EP1454106B1 - Heat exchanger - Google Patents

Description

The invention relates to a heat exchanger according to the Obergegriff of the first claim, in particular for use in a motor vehicle and a circuit with a heat exchanger. Such a heat exchanger is from the FIG. 3 from US 4,516,630 known. WO 02/48516 A1 is state of the art under Article 54 (3) EPC and discloses in FIG. 3 also such a heat exchanger.

Heat exchangers are often used in a motor vehicle, for example as coolers, heating elements, condensers or evaporators. In a modern vehicle you will find a variety of different heat exchangers, which are designed for example as a cooler and cool different vehicle units, components or media in vehicle units or components. For example, a coolant radiator for cooling the drive motor, such as internal combustion engine or electric motor, a transmission oil cooler, an exhaust gas cooler, a charge air cooler, a hydraulic oil cooler for a variety of applications in a vehicle and / or other coolers is provided.

The arrangement of many heat exchangers in the vehicle requires an increased space requirement and always leads to conflicts between existing space and the respective arrangement of the heat exchanger. This can lead to certain compromises with regard to the arrangement of the individual heat exchangers, which may be necessary thermodynamic view is not ideal. Also, it comes through the individual arrangement of the respective heat exchanger to an increased space requirement, since due to existing manufacturing tolerances more space must be made available, if necessary necessary.

The object of the invention is to provide a heat exchanger which is improved over the prior art.

This is achieved according to the invention by the features of the characterizing part.

It is particularly expedient if a further third outlet is arranged and a further region of fluid connections is provided between the second outlet and the third outlet. However, it may also be expedient if a further n-th outlet is arranged and a further region of fluid connections is provided between the n-th-th outlet and the n-th outlet, where n is preferably 3, 4, 5, 6, 7, 8, 9, 10 or greater than 10.

It is also advantageous if individual areas of Fluidverbindurigen by input, collection deflecting and / or outlet chambers with others Areas of fluid connections and / or with at least one inlet and / or at least one outlet are connected.

It is expedient if the input, collection deflecting and / or outlet chambers are preferably arranged in lateral side of the fluid connections arranged side boxes, wherein the side boxes are divided by partitions into different chambers. It is advantageous if the partitions as a vertical, horizontal or I-shaped, z-shaped. C-shaped, T-shaped or composite formed walls are formed.

In a further embodiment it is expedient if there is a deflection in the depth and in the width, ie in a plane of the fluid connections and in a plane perpendicular to a plane of the fluid connections, between at least one first area of fluid connections and a second area of fluid connections ,

It is also advantageous, when two areas of fluid connections without an outlet between them, are guided in countercurrent.

Furthermore, it is expedient if channels are provided for a further medium or fluid between the fluid connections. It may be particularly expedient if these channels are formed by ribs between the fluid connections. The medium can advantageously be air. The medium may advantageously be a fluid or liquid medium.

It is expedient if the fluid connections are pipes, such as preferably flat tubes or round tubes or oval tubes. It is also expedient if the tubes have a plurality of fluid channels which do not communicate with each other over the length of the tubes. Furthermore, it is expedient if the fluid connections or tubes have a plurality of fluid channels which communicate with each other over the length of the tubes. Furthermore, it may be expedient if the fluid connections or tubes are arranged in a single-row or multi-row side by side per plane of the fluid connections.

According to a further inventive concept, a fluid circuit is provided, comprising at least one heat exchanger with at least one inlet and at least two outlets, with at least two units, which can be supplied with the heat exchanger by means of fluid lines and have a fluid inlet and a fluid outlet, characterized in that between an outlet the at least one heat exchanger and an inlet of at least one unit a pump with inlet and outlet is arranged and at least one outlet of another unit with the inlet side of the pump is connectable. This advantageously achieves that the number of pumps used can be reduced and at the same time the fluid flow for cooling the other units also for cooling the main unit, such as the engine of the vehicle can be used. Thus, the efficiency of the cooling system continues to increase. As a result, for example, the entire system designed changed and possibly components and costs can be saved or dimensioned smaller.

As aggregates of the vehicle, the drive motor, a transmission, a turbocharger, an injection pump, electronics, an exhaust system, hydraulic systems or other aggregates can be regarded as heat sources. In such heat sources, the removal of heat to the environment for cooling and temperature control is often necessary.

It is advantageous if the further unit is in communication with its inlet to an outlet of the heat exchanger. It is also expedient if a plurality of further units are connected in series and through which the fluid flows. It is also advantageous if a plurality of further units are connected in parallel and through which the fluid flows. It is particularly advantageous if the inlet of another unit is connected to an outlet of the heat exchanger.

Fig. 1

eine schematische Darstellung eines Wärmetauschers,

Fig. 2

eine schematische Darstellung eines Wärmetauschers,

Fig. 3

eine schematische Darstellung eines Wärmetauschers,

Fig. 4

eine schematische Darstellung eines Wärmetauschers,

Fig. 5

eine schematische Darstellung eines Wärmetauschers,

Fig. 6

eine schematische Darstellung eines Wärmetauschers,

Fig. 7

eine schematische Darstellung eines Wärmetauschers,

Fig. 8

eine schematische Darstellung eines Wärmetauschers,

Fig. 9

eine schematische Darstellung eines Wärmetauschers,

Fig. 10

eine schematische Darstellung eines Wärmetauschers,

Fig. 11

eine schematische Darstellung eines Wärmetauschers,

Fig. 12

eine schematische Darstellung eines Wärmetauschers,

Fig. 13

eine schematische Darstellung eines Wärmetauschers,

Fig. 14

eine schematische Darstellung eines Wärmetauschers,

Fig. 15

eine schematische Darstellung eines Wärmetauschers,

Fig. 16

eine schematische Darstellung eines Wärmetauschers,

Fig. 17

eine schematische Darstellung eines Wärmetauschers,

Fig. 18

eine schematische Darstellung eines Wärmetauschers und

Fig. 19

eine schematische Darstellung eines Kühlkreislaufs.

