EP1738125A1

EP1738125A1 - Heat exchanger for motor vehicles

Info

Publication number: EP1738125A1
Application number: EP05739595A
Authority: EP
Inventors: Michael Kranich; Karl-Heinz Staffa; Christoph Walter
Original assignee: Behr GmbH and Co KG
Current assignee: Mahle Behr GmbH and Co KG
Priority date: 2004-04-13
Filing date: 2005-04-12
Publication date: 2007-01-03
Also published as: JP2007532856A; WO2005100895A1; US20090050304A1; DE102004018317A1; JP4743203B2

Abstract

Disclosed is a heat exchanger for motor vehicles, comprising two spaced-apart manifold devices (10, 12) and several connecting tubes (14a, 14b, 16a, 16b). Said connecting tubes (14a, 14b, 16a, 16b) are disposed so as to form two rows of tubes (30a, 30b) which are located next to each other, are penetrated in parallel by the first medium, and are respectively formed by several connecting tubes (14a, 14b, 16a, 16b) that succeed each other in the longitudinal direction (10a, 10b) of the manifold devices (10, 12). The direction of flow of the first medium is deflected at least once between the two manifold devices (10, 12) in each of the rows of tubes (30a, 30b) while the number of changes in the direction of flow between the manifold devices (10, 12) is identical in the rows of tubes (30a, 30b).

Description

Heat exchangers for motor vehicles

The invention relates to a heat exchanger or heat exchanger for motor vehicles, and in particular to a cooler for cooling refrigerant for a heating or air conditioning system of motor vehicles, and to 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 in motor vehicles generally have a refrigerant circuit. Carbon dioxide (C0 ₂ ) has been increasingly used as a refrigerant recently. The cooling capacity of a CO 2 circuit is largely determined by the gas cooler. When designing such gas coolers, care is generally taken to ensure that they are pressure-stable even at high temperatures, have a small internal volume and take advantage of the installation space, taking into account the low weight. In order to minimize power-reducing heat return flows, a meaningful connection to areas through which refrigerant flows can be a criterion when designing or arranging such gas coolers in motor vehicles.

The applicant's German patent application 10229 973.0 discloses a gas cooler in which a cross-countercurrent circuit is provided. In this design, two header pipes are provided, which are arranged parallel and adjacent to one another. The two manifolds are connected by a large number of U-shaped flat tubes, each of which ends in one of the manifolds with its free ends. These flat tubes follow one another in the longitudinal direction of the header tubes, with two adjacent tubes hard flat tubes each have an intermediate space through which air can flow, so that heat transfer between the refrigerant guided in the flat tubes and the flowing air is made possible. The two header tubes arranged on the same side of the flat tube package are each divided in such a way that two chambers are formed in each of these two header tubes. A lower chamber of the one collecting pipe is connected in terms of flow technology to an upper chamber of the other collecting pipe via a transition piece. This transition piece can be attached at any height of the gas cooler and allows the refrigerant flowing through to pass from the area facing away from the air to the area facing the air, or vice versa. An aim of this embodiment is to prevent the already cooled refrigerant from being warmed up again by warm engine return flows by skillful refrigerant guidance.

From the German patent application 102 52 263.4 of the applicant, an embodiment of the gas cooler with four manifolds is known, two of which are arranged in pairs to form a manifold device. The two manifold devices formed in this way are spaced apart from one another and are connected in terms of flow technology via a multiplicity 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 essentially straight and open with their distal ends in one of the two manifold devices or in separate manifolds. With this design, two tubes of the same length are used instead of the tube forks or U-shaped flat tubes known from DE 10229 973.0. Two axially spaced chambers are formed in the manifolds. On a gas cooler side, a lower chamber of one header pipe is connected to an upper chamber of the other header pipe via a transition piece. The connecting pipes are connected in such a way that the refrigerant first flows through the entire face surface and finally passes through the transition piece into the front or back plane.

In the above-mentioned designs, a transition piece is required which connects area quadrants with one another. Both the manufacture and the assembly of such a transition piece are cost-intensive and can cause leaks, in particular if different temperatures of the quadrants additionally stress the soldered seams. In addition, the transition can form a constriction, which can adversely affect the pressure drop on the refrigerant side, resulting in a lower refrigerant output. Furthermore, one or two rows of pipes are lost for the cooling capacity in the transition area. A parallel flow solution cannot be achieved with this design.

A heat exchanger is known from EP 0 414433 B1, in which two rows of flat tubes arranged in parallel are formed, each of which connects two spaced header tubes in terms of flow technology. Between the flat tubes adjacent in the longitudinal direction of the collecting tubes, ribs are provided in the respective rows, through which air can flow through the heat exchanger transversely to the longitudinal expansion of the flat tubes. The inflow is connected to both rows of flat tubes on the same side of the heat exchanger. The flow direction changes once in the row of pipes facing the fresh air and the flow direction changes three times in the row of pipes facing away from the fresh air.

