends (the Vibindungsrohre), the most advantageous way may be formed that the respective openings provided there are arranged on the front side, these are connecting pipes 14a , 16a . 14b . 16b each in the header pipe facilities 10 . 12 plugged in, so that the two header pipe facilities 10 . 12 over each of the connecting pipes 14a . 16a . 14b . 16b are fluidically connected. The connecting pipes 14a . 16a open on the one hand in the first manifold 22 the first header pipe device 10 and on the other hand into the first manifold 26 the second manifold device 12 , and the connecting pipes 14b . 16b on the one hand lead into the second manifold 24 the first header pipe device 10 and on the other hand into the second manifold 28 the second manifold device 12 , For this purpose, corresponding openings in the lateral surfaces of the manifolds are formed, which are each slot-shaped in an advantageous configuration, and particularly preferably extend in the longitudinal direction of the respective manifold. It may also be provided that such slots are dimensioned so that they can accommodate the ends of several connecting pipes. But it is also preferable that each slot receives exactly one connecting pipe. The connecting pipes 14a . 16a . 14b . 16b are in these areas each with the relevant headers 22 . 24 . 26 . 28 or manifolds connected, in particular soldered, preferably brazed.

The - each - two transition areas between the two twisted or twisted end portions 32 respectively. 34 , on the one hand, and the area located between these ends, on the other hand, can serve, for example, as a stop; in other words, the connecting pipes can 14a . 16a . 14b . 16b with their ends 32 . 34 each inserted into a collecting tube as far as the area located between these ends - which is twisted relative to the ends and vice versa, strikes the respective affected manifold. These transition areas can thus form an assembly aid. However, the ends can also be inserted so that it does not come to a striking in the aforementioned sense.

Between each adjacent connecting pipes 14a . 16a the first row of pipes 30a are each interspaces 36a . 38a . 40a formed for the air flow. In a corresponding manner between each adjacent connecting pipes 14b . 16b the second row of pipes 30b each intermediate spaces 36b . 38b . 40b formed for the air flow. Transverse to the longitudinal direction of the connecting pipes 14a . 16a . 14b . 16b can the heat exchanger 1 thus be traversed by air, so that in operation between the through the connecting pipes 14a . 16a . 14b . 16b flowing medium and through the spaces 36a . 38a . 40a . 36b . 38b . 40b flowing air heat can be transferred. The flowing air and its flow direction is in 1 schematically by the arrow ends or arrows 42 indicated. In the intervals 36a . 38a . 40a are advantageously arranged ribs. These can be traversed in the air flow direction of air.

The first collection pipe 22 the first header pipe device 10 , the first collection pipe 26 the second manifold device 12 , and those in these headers 22 . 26 with their ends opening connecting pipes 14a . 16a form a first partial heat exchanger or first partial cooler 44a of the heat exchanger 1 ; in a corresponding manner form the second manifold 24 the first header pipe device 10 , the second manifold 28 the second manifold device 12 , and those in these headers 24 . 28 with their ends opening connecting pipes 14b . 16b a second partial heat exchanger or second partial cooler 44a of the heat exchanger 1 , These partial heat exchangers 44a . 44b are in the air flow direction 42 arranged one behind the other, wherein in a particularly preferable embodiment, the spaces 36a . 38a . 40a the first part heat exchanger 44a aligned with those of the second part heat exchanger.

In the longitudinal direction of the headers 22 . 24 . 26 . 28 seen has the heat exchanger 1 one end plate at the top and bottom 46 . 48 on. These end plates 46 . 48 For example, they may be such that they essentially cover the arrangement of the connecting tubes-viewed in the longitudinal direction and transversely thereto. In particular, they can cover both rows of connecting pipes. They can also be such that they additionally cover the headers at the top and bottom; but these can also be each end of the end plates 46 . 48 have different closures. The end plates 46 . 48 can be formed for example by sheets.

One or more manifolds 22 . 24 are each with at least one partition 50 . 52 Mistake. Through such partitions 50 . 52 can have different chambers 54 . 56 respectively. 58 . 60 in the respective manifold 22 respectively. 24 be formed. This may in particular be such that the partition 50 respectively. 52 chambers 54 . 56 respectively. 58 . 60 separates, which may be arranged adjacent in the axial direction of the respective manifold.

