COLLECTING TANK OF A HEAT EXCHANGER

Abstract

A collecting tank of a heat exchanger may include a first collecting pipe and a second collecting pipe arranged adjacent to the first collecting pipe structured to accommodate a plurality of heat exchanger pipes. The first collecting pipe and the second collecting pipe may each have a hollow space which is flowable through. The first collecting pipe and the second collecting pipe may have a respective flattened bottom and a plurality of tank accommodations configured to accommodate the plurality of heat exchanger pipes disposed spaced apart from one another in the respective bottom. The respective bottom of the first collecting pipe and the second collecting pipe may extend at a predetermined angle α not equal to 180° relative to one another.

Description

CROSS-REFERENCE TO RELATED APPLICATION

This application claims priority to German Application No. DE 10 2017 218 810.3 filed on Oct. 20, 2017, the contents of which are hereby incorporated by reference in its entirety.

TECHNICAL FIELD

The present invention relates to a collecting tank of a heat exchanger, in particular of an evaporator. The invention furthermore relates to a heat exchanger comprising such a collecting tank.

BACKGROUND

Heat exchangers serve the purpose of exchanging heat between two fluids. One of these fluids typically flows via a collecting tank through heat exchanger pipes, around which the other fluid flows, so that heat is exchanged between the two fluids. As a result of the temperature differences, which thus arise, condensate accumulates inside the heat exchanger, in particular when a gas, for example air, flows around the heat exchanger pipes. This accumulating condensate needs to be discharged, so as to attain an interruption-free operation of the heat exchanger and/or an increased efficiency of the heat exchanger.

A heat exchanger comprising a collecting tank is known from CA 2 123 368 A1, which has two collecting pipes, each comprising a bottom, in which heat exchanger pipes, which are embodied as flat pipes, are accommodated. To collect and discharge accumulating condensate, a separate condensate tank, which has a w-shaped cross section comprising openings for discharging the condensate, is arranged on the side of the collecting tank facing away from the heat exchanger pipes. The heat exchanger thereby requires a larger installation space and the production thereof is more expensive and/or more complicated. In addition, the heat exchanger has an increased weight.

U.S. Pat. No. 7,971,636 B2 as well as U.S. Pat. No. 7,231,966 B2 show collecting tanks of heat exchangers, which are provided with grooves in the form of indentations or deformations, so as to be able to better discharge the accumulating condensate. In U.S. Pat. No. 7,231,966 B2, the grooves are arranged laterally on the bottoms of the collecting tank and offset to the heat exchanger pipes. In U.S. Pat. No. 7,971,636 B2, the grooves are introduced into the respective bottom and surround the accommodations for accommodating the heat exchanger pipes. The introduction of the grooves requires an extensive machining, for example deforming, of the collecting tank, in particular of the bottoms, and leads to additional production steps, which, in turn, make the production of the collecting tanks and thus of the heat exchanger, complicated and/or expensive.

A collecting tank of a heat exchanger is known from DE 11 2005 000 423 T5, in the case of which the bottoms of the collecting tank are in each case embodied so as to be curved and are provided with grooves, so as to be able to better discharge condensate. This also leads to an extensive and/or expensive production of the collecting tank and thus of the heat exchanger. This furthermore leads to an uneven contact between the bottoms and the heat exchanger pipes and a larger installation space is required.

SUMMARY

The present invention thus deals with the object of at least reducing the above-mentioned disadvantages and of specifying improved or at least alternative embodiments for a collecting tank of a heat exchangers as well as for such a heat exchanger, which are in particular characterized by a simplified production and/or an increased efficiency and/or a reduced installation space requirement and/or an improved transport of accumulating condensate.

This object is solved according to the invention by means of the subject matter of the independent claim(s). Advantageous embodiments are the subject matter of the dependent claim(s).

