DE102017218810A1 - Collection box of a heat exchanger - Google Patents

Abstract

The present invention relates to a collecting box (14) of a heat exchanger (9) with two collecting tubes (15, 16) which are arranged adjacent and each having a flattened bottom (17) with box receptacles (24) for receiving heat exchanger tubes (11) of the heat exchanger ( 9). A space-reduced design and / or increased efficiency of the collecting tank (14) and of the heat exchanger (9) is achieved in that the bottoms (17) of the collecting pipes (15, 16) are inclined relative to one another. The invention further relates to a heat exchanger ( 9), in particular an evaporator (8) with such a collecting box (14).

Description

The present invention relates to a header of a heat exchanger, in particular an evaporator, according to the preamble of claim 1. The invention further relates to a heat exchanger with such a collecting box.

Heat exchangers serve the purpose of exchanging heat between two fluids. One of these fluids usually flows via a collecting tank through heat exchanger tubes, which are flowed around by the other fluid, so that heat is exchanged between the two fluids. Due to the resulting temperature differences condensate falls within the heat exchanger, especially when the heat exchanger tubes of a gas, eg. Air, are flowed around. This accumulating condensate should be removed in order to achieve a trouble-free operation of the heat exchanger and / or increased efficiency of the heat exchanger.

From the CA 2 123 368 A1 a heat exchanger with a collecting box is known, which has two manifolds, each having a bottom, in which formed as flat tubes heat exchanger tubes are added. For collecting and removing accumulating condensate, a separate condensate box is arranged on the side remote from the heat exchanger tubes side of the collecting tank, which has a w-shaped cross section with openings for discharging the condensate. As a result, the heat exchanger requires an enlarged space and is more expensive and / or more complicated to manufacture. In addition, the heat exchanger has an increased weight.

The US Pat. No. 7,971,636 B2 as well as the US Pat. No. 7,231,966 B2 show headers of heat exchangers, which are provided with grooves in the form of indentations or deformations in order to better dissipate the resulting condensate can. In the US Pat. No. 7,231,966 B2 the grooves are laterally arranged on the floors of the collecting tank and offset from the heat exchanger tubes. In the US Pat. No. 7,971,636 B2 the grooves are introduced in the respective floor and surround the receptacles for receiving the heat exchanger tubes. The introduction of the grooves requires a complex processing, such as deformation, of the collecting tank, in particular the floors, and leads to additional manufacturing steps, which in turn make the preparation of the collecting tank and thus the heat exchanger complicated and / or expensive.

From the DE 11 2005 000 423 T5 is a collection box of a heat exchanger is known, in which the bottoms of the header are each formed curved and grooved to better dissipate condensate can. This too leads to a complicated and / or expensive production of the collecting tank and thus of the heat exchanger. In addition, this results in an uneven contact between the floors and the heat exchanger tubes state and it is a larger space required.

The present invention therefore has for its object to at least reduce the above-mentioned disadvantages and to provide for a header of a heat exchanger and for such a heat exchanger improved or at least alternative embodiments which are characterized in particular by simplified production and / or increased efficiency and / or or a reduced space requirement and / or improved transport of accumulating condensate distinguished.

This object is achieved by the subjects of the independent claims. Advantageous embodiments are the subject of the dependent claims.

The present invention is based on the general idea, in a collection box of a heat exchanger having two adjacent headers each having a bottom, wherein in the respective bottom receptacles for receiving heat exchanger tubes of the heat exchanger are provided, the floors in the manner of a saddle roof or an inverted Trough relative to each other inclined to arrange, so that in principle the entire surface of the respective soil outside the receptacles or the heat exchanger tubes is used for a targeted and improved outflow of condensate arising on the ground. As a result, there is a larger area available for discharging the condensate, so that condensate can be removed in an improved overall manner and consequently an improved efficiency of the collecting tank or the heat exchanger is achieved. In addition, formations or indentations in the collecting box for discharging the condensate are not necessary, so that on the one hand simplifies the production of the header tank and thus the heat exchanger and cheaper and on the other hand, a smaller volume sufficient for condensate removal, so that the collection box and the heat exchanger made cheaper and space-saving can be. According to the idea of the invention, the collecting box has the two collecting pipes, which are arranged adjacent, in particular adjoining one another. The respective manifold has a flattened tube bottom or shortly bottom, in which said receptacles are designed for receiving the heat exchanger tubes and arranged spaced from each other. The heat exchanger tubes can do this Be flat tubes, so that the respective receptacle is elongated. The headers each have a cavity, which is fluidly connected to the heat exchanger tubes via the receptacles, so that the heat exchanger tubes are supplied via the respective manifold with a fluid, for example. Refrigerant. This means that the fluid flows into the heat exchanger tubes via the collecting box or the collecting tubes and / or the fluid flows from the heat exchanger tubes into the collecting box, in particular into at least one of the collecting tubes. According to the invention the floors are inclined to each other. The floors form an angle α of 180 °.