The invention has for its object to provide a heat exchanger for motor vehicles, in particular cooler for cooling refrigerant for a heating or air conditioning system of a motor vehicle, which has good transmission behavior, and can be manufactured inexpensively and in terms of production technology.

According to the invention, a heat exchanger according to claim 1 or according to claim 2 or according to claim 4 is proposed. A device according to the invention for heating and / or air conditioning the passenger compartment le of a motor vehicle is the subject of claim 13. A motor vehicle according to the invention is the subject of claim 14. Preferred configurations are the subject of the dependent claims.

Each manifold device preferably has at least two manifolds. Particularly preferably, each header pipe device has separate header pipes for each connecting pipe row or for each partial heat exchanger. In particular, it is provided that the longitudinal axes of these header tubes are spaced apart from the same header tube device and, for example, run parallel to one another. A manifold can also be formed by a plurality of separate, and in particular concentric, manifold sections which are spaced apart in the axial direction, to be precise with the formation of a space or without the formation of such spaces.

In a particularly preferred embodiment, two rows of manifolds or two partial heat exchangers are provided, the two rows of manifolds each having two manifolds arranged parallel and offset from one another. In this case, connecting pipes of one row of connecting pipes or of one partial heat exchanger open into the respective collecting pipe and connecting pipes of the other row of pipes or of the other partial heat exchanger into the respective other collecting pipe. In particular, four collecting tubes are provided.

The partial heat exchangers are preferably each designed essentially identically. It can be provided that they differ in the position of their inlet and / or outlet opening and are otherwise identical. However, it is preferably provided that different positions of the inlet and / or outlet opening are such that they still open into corresponding areas or chambers in relation to the different partial heat exchangers.

The connecting tubes are preferably each flat tubes. In a particularly preferred embodiment, it is provided that their respective - both - End areas are twisted or twisted relative to the area in between. The angle of rotation is in each case preferably between 10 ° and 110 °, particularly preferably between 80 ° and 100 °. For example, it is essentially 90 °.

In a particularly preferred embodiment, the flat tubes with their twisted or twisted end regions each open into header tubes in such a way that their cross sections — viewed perpendicular to the longitudinal axis of the flat tubes — extend essentially in the direction of the longitudinal axes of the header tubes. Particularly preferably, they extend - apart from the twisted or twisted transition areas - between the end areas with their longer sides of the cross-sectional areas perpendicular to the longitudinal axes of the header tubes.

The connecting pipes, in particular flat pipes, can be designed in such a way that they form exactly one channel in their interior, or in such a way that several, in particular parallel, channels are formed in their interior. All connecting pipes are preferably designed to be straight throughout. All connecting pipes are particularly preferably parallel to one another. In an advantageous design, all connecting pipes are of the same length. It is further preferred that all header pipes are of the same length. The manifolds preferably each have a circular inner cross section. For example, the header pipes can each be designed essentially rotationally symmetrical with respect to their respective longitudinal axes.

The connecting pipes of a respective row of connecting pipes or of a respective partial heat exchanger are preferably arranged in a respective plane. In a particularly preferred embodiment, the levels of different connecting pipe rows or partial

Heat exchangers located parallel and offset from one another.

In a preferred embodiment, the various rows of connecting pipes or partial heat exchangers are arranged with respect to one another in such a way that transversely to air flowing through the connecting pipes successively flows through the gaps formed between the connecting pipes of the various connecting pipe rows or partial heat exchangers. In particular, it is provided that air, which in particular forms a second heat exchanger medium, flows successively or in series through the various connecting pipe rows or partial heat exchangers, specifically outside the connecting pipes. In particular, it is provided that the second heat exchange medium, in particular air, is guided in cross-flow past the first heat exchange medium, in particular refrigerant, in order to bring about heat transfer.

A plurality of connecting pipes are preferably connected in parallel in a respective row of connecting pipes or in a respective partial heat exchanger. In particular, this can be such that in each connection pipe row several such connection pipes are flowed through in parallel, and then - particularly in the opposite direction of flow - other connection pipes of the same connection pipe row or the same partial heat exchanger are likewise flowed through in parallel. This can be such that for each connecting pipe row or partial heat exchanger, a plurality of groups of connecting pipes flowed through in parallel are connected in series by means of assigned header pipes in such a way that the connecting pipes can be flowed through by the first medium, in particular refrigerant, in opposite flow directions in each case. In particular, it can be provided that the first medium is guided in a serpentine manner in each of the partial heat exchangers or connecting pipe rows.

The number of diversions or the successive, opposite flow directions is preferably identical in the partial heat exchangers or connecting pipe rows. It can be provided that the number of connecting pipes, which in each case forms a group of connecting pipes through which flow flows in parallel in the flow direction, increases or decreases downstream in a respective connecting pipe row or in a respective partial heat exchanger or is identical. Two or more such groups are connected in series in the respective partial heat exchanger or the respective row of connecting pipes. Other designs are also preferred.