The present invention is based on the general idea of, in the case of a collecting tank of a heat exchanger, which has two adjacent collecting pipes each comprising a bottom, wherein accommodations for accommodating heat exchanger pipes of the heat exchanger are provided in the respective bottom, to arrange the bottoms at an incline relative to one another in the manner of a gabled roof or of an upside-down channel, respectively, so that the entire surface of the respective bottom outside of the accommodations or of the heat exchanger pipes, respectively, is on principle used for a specific and improved drainage of condensate, which arises on the bottom. A larger surface is thereby available for discharging the condensate, so that condensate can be discharged in an improved manner as a whole and an improved efficiency of the collecting tank or of the heat exchanger, respectively, is thus attained. In addition, recesses or indentations, respectively, in the collecting tank for discharging the condensate are not necessary, so that, on the one hand, the production of the collecting tank and thus of the heat exchanger is simplified and becomes more cost-efficient and, on the other hand, a smaller volume is sufficient for the condensate discharge, so that the collecting tank and the heat exchanger can be produced more cost-efficiently and so as to save more installation space. According to the idea of the invention, the collecting tank has the two collecting pipes, which are arranged adjacently, in particular so as to adjoin one another. The respective collecting pipe has a flattened pipe bottom or bottom, in short, in which said accommodations for accommodating the heat exchanger pipes are embodied and are arranged at a distance from one another. The heat exchanger pipes can thereby be flat pipes, so that the respective accommodation is embodied so as to be elongated. The collecting pipes each have a hollow space, which is fluidically connected to the heat exchanger pipes via the accommodations, so that the heat exchanger pipes are supplied with a fluid, for example coolant, via the respective collecting pipe. This means that the fluid flows into the heat exchanger pipes via the collecting tank or the collecting pipes, respectively, and/or that the fluid flows from the heat exchanger pipes into the collecting tank, in particular into at least one of the collecting pipes. According to the invention, the bottoms run at an inline to one another. The bottoms thereby form an angle α of not equal to 180°.

The incline of the bottoms preferably applies in installation position of the collecting tank or of the heat exchanger, respectively, relative to the gravitational direction, so that accumulating condensate can flow along the respective bottom as a result of the incline. This means in particular that the respective bottom in installation position preferably does not form a right angle with the gravitational direction. The incline of the bottoms further applies such that they are inclined in the cross section, in particular evenly.

It is preferred when the bottoms are each embodied as a flat plate comprising the respective accommodations. This allows for a particularly cost-efficient production of the collecting tank as well as an efficient discharge of accumulating condensate.

Embodiments, in the case of which the bottoms, which are inclined towards one another, draw and form an angle α between 177° and 171°, preferably of 174° relative to one another, prove to be advantageous. Such an angle has proven to be capable of being realized particularly easily and particularly effectively for discharging the accumulating condensate. In addition, the collecting tank can be produced in an installation space-saving manner with such an angle. However, smaller angles α are conceivable as well. The angle α is preferably attained in that the respective bottom in installation position relative to the perpendicular course to the gravitational direction differs by at least 1.5°, in particular by 3°, is inclined to the gravitational direction between 85.5° and 88.5°, in particular by 87°.

On principle, the incline of the bottoms relative to one another is embodied arbitrarily. It is conceivable that the bottoms are inclined all the way to the corresponding hollow space. In this case, the bottoms thus form the angle α on the side facing the hollow space, or the angle is α>180°, respectively, provided that it is measured on the side facing away from the hollow space.

Alternatives, in the case of which the bottoms are inclined away from the corresponding hollow space, are also conceivable. The bottoms thereby form the angle α on the side facing away from the hollow space, or the angle is α>180°, provided that it is measured on the side facing the hollow space.

A fluid, which flows through the corresponding heat exchanger during operation, can flow through the hollow space of the respective collecting pipe, in particular a coolant. A flow cross section of the respective collecting pipe is thereby preferably bounded or formed, respectively, by the bottom and a wall connected to the bottom.

Alternatives, in the case of which the wall has a circular section in the shape of a circular segment located opposite the corresponding bottom and transition sections connected thereto on both sides, which transition into the bottom, thereby prove to be advantageous. The respective transition section is thereby formed and embodied in such a way that the circular section, together with the transition sections, bounds or defines an Ω-shaped flow cross section or a flow cross section close thereto, respectively. This allows in particular to realize a fluidic supply of the collecting pipe, which preferably takes place at an end of the collecting pipe or on the front side of the collecting pipe, respectively, or of the collecting tank, in a particularly effective manner and with reduced pressure losses.

The accommodations of the respective collecting pipe, hereinafter also referred to as tank accommodations, can on principle be embodied arbitrarily. The tank accommodations of the respective collecting tank are preferably arranged spaced apart in the longitudinal direction of the collecting pipe. It is furthermore preferred when the tank accommodations are formed by passages of the bottom. This allows in particular for a fluid-tight and/or stable connection of the bottom and thus of the collecting pipe or of the collecting tank, respectively, with the heat exchanger pipes, in particular flat pipes, accommodated therein.

It is advantageous when the passages of at least one of the bottoms are directed to the outside and thus away from the corresponding hollow space. This means that the passages do not penetrate into the hollow space, but protrude to the outside from the bottom relative to the hollow space. This in particular has the result that the portion inside the respective collecting pipe, which can be flown through, is increased, so that the respective collecting pipe and thus the collecting tank as a whole can be produced to be smaller and thus in a more installation space-saving manner. The increased portion, which can be flown through, likewise leads to an increased efficiency of the corresponding heat exchanger.

It is preferred when the passages are produced by a ripping of the bottom, thus when they are in particular ripped to the outside. This allows for a cost-efficient production of the collecting tank and for an optimized use of the available volume.