The inclination of the floors preferably applies in the installed position of the collecting tank or the heat exchanger relative to the gravitational direction, so that accumulating condensate can flow due to the inclination along the respective floor. This means, in particular, that the respective floor preferably does not form a right angle in the installed position with the gravitational direction. The inclination of the floors is also such that they are inclined in cross-section, in particular evenly.

It is preferred if the bottoms are each formed as a flat plate with the respective receptacles. This allows a particularly cost-effective production of the collecting tank and an efficient discharge of accumulating condensate.

Embodiments in which the bottoms form and enclose an angle α between 177 ° and 171 °, preferably 174 °, prove to be advantageous. Such an angle has proved to be particularly easy to implement and particularly effective for removing the resulting condensate. In addition, the collection box can be made to save space with such an angle. But are also conceivable smaller angle α.

Preferably, the angle α is achieved in that the respective floor deviates in installation position from a vertical course relative to the gravitational direction by at least 1.5 °, in particular from 3 ° to the gravitational direction in particular between 85.5 ° and 88.5 °, in particular 87 °, is inclined.

The inclination of the floors relative to each other is in principle designed arbitrarily. It is conceivable that the floors are inclined towards the associated cavity. In this case, the bottoms form the angle α on the side facing the cavity, or it is the angle α> 180 °, if this is measured on the side facing away from the cavity.

Also conceivable are variants in which the floors are inclined away from the associated cavity. The bottoms form the angle α on the side facing away from the cavity, or it is the angle α> 180 °, provided that it is measured on the side facing the cavity.

The cavity of the respective manifold can be flowed through for a fluid flowing through the associated heat exchanger during operation, in particular for a coolant. A flow cross-section of the respective collection tube is preferably bounded or formed by the bottom and a wall adjoining the bottom.

In this case, variants prove to be advantageous in which the wall has a circular segment-shaped circular section opposite the associated floor and transition sections adjoining it on both sides, which transition into the floor. The respective transition section is shaped and formed in such a way that the circular section together with the transition sections delimits or defines an Ω-shaped flow cross-section or a flow cross-section approximating thereto. This makes it possible, in particular, to realize a fluidic supply of the collecting tube, which preferably takes place at one end of the collecting tube or the front side of the collecting tube or the collecting box, particularly effectively and with reduced pressure losses.

The recordings of the respective collection tube, also referred to below as box receptacles, can in principle be designed as desired. Preferably, the box receptacles of the respective collecting tube are arranged spaced apart in the longitudinal direction of the collecting tube. It is also preferred if the box receptacles are formed by passage of the soil. This allows in particular a fluid-tight and / or stable connection of the bottom and thus of the collecting tube or the collecting box with the heat exchanger tubes accommodated therein, in particular flat tubes.

It is advantageous if the passages of at least one of the floors are directed outwards and thus away from the associated cavity. That is, the passages do not penetrate into the cavity, but protrude outward from the bottom with respect to the cavity. This leads, in particular, to an enlargement of the flow-through portion within the respective manifold so that the respective manifold and thus the collector can be made smaller overall and thus less bulky. Likewise, the increased flow-through proportion leads to an increased efficiency of the associated heat exchanger.

It is preferred if the passages produced by tearing the soil, so in particular are torn to the outside. This allows a cost-effective production of the collecting tank and a optimized use of the available volume.

Preferred embodiments are those in which the passages project from the associated floor by less than 3 mm. The passages thus have a height of less than 3 mm. Particularly preferred are heights of less than 2.5 mm and 2.2 mm, most preferably a height of 2 mm.

Embodiments prove to be advantageous in which at least one of the passages, preferably the respective pass, has an end face facing away from the associated bottom, which runs in a curved manner. The curved course applies in particular in the transverse direction or transversely to the distance direction of the passages. Particularly preferably, the end faces are convexly curved relative to the associated bottom, such that a central region of the end face is farther away from the ground than transversely extending outer regions of the passage. Such a curved course of the passage or the end face makes it possible, in particular, to contact corrugated ribs arranged in the heat exchanger between the heat exchanger tubes at the further areas of the end faces projecting from the bottom with the heat exchanger tubes and the end faces and thus an enlarged contact area between the corrugated ribs and the heat exchanger tubes To make available so that the heat exchanger has a total of increased efficiency and / or space-saving can be produced.