In the following, the invention will be explained in more detail with reference to embodiments in the figures. Showing:

Fig. 1

a schematic representation of a heat exchanger,

Fig. 2

a schematic representation of a heat exchanger,

Fig. 3

a schematic representation of a heat exchanger,

Fig. 4

a schematic representation of a heat exchanger,

Fig. 5

a schematic representation of a heat exchanger,

Fig. 6

a schematic representation of a heat exchanger,

Fig. 7

a schematic representation of a heat exchanger,

Fig. 8

a schematic representation of a heat exchanger,

Fig. 9

a schematic representation of a heat exchanger,

Fig. 10

a schematic representation of a heat exchanger,

Fig. 11

a schematic representation of a heat exchanger,

Fig. 12

a schematic representation of a heat exchanger,

Fig. 13

a schematic representation of a heat exchanger,

Fig. 14

a schematic representation of a heat exchanger,

Fig. 15

a schematic representation of a heat exchanger,

Fig. 16

a schematic representation of a heat exchanger,

Fig. 17

a schematic representation of a heat exchanger,

Fig. 18

a schematic representation of a heat exchanger and

Fig. 19

a schematic representation of a cooling circuit.

The FIG. 1 shows a heat exchanger, such as a radiator, a heater, a condenser or an evaporator. The heat exchanger is described below without limitation of generality in a function as a coolant radiator.

The heat exchanger 1 has a fluid inlet 2 and a fluid outlet 3, so that a fluid between the inlet and the outlet can flow through the heat exchanger. The inlet is connected to a collection chamber 4 and the outlet is connected to a collection chamber 5. The fluid flows from the inlet 2 into the first collection chamber 4, an inlet-side collection chamber. From the second collection chamber 5, an outlet-side collection chamber, the fluid flows into the outlet 3. In the FIG. 1 is the inlet-side collecting chamber 4 or the outlet-side collecting chamber formed by a box-shaped element 6 and 7, such as water tank or fluid box, which is connectable to a wall, such as tube sheets, 8 and 9 and is formed fluid-tight to the outside. The parts 6 and 8 on the inlet side and the parts 7 and 9 on the outlet side are connected to each other in such a way that the fluid located inside can not escape substantially.

Between the collecting chambers 4 and 5 fluid connections 10 are provided, through which the fluid can flow from the one collecting chamber 4 to the other collecting chamber.

The fluid connection 10 consists essentially of a plurality of parallel tubes 11, through which the fluid can flow from one side to the other in the interior. These tubes can be flat tubes or round tubes or other connecting tubes. Also, these tubes may have different flow channels in their interior, which are formed separately or at least partially at least partially connected to each other. The tubes 11 are arranged such that free spaces are provided between them as an air passage. In at least some of these free spaces 12, ribs 13 are preferably arranged to form flow channels for the passage of air according to arrow 14 and to improve the heat exchange between the air passing through and the fluid. As a result, the surface is increased as effectively as possible on the cooling air side.

The heat exchanger has the feature that the two involved media, for example, the cooling air and the fluid are cross-flowed.

Tube bottoms and water boxes or fluid boxes form chambers which serve on the inlet side of the distribution of the coolant flow or fluid flow to the tubes and on the outlet side of the merging of the coolant flow from the tubes. The ports 2, 3, such as ports on the chambers, allow the connection of the heat exchanger to a fluid circuit, such as a coolant circuit.

In FIG. 1 the radiator network is shown in a design preferably made of flat tubes and corrugated fins. The tubes may have the following types: round tube design, oval tube design or package construction.

The FIG. 2 shows a schematically illustrated heat exchanger 101 according to the invention, which operates on the basis of a cross-flow and / or cross-countercurrent flow. The cross flow guide states that the one fluid flow and the second fluid flow intersect. The cross-countercurrent flow means that the one fluid flow and the second fluid flow intersect, wherein the second fluid flow still undergoes a deflection, so that both a leading and a recirculating fluid flow intersect with the first fluid flow, thus opposing fluid flows with the cross other fluid flow.

The heat exchanger 101 has at least a first fluid inlet 102 and a first fluid outlet 103 and a second fluid outlet 103a, so that a fluid between the inlet 102 and the first and second outlet can flow through the heat exchangers 101. The inlet 102 is connected to a collection chamber 104, the first outlet to a collection chamber 104a and the outlet is connected to another collection chamber 105. The fluid flows from the inlet 102 into the first collection chamber 104, an inlet side collection chamber. From there, the fluid flows through the fluid connections 110 into a further collection chamber 104b, an intermediate chamber. The fluid is deflected in the intermediate chamber 104b and passed through the fluid connections 110a against the flow direction in the fluid connections 110 to the collection chamber 104a. From the collection chamber 104a, a first part of the fluid flow is branched off through the one outlet 103 and discharged into a fluid circuit. Another portion of the fluid stream is directed to the collection chamber 105 through another portion of fluid connections 110b. There it occurs Fluid from the heat exchanger and is fed to another fluid circuit or partial circuit.

Advantageously, a design of the heat exchanger with a first stage, which is represented by the components 102, 104, 110, 104 b 110 a and 104 a and 103. It is a cross-countercurrent heat exchanger. In this stage, in the case of the coolant cooler, the fluid is already cooled to a first temperature. In the second stage, which is represented by the parts 104a, 110b, 105 and 103a, a part of the fluid which has already been cooled, for example, in the first stage, is again cooled, so that this part of the fluid is cooled down more. The arrangement of the tubes takes place, for example, in the upper first region 110, 110a, viewed in the flow direction of the second medium, one behind the other, so that the tubes or fluid connections 110, 110a are arranged in pairs and preferably on one level. In this case, two or more individual tubes can be arranged one behind the other or it can be a single tube having within its extent a plurality of fluid channels, which are interconnected, so that a part of the channels represent the fluid connection 110 and a part of the channels fluid communication 110a represent and train.