Partition walls are preferably introduced in at least one header pipe device. Particularly preferably, at least one partition is provided in different collecting pipes of the same collecting pipe device. Such partitions are in particular such that they separate areas or chambers that follow one another in the longitudinal direction of the relevant collecting tube. It can also be provided that at least one partition is provided in each of the two manifold devices or the corresponding manifolds. A plurality of axially spaced dividing walls can also be provided in the collecting tubes of the same collecting tube device, the number of dividing walls in different collecting tubes of the same collecting tube device being particularly preferably identical.

A thermal separation is preferably provided between connecting tube groups which are successively flowed through in opposite directions. For this purpose, for example, the division or the spacing of adjacent connecting pipes between these groups can be greater than within the respective groups.

The two or adjacent partial heat exchangers can be arranged relative to one another in such a way that they contact one another. For example, they can be soldered together. Only one medium, the first medium, such as refrigerant, preferably flows inside the system formed from the collecting tubes and the connecting tubes. During operation, the second heat exchange medium, such as air, preferably flows outside the connecting pipes, in particular transverse to the longitudinal extension of the connecting pipes. The heat exchanger or heat exchanger according to the invention is preferably a gas cooler or condenser for a motor vehicle. The heat exchanger is preferably made of aluminum. According to the invention, a device according to claim 13 is also proposed.

According to the invention, a motor vehicle according to claim 14 is also proposed. The heat exchanger according to the invention is preferably installed in the motor vehicle in such a way that the planes spanned by the partial heat exchangers or the rows of pipes are located transversely, in particular perpendicularly, to the direction of travel. It is further preferred that a fan is provided for the heat exchanger according to the invention, which in operation drives air through the spaces formed between the connecting pipes. The heat exchanger is preferably arranged with respect to the internal combustion engine of the motor vehicle in such a way that the area of the refrigerant inlet is warmed more strongly by the backflow of warm air from the internal combustion engine than the area of the refrigerant outlet.

Exemplary embodiments of the invention are explained below with reference to the figures. It shows:

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

FIG. 2 shows a schematic diagram of the flow control of the refrigerant in the design according to FIG. 1;

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

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

3c shows a third exemplary design and arrangement of rows of pipes and corrugated fins. 1 shows an exemplary heat exchanger or heat exchanger 1 according to the invention with a first header pipe device 10, a second header pipe device 12, a plurality of connecting pipes 14a, 14b, 16a, 16b and with an inlet opening 18 and an outlet opening 20 for a first medium, in particular Carbon dioxide (CO≥).

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

The manifold devices 10, 12 each have two manifolds 22, 24 and 26, 28, respectively. The manifolds 22, 24 of the first manifold device 10 and the manifolds 26, 28 of the second manifold device 12 are each arranged in pairs adjacent to one another. in particular in such a way that their longitudinal axes 22a, 24a and 26a, 28a extend parallel and spaced apart. Furthermore, the longitudinal axes 22a, 24a are arranged parallel to the longitudinal axes 26a, 28a or the longitudinal axis 10a of the first header pipe device 10 is arranged parallel to the longitudinal axis 12a of the twin header pipe device 12.

The heat exchanger 1 has two rows of pipes 30a, 30b. These rows of pipes 30a, 30b are each formed by a plurality of connecting pipes 1a, 16a and 14b, 16b, which - seen in the longitudinal direction 10a, 10b of the header pipe devices 10, 12 - follow one another, the longitudinal axes of these connecting pipes 14a, 16a and 14b, 16b are aligned parallel to one another. The row of pipes 30a is arranged adjacent to the row of pipes 30b, the or all connecting pipes 14a, 16a of the first row of pipes 30a respectively connecting the first collecting pipe 22 of the first collecting pipe device 10 to the first collecting pipe 26 of the second collecting pipe device 12, and the or all connecting pipes 14b, 16b of the second row of tubes 30b each connect the second header pipe 24 of the first header pipe device 10 to the second header pipe 28 of the second header pipe device 12. The connecting pipes belonging to a row of pipes 30a or 30b lie in one plane. The longitudinal axes of the or all of the connecting tubes 14a, 14b, 16a, 16b each run perpendicular to the longitudinal axes 10a, 12a of the manifold devices 10, 12.

The connecting tubes 14a, 14b, 16a, 16b or the tube rows 30a, 30b are arranged in the design according to FIG. 1 essentially according to the type as explained or shown with reference to FIG. 3a. In particular, ribs or corrugated ribs 70 are provided. However, it can also be provided that this design is different, for example, as explained or shown with reference to FIG. 3b or with reference to FIG. 3c. It can thus be provided in particular that the row of pipes π 30a, 30b are offset from one another by the amount t / 2 (half division), in particular in the longitudinal direction of the collecting pipe devices 10, 12. It can be provided that two separate corrugated ribs 70a, 70b are provided in each case instead of continuous corrugated ribs 70 (see FIG. 3a) (see FIG. 3b). However, it can also be provided that a common, offset corrugated fin 70 is provided in each case (cf. FIG. 3c).