Embodiments, in the case of which the passages protrude from the corresponding bottom by less than 3 mm, are considered to be preferred. The passages thus have a height of less than 3 mm. Heights of less than 2.5 mm and 2.2 mm are particularly preferred, a height of 2 mm is very much preferred.

Embodiments, in the case of which at least one of the passages, preferably the respective passage, has a front side, which faces away from the corresponding bottom and which runs in a curved manner, prove to be advantageous. The curved course thereby applies in particular in the transverse direction or transversely to the distance direction of the passages, respectively. Particularly preferably, the front sides are curved convexly relative to the corresponding bottom in such a way that a central area of the front side is spaced apart farther from the bottom than outer areas of the passage, which run in the transverse direction. Such a curved course of the passage or of the front side, respectively, allows in particular to contact corrugated fins arranged in the heat exchanger between the heat exchanger pipes at the further areas of the front sides, which protrude from the bottom, with the heat exchanger pipes and the front sides, and to thus provide an enlarged contact area between the corrugated fins and the heat exchanger pipes, so that the heat exchanger as a whole has an increased efficiency and/or can be produced in a more installation space-saving manner.

To mechanically reinforce the collecting tank, in particular the respective collecting pipe, the collecting tank can be provided with beads, in particular reinforcing beads. The respective collecting pipe is preferably provided with a plurality of such beads, which are advantageously introduced so as to be located opposite to the bottom, in particular in the wall, preferably in the circular section. In addition, the beads of the respective collecting pipe are advantageously spaced apart in the distance direction of the corresponding tank accommodations and thus in particular in the longitudinal direction. This provides for a particularly effective and simple mechanical stabilizing of the collecting tank.

It is particularly advantageous when both collecting pipes have such beads, wherein one bead of the first collecting pipe and one bead of the second collecting pipe each touch one another in an area between both collecting pipes or are in mechanical contact, respectively. The beads, which touch one another, can in particular run in parallel. Such an embodiment of the collecting tank has proven to be particularly stable. This mechanical stability is improved when the area between the two collecting pipes is a central seam of the collecting tank, at which the walls of the collecting pipes, in particular a transition section of one of the collecting pipes, is in contact with the transition section of the other collecting pipe. A mechanical stabilization is thereby attained across an increased height of the collecting tank.

On principle, the collecting pipes of the collecting tank can be produced separately and can subsequently be attached to one another, in particular connected to one another.

Preferred embodiments provide for the integral production of both collecting pipes, in particular of the entire collecting tank. The collecting pipes are thus produced monolithically or of the same base material, respectively. The collecting pipes can in particular be made of one sheet metal part, in particular by forming the sheet metal part. The collecting pipes are thus in particular made of the same sheet metal part, which is processed to produce the collecting pipes, in particular deformed, and which is provided with the collecting tank accommodations. The collecting tank, in particular the inclined course of the bottoms, can thus be realized in a cost-efficient and simple manner. In addition, the tank accommodations can thus be introduced into the respective bottom in a simplified manner. The sheet metal part can have a thickness of less than 1.2 mm, for example 1 mm or less, for example 0.9 mm or less, in particular between 0.8 mm and 0.9 mm, for example 0.8 mm.

It goes without saying that, in addition to the collecting tank, a heat exchanger comprising such a collecting tank also belongs to the scope of this invention. The heat exchanger thereby has at least one such collecting tank, which accommodates heat exchanger pipes of the heat exchanger, in particular flat pipes, via the tank accommodations of the collecting pipes. The collecting pipes of the at least one collecting tank, together with the heat exchanger pipes, form a first duct system of the heat exchanger, through which a first fluid, in particular coolant, flows. The heat exchanger pipes are arranged spaced apart relative to one another and thus form a second duct system for a second fluid, in particular for a gas, for example for air, wherein the second fluid exchanges heat with the first fluid, which flows through the heat exchanger pipes, via the second duct system via the heat exchanger pipes, if applicable via corrugated fins arranged between the heat exchanger pipes.

On principle, the heat exchanger can be used arbitrarily. The heat exchanger is in particular an evaporator, which is used in an air conditioning system, for example of a motor vehicle.

Further important features and advantages of the invention follow from the subclaims, from the drawings, and from the corresponding figure description by means of the drawings.

It goes without saying that the above-mentioned features, and the features, which will be described below, cannot only be used in the respective specified combination, but also in other combinations or alone, without leaving the scope of the present invention.

Preferred exemplary embodiments of the invention are illustrated in the drawings and will be described in more detail in the description below, wherein identical reference numerals refer to identical or similar or functionally identical components.