A partition 50 . 52 can for example - as in 1 shown - on the inlet side or refrigerant inlet side or the one or more collecting tubes arranged there 22 . 24 be provided, or in the headers in which the inlet openings for the entry of the first medium, such as CO ₂ , are arranged.

According to 1 have both manifolds 22 . 24 , which lie on the refrigerant inlet side, in each case a partition wall 50 . 52 on; It can be provided in particular that all manifolds 22 . 44 the first header pipe device in each case a partition 50 . 52 exhibit.

The partitions 50 . 52 in different or the two headers 22 . 24 the same header pipe device 10 can be positioned so that they demarcate area or volume equal areas. This may in particular be such that in the one 22 the headers 22 . 24 through the partition wall positioned there 50 delimited areas are equal in area or volume with the areas in the other 24 of the two headers 22 . 24 through the partition wall provided there 52 be demarcated. It is especially provided that these two manifolds 22 . 24 are the same length. It can also be independent of the location of such partitions 50 . 52 be provided that the headers 22 . 24 respectively. 26 . 28 the same header pipe device 10 respectively. 12 are the same length. Furthermore, it can be provided that all manifolds 22 . 24 . 26 . 28 are the same length. In an advantageous design are also all connecting pipes 14a . 14b . 16a . 16b of equal length.

It can - as in 1 shown - be provided that the headers 22 . 24 . 26 . 28 - and in particular the adjacent ones 22 . 24 respectively. 26 . 28 - are aligned with each other at their ends.

In the design according to 1 have the (two) manifolds 22 . 24 the first header pipe device 10 , which lie on the refrigerant inlet side, in each case a partition wall 50 . 52 which separate the "warm" and "colder" zones. The two partitions delimit areas of equal area or volume equal to each other. It can also be provided that the partitions 50 . 52 delimiting different areas or slightly different areas. For example, it may be provided to design the area facing the fresh air by 1 to 3 flat or connecting pipes differently. But is particularly advantageous hen vorgese that the partitions 50 . 52 are located so that in the thus separated areas of the headers 22 . 24 the same header pipe device 10 in each case the same number of connecting pipes opens.

That through the entrance opening 18 entering refrigerant there advantageously has an inlet temperature which is in the range of 150 ° C to 180 ° C. By means of the air flowing transversely to the connecting tubes of this refrigerant is cooled along the flow paths. This can be done, for example, that the outlet temperature of the refrigerant is about 50 to 140 Kelvin below the inlet temperature. For example, the inlet temperature about 180 ° C and the outlet temperature about 45 ° C.

The entrance opening 18 the heat exchanger forms a common inlet opening, through which the subsequently - in the flow direction - to the two partial heat exchanger 44a . 44b split medium occurs. To enter the two partial heat exchangers 44a . 44b is downstream of the inlet 18 one in 1 not shown inlet opening in the first manifold 22 the first header pipe device 10 provided, as well as a likewise in 1 not shown inlet opening in the second manifold 24 the first header pipe device 10 , In a corresponding manner forms the outlet opening 20 of the heat exchanger 1 a common outlet opening, wherein in the first manifold 22 the first header pipe device 10 as well as in the second manifold 24 the first header pipe device 10 each outlet openings, not shown, are provided, the upstream of the outlet opening 20 are provided.

The medium is in the design after 1 Guided so that it is on the entry side, here on the side of the first header pipe device 10 is located, also exits again; It can also be provided that the inlet side and the outlet side of the heat exchanger 1 are located on different sides, so for example, the inlet side on the side of the first header pipe device 10 and the exit side on the side of the second header pipe device 12 , wherein then outlet openings in the first 26 and second manifold 28 the second manifold device 12 are provided, and the common outlet opening 20 downstream of these outlets on the side of the second header pipe means 12 is located.

In the area of the entrance opening 18 and the outlet opening 20 is in each case a flange or fluid connector 62 . 64 provided for the entering or exiting medium, in which the inlet opening 18 or the outlet opening 20 is provided.

In the design after 1 act or acts as a manifold - or respectively their manifolds - as a deflection.

After the refrigerant of both rows of tubes 30a . 30b the heat exchanger 1 in its width, it is in the two opposite headers 26 . 28 deflected, then on the entry side the heat exchanger 1 to leave again.

But it can also be provided that the medium or refrigerant is guided serpentine by using multiple partitions. This can, for example, lead to the inlet and outlet of the refrigerant being positioned diagonally. However, more partitions, which may be partially positioned in the header pipes of the first header pipe means and partly in the headers of the second header pipe means, may also be arranged so that the refrigerant exits again on the inlet side.