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

The respective opposite end regions of the flat tubes are, however, twisted in a preferred design about the longitudinal axis of the flat tube in question, and preferably by 90 °, but there may also be different twist angles. In designs in which the angle of rotation is 90 °, it is preferably provided that the main direction of extension of these ends - in cross section perpendicular to the longitudinal considered axis of the respective flat tube - is located in the direction of the longitudinal axes 10a, 1 a. Between these ends of the respective main direction of extent is of or all flat tubes - as already mentioned - substantially perpendicular to de ^'n longitudinal axes 10a, 1 a of the collection tube devices 10, 12. This has the advantage that smaller NEN (in- ) Cross sections of the manifolds 10, 12 can be realized. For example, in the design according to FIGS. 14 and 15 of EP 0 814433 B1, the inside diameter of the header tubes is limited at the bottom by the flat tube width, which according to the invention does not necessarily have to be. However, according to the invention, the respective inner diameter of the header tubes can also be larger than the flat tube width.

The or all header tubes 22, 24, 26, 28 advantageously have a circular inner cross section, in particular continuously. Its outer jacket can also be particularly preferably circular or cylindrical.

With their respective opposite ends (the connecting pipes), which can be particularly advantageously designed such that the openings provided there are arranged on the end face, these connecting pipes 14a. 16a, 14b, 16b are each inserted into the manifold devices 10, 12, so that the two manifold devices 10, 12 are fluidically connected via each of the connecting pipes 14a, 16a, 14b, 16b. The connecting pipes 14a, 16a open on the one hand into the first collecting pipe 22 of the first collecting pipe device 10 and on the other hand into the first collecting pipe 26 of the second collecting pipe device 12, and the connecting pipes 14b, 16b open out on the one hand into the second collecting pipe 24 of the first collecting pipe device 10 and on the other hand into the second Collecting pipe 28 of the second collecting pipe device 12. For this purpose, corresponding openings are formed in the lateral surfaces of the collecting pipes, each of which, in an advantageous embodiment, are slot-shaped and particularly preferably extend in the longitudinal direction of the relevant collecting pipe. It can also be provided that such slots are dimensioned such that they can accommodate the ends of a plurality of connecting pipes. But is preferred also that each slot receives exactly one connecting pipe. The connecting pipes 14a, 16a, 14b, 16b are each connected in these areas to the relevant collecting pipes 22, 24, 26, 28 or collecting pipe devices, in particular soldered, preferably brazed.

The - in each case - two transition regions between the two twisted or twisted end regions 32 and 34, on the one hand, and the region located between these ends, on the other hand, can serve, for example, as a stop; in other words, the ends of the connecting pipes 14a, 16a, 14b, 16b can each be inserted into a collecting pipe until the region located between these ends - which is twisted relative to the ends or vice versa - strikes the respective collecting pipe , These transition areas can thus form an assembly aid. However, the ends can also be inserted in such a way that there is no striking in the aforementioned sense.

Gaps 36a, 38a, 40a for the air flow are respectively formed between adjacent connecting pipes 14a, 16a of the first row of pipes 30a. Correspondingly, gaps 36b, 38b, 40b for the air flow are formed between adjacent connecting pipes 14b, 16b of the second row of pipes 30b. Air can thus flow through the heat exchanger 1 transversely to the longitudinal direction of the connecting pipes 14a, 16a, 14b, 16b, so that, during operation, the medium flowing through the connecting pipes 14a, 16a, 14b, 16b and the medium through the spaces 36a, 38a, 40a , 36b, 38b, 40b flowing air heat can be transferred. The flowing air and its direction of flow is indicated schematically in FIG. 1 by the arrow ends or arrows 42. Ribs are advantageously arranged in the spaces 36a, 38a, 40a. Air can flow through these in the air flow direction.

The first header pipe 22 of the first header pipe device 10, the first header pipe 26 of the second header pipe device 12, and the connecting pipes 14a, which open into these header pipes 22, 26 with their ends. 16a form a first partial heat exchanger or first partial cooler 44a of the heat exchanger 1; In a corresponding manner, the second header pipe 24 of the first header pipe device 10, the second header pipe 28 of the second header pipe device 12, and the connecting pipes 14b, 16b opening at the ends of these header pipes 24, 28 form a second partial heat exchanger or second partial cooler 44a of the heat exchanger 1. These partial heat exchangers 44a, 44b are arranged one behind the other in the air flow direction 42, the gaps 36a, 38a, 40a of the first partial heat exchanger 44a being aligned with those of the second partial heat exchanger in a particularly preferred embodiment.

Seen in the longitudinal direction of the collecting pipes 22, 24, 26, 28, the heat exchanger 1 has an end plate 46, 48 at the top and bottom. These end plates 46, 48 can, for example, be such that they essentially cover the arrangement of the connecting pipes - viewed in the longitudinal direction thereof and transversely thereto. In particular, you can cover both rows of connecting pipes. They can also be such that they additionally cover the header pipes at the top or bottom; however, these can also have different closures at the ends of the end plates 46, 48. The end plates 46, 48 can be formed, for example, by metal sheets.