BRIEF DESCRIPTION OF THE DRAWINGS

In each case schematically,

FIG. 1 shows a highly simplified, circuit diagram-like illustration of an air conditioning system in a vehicle,

FIG. 2 shows an isometric partial view of a heat exchanger of the air conditioning system comprising a collecting tank and a connector assembly,

FIG. 3 shows a cross section through the heat exchanger in partial view,

FIG. 4 shows a cross section of the collecting tank,

FIG. 5 shows an isometric partial view of the collecting tank,

FIG. 6 shows an isometric partial view of the heat exchanger comprising the connector assembly in exploded illustration,

FIG. 7 shows a partial view of the heat exchanger,

FIG. 8 shows a cross section through the connector assembly in a further exemplary embodiment.

DETAILED DESCRIPTION

An air conditioning system 1, which can be used in a vehicle 2, so as to climatize for example a vehicle interior 3 of the vehicle 2, is illustrated in FIG. 1 in a highly simplified manner. The air conditioning system 1 has a circuit 4, in which a coolant is driven by a conveying device 5 and circulates. The coolant thereby flows through a capacitor 6, an expander 7, as well as an evaporator 8 in succession, wherein the capacitor 6 and the evaporator 8 in each case act as a heat exchanger 9. The coolant and a further fluid flows through the respective heat exchanger 9 in such a way that a heat exchange results between the coolant and the further fluid. In the case of the evaporator 8, the further fluid is air 10, which flows through the evaporator 8 and is cooled thereby, wherein the cooled air 10 is supplied to the vehicle interior 3.

FIG. 2 shows an isometric partial view of one of the heat exchangers 9, in particular of the evaporator 8. The heat exchanger 9 has a plurality of heat exchanger pipes 11, through which the coolant flows and which are arranged spaced apart from one another. In the shown example, the heat exchanger pipes 11 are embodied as flat pipes 12. As a result of the spaced-apart arrangement of the heat exchanger pipes 11, air 10 can flow between the heat exchanger pipes 11 and can thereby flow around them and can hereby exchange heat with the coolant, which flows through the heat exchanger pipes 11, and can thus be cooled. An improved heat exchange between the air 10 and the coolant can be attained in that corrugated fins 13, which can be flown through between adjacent heat exchanger pipes 11, are provided. The fluidic supply of the heat exchanger pipes 11 with the coolant takes place with the help of at least one collecting tank 14, wherein a collecting tank 14 can be seen at an upper end of the heat exchanger 8 in FIG. 2. At an opposite lower end, which is not shown, the heat exchanger 9 preferably has a further second collecting tank 14, which is not shown.

As follows from a combined view of FIG. 2 and FIG. 3, in which the corrugated fin 13 is suggested by a dashed line course and is illustrated in a transparent manner, the collecting tank 14 has two collecting pipes 15, 16, namely a first collecting pipe 15, and a second collecting pipe 16. On the side facing the heat exchanger pipes 11, the respective collecting pipe 15, 16 has a flattened pipe bottom 17, or bottom 17 in short. A wall 18 of the corresponding collecting pipe 15, 16, which bounds a hollow space 19 of the collecting pipe 15, 16, which can be flown through, with the bottom 17, connects at the respective bottom 17. The collecting pipes 15, 16 each run in a longitudinal direction 20 and thus essentially in parallel and are arranged adjacent to one another in a transverse direction 21, which runs transversely to the longitudinal direction 20, in particular so as to adjoin one another directly. The walls 18 of the collecting pipes 14, 15 thereby meet in a central area 22 of the collecting tank 14 in the transverse direction 21, and thus form a central seam 23 of the collecting tank 14, which is arranged centrally in the transverse direction 21 and which extends in the longitudinal direction 20. In the bottom 17, the respective collecting pipe 15, 16 has accommodations 24 for the heat exchanger pipes 11, which will also be identified below as tank accommodations 24. The tank accommodations 24 of the respective collecting pipe 14, 15 are spaced apart in the longitudinal direction 20 and in each case accommodate a heat exchanger pipe 11. In the shown example, the tank accommodations 24 of both collecting pipes 14, 15 are thereby arranged equidistant in the longitudinal direction 20, wherein a tank accommodation 24 of the second collecting pipe 16 is arranged adjacent to the respective tank accommodation 24 of the first collecting pipe 15 in the transverse direction 21 in such a way that two heat exchanger pipes 11, which are aligned with one another and which are spaced apart from one another in each case, are arranged in the transverse direction 21 and that this arrangement repeats itself in the longitudinal direction 20.