Individual tubes can also be used in the second region of the heat exchanger with the fluid connections 110b, or several tubes can be used per plane of the fluid connections which are connected in parallel with respect to the fluid flow. Also, a single tube or a plurality of tubes may be arranged as a fluid connection, wherein these tubes at least partially or in each case again have individual fluid channels.

The number of fluid connections 110, 110a respectively belonging to the first region and the number of fluid connections belonging to the second region can be designed according to the size of the volume flow of the partial volume flows and the corresponding target temperature of the fluid of the partial flow. Preferably, the first region from the inlet 102 to the first outlet 103 is the partial region having a plurality of fluid connections than the second partial region of the fluid connections 110b. Depending on the target temperature and volume flow, however, this can also be chosen differently.

The distribution of the volume flows in the partial volume flows takes place, inter alia, in the collecting chambers. These are separated by walls in the outer boxes 120, 121 of the heat exchanger. The first outer box 120 is configured to include a first partition wall 130 between the collection chambers 104 and 104a, which effects a fluid-tight separation between these chambers.

The one chamber 104 is an inlet chamber bounded by, for example, the box-shaped outer wall of the outer box and by the wall 130. Furthermore, the chamber 104 is defined by the wall 130 having a first wall portion 130b oriented perpendicular to the planes of the fluid connections 110, 110a, 110b and a second wall portion substantially parallel to the respective planes of the fluid connections 110, 110a , 110b is aligned.

The outer box 121 is separated in its interior by the partition wall 140 into two regions 104b, 105, wherein the partition wall 140 is aligned substantially parallel to the respective planes of the fluid connections. In a vertical arrangement of the heat exchanger thus the partition wall 140 is aligned horizontally, according to FIG. 2 ,

In the embodiment of FIG. 2 is the area 104b as an intermediate chamber or deflection or distribution chamber, the chamber 104 serves as an inlet chamber, the chamber 105 as an outlet chamber and the chamber 104a both as an outlet chamber and as an intermediate, distribution or deflection chamber.

The outer or side boxes 120, 121 may preferably be made of metal or plastic, wherein in the plastic variant, the partition walls 130, 140 may be formed as integrally formed with the box parts. In this case, the box can be produced as a whole as an injection molded part.

In the FIG. 2 the tubes 110, 110a, 110b are arranged such that between them free spaces 112 are provided as an air passage. In at least some of these clearances 112, ribs 113 are preferably arranged to form flow passages for the passage of air and to improve the heat exchange between the sweeping air and the fluid. As a result, the surface is increased as effectively as possible on the cooling air side. In a medium other than air and other channels may be provided, instead of an air passage.

The heat exchanger has the feature that the two involved media, for example, the cooling air and the fluid in the first upper portion of the fluid connections 110, 110a are cross-flow circulated. In the lower part of the fluid connections, the two media involved are arranged in crossflow.

Tube plates and water boxes or fluid box form chambers, which on the inlet side of the distribution of the coolant flow or fluid flow to the Serve pipes and on the exit side of the merger of the coolant flow from the pipes. The ports 102, 103, 103a, such as ports on the chambers, allow the heat exchanger to be connected to a respective fluid circuit, such as a coolant circuit.

In FIG. 1 the radiator network is shown in a design preferably made of flat tubes and corrugated fins. The tubes may have the following types: round tube design, oval tube design or package construction

The invention described herein relates to cross-flow and / or cross-countercurrent fluid / fluid heat exchangers to which one or more high-level fluid flows are supplied and from which two or more fluid streams cooled to different temperatures exit.

As the fluid according to the present application documents, both liquids, gases or liquid-gas mixtures can be considered.

In the design according to the invention, the heat exchanger preferably consists of a first one-, two- or more-row pipe-fin system with distribution and collection chambers, wherein at least a part of the heat exchanger has at least one deflection in the depth with cross-countercurrent flow. As deflection in the depth is to be understood a deflection substantially in a plane of the tubes zw. Fluid channels. This deflection from the fluid connections 110 to the fluid connections 110a takes place in the chamber 104b. Another part of the heat exchanger can also be flowed through only simply or in countercurrent, ie without or with deflection in the depth.

A deflection takes place in the width, wherein the deflection in the width is defined such that the deflection is oriented substantially perpendicular to planes of the fluid channels.

Instead of the two or more rows arranged fluid connections or tubes can also be a single-row arrangement of tubes use, these tubes then preferably in their core have a separation of different fluid channels, which correspond to the function of in FIG. 2 take over shown fluid connections.

The tube and fin system can be a system with flat, oval or round tubes or even a system with other cross-sectional shapes. The system can be mechanically joined or soldered. The pipe-to-floor connection can be made by mechanical deformation, soldering, welding or gluing. The pipe-fin system and the distribution and collection chambers may for example be composed of the following materials, in particular aluminum, non-ferrous metal, steel or plastic.

In the design according to the invention, the heat exchanger is subdivided into two or more regions by partition walls in the collecting chambers, for example one region representing the cooler of a main coolant circuit and one or more further regions having the function of low-temperature coolers or other coolers. The flow of electricity through the areas of the heat exchanger is determined by the partitions in the distribution and collection chambers and by nozzles on the distribution and collection chambers. Each cooler region thus defined may have deflections in width or depth in itself.

These additional deflections are realized by additional partitions in the distribution and collection chambers.

The partitions in the boxes are arranged or oriented to form the chambers straight, preferably horizontally or vertically, in other embodiments, however, it may also be appropriate if they are in the I-shaped, z-shaped, T-shaped and / or U-shaped. shaped or also have another, composite form.