One or more manifolds 22, 24 are each provided with at least one partition 50, 52. Such chambers 50, 52 can be used to form different chambers 54, 56 and 58, 60 in the respective header 22 and 24, respectively. In particular, this can be such that the partition 50 or 52 separates chambers 54, 56 or 58, 60 which are arranged adjacent in the axial direction of the relevant collecting tube.

A partition 50, 52 can, for example - as shown in FIG. 1 - be provided on the inlet side or refrigerant inlet side or the manifold 22 or 24 arranged there, or in the manifolds in which the inlet openings for the entry of the first medium , such as CO ₂ , are arranged. 1, both header pipes 22, 24, which are on the refrigerant inlet side, each have a partition 50, 52; In particular, it can be provided that all header pipes 22, 44 of the first header pipe device each have a partition 50, 52.

The dividing walls 50, 52, which are arranged in different or in the two header pipes 22, 24 of the same header pipe device 10, can be positioned such that they delimit areas with the same area or volume. In particular, this can be such that the areas delimited in one 22 of the collecting pipes 22, 24 by the partition 50 positioned there are of the same area or volume as the areas which are in the other 24 of the two collecting pipes 22, 24 by the areas provided there Partition 52 are delimited. In particular, it is provided that these two manifolds 22, 24 have the same length. Regardless of the position of such partition walls 50, 52, it can also be provided that the header tubes 22, 24 or 26, 28 of the same header tube device 10 or 12 are of the same length. Furthermore, it can be provided that all manifolds 22, 24, 26, 28 have the same length. In an advantageous embodiment, all connecting tubes 14a, 14b, 16a, 16b are of the same length.

It can be provided, as shown in FIG. 1, that the header tubes 22, 24, 26, 28 - and in particular the respectively adjacent 22, 24 and 26, 28 - are aligned with one another at their ends.

In the design according to FIG. 1, the (two) header pipes 22, 24 of the first header pipe device 10, which are located on the refrigerant inlet side, each have a partition 50, 52 which separate the area of the "warm" and the "colder" zone. The two partitions delimit areas with the same area or volume. It can also be provided that the partitions 50, 52 delimit different areas or slightly different areas. For example, provision can be made to design the area facing the fresh air differently by 1 to 3 flat or connecting pipes. However, it is particularly advantageous hen that the partitions 50, 52 are located such that the same number of connecting pipes each opens in the regions of the collecting pipes 22, 24 of the same collecting pipe device 10 which are separated from one another thereby.

The refrigerant entering through the inlet opening 18 advantageously has an inlet temperature there that is in the range from 150 ° C. to 180 ° C. This refrigerant is cooled along the flow paths by means of the air flowing transversely to the connecting pipes. This can be done, for example, in such a way that the outlet temperature of the refrigerant is approximately 50 to 140 Kelvin below the inlet temperature. For example, the inlet temperature can be approximately 180 ° C and the outlet temperature approximately 45 ° C.

The inlet opening 18 of the heat exchanger forms a common inlet opening through which the medium subsequently divided - in the direction of flow - onto the two partial heat exchangers 44a, 44b enters. For entry into the two partial heat exchangers 44a, 44b, downstream of the inlet opening 18, an inlet opening, not shown in FIG. 1, is provided in the first header pipe 22 of the first header pipe device 10, and an inlet opening, also not shown in FIG. 1, in the second header pipe 24 of the first In a corresponding manner, the outlet opening 20 of the heat exchanger 1 forms a common outlet opening, outlet openings (not shown), which are provided upstream of the outlet opening 20, being provided in the first header 22 of the first header 10 and in the second header 24 of the first header 10.

In the design according to FIG. 1, the medium is guided in such a way that it also exits on the entry side, which is located here on the side of the first header pipe device 10; It can also be provided that the inlet side and the outlet side of the heat exchanger 1 are located on different sides, for example the inlet side on the side of the first header pipe device 10 and the outlet side on the side of the second header pipe device 12, with outlet openings in the first 26 and second header pipe 28 of the second header pipe device 12 are provided, and the common outlet opening 20 is located downstream of these outlet openings on the side of the second header pipe device 12.

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

In the design according to FIG. 1, the manifold device - or respectively its manifold - acts as a deflection device.

After the refrigerant of both rows of pipes 30a, 30b has flowed through the width of the heat exchanger 1, it is deflected in the two opposite collecting pipes 26, 28 in order to then leave the heat exchanger 1 again on the inlet side.

However, it can also be provided that the medium or refrigerant is guided in a serpentine manner by using several partition walls. This can e.g. cause the refrigerant inlet and outlet to be positioned diagonally. However, more partition walls, which can be positioned partly in the header pipes of the first header pipe device and partly in the header pipes of the second header pipe device, can also be arranged such that the refrigerant emerges again on the inlet side.