In the shown example, the coolant, which flows into the first collecting pipe 15 and in the heat exchanger pipes 11, which are arranged in the tank accommodations 24 of the first collecting pipe 15 and are thus fluidically connected thereto, is supplied to the first collecting pipe 15 via a connector assembly 25. The coolant flows through these heat exchanger pipes 11 and, in particular in the non-illustrated, opposite, lower or second collecting tank 14, respectively, is deflected into the heat exchanger pipes 11, which are accommodated in the tank accommodations 24 of the second collecting pipe 16, so that the coolant subsequently flows via these heat exchanger pipes 11 into the second collecting pipe 16, wherein the coolant is sucked from the second collecting pipe 16 via the connector assembly 25. The coolant is thus pumped/injected into the first collecting pipe 15 with the help of the conveying device 5, and is sucked/discharged from the second collecting pipe 16.

As a result of the heat exchange between the coolant, which flows through the heat exchanger pipes 11 and the collecting pipes 15, 16, and the air 10, the air 10 is cooled. As a result of the cooling of the air 10, condensate accumulates, which can in particular deposit on the bottom 17 of the respective collecting pipe 15, 16. As can in particular be gathered from FIGS. 3 and 4, wherein FIG. 4 only shows the collecting tank 14 in cross section, the bottoms 17 of the collecting pipes 15, 16 run at an incline relative to one another in the manner of a gabled roof or of an upside-down channel, so that they form a predetermined angle 26, hereinafter also referred to as angle α, of not equal to 180°, in particular between 171° and 177°, advantageously of approx. 174°. The respective bottom 17 is thereby inclined relative to the transverse direction 21, wherein said angle 26 is formed by the outer surface 27 of the bottoms 17 facing the heat exchanger pipes 11, which, with the exception of the tank accommodations 24, run in an essentially plane and in a plate-shaped manner, so that the bottoms 17 are each embodied as a plane plate 28. In an installation position 29 or use position 29, which is illustrated for example in FIGS. 3 and 4, the bottoms 17 are thereby also inclined relative to the gravitational direction G in such a way that, in the cross section with the gravitational direction G, they form an angle of smaller than 90°. In other words, the outer surfaces 27 of both bottoms 17 are inclined relative to the gravitational direction G in the installation position 29, so that condensate accumulating on the bottoms 17 can flow along the outer surface 27 in a simplified manner and can thus be discharged in a simplified manner. In the case of the example shown in FIGS. 3 and 4, both bottoms 17 are thereby inclined to the corresponding hollow space 19, so that the bottoms 17 or the outer surfaces 27, respectively, form an angle 26 of smaller than 180°, in particular of 174°, on the side facing the hollow spaces 19 or facing away from the heat exchanger pipes 11, respectively. The accumulating condensate can thus flow all the way to the central area 22. This accumulating condensate can then flow in the central area 22 or between the heat exchanger pipes 11, which are adjacent in the transverse direction 21, respectively, in the direction of the opposite, lower collecting tank 14, which is not shown, and can flow there to the outside from the central area 22 of this collecting tank in the transverse direction 21, where the condensate can flow away and/or is discharged.

It can in particular be seen in FIGS. 3 to 5 that the tank accommodations 24 of the respective bottom 17 or of the collecting pipe 14, 15, respectively, are each formed by a passage 30, which can be produced by means of a tearing of the corresponding bottom 17. It can be seen thereby that the passages 30 are each directed away from the corresponding hollow space 19 and thus do not penetrate into the hollow space 19. It is in particular possible hereby to insert the heat exchanger pipes 11 into the collecting pipes 14, 15 with a smaller penetration depth, so that the volume of the hollow space 19, which can be flown through or which can be used, respectively, is increased. It can furthermore be gathered in particular from FIGS. 3 and 4 that the passages 30 have front sides 31, which face away from the corresponding hollow space 19, wherein the front sides 31 run in a curved manner in the transverse direction 21, in particular curved in the shape of a circular segment. As can be gathered from FIG. 3, a reduced contact area results between the front side 31 and the adjacent corrugated fin 13 at the area of the front side 31, which protrudes the most. This volume can thus also be improved and can be used more efficiently for providing with the corrugated fins 13.

As follows in particular from FIGS. 3 to 5, the collecting tank 14 in the shown example is produced integrally from one sheet metal part 32 or by forming the sheet metal part 32, respectively. It can further be seen that the wall 18 of the respective collecting pipe 15, 16 has a circular section 33 in the shape of a circular segment located opposite the corresponding bottom 17, as well as transition sections 34, which connect to the circular section 33 on both sides and which transition into the bottom 17, wherein the circular section 33 and the transition sections 34 define a flow cross section 35 of the corresponding collecting pipe 15, 16 or the corresponding hollow space 19, respectively. The flow cross section 35 is thereby preferably Ω-shaped or is close to an Ω-shape, respectively, in the area of the circular section 33 and in the adjacent area of the corresponding transition sections 34. In the central area 22, a transition section 34 each of both collecting pipes 15, 16 adjoin one another and thus form the central seam 23.