In a preferred embodiment enters into a heat exchanger with two or more rows of tubes 110,110a only through a connecting piece 102, a fluid, such as a coolant, in the area that is the cooler of the main coolant circuit. In addition, the heat exchanger has outlet ports 103, 103a, one each for the region of the radiator of the main coolant circuit and for each low-temperature radiator region. This is associated with cascading the fluid flow, such as the coolant flow, i. At each outlet nozzle, only a portion of the fluid or coolant stream exiting from the respective radiator region is led out, the remainder being the fluid or coolant stream entering the subsequent radiator region.

The low-temperature ranges in an integrated heat exchanger are preferably arranged so that areas, which are flowed through by coolant of higher temperature in the cooling air flow behind or next to areas, which are flowed through by coolant of lower temperature.

The fluid- or coolant-side inlet cross-sections in the regions are advantageously optionally in accordance with the cascading of the fluid flow or the coolant flow also graded. The gradation of the size of the inlet cross-sections should be chosen so that the flow rate of the refrigerant on the one hand does not drop so much that the performance of the area is impaired, on the other hand, does not rise so much that the pressure loss is excessively large. Preferably, the gradation of the size of the inlet cross sections is selected so that the inlet cross section of the subsequent region of the heat exchanger or radiator region is between 1/5 and 1/2 of the outlet cross section of the preceding region of the heat exchanger or radiator region. In further embodiments, the inlet cross-section can also amount to only 1/10 of the outlet cross-section of the previous area or be the same size. It is also advantageous if the gradation of the size of the inlet cross-sections is selected so that the flow velocity of the fluid or the coolant is approximately the same in all areas. In particular, it is favorable if the flow velocity of the coolant in a subsequent cooler region is between 0.8 times and 1.2 times the flow velocity of the coolant in the preceding cooler region.

In the first preferred embodiment, the flow of the coolant through the areas of the radiator is chosen so that all the stubs can be arranged as a simple, arranged on the back of the radiator nozzle. In a further embodiment of the invention, at least individual nozzles could be arranged as an inlet or outlet both on the back of the radiator or on the side or possibly also on the radiator front. The rear of the radiator is defined to be the side facing the engine compartment when the radiator is installed in the vehicle.

The FIG. 3 shows again an embodiment of a heat exchanger 200 according to FIG. 2 in a schematic representation. The fluid or coolant enters the first portion 202 of the radiator through the inlet 201. From there, the fluid flows through the fluid connections 203 into the region 204. This region 204 is designed as a chamber and has a deflection in the depth, that is substantially in the plane of the fluid connections. The fluid is directed from the region 204 into the fluid connections 205. From there, the fluid flows into the chamber 206. This chamber has on the one hand a deflection in the width, since the fluid is passed to the lower portion of the chamber and is partially discharged there through the outlet 207 and partly through the fluid lines 208th to be led. The region 208 represents a low-temperature region without deflection in depth. From there, the fluid flows in the region 209 and then through the outlet 210. As a result, the outlet port of the first radiator region, where the entry into the low-temperature region, on the back of the radiator attached to the chamber. The flow is cascaded, ie a part of the coolant exits after the first cooler area, the other part enters the subsequent low temperature range.

The FIG. 4 shows a heat exchanger in a schematic representation, wherein parts of the heat exchanger 300 of the FIG. 4 will not be described again, as far as they are already in FIG. 2 or 3 are shown. The heat exchanger 300 has, in addition to the inlet nozzle 310 and the outlet nozzle 303 and 305, a further outlet nozzle 301. This creates a further low temperature range of the heat exchanger. This low-temperature region of the heat exchanger arises in the region 302, the region 304 representing a further low-temperature region. Thus, the heat exchanger has three respective areas 302, 304 and 306, each having an outlet 301, 303, 305 is associated with only one inlet 310. Each of the three cooler areas is simply flowed through. From the region 302 to the region 304 is a deflection in depth, preferably in the chamber 311. The intermediate walls 312, 313 of the chambers are arranged horizontally at 312 and at 313 in section I-shaped with a long leg in the vertical and a short thigh in the horizontal. With regard to the partitions, however, other variants depending on the design of the chambers of the side boxes may also be advantageous.

The FIG. 5 shows a heat exchanger 350 in a schematic representation, wherein parts of the heat exchanger 350 of FIG. 5 will not be described again, as far as they are already in the FIGS. 1 to 4 are shown. The heat exchanger 350 of the FIG. 5 has in the first side box 360 a t-shaped intermediate wall 351, consisting of a horizontal wall 351 b and a vertical wall 351 a, which is substantially on the horizontal wall. By this design of the intermediate wall 351, the side box 360 is divided into three areas 361, 362 and 363, two areas on both sides of the wall 351 a and one below the wall 351 b.

The heat exchanger 350 has in the second side box 390 a substantially z-shaped partition 392 consisting of a horizontal wall 392a, a vertical wall 392b and another horizontal wall 392c. This design of the intermediate wall 392 divides the side box 390 into two areas 391 and 393.

The region 361 communicates with the inlet 370. Starting from the region 361, the fluid flows through the fluid connections of the region 380. From there, the fluid flows into the region 393, where it is deflected both in depth and optionally in width and from there flows at least partially into the region 381. Another part flows out through the outlet 395a. The fluid flow passing through the region 381 is deflected in the region 362 in depth and then flows through the region 382 back into the region 391. From the region 391 flows another part of the fluid from the outlet 395 and another part flows through the region 383 after a deflection in depth in the region 391. From the region 383, the fluid flows into the region 363 and thence through the outlet 395b. The heat exchanger thus consists of a first cooler area and two further downstream coolers, wherein a deflection in the depth, that is, in the plane of the fluid connections, is present in the area of the second cooler and further this also has a deflection in the width. The areas 380, 381, 382 and 383 of the fluid connections are arranged such that the areas 381 and 382 are preferably located in the air flow direction in front of the area 230 and the area 383 is located below these areas.