It can also be provided that between the warm and the cold Zone or respectively adjacent, through-flow in opposite directions connecting pipes the same part heat exchanger or the same row of pipes given a thermal break is. This can be achieved, for example, by the fact that the Collecting pipes in the places where the dividing wall comes to rest, one gets another division, so that the rib there only at one of the (two) adjacent Connection or Flat tubes one or a respective connection or flat tube row is soldered.

The pitch or the distance between adjacent connecting or flat tubes can be the same in each case. It may be provided that to achieve a thermal separation in the transition region between one or the colder zone and one or the warmer zone, a greater distance between the adjacent, through-flow in different directions connecting pipes of each same connecting pipe row 30a . 30b given is. It can be provided that the extension of all ribs in the direction of the longitudinal axes 10a . 12a the header pipe equipment is identical. These ribs can, for example, with each (in the longitudinal direction 10a . 12a seen) soldered adjacent connecting pipes. It can also be provided that the ribs each extend over both partial heat exchangers, so that between each adjacent connecting tubes in each case one for both partial heat exchanger or both rows of tubes 30a . 30b common rib is provided.

If a thermal separation is provided, it can be provided that in the region in which there is a greater distance between adjacent connecting tubes for thermal separation, the rib arranged there or the ribs arranged there is only in one of them in the longitudinal direction 10a . 12a is soldered adjacent connecting pipes.

Ribs may be in the connecting pipe rows 30a . 30b each also between the upper end plate 46 and in the longitudinal direction 10a . 12a adjacent connecting pipe 14a respectively. 14b be given. Further, ribs in the connecting pipe rows 30a . 30b in each case also between the lower end plate 48 and in the longitudinal direction 10a . 12a adjacent connecting pipe 14a respectively. 14b be given a respective connecting pipe row.

In an advantageous embodiment, the heat exchanger 1 which is the two part heat exchanger 44a . 44b has, integrally designed or connected to a one-piece part. It can be designed in an advantageous embodiment as Lötkonstruktion.

Instead of a manifold, passing through a partition 50 . 52 in chambers 54 . 56 . 58 . 60 is divided, also separate axially spaced or successive collecting pipe sections may be provided, wherein preferably, the cross-sections of such collecting pipe sections are identical, and these are arranged concentrically.

When designing after 1 are in the same part heat exchanger 44a . 44b On the input side each less (in the same flow direction) flowing through parallel connecting pipes provided as the output side.

The partial heat exchangers 44a . 44b are in the design according to 1 each designed identically, in particular with regard to the flow guidance between the inlet opening and the outlet opening of the respective partial heat exchanger 44a . 44b , Also, the ribs can - especially if not provided common - can in both partial heat exchangers 44a . 44b be identically designed and arranged. The identical flow guide may have fluidic advantages in certain applications. Particularly advantageous can be provided that both partial heat exchangers are designed identically, which is manufacturing technology advantageous, especially since the variety of differently shaped parts can be reduced. It should be noted, however, that the respective inlet and outlet openings of the two partial heat exchangers can be positioned differently, in particular so that they are twisted at different heights and / or around the longitudinal axis of the headers into corresponding chambers; but they can also be designed in the same way.

It is particularly in the design according to 1 provided that the first medium, in particular refrigerant, upon entry into the first header pipe means 10 in at least two partial streams, preferably exactly two partial streams, on the connecting pipes 14a . 16a respectively. 14b . 16b , in particular flat tubes, the first row of tubes 30a and the second rows of tubes 30b is split. This may in particular be such that this distribution by means of of the connector 62 is effected for the entry of first medium. For example, it can be provided for this purpose that the connection piece 62 has at least one inlet opening and at least two outlet openings, wherein via one of these outlet openings a flow connection with the interior of the first collection tube 22 the first header pipe device 10 is generated, and wherein via another of these outlet openings, a flow connection with the interior of the second seed tube 24 the first header pipe device 10 is produced. Corresponding openings, the entry of the medium in the headers 22 . 24 allow are in the headers 22 . 24 intended. The volume flow of the first medium can be divided, for example, in the ratio of 50%: 50%; but also softening conditions are preferred.

The refrigerant occurs - preferably considering the location of the warmest Zone - over the Flange in both rows simultaneously.