On the side facing away from the heat exchanger pipes 11, in particular in the area of the wall 18, the respective collecting pipe 15, 16 has a plurality of beads 36, which will also be identified below as reinforcing beads 36. The reinforcing beads 36 are each embodied as indentations 37, which are directed to the outside. The reinforcing beads 36 run in the transverse direction 21 and are spaced apart from one another in the longitudinal direction 20. A reinforcing bead 36 of the first collecting pipe 15 and a reinforcing bead 36 of the second collecting pipe 16 thereby each meet in the central area 22 of the collecting tank 14 or in the area of the central seam 23, respectively, in which the transition sections 34 of the collecting pipes 15, 16 adjoin one another. An improved mechanical stability of the entire collecting tank is thus attained, also outside of the beads 36, in particular also in a height direction 47, which runs transversely to the longitudinal direction 20 and transversely to the transverse direction 21.

According to FIG. 2 as well as FIGS. 6 and 7, the connector assembly 25 has a base plate 38 as well as an outer shell 39. The base plate 38 has a first plate opening 40 and a second plate opening 41. The base plate 38 abuts on a front side 46 of a pipe bundle 42, which consists of the heat exchanger pipes 11 and the at least one collecting tank 14. The first plate opening 40 is thereby fluidically connected to a first collecting pipe opening 43 on the front side or longitudinal end side, respectively, of the first collecting pipe 15 in a fluidic manner, whereas the second plate opening 41 is fluidically connected to a second collecting pipe opening 44 on the front side or longitudinal end side, respectively, of the second collecting pipe 16. The respective plate opening 40, 41 is embodied as an aperture 45 in the base plate 38. The base plate 38 extends in the transverse direction 21 as well as in the height direction 47 and abuts on the front side 46 of the collecting tank 14 as well as on the adjacent, outer corrugated fin 13. On the end of the base plate 38, which is spaced apart from the collecting tank 14, a first plate molding 48 protrudes from the corrugated fin 13 in the transverse direction 21, and a second plate molding 49 adjacent thereto in the height direction 48 and offset to the collecting tank 14. The outer shell 39 follows the course of the base plate 38 and has a first shell molding 50 located opposite the first plate molding 48, and a second shell molding 51 located opposite the second plate molding 49. The first plate molding 48, together with the first shell molding 50, forms a first pipe accommodation 42 for a first supply pipe body 53, whereas the second plate molding 49 forms, with the second shell molding 51, a second pipe accommodation 54, which is separate from the first pipe accommodation 52 and is spaced apart in the height direction 47, for a second supply pipe body 55 of the assembly 25. The respective supply pipe body 53, 55 has a pipe-shaped adapter element 56, which is accommodated in the corresponding pipe accommodation 52, 54 and is enclosed in a positive manner in such a way that the supply pipe body 53, 55 is fastened in the corresponding pipe accommodation 52, 54 in a mechanically stable manner. Even through the respective supply pipe body 53, 55 is illustrated so as to be spaced apart from the corresponding adapter element 56 in FIG. 6, the respective supply pipe body 53, 55 and the corresponding adapter element 56 can be made integrally, in particular monolithically, so that no separate connection between the adapter element 56 and the corresponding supply body 53, 55 is necessary.

The first supply pipe body 53 is fluidically connected to the first plate opening 40 and thus to the first collecting pipe 15 via a first supply duct 57 connected to the first accommodation 52. In contrast, the second supply pipe body 55 is fluidically connected to the second plate opening 41 and thus to the second collecting pipe 16 via the second pipe accommodation 54 and a second supply duct 58, which is separated from the first supply duct 57. Coolant is thus introduced into the first accumulating pipe 15 via the first supply pipe body 53, whereas coolant is sucked from the second collecting pipe 16 via the second supply pipe body 55. The respective supply duct 57, 58 thereby connects to the corresponding pipe accommodation 52, 54, and is formed by the base plate 38 as well as a duct section 59 of the outer shell 39, which is embodied by a molding.

As can in particular be gathered from FIG. 6, the first plate opening 40 is smaller, has in particular a smaller cross section than the second plate opening 41. It can further be seen that the second plate opening 41 has a shape, which is adapted to the circular section 33 of the second collecting pipe 16 in the area of the second collecting pipe opening 44, or an adapted cross section, respectively. This means in particular that the cross section of the second plate opening 41 is embodied complementary to the cross section of the second collecting pipe opening 44. The coolant can thereby be sucked from the second collecting pipe 16 particularly effectively and with little loss of pressure.