The heat exchanger 400 according to FIG. 6 represents a further embodiment, which differs from the variant FIG. 3 differs in that the low temperature region with respect to the cooling air flow is partially in front of the first radiator area. The intermediate wall 402 of the side box 401 is Z-shaped, so that the fluid flow from the inlet 403 into the region 404 flows. This area is formed in the upper area over the width of the side box and has in the lower area a restriction of the expansion by the division by the vertical partition wall. The fluid connections of the central area are also divided by a z-shaped division into the areas 410 and 411. The fluid flows from the chamber 404 through the region 410 into the side box 430, where it is partially deflected in depth and width, and flows in part through the outlet 431 and into the region 411 and thence into the region of A portion of the region 411 second cooler is located with its fluid connections in the direction of air flow in front of a part of the radiator of the first region 410. The areas 410 and 411 are formed in section I-shaped.

FIG. 7 represents a variant of a heat exchanger 450, which compared to the heat exchanger of the FIG. 6 a horizontal intermediate wall 451 in the one side box and a further outlet 452 in the region of the chamber 453 has. As a result, the fluid flow from region 460 is deflected both into region 461 and into outlet 452. From area 461, the fluid then flows into the chamber of the side box FIG. 6 , In the area of the side box, starting from the area 461, there is a deflection in the width. Thus, the low temperature region of the heat exchanger is the FIG. 6 divided by an additional partition and an additional nozzle in two low-temperature areas. The region 460 is I-shaped in section.

The FIG. 8 shows a further embodiment of a heat exchanger 500, wherein the side boxes compared to FIG. 7 with respect to the arrangement and shape of the partition walls, that is, in the first side box 501, a partition wall 502 is arranged in a horizontal orientation and the side box 501 is divided into two sections, such as chambers 503 and 504, which are arranged substantially one below the other. In the second side box 520, a z-shaped partition 521 is disposed and divides the side box 520 into two portions 530 and 531, which are substantially I-shaped in section.

The area 503 is connected as an upper chamber to the inlet 505. From there, the fluid flows through the fluid communication region 510, which is referred to as Cut cuboidal arrangement of fluid connections is formed. From there, the fluid flows in a deflection in the width and in the depth in the region 511, which is formed as a section cuboid arrangement of fluid connections. Also, the fluid flows from the region 530 through the outlet 533. Also, the fluid flows through the region 511 and from there into the region of the chamber 504, where a deflection takes place in the depth and possibly in the width, wherein a portion of the fluid in the chamber 504 through the outlet 534 and continues to flow through the region 512, which is formed as a sectional I-shaped arrangement of fluid connections. From there, the fluid flows into the chamber 531 and from there through the outlet 535. The heat exchanger of FIG. 8 represents a variant of the embodiment of the heat exchanger according to FIG. 6 characterized in that a further low-temperature region is separated from the first radiator area by a change in the partitions and an additional nozzle.

The FIG. 9 represents a variant of the embodiment of the heat exchanger of the FIG. 8 characterized in that the second low-temperature region is divided by an additional horizontal partition 550 and an additional port 551 in two low-temperature regions.

The heat exchangers of FIGS. 2 to 8 have a cascaded flow and at least for a partial flow to a deflection in the depth.

The FIG. 10 shows a section of a heat exchanger in the vertical direction, for example, vertical to a plane of the fluid connections. The tube-and-fin system 600 of the fluid connections is in the central region at least two rows with the fluid connection regions 601 and 602 formed. This is useful for the arrangement of the individual areas of the radiator, wherein at least a partial deflection is provided in the depth.

The deflection can be done for example in the side boxes, which are not shown here. The deflection in the depth is preferably carried out in cross-counterflow. The integrated heat exchanger is divided into four sections 601, 602, 603 and 604, each section having one or more rows of tubes. Each sub-area can be easily flowed through or have a deflection in the width or in the depth. In some embodiments, portion 603 may be omitted. It is also possible to combine the partial areas 603 and 601 as well as the partial areas 602 and 604 into one area in each case. The dimensions a, b and c transversely to the direction of flow of the integrated heat exchanger can be varied within certain limits. The sum a + b + c corresponds to the overall dimension of the heat exchanger. A possible measure of the dimensions a, b and c could be given for example by the inner diameter of the associated or the nozzle. When the partial area 603 is omitted, a = 0. The portion 604 is conveniently present and optionally without deflection in depth.

In a further preferred embodiment of a heat exchanger, the flow of the coolant through the areas of the radiator is chosen so that the majority of the nozzle can be arranged as a simple, arranged on the back of the radiator nozzle, while other nozzles are arranged differently and eg laterally or at the front be led out of the distribution and collection chambers. Different variants of this design form are in the FIGS. 11 to 14 shown.

The heat exchanger 700 of the embodiment of the FIG. 11 essentially represents a variant that differs from the heat exchanger FIG. 8 differs in that both low-temperature regions 701 and 702 are the same size and thereby the second low-temperature region is not only partially, but completely before the first low-temperature region. Furthermore, the wall 703 is I-shaped and divides the side box into two chambers or areas 704 and 705, the area 705 at least partially lying in the air flow direction in front of the area 704. Connected to the area 705 is an outlet 710, which may be directed to the side or to the front.

The heat exchanger 750 of the embodiment of the FIG. 12 essentially represents a further variant, which differs from the heat exchanger FIG. 11 differs in that the main region 751 is greater than the main region 711 and a low-temperature region 752 is smaller than the low-temperature region 701. This is achieved in that the fluid connections are connected accordingly and the wall 753 is formed in section z-shaped. The main region 751 is thus partially adjacent to and behind the region 754 and above the region 752, respectively. The two low temperature regions 752 and 754 are of different sizes and the second low temperature region 754 is located partially in front of the main region 751 and before the low temperature region 752 ,