It can also be provided that there is a thermal separation between the warm and the cold zone or respectively adjacent connecting pipes of the same partial heat exchanger or respectively the same row of pipes through which flow flows in opposite directions. This can be achieved, for example, by giving the header pipes a different division at the points where the partition wall is to be located, so that the rib there only on one of the (two) adjacent connections or flat tubes of one or a respective connection or flat tube row is soldered.

The division or the distance between adjacent connecting or flat tubes can be the same in each case. It can be provided that, in order to achieve a thermal separation in the transition area between one or the colder zone and one or the warmer zone, there is a greater distance between the adjacent connecting pipes through which the same connecting pipe row 30a, 30b flows in different directions. It can be provided that the expansion of all the ribs in the direction of the longitudinal axes 10a, 12a of the header pipe devices is identical. These ribs can, for example, be soldered to the respective connecting tubes (seen in the longitudinal direction 10a, 12a). It can also be provided that the ribs each extend over both partial heat exchangers, so that a rib common to both partial heat exchangers or both tube rows 30a, 30b is provided between adjacent connecting pipes.

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

Ribs can also be provided in the connecting tube rows 30a, 30b in each case between the upper end plate 46 and the connecting tube 14a or 14b adjacent in the longitudinal direction 10a, 12a. Furthermore, ribs in the connecting pipe rows 30a, 30b can also be provided between the lower end plate 48 and the connecting pipe 14a or 14b adjacent in the longitudinal direction 10a, 12a of a respective connecting pipe row.

In an advantageous embodiment, the heat exchanger 1, which has the two partial heat exchangers 44a, 44b, is designed in one piece or as one connected in one piece. In an advantageous embodiment, it can be designed as a solder construction.

Instead of a header pipe, which is divided into chambers 54, 56, 58, 60 by a partition 50, 52, separate axially spaced or successive header pipe sections can also be provided, the cross sections of such header pipe sections preferably being identical, and these are arranged concentrically.

In the design according to FIG. 1, in each case the same partial heat exchanger 44a, 44b, fewer connecting tubes (in the same direction of flow) with parallel flow through connecting tubes are provided on the inlet side than on the outlet side.

The partial heat exchangers 44a, 44b are each configured identically in the design according to FIG. 1, in particular with regard to the flow guidance between the inlet opening and the outlet opening of the respective partial heat exchanger 44a, 44b. The ribs, too - in particular if no common ones are provided - can be designed and arranged identically in both partial heat exchangers 44a, 44b. The identical flow control can have fluidic advantages in certain applications. It can be particularly advantageously provided that both partial heat exchangers are designed identically, which is advantageous in terms of production technology, especially since the variety of differently designed parts can be reduced. However, it should be noted that the respective inlet and outlet openings of the two partial heat exchangers can be positioned differently, in particular in such a way that they open into corresponding chambers at different heights and / or around the longitudinal axis of the header pipes; but they can also be designed in the same way.

It is provided in particular in the design according to FIG. 1 that the first medium, in particular refrigerant, preferably at least when entering the first manifold devices 10 in exactly two partial flows two partial flows, on which connecting pipes 14a, 16a or 14b, 16b, in particular flat pipes, of the first row of pipes 30a and the second row of pipes 30b is divided. In particular, this can be such that this division is effected by means of the connection piece 62 for the entry of the first medium. For example, it can be provided for this that the connecting piece 62 has at least one inlet opening and at least two outlet openings, a flow connection being produced via one of these outlet openings to the interior of the first header pipe 22 of the first header pipe device 10, and one via another of these outlet openings Flow connection is generated with the interior of the second header pipe 24 of the first header pipe device 10. Corresponding openings, which enable the medium to enter the manifolds 22, 24, are provided in the manifolds 22, 24. The volume flow of the first medium can be divided, for example, in a ratio of 50%: 50%; however, softening ratios are also preferred.

The refrigerant enters the two rows of pipes at the same time - preferably taking into account the location of the warmest zone.

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

FIG. 2 schematically shows the flow guidance for the design according to FIG. 1. FIG. 2 can also be seen that the first medium enters the first manifold device 10 in two partial flows onto the flat pipes or connecting pipes 14a, 16a or 14b, 16b , the first row of tubes (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 pipes 30a, 30b or their relative arrangement or exemplary embodiments for the design of fins which are arranged between connecting pipes of the rows of pipes. These designs shown in FIGS. 3a to 3c can be given in a preferred further development in designs according to the invention, in particular in the design according to FIG. 1 or FIG. 2. It should be noted here that the number of fins or connecting tubes (each Row) is generally larger or significantly larger than is shown schematically or in sections in FIGS. 3a to 3b.

3a to 3c, corrugated ribs or ribs 70 are provided in spaces 36a, 36b or 38a, 38b or 40a, 40b, preferably in all spaces 36a, 36b, 38a, 38b, 40a, 40b , are positioned, which are given between respectively adjacent connecting pipes 14a-14a, or 14a-16a, or 16a-16a, or 14b-14b, or, 14b-16b or 16b-16b of the pipe rows 30a, 30b.