FIG. 8 shows a further exemplary embodiment of the base plate 38, in the case of which the second plate opening 41 has a cross section, which corresponds to the flow cross section 35 of the second collecting pipe 16 in FIGS. 3 and 4, which, in the case of the shown example, preferably also corresponds to the flow cross section 35 of the second collecting pipe opening 44. It can further be seen in FIG. 8 that the plate openings 40, 41 are each arranged in a depression 60, which is directed towards the collecting tank 14, wherein the depressions 60 each slightly penetrate into the corresponding collecting pipe opening 43, 44 and have a form filling one of the corresponding collecting opening 43, 44. The second plate opening 41 is thereby embodied in the entire corresponding depression 60, whereas the first plate opening 40 has a round form and is arranged approximately in the center in the corresponding depression 60. It can also be seen that the depressions 60 follow the inclined course of the bottoms 17.

In the case of the exemplary embodiment shown in FIG. 8, the first plate molding 48 differs from the second plate molding 49, so that the first pipe accommodation 52 also differs from the second pipe accommodation 54. The adapter element 56 of the first supply pipe body 53 and the adapter element 56 of the second supply pipe body 55 are thus embodied differently in this exemplary embodiment. In contrast, the respective pipe accommodation 52, 54 is embodied identically in FIGS. 2, 6 and 7, so that the adapter elements 56 of both supply pipe bodies 53, 55 are embodied identically as well. It can further be seen in FIG. 6 that the first supply pipe body 53 outside of the corresponding adapter element 56 is smaller than the second supply pipe body 55 and has a correspondingly smaller flow cross section.

The base plate 38, the outer shell 39 as well as the supply pipe bodies 53, 55, in particular the adapter elements 56, are preferably joined integrally to one another by means of a joint process, whereby it is preferred when they are soldered to one another. For this purpose, the outer shell 39 and the base plate 38 can be solder-plated at least on one side. The respective adapter element 56 can thereby be placed in the corresponding plate molding 48, 49, and the outer shell 39 can subsequently be brought into contact with the base plate 38, and can be fixed thereto so as to attain the form of the connector assembly 25 shown in FIGS. 2 and 7, wherein the assembly 25 is joined integrally subsequently, in particular soldered. It is also conceivable to join the assembly 25 integrally, in particular to weld it, together with further parts of the heat exchanger 9. In addition to the production of the connector assembly 25, a connection of the connector assembly 25 to the remaining heat exchanger 9 is simultaneously attained as well thereby. In this case, as little solder as possible is attached to the side of the base plate 38 facing away from the outer shell 39, in particular a solder-plating comprising a solder portion of less than 5%, so as to prevent or so as to at least reduce a combustion or damages, respectively, to the adjacent corrugated fin 13.

As can in particular be gathered from FIGS. 2, 6 and 7, the outer shell 39 has, in the area of the plate openings 40, 41, a handle section 61, which protrudes on the edge side, follows the form of the collecting tank 41 and of the base plate 38, and which protrudes beyond the base plate 38 on the edge side. The handle section 61 encompasses the front side 46 of the collecting tank 14 on the edge side and is mechanically connected to the collecting tank 14 via a plurality of connecting elements 62, which are arranged so as to be distributed and which interact in a positive manner with mating connecting elements 63 provided on the walls 18 of the collecting pipes 15, 16. The collecting pipe openings 43, 44 and the base plate 38 are thereby encompassed by the handle section 61 on the edge side, because the handle section 61 abuts on the outer side of the wall 18 of the respective collecting pipe 15, 16. This stabilizes the connection between the collecting tank 14 and the connector assembly 25 and leads to smaller pressure losses in the coolant or to an improved sealing, respectively, of the flow path of the coolant. The connecting elements 62 and mating connecting elements 63 can further be used to fix the assembly 25 in a relative manner to the remaining heat exchanger 9 prior to an integral joining.

In the case of the shown examples, both pipe accommodations 52, 54 extend along the base plate 38, so that they are oriented perpendicularly to the corresponding plate opening 40, 41 or so that the pipe accommodations 52, 54 can each be flown through in a plane, which runs perpendicular to the corresponding plate opening 40, 41, respectively. The respective supply duct 57, 58 thereby runs in a curved manner, in particular by 90°.

As shown in FIG. 3, the collecting tank 14 has a tank height 65, which runs in the height direction 47, which can be less than 48 mm, in particular less than 46 mm, for example between 40 mm and 43 mm, in particular 42 mm. A corresponding height 66 of the passages 30, hereinafter referred to as passage height 66, can be less than 3 mm, preferably less than 2.5 mm and 2.2 mm, particularly preferably 2 mm.

A height 76, which runs in the height direction 47, of a net 75, which consists of the heat exchanger pipes 11 and corrugated fins 13, of the heat exchanger 9, also referred to as net height 76 (see also FIG. 7) is preferably less than 45 mm, in particular less than 42 mm. Advantageously, the net height 76 is between 39 mm and 40 mm, in particular between 39.4 mm and 40 mm.