The heat exchanger 800 of the embodiment of the FIG. 13 essentially represents a further variant, which differs from the heat exchanger FIG. 12 characterized in that the one low-temperature region 801 is greater than the low-temperature region 752 and the low-temperature region 802 is smaller than the low-temperature region 754. This is achieved in that the fluid connections are connected in accordance with and the wall 810 is C-shaped and is formed essentially of two horizontal walls with a vertical wall. The main area 804 is thus located partially behind the area 802 and above the areas 802 and 801, viewed in the direction of air flow. The low temperature area 802 is above the area 801. The area 802 is thus arranged between the areas 801 and 804, the area 801 being partly direct adjacent to area 804. The two low temperature ranges 801 and 802 are different sizes. The heat exchanger 800 of FIG. 13 represents a variant of the heat exchanger of FIG. 7 is that differs in that the order of flow through the two low-temperature regions 801, 802 is reversed. This means that, starting from the inlet pipe 811, first the area 804 flows through, then the area 801 and then the area 802, wherein in the chambers 812 and 813 a corresponding deflection of the fluid flow takes place

The heat exchanger 850 of the embodiment of FIG. 14 essentially represents a further variant, which differs from the heat exchanger FIG. 12 characterized in that the one low-temperature region 754 is divided by a further division into two low-temperature regions 851, 852, so that a total of three low-temperature regions 851, 852, 853 are present. This is achieved in that the fluid connections are interconnected and the wall 860 is H-shaped and formed essentially of two horizontal walls with a vertical wall, the lower horizontal wall extending across the width of the side box and the upper horizontal Wall extends only over a portion of the width of the side box. The main area 854 is thus partially in Air flow direction is seen behind the region 851 and above the regions 852 and 853. The low temperature region 851 is above the region 852. The region 853 is arranged in the air flow direction in front of the region 852.

The presentation of the FIG. 15 shows a section through a heat exchanger 880 in the vertical direction. The pipe-fin system is at least partially at least two rows, wherein an at least partial deflection is provided in the depth. The deflection in the depth can be carried out in cross-countercurrent.

The integrated heat exchanger is subdivided into regions 881, 882, 883, 884, and 885 of fluid connections, each subregion having one or more rows of tubes. Each subregion can simply flow through or have a deflection in the width and / or in the depth. Optionally, for example, the subarea 884 and / or 885 could be omitted. It is also possible to combine the partial areas 881 and 882 as well as the partial areas 883 and 885 into one area in each case. The dimensions a, b and c transverse to the flow direction 890 of the integrated heat exchanger can be varied according to the invention. The sum a + b + c is advantageously the overall dimension of the heat exchanger. A minimum of each of the dimensions a, b and c is optionally given by an inner diameter of the associated nozzle (s). If the partial area 884 and 885 are omitted, c = 0. The portion 881 is preferably present and optionally without / with deflection in depth.

The FIG. 16 shows a heat exchanger 900, which is equipped by a central region 901 with a tube-fin system, which is divided into different areas. Furthermore, the Heat exchanger via laterally arranged side boxes 902 and 903, wherein the side boxes is divided by the arrangement of partitions into individual chambers. Some of the chambers are connected to at least one inlet and / or at least one outlet.

The central area 901 is subdivided into five separate areas of fluid connections, the areas individually having parallel fluid connections which are not connected within the areas to fluid connections of the other areas. Viewed in the direction of air flow, two regions 910, 911 are arranged at the upper end of the heat exchanger 900, with the region 910 being arranged in the air flow direction in front of the region 911. The two areas share the depth of the heat exchanger at substantially the same extent in width. In this regard, also different expansions may be present in the depth and possibly also in the width. Below these two regions, a third region 912 is arranged, which extends over the entire depth of the heat exchanger. Below this area, two further areas 913, 914 are arranged, viewed in the air flow direction, at the lower end of the heat exchanger 900, wherein the area 913 is arranged in the air flow direction in front of the area 914. The two areas share the depth of the heat exchanger at substantially the same extent in width. In this regard, also different expansions may be present in the depth and possibly also in the width.

The fluid flows through the inlet or inlet 920 through the spigot into the chamber 921 formed in the side box through the wall 922 and the side box wall. Subsequently, the fluid flows through the region 911 and is at least partially in the chamber 930 in the depth diverted. The chamber 930 is formed by the wall of the side box 903 and the intermediate wall 931. Further, a portion of the fluid flows out through the outlet 940. The fluid that is diverted in the chamber 930 then flows back through the area 910 and enters the chamber 923 formed by the wall 922 and the horizontal wall 924 in the side box 902. In the area of the chamber 923, the fluid partially deflected in width so that it flows into the area 912 and another part of the fluid exits at the outlet 940.

The fluid flowing through the region 912 passes from there into the chamber 932, where it is partially deflected again and flows partly into the region 914. Another part can flow out through the outlet 941. The fluid flowing through the region 914 enters the chamber 925, which is formed by the side box wall and the horizontal partition wall. In this chamber, the fluid is partially deflected in depth, and in part, the fluid flows through the outlet 942. The deflected fluid then flows through the region 913 and from there into the chamber 933, from where it flows out through the outlet 943. The heat exchanger thus has an inlet and four outlets. Overall, this results in an integrated heat exchanger, in which a large part of the nozzle could be arranged on the back of the radiator, while other nozzles are arranged differently or can be, for example, led out laterally or from the front of the distribution and collection chambers. In this embodiment, a plurality of partial areas can be represented, which may each have one or more rows of tubes. Each subregion can simply flow through or have a deflection in the width and / or in the depth.

In a further preferred embodiment, the heat exchanger has more than one inlet. Instead of a "cascaded" flow through all the radiator areas, which is supplied with coolant from a single inlet connection thus occurs independent coolant supply of individual subregions or groups of subregions. This design form can be represented from all previously described designs and variants by means of additional partitions and sockets.

The FIG. 17 shows a further schematic representation of a heat exchanger 1000, in which two inlets are provided and further three outlets. The FIG. 17 shows a heat exchanger 1000, which is equipped by a central region 1001 with a tube-fin system, which is divided into different areas. Furthermore, the heat exchanger has laterally arranged side boxes 1002 and 1003, wherein the side boxes is divided by the arrangement of partitions into individual chambers. Some of the chambers are connected to at least one inlet and / or at least one outlet.