The heat exchanger 1 according to 1 has - especially by using two narrow rows of flat tubes and / or by using thin-walled headers a low weight. A costly transition piece is eliminated and the soldering security is increased. A refrigerant side pressure drop is reduced. All flat tubes contribute to the cooling capacity, which causes an increase in performance.

2 schematically shows the flow guide to the design 1 ,

2 can also be seen that the first medium entering the first header pipe device 10 in two partial flows on the flat tubes or connecting pipes 14a . 16a respectively. 14b . 16b , the first row of pipes ( 30a ) and the second row of tubes ( 30b ) is divided.

3a . 3b and 3c show - each in a partially sectioned view - exemplary embodiments for the rows of tubes 30a . 30b or their relative arrangement or exemplary embodiments for the design of ribs which are arranged between connecting tubes of the rows of tubes. These in the 3a to 3c shown embodiments may be given in a preferred embodiment of embodiments of the invention, in particular in the design according to 1 respectively. 2 , It should be noted that the number of ribs or connecting tubes (each row) is usually larger or significantly larger than in the 3a to 3b is shown schematically or in part.

In the designs according to the 3a to 3c is provided that corrugated ribs or ribs 70 in intervals 36a . 36b respectively. 38a . 38b respectively. 40a . 40b , preferably in all spaces 36a . 36b . 38a . 38b . 40a . 40b , which are positioned between each adjacent connecting tubes 14a - 14a , respectively. 14a - 16a respectively. 16a - 16a respectively. 14b - 14b , respectively. 14b - 16b respectively. 16b - 16b the rows of pipes 30a . 30b given are.

In the designs according to the 3a to 3b In particular, it is provided that the division t of the first row of tubes 30a the division t of the second row of tubes 30b corresponds, and is particularly preferably constant. It can also be provided that between successive, through-flow in opposite directions connecting pipes 14a - 16a respectively. 14b - 16b in the respective rows of pipes 30a . 30b a different distance of these connecting pipes or a different pitch is provided. This deviating distance or deviating pitch may be greater, for example, for the purpose of thermal separation than between the remaining, respectively adjacent connecting tubes of the same row of tubes 30a . 30b ,

In the 3a to 3b illustrates the respective arrow 42 the (preferred) inflow direction of the air. It should be noted that like reference numerals in the figures essentially denote corresponding parts.

3a shows an exemplary configuration in which the connecting pipes of adjacent rows of pipes 30a . 30b are not substantially offset from each other. Perpendicular to the longitudinal direction of the rows of tubes 30a . 30b seen is adjacent to each connecting pipe 14a respectively. 16a the first row of pipes 30a a connecting pipe 14b respectively. 16b the second row of pipes 30b is arranged. In this connection, it should be noted, however, that the number of connecting pipes in the two pipe rows can also be different, so that not next to each connecting pipe 14a respectively. 16a the first row of pipes 30a a connecting pipe 14b respectively. 16b the second row of pipes 30b is arranged. In the design according to 3a are the connecting pipes 14a . 14b respectively. 16a . 16b designed as flat tubes, with adjacent flat tubes of different rows of tubes 30a . 30b span essentially the same levels.

Ribs 70 are in the design according to 3a common or continuous ribs 70 for both rows of tubes 30a . 30b , So it is envisaged that the ribs 70 each between adjacent connecting pipes 14a respectively. 16a the first row of pipes 30a and between adjacent connecting pipes 14b respectively. 16b the second row of pipes 30b extend, in particular, it is provided that these ribs 70 each designed in one piece are.

3b shows a design in which the rows of tubes 30a . 30b mutually offset by half the pitch t / 2 are arranged. In the design according to 3b are for the rows of pipes 30a . 30b separate or different corrugated ribs or ribs 70a . 70b intended.

At the in 3c The design shown are the rows of tubes 30a . 30b - As in the design according to 3b - offset by half the pitch t / 2 to each other. The design according to 3c is different from the one in 3b shown essentially in that instead of different corrugated ribs or ribs 70a . 70b (see. 3b ) common, stepped corrugated ribs or ribs 70 for the rows of pipes 30a . 30b are provided.