In the designs according to FIGS. 3a to 3b, it is particularly provided that the pitch t of the first row of tubes 30a corresponds to the pitch t of the second row of tubes 30b, and is particularly preferably constant in each case. It can also be provided that a different spacing of these connecting pipes or a different division is provided between successive connecting pipes 14a-16a or 14b-16b in the respective pipe rows 30a, 30b. For example, for the purpose of a thermal separation, this different distance or this different division can be greater than between the remaining, respectively adjacent connecting pipes of the same row of pipes 30a, 30b.

3a to 3b, the respective arrow 42 illustrates the (preferred) flow direction of the air. It should be noted that the same reference symbols in the figures essentially denote corresponding parts. 3a shows an exemplary design in which the connecting pipes of adjacent rows of pipes 30a, 30b are essentially not offset from one another. Seen perpendicular to the longitudinal direction of the tube rows 30a, 30b, a connection tube 14b or 16b of the second tube row 30b is arranged adjacent to each connecting tube 14a or 16a of the first tube row 30a. In this context, however, it should be noted that the number of connecting pipes in the two rows of pipes can also be different, so that a connecting pipe 14b or 16b of the second row of pipes 30b is not arranged next to each connecting pipe 14a or 16a of the first pipe row 30a. 3a, the connecting tubes 14a, 14b and 16a, 16b are designed as flat tubes, with adjacent flat tubes of different tube rows 30a, 30b spanning essentially the same planes.

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

3b shows a design in which the rows of pipes 30a, 30b are offset from one another by half the pitch t 2. 3b, separate or different corrugated ribs or ribs 70a, 70b are provided for the tube rows 30a, 30b.

In the configuration shown in FIG. 3c, the rows of tubes 30a, 30b are offset from one another by half the pitch t / 2, as in the configuration according to FIG. 3b. The design according to FIG. 3c differs from the design shown in FIG. 3b essentially in that instead of different corrugated fins or ribs 70a, 70b (cf. FIG. 3b), common, offset corrugated fins or ribs 70 for the raw rows 30a , 30b are provided. Reference number heat exchanger, gas cooler BS 38a gaps between first header pipe device 14a and 16aa longitudinal axis of 10 38b gaps between second header pipe device 14b and 16b device 40a gaps betweena longitudinal axis of 12 40 16a and 16aa connecting or flat tube 40b gaps between connecting tube or flat tube 14b and 16ba Connection or flat tube 42 arrow, air flowb Connection or flat tube 44a first partial heat exchanger inlet opening 45 of 1 outlet opening 44b second partial heat exchanger header tube of 1a longitudinal axis of 22 46 end plate header tube 48 end plate longitudinal axis of 24 50 50 partition in 22 header tube 52 Partition in 24a longitudinal axis of 26 54 first chamber in 22 manifold 56 second chamber in 22a longitudinal axis of 28 58 first chamber in 24a first row of pipes 55 60 second chamber in 24b second row of pipes 62 flange or connecting piece first end area of 14a, for the entry of medium 14b, 16a, 16b 6 4 flange or connecting piece second end area of 14a, for the outlet of medium 14b, 16a, 16b 60 70 corrugated ribs spaces between 70a corrugated ribs 14a and 14a 70b corrugated ribs spaces between 14b and 16b

Claims

P a t e n t a n s r u e h e

Heat exchanger for motor vehicles, in particular coolers for cooling refrigerant for a heating or air conditioning system in a motor vehicle

an inlet (18) and an outlet (20) for a first medium, such as refrigerant,

a plurality of manifolds (22, 24, 26, 28) which form two spaced-apart manifold devices (10, 12), and with

a plurality of connecting pipes (14a, 14b, 16a, 16b) arranged between these collecting pipe devices (10, 12), which for fluidic connection of the two collecting pipe devices (10, 12) each with one end into the one collecting pipe device (10) and with it the other end opens into the other header pipe device (12);

wherein these connecting pipes (14a, 14b, 16a, 16b) are arranged in such a way that they form at least two adjacent rows of pipes (30a, 30b) through which the first medium can flow in parallel, each of them in the longitudinal direction (10a, 10b) of the collecting pipe devices (10, 12) successive connecting pipes (14a, 14b, 16a, 16b) are formed, between which gaps (36a, 38a, 40a, 36b, 38b, 40b) are formed for an air flow (42), wherein at least one of the manifold devices (10, 12) acts as a deflection device such that in each of the pipe rows (30a, 30b) the flow direction of the first medium between the two manifold devices (10, 12) is deflected at least once, characterized in that the number the change of the flow directions between the collecting pipe devices (10, 12) in the pipe rows (30a, 30b) is identical.