The central area 1001 is subdivided into three separate areas of fluid connections, the areas individually having fluid connections connected in parallel, which are not connected within the areas with fluid connections of the other areas. When viewed in the direction of air flow 1099, two regions 1010, 1011 are arranged at the upper end of the heat exchanger 1000, the region 1010 being arranged upstream of the region 1011 in the direction of air flow. The two areas divide at substantially the same extent in width, the depth of the heat exchanger. In this regard, also different extensions can be present in the depth and possibly also in width. Below these two regions, a third region 1012 is arranged, which extends over the entire depth of the heat exchanger.

The fluid flows through the inlet or inlet 1020 through the spigot into the chamber 1021 formed in the side box through the wall 1022 and the side box wall. Thereafter, the fluid flows through the region 1010 and is at least partially deflected in the chamber 1030 in depth. The chamber 1030 is formed by the wall of the side box 1003 and the intermediate wall 1031. Further, a portion of the fluid flows out through the outlet 1040. Through another inlet 1041 further fluid flows into the chamber 1030. The fluid that is diverted in the chamber 1030, or that flows into the chamber through the other inlet, then flows back through the area 1011 and enters the chamber 1023, which is formed by the wall 1022 and the wall of the side box 1002. In the region of the chamber 1023, the fluid is partially deflected in width so that it flows into the area 1012 and another part of the fluid exits at the outlet 1042.

The fluid flowing through the area 1012 passes from there into the chamber 1032 and flows out there through the outlet 941. The heat exchanger thus has two inlets and three outlets.

In a further preferred embodiment of the invention according to FIG. 18 For example, the heat exchanger 1100 has a single-row tube-and-fin system 1101 and two side boxes 1102 and 1103. This heat exchanger is preceded by a further heat exchanger 1199 in the cooling air flow 1198. Also, the heat exchanger of only one row of tubes or several rows of tubes, provided for no deflection in depth is to be trained. In this case, however, deflections can be provided in the width or it is the subareas of an integrated heat exchanger side by side.

The design principles described above can also be applied in this case if the integrated heat exchanger is preceded by at least one further heat exchanger in the cooling air flow and these are connected, for example, to form a module. This or these upstream heat exchangers are advantageously positioned to the individual regions of the integrated heat exchanger, that current flow and temperature level in the upstream heat exchangers corresponds approximately to the situation in the "front half" of an integrated heat exchanger according to the design principles of the figures described above.

According to the invention, it may be expedient if the heat exchangers. Nozzle for inlet and / or outlet can be led out not only on the back of the radiator or laterally, but optionally also above and below or on the radiator front, viewed in the air flow direction. The nozzles can be placed, be designed as an elbow or run through nozzles.

The design features of the heat exchangers are applicable not only to the described cross-flow coolers, but also to falling stream or riser coolers

The design features are also reversible with regard to right / left, up / down.

The integration of a plurality of heat exchangers in a unit saves in particular space for the cooling module. While single Heat exchangers in the cooling module must have minimum distances from each other, close the heat exchanger areas in a unit directly to each other. Also, certain parts can assume a dual function, since they can take over functions as an intermediate elements for several heat exchanger areas.

A deflection in the depth and / or the arrangement of cooler areas with a low temperature level in the cooling air flow before radiator areas with high temperature level advantageously improves the effectiveness of the heat exchanger.

The cascading of the coolant flow over several radiator areas expediently reduces the number of nozzles required and thus the number of interfaces. This also reduces the number of required hoses, hose connections and the coolant content.

The gradation of the inlet cross sections of the radiator areas advantageously allows the maintenance of favorable conditions for heat transfer and pressure drop over all radiator areas.

Advantageously, large low-temperature ranges are possible, which may comprise a plurality of low-temperature coolers.

The cascaded low-temperature ranges can each provide cooling capacity for their associated unit and additionally for other units. In this case, cascading means that in each case parts are branched off from a fluid flow in steps or steps and the remaining remainder of the fluid continues to flow through the heat exchanger. The further flowing through the heat exchanger fluid quantity is additionally cooled, so that fluid quantities at different outlets of the heat exchanger or mass flows with different temperature are available. The respective quantities of the fluid at a given temperature can be controlled in a targeted manner by designing the respective regions of the heat exchanger.

Preferably, the regions of the heat exchanger that generate fluid at a lower temperature are preferably arranged in the cooling air flow or in another cooling mass flow, viewed in front of or alongside other regions.

The FIG. 19 12 shows a cooling circuit in schematic representation with a heat exchanger 1201, a condenser 1202, and units such as a drive motor 1203, a starter generator 1204, a transmission with a transmission oil cooler 1206, a radiator for an electronics 1207 of the vehicle, a charge air coolant radiator 1208 Pump 1209 and a bypass thermostatic valve 1210 and a plurality of lines.

The condenser 1202 may be arranged as a separate component or designed as a structural unit with the heat exchanger or be integrated with the heat exchanger 1201.

The schematic illustration shows an example of a heat exchanger 1201 according to a representation of FIG. 17 , The heat exchanger 1201 has an inlet 1220 through which a fluid from line 1221, such as coolant, flows into the heat exchanger. Then, the fluid flows through the fluid connections, for example, a pipe-fin system and flows out in part at the respective outlets 1222, 1223, 1224 again. The temperatures of the respective coolant flow at the respective outlets are different and, depending on the design, can be between approx. 10 degrees Celsius and 40 degrees Celsius or more differ. In the present example, the temperature at the inlet is about 115 degrees, at outlet 1222 about 110 degrees, at outlet 1224 about 80 degrees and at outlet 1223 about 60 degrees. However, these values depend on the particular design of the heat exchanger and the circuit.