1

Heat exchanger, gas cooler

10

first Header tube device

10a

Longitudinal axis of 10

12

second Sammelrohreinrich

tung

12a

Longitudinal axis of 12

14a

connection or flat tube

14b

connection or flat tube

16a

connection or flat tube

16b

connection or flat tube

18

inlet opening

20

outlet opening

22

manifold

22a

Longitudinal axis of 22

24

manifold

24a

Longitudinal axis of 24

26

manifold

26a

Longitudinal axis of 26

28

manifold

28a

Longitudinal axis of 28

30a

first tube row

30b

second tube row

32

first end of 14a .

14b . 16a . 16b

34

second end of 14a .

14b . 16a . 16b

36a

Spaces between

14a and 14a

36b

Spaces between

14b and 16b

38a

Spaces between

14a and 16a

38b

Spaces between

14b and 16b

40a

Spaces between

16a and 16a

40b

Spaces between

14b and 16b

42

Arrow, airflow

44a

first Component heat exchanger

from 1

44b

second Component heat exchanger

from 1

46

End plate

48

End plate

50

Partition in 22

52

Partition in 24

54

first chamber in 22

56

second chamber in 22

58

first chamber in 24

60

second chamber in 24

62

flange or connecting piece

for the entrance from medium

64

flange or connecting piece

for the exit from medium

70

corrugated fin

70a

corrugated fin

70b

corrugated fin

Claims (14)