Claims

1. A collecting tank of a heat exchanger, comprising:

a first collecting pipe and a second collecting pipe arranged adjacent to the first collecting pipe structured to accommodate a plurality of heat exchanger pipes, the first collecting pipe and the second collecting pipe each having a hollow space which is flowable through;

the first collecting pipe and the second collecting pipe having a respective flattened bottom; and

a plurality of tank accommodations configured to accommodate the plurality of heat exchanger pipes disposed spaced apart from one another in the respective bottom of the first collecting pipe and the second collecting pipe;

wherein the respective bottom of the first collecting pipe and the second collecting pipe extend at a predetermined angle α not equal to 180° relative to one another.

2. The collecting tank according to claim 1, wherein the predetermined angle α is from 177° to 171°.

3. The collecting tank according to claim 1, wherein the respective bottoms of the first collecting pipe and the second collecting pipe is structured as a plane plate.

4. The collecting tank according to claim 1, wherein the respective bottoms of the first collecting pipe and the second collecting pipe is inclined towards a corresponding hollow space.

5. The collecting tank according to claim 1, wherein the predetermined angle α is greater than 180°, and wherein the respective bottom of the first collecting pipe and the second collecting pipe is inclined away from a corresponding hollow space.

6. The collecting tank according to claim 1, wherein at least one of the first collecting pipe and the second collecting pipe includes a wall coupled to the respective bottom and defining a flow cross section with the respective bottom.

7. The collecting tank according to claim 6, wherein the wall has a circular section in the shape of a circular segment disposed opposite the respective bottom and a plurality of transition sections connected thereto on both sides, which transition into the respective bottom.

8. The collecting tank according to claim 1, wherein the plurality of tank accommodations of the respective bottom of at least one of the first collecting pipe and the second collecting pipe are defined by a plurality of passages directed away from a corresponding hollow space.

9. The collecting tank according to claim 8, wherein at least one of the plurality of passages protrudes from the respective bottom by less than 3 mm.

10. The collecting tank according to claim 8, wherein at least one of the plurality of passages has a passage front side extending in a curved manner.

11. The collecting tank according to claim 1, wherein:

the first collecting pipe and the second collecting pipes each have a plurality of beads disposed on a respective side arranged opposite the respective bottom; and

a bead of the first collecting pipe and a bead of the second collecting pipe are in mechanical contact in an area between the first collecting pipe and the second collecting pipes.

12. The collecting tank according to claim 1, wherein the first collecting pipe and the second collecting pipe are integrally provided as a single sheet metal part.

13. A heat exchanger comprising:

at least one collecting tank including: a first collecting pipe and a second collecting pipe arranged adjacent to the first collecting pipe each having a hollow space which is flowable through; the first collecting pipe and the second collecting pipe having a respective flattened bottom; and a plurality of tank accommodations disposed spaced apart from one another in the respective bottom of the first collecting pipe and the second collecting pipe;

a plurality of heat exchanger pipes accommodated in the plurality of tank accommodations of the respective bottoms of the first collecting pipe and the second collecting pipe;

wherein the respective bottom of the first collecting pipe and the second collecting pipe extend relative to one another at a predetermined angle α not equal to 180°.

14. The heat exchanger according to claim 13, wherein at least one of the first collecting pipe and the second collecting pipe includes a wall coupled to the respective bottom and defining a flow cross section with the respective bottom.

15. The heat exchanger according to claim 13, wherein the plurality of tank accommodations of the respective bottom of at least one of the first collecting pipe and the second collecting pipe are defined by a plurality of passages directed away from a corresponding hollow space.

16. The heat exchanger according to claim 15, wherein at least one of the plurality of passages protrudes from the respective bottom by less than 3 mm.

17. The collecting tank according to claim 2, wherein the predetermined angle α is 174°.

18. A collecting tank of a heat exchanger comprising:

a first collecting pipe and a second collecting pipe arranged adjacent thereto each defining a respective hollow space through which a flow is flowable, the first collecting pipe and the second collecting pipe including a respective flattened bottom, a respective wall coupled to the respective bottom, and a flow cross section defined between the respective wall and the respective bottom; and

a plurality of tank accommodations disposed spaced apart in the respective bottom configured to accommodate a plurality of heat exchanger pipes;

wherein the respective bottom of the first collecting pipe and the second collecting pipe extend transversely to one another at a predetermined angle α.

19. The collecting tank according to claim 18, wherein the predetermined angle α is greater than 180°, and wherein the respective bottom of the first collecting pipe and the second collecting pipe is inclined away from a corresponding hollow space.

20. The collecting tank according to claim 18, wherein the predetermined angle α is 171° to 177°, and wherein the respective bottom of the first collecting pipe and the second collecting pipe is inclined towards a corresponding hollow space.