The fluid having the highest temperature flows from the outlet 1222 to the coolant inlet of the engine 1203 via the pump 1209. There, it is heated and the heated fluid flows from the coolant outlet of the engine 1203 through the conduit 1221 to the heat exchanger inlet 1220. Between the conduit 1230 and the conduit 1221 a bypass thermostatic valve is arranged, which at least partially opens or closes the bypass connection according to predetermined characteristics, so that the engine can warm up faster, for example in a cold start situation, when the fluid is not or not completely through the radiator.

Connected to the outlet 1224 is another conduit 1231 which is connected to an oil cooler in which a heat exchange takes place between the fluid and the transmission oil. The fluid heated in the oil cooler 1206 flows through the conduit 1232 and enters the conduit 1230.

Connected to the outlet 1223 is a further conduit 1233 which is connected to a radiator 1207 for electronics and thus in series with a charge air coolant cooler 1208. The thus heated fluid flows through the conduit 1234 and enters the conduit 1230 and, after flowing through the engine, returns to the heat exchanger 1201.

It is particularly advantageous that only one pump 1209 is used in this arrangement of a main cooling circuit and of secondary cooling circuits. This is achieved in that the returns of the Secondary circuits in the main circuit before the pump open, so are connected to the suction side of the pump or the low pressure side of the pump. The auxiliary cooling circuits are guided parallel to the bypass valve 1210.

This pump may be a pump driven by an electric motor or a pump driven by the drive motor 1203, wherein the pump driven by the electric motor may preferably be operated according to the cooling requirements, that is also in electrically or electronically controlled operation.

The arrangement of a pump for supplying a main cooling circuit and at least one secondary circuit can be advantageously provided, since the at least one secondary circuit is guided parallel to the bypass valve 1210.

Claims (21)

1. A heat exchanger (101), in particular for motor vehicle cooling systems, with at least one fluid inlet (102) and at least two fluid outlets (103, 103a), with an arrangement of fluid connections between inlet, collecting, deflecting and/or outlet chambers (104, 104a, 104b, 105), wherein the fluid connections being subdivided into various regions and a first region of fluid connections being arranged between at least one inlet (102) and one first outlet (103), and a further region of fluid connections being arranged between the first outlet (103) and a second outlet (103a), characterised in that a deflection in depth, that is to say in a plane of the fluid connections, is present between at least one first region of fluid connections and one second region of fluid connections and a deflection in width, that is to say in a plane perpendicular to a plane of the fluid connections, is present between at least one first region of fluid connections and one second region of fluid connections.
2. The heat exchanger as claimed in claim 1, characterised in that a further third outlet is arranged and a further region of fluid connections is provided between the second outlet and the third outlet.
3. The heat exchanger as claimed in claim 1 or 2, characterised in that a further nth outlet is arranged and a further region of fluid connections is provided between the n-1-th outlet and the nth outlet, wherein n preferably being 3, 4, 5, 6, 7, 8, 9, 10 or greater than 10.
4. The heat exchanger as claimed in one of the preceding claims, characterised in that individual regions of fluid connections are connected to other regions of fluid connections and/or to an inlet and/or an outlet by means of inlet, collecting, deflecting and/or outlet chambers.
5. The heat exchanger as claimed in claim 4, characterised in that the inlet, collecting, deflecting and/or outlet chambers are arranged preferably in side boxes arranged laterally with respect to the fluid connections, wherein the side boxes being capable of being subdivided into various chambers by means of partitions.
6. The heat exchanger as claimed in claim 5, characterised in that the partitions are designed as vertical, horizontal or l-shaped, z-shaped, c-shaped, t-shaped walls or as walls formed compositely from these.
7. The heat exchanger as claimed in one of the preceding claims, characterised in that a deflection in depth and in width, that is to say in a plane of the fluid connections and in a plane perpendicular to a plane of the fluid connections, is present between at least one first region of fluid connections and one second region of fluid connections.
8. The heat exchanger as claimed in one of the preceding claims, characterised in that two regions of fluid connections are routed in countercurrent without an outlet between them.
9. The heat exchanger as claimed in a preceding claim, characterised in that ducts for a further medium or fluid are provided between the fluid connections.
10. The heat exchanger as claimed in claim 9, characterised in that these ducts are formed by ribs between the fluid connections.
11. The heat exchanger as claimed in claim 9, characterised in that the medium is air.
12. The heat exchanger as claimed in claim 9, characterised in that the medium is a fluid or liquid medium.
13. The heat exchanger as claimed in one of the preceding claims, characterised in that the fluid connections are tubes, preferably such as flat tubes or round tubes or oval tubes.
14. The heat exchanger as claimed in one of the preceding claims, characterised in that the tubes have a plurality of fluid ducts which do not communicate with one another over the length of the tubes.
15. The heat exchanger as claimed in one of the preceding claims, characterised in that the fluid connections or tubes have a plurality of fluid ducts which communicate with one another over the length of the tubes.
16. The heat exchanger as claimed in one of the preceding claims, characterised in that the fluid connections or tubes are arranged in a single row or in a plurality of rows next to one another for each plane of the fluid connections.
17. A fluid circuit with at least one heat exchanger having at least one inlet and at least two outlets as claimed in at least one of the preceding claims, with at least two assemblies which can be supplied by the heat exchanger by means of fluid lines and have a fluid inlet and a fluid outlet, characterised in that a pump with an inlet and outlet is arranged between one outlet of the at least one heat exchanger and one inlet of at least one assembly, and at least one outlet of a further assembly can be connected to the inlet side of the pump.
18. The fluid circuit as claimed in claim 17, characterised in that the further assembly is connected with its inlet to an outlet of the heat exchanger.
19. The fluid circuit as claimed in claim 17 or 18, characterised in that a plurality of further assemblies are connected in series and have a fluid flowing through them.
20. The fluid circuit as claimed in claim 17 or 18, characterised in that a plurality of further assemblies are connected in parallel and have a fluid flowing through them.
21. The fluid circuit as claimed in one of claims 17 to 20, characterised in that the inlet of a further assembly is connected to an outlet of the heat exchanger.

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