Heat exchanger for motor vehicles, in particular radiator for cooling refrigerant for a heating or air conditioning system of a motor vehicle, having an inlet ( 18 ) and an exit opening ( 20 ) for a first medium, such as refrigerant, several headers ( 22 . 24 . 26 . 28 ), the two spaced manifolds ( 10 . 12 ) and with a plurality of these manifolds ( 10 . 12 ) arranged connecting pipes ( 14a . 14b . 16a . 16b ), for the fluidic connection of the two header pipe devices ( 10 . 12 ) each with its one end into the one header pipe device ( 10 ) and with its other end into the other header pipe device ( 12 ); these connecting tubes ( 14a . 14b . 16a . 16b ) are arranged so that they at least two adjacent rows of tubes, through which the first medium can flow ( 30a . 30b ), each of several longitudinally ( 10a . 10b ) of the headers ( 10 . 12 ) successive connecting tubes ( 14a . 14b . 16a . 16b ), between each of which spaces ( 36a . 38a . 40a . 36b . 38b . 40b ) for an air flow ( 42 ), wherein at least one of the headers ( 10 . 12 ) acts as a deflection, that in each of the row of pipes ( 30a . 30b ) the flow direction of the first medium between the two header pipe devices ( 10 . 12 ) is deflected at least once, characterized in that the number of changes of the flow directions between the manifolds ( 10 . 12 ) in the rows of tubes ( 30a . 30b ) is identical. Heat exchanger for motor vehicles, esp in particular radiator for cooling refrigerant for a heating or air conditioning system of a motor vehicle, in particular according to claim 1, with an inlet ( 18 ) and an exit opening ( 20 ) for a first medium, such as refrigerant, several headers ( 22 . 24 . 26 . 28 ), the two spaced manifolds ( 10 . 12 ) and with a plurality of these manifolds ( 10 . 12 ) arranged connecting pipes ( 14a . 14b . 16a . 16b ), for the fluidic connection of the two header pipe devices ( 10 . 12 ) each with its one end into the one header pipe device ( 10 ) and with its other end into the other header pipe device ( 12 ); these connecting tubes ( 14a . 14b . 16a . 16b ) are arranged so that they at least two adjacent rows of tubes, through which the first medium can flow ( 30a . 30b ), each of several longitudinally ( 10a . 10b ) of the headers ( 10 . 12 ) successive connecting tubes ( 14a . 14b . 16a . 16b ), between each of which spaces ( 36a . 38a . 40a . 36b . 38b . 40b ) for an air flow ( 42 ), wherein at least one of the headers ( 10 . 12 ) acts as a deflection, that in each of the row of pipes ( 30a . 30b ) the flow direction of the first medium between the two header pipe devices ( 10 . 12 ) is deflected at least once, characterized in that the first medium when entering the first header pipe device ( 10 ) in two partial streams on the connecting pipes ( 14a . 16a respectively. 14b . 16b ), in particular flat tubes, the first row of tubes ( 30a ) and the second row of tubes ( 30b ) is divided. Heat exchanger according to one of the preceding claims, characterized in that each of the manifolds ( 10 . 12 ) for different connecting pipe rows ( 30a . 30b ) different collection tubes ( 22 . 24 . 26 . 28 ) having. Heat exchanger for motor vehicles, in particular radiator for cooling refrigerant for a heating or air conditioning system of a motor vehicle, in particular according to one of the preceding claims, characterized by a first ( 44a ) and a second partial heat exchanger ( 44b ), each comprising: - an inlet opening and an outlet opening; - two spaced headers ( 22 . 26 respectively. 24 . 28 ); and - a plurality of longitudinally ( 22a . 26a respectively. 24a . 28a ) of the headers ( 22 . 26 respectively. 24 . 28 ) successive connecting tubes ( 14a . 16a respectively. 14b . 16b ) used to form flow connections between the headers ( 22 . 26 respectively. 24 . 28 ) each with its one end in one and with its other end in the other manifold ( 22 . 26 respectively. 24 . 28 ), wherein in the collecting tube longitudinal direction ( 22a . 26a respectively. 24a . 28a ) successive connecting tubes ( 14a . 16a respectively. 14b . 16b ) forming a respective interspace ( 36a . 38a . 40a respectively. 36b . 38b . 40b ) for a transverse to the connecting pipes ( 14a . 16a respectively. 14b . 16b ) flowing air flow ( 42 ) are spaced from each other, and wherein at least one of the two manifolds ( 22 . 26 respectively. 24 . 28 ) acts as a deflection, so that different groups of parallel through-flow of connecting pipes ( 14a . 16a respectively. 14b . 16b ) are connected in series, so that they can be flowed through in succession in opposite directions by a first medium, such as refrigerant, wherein the flow guide of this first part heat exchanger ( 44a ) and this second partial heat exchanger ( 44b ) is configured substantially identically for the first medium, such as refrigerant, between the respective inlet opening and the respective outlet opening, and on the one hand the inlet openings of these partial heat exchangers ( 44a . 44b ) are connected, and on the other hand, the outlet openings of these partial heat exchanger ( 44a . 44b ), in such a way that these partial heat exchangers ( 44a . 44b ) are flowed through in parallel by the first medium. Heat exchanger according to claim 4, characterized in that the partial heat exchanger are designed essentially identical. Heat exchanger according to one of the preceding claims, characterized in that the connecting pipes ( 14a . 14b . 16a . 16b ) are each designed as flat tubes, wherein preferably the two respective end regions ( 32 . 34 ) of the flat tubes with respect to a respective one of these end regions ( 32 . 34 ) are twisted, and more preferably by 90 °. Heat exchanger according to claim 6, characterized in that the flat tubes with Their twisted end portions each open into a manifold, wherein in the mouth areas the viewed in the direction perpendicular to the connecting pipe longitudinal cross-section the connecting pipes given longer Side of the cross section with the longitudinal axes of the headers or Collection tube means include an angle which is less than 80 °, wherein these longer ones Sides preferably in the mouth areas aligned parallel to the longitudinal axes are. Heat exchanger according to one of the preceding claims, characterized in that the partial heat exchanger ( 44a . 44b ) and / or rows of tubes ( 30a . 30b ) are arranged adjacent. Heat exchanger for motor vehicles according to one of the preceding claims, characterized in that in the spaces ( 36a . 38a ; 40a respectively. 36b . 38b . 40b ) for an air flow ( 42 ) are each arranged ribs. Heat exchanger according to one of the preceding claims, characterized in that the collecting tube means ( 10 . 12 ) are each formed by a plurality of manifolds with a circular or close to circular inner cross section. Heat exchanger according to one of the preceding claims, characterized in that in the collecting pipes ( 22 . 24 ) of at least one of the header pipes ( 10 . 12 ) Partitions are ge give, in particular those which separate in the longitudinal direction of the headers regions of the interior of the respective manifold. Heat exchanger according to one of the preceding claims, characterized in that between adjacent connecting tubes which can be flowed through in opposite directions, a thermal separation is given, in particular by a increased distance this connecting pipes compared to the distance of other adjacent Connecting pipes of the same connecting pipe row or the same Partial heat exchanger is formed. Device for heating and / or air conditioning the passenger compartment of a motor vehicle, characterized that the device has a heat exchanger according to one the preceding claims having. Motor vehicle with a passenger compartment and a Device for heating and / or air conditioning this passenger compartment, characterized in that the device for heating and / or Air conditioning this passenger compartment a heat exchanger according to a the claims 1 to 11.