2. Heat exchanger for motor vehicles, in particular cooler 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 outlet opening (20) for a first medium, such as refrigerant, a plurality of manifolds ( 22, 24, 26, 28), which form two spaced-apart manifold devices (10, 12), and with a plurality of connecting pipes (14a, 14b, 16a, 16b) arranged between these manifold devices (10, 12), which are used for the fluidic connection of the two manifold devices - gen (10, 12) each end with one end into a header pipe device (10) and with its other end into the other header pipe device (12); wherein these connecting pipes (14a, 14b, 16a, 16b) are arranged in such a way that they form at least two adjacent rows of pipes (30a, 30b) through which the first medium can flow in parallel, each of them in the longitudinal direction (10a, 10b) of the collecting pipe devices (10, 12) successive connecting pipes (14a, 14b, 16a, 16b) are formed, between which intermediate spaces (36a, 38a, 40a, 36b, 38b, 40b) for an air flow (42) are formed, at least one of the manifold devices (10, 12) acting as a deflection device such that the flow direction in each of the pipe rows (30a, 30b) of the first medium between the two header pipes (10, 12) is deflected at least once, characterized in that the first medium enters the connecting pipes (14a, 16a and 14b, 16b) in two partial flows upon entry into the first header pipe device (10), in particular flat tubes, the first row of tubes (30a) and the second row of tubes (30b) is divided.

3. Heat exchanger according to one of the preceding claims, characterized in that each of the manifold devices (10, 12) for different connecting pipe rows (30a, 30b) has mutually different manifolds (22, 24, 26, 28).

4. Heat exchanger for motor vehicles, in particular cooler 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), which each have: a Inlet opening and an outlet opening; two spaced manifolds (22, 26 and 24, 28); and a plurality of connecting pipes (14a, 16a or 14b, 16b) which follow one another in the longitudinal direction (22a, 26a or 24a, 28a) of the collecting pipes (22, 26 or 24, 28) and which are used to form flow connections between the collecting pipes ( 22, 26 or 24, 28) each end with one end in one and with the other end in the other header (22, 26 or 24, 28), the longitudinal direction of the header (22a, 26a or 24a, 28a ) successive connecting pipes (14a, 16a or 14b, 16b) with the formation of a respective intermediate space (36a, 38a, 40a or 36b, 38b, 40b) for an air flow flowing transversely to the connecting pipes (14a, 16a or 14b, 16b) (42) are spaced apart from one another, and at least one of the two collecting tubes (22, 26 or 24, 28) acts as a deflection device, so that different groups of connecting tubes (14a, 16a or 14b, 16b) through which flow can occur in parallel Series are connected so that they are successively in opposite directions from a first medium, such as refrigerant, can be flowed through, the flow of this first partial heat exchanger (44a) and this second partial heat exchanger (44b) for the first medium, such as refrigerant, between the respective inlet opening and the respective outlet opening being essentially identical , 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 exchangers (44a, 44b) are connected in such a way that these partial heat exchangers (44a, 44b) are connected in parallel can be flowed through by the first medium.

5. Heat exchanger according to claim 4, characterized in that the partial heat exchangers are designed essentially identically.

6. Heat exchanger according to one of the preceding claims, characterized in that the connecting tubes (14a, 14b, 16a, 16b) are each designed as flat tubes, preferably the two respective end regions (32, 34) of the flat tubes compared to a respective one between them End regions (32, 34) lying area are rotated, and particularly preferably by 90 °.

7. Heat exchanger according to claim 6, characterized in that the flat tubes each open into a manifold with their twisted end regions, the longer sides of the cross section given in the mouth regions in the cross section of the connecting tubes viewed perpendicular to the longitudinal axis of the connecting tube being one with the longitudinal axes of the collecting tubes or collecting tube devices Include an angle that is less than 80 °, these longer sides preferably being aligned in the mouth regions parallel to the longitudinal axes.

8. Heat exchanger according to one of the preceding claims, characterized in that the partial heat exchangers (44a, 44b) and / or rows of pipes (30a, 30b) are arranged adjacent.

9. Heat exchanger for motor vehicles according to one of the preceding claims, characterized in that ribs are arranged in the intermediate spaces (36a, 38a, 40a or 36b, 38b, 40b) for an air flow (42).

10. Heat exchanger according to one of the preceding claims, characterized in that the manifold devices (10, 12) are each formed by a plurality of manifolds with a circular or near to circular inner cross section.

11. Heat exchanger according to one of the preceding claims, characterized in that in the manifolds (22, 24) of at least one of the manifold devices (10, 12) partition walls are given, in particular those which separate regions of the interior of the respective collector pipe in the longitudinal direction of the collector pipes.

12. Heat exchanger according to one of the preceding claims, characterized in that between adjacent, flowable in opposite directions connecting pipes, there is a thermal separation, in particular by an increased distance of these connecting pipes compared to the distance of other adjacent connecting pipes of the same connecting pipe row or same partial heat exchanger is formed.

13. A device for heating and / or air conditioning the passenger compartment of a motor vehicle, characterized in that the device has a heat exchanger according to one of the preceding claims.

14. 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 has a heat exchanger according to one of claims 1 to 11.