For mechanical reinforcement of the collecting tank, in particular of the respective collecting pipe, the collecting box can be provided with beads, in particular stiffening beads. Preferably, the respective manifold is provided with a plurality of such beads, which are advantageously opposite to the ground, in particular in the wall, preferably in the circular section, are introduced. In addition, the beads of the respective manifold are advantageously spaced in the direction of spacing of the associated box receptacles and thus in particular in the longitudinal direction. This enables a particularly effective and simple mechanical stabilization of the collecting tank.

It is particularly advantageous if both headers have such beads, wherein in each case a bead of the first header and a bead of the second header touch or are in mechanical contact in a region between the two headers. In particular, the contacting beads can run parallel. Such a design of the collecting tank has proven to be particularly stable. This mechanical stability is improved if the area between the two header pipes is a center seam of the header tank, at which the walls of the header pipes, in particular a transition section of one of the header pipes, is in contact with the transition section of the other header pipe. As a result, a mechanical stabilization over an increased height of the collecting tank is achieved.

The headers of the header tank can in principle be made separately and then attached to each other, in particular, connected to each other.

Preferred embodiments provide for the one-piece production of both manifolds, in particular of the entire header tank. The headers are therefore made monolithic or from the same base material. In particular, the headers can be made of a sheet metal part, in particular by forming the sheet metal part. The headers are thus in particular made of the same sheet metal part, which is processed for producing the headers, in particular deformed and provided with the Sammelkastenaufnahmen is. Thus, the collection box, in particular the inclined course of the floors can be realized inexpensively and easily. In addition, thus, the box receptacles can be easily introduced into the respective soil. The sheet metal part may 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 is understood that in addition to the collection box and a heat exchanger with such a collecting box belongs to the scope of this invention. The heat exchanger has at least one such collecting box, which receives heat transfer tubes of the heat exchanger, in particular flat tubes, via the box receptacles of the headers. The header pipes of the at least one header tank together with the heat exchanger tubes form a first duct system of the heat exchanger, through which a first fluid, in particular refrigerant, flows. The heat exchanger tubes are spaced from each other and thus form a second channel system for a second fluid, in particular for a gas, eg. For air, wherein the second fluid when flowing through the heat exchanger via the second channel system via the heat exchanger tubes, possibly arranged between the heat exchanger tubes Corrugated ribs, with the first fluid flowing through the heat exchanger tubes exchanges heat.

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

Other important features and advantages of the invention will become apparent from the dependent claims, from the drawings and from the associated figure description with reference to the drawings.

It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

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

• 1 eine stark vereinfachte, schaltplanartige Darstellung einer Klimaanlage in einem Fahrzeug,
• 2 eine isometrische Teilansicht eines Wärmeübertragers der Klimaanlage mit einem Sammelkasten und einer Anschlussanordnung,
• 3 einen Querschnitt durch den Wärmeübertrager in Teilansicht,
• 4 einen Querschnitt des Sammelkastens,
• 5 eine isometrische Teilansicht des Sammelkastens,
• 6 eine isometrische Teilansicht des Wärmeübertragers mit der Anschlussanordnung in Explosionsdarstellung,
• 7 eine Seitenansicht des Wärmeübertragers,
• 8 einen Querschnitt durch die Anschlussanordnung bei einem weiteren Ausführungsbeispiel.

Show, in each case schematically,

• 1 a highly simplified schematic diagram of an air conditioning system in a vehicle,
• 2 4 is a partial isometric view of a heat exchanger of the air conditioning system with a collecting box and a connection arrangement,
• 3 a cross section through the heat exchanger in partial view,
• 4 a cross section of the collecting tank,
• 5 an isometric partial view of the collecting tank,
• 6 an isometric partial view of the heat exchanger with the connection arrangement in exploded view,
• 7 a side view of the heat exchanger,
• 8th a cross section through the connection arrangement in a further embodiment.

In 1 is an air conditioner 1 Simplified in a vehicle 2 can be used to, for example, a vehicle interior 3 of the vehicle 2 to air-condition. The air conditioner 1 has a cycle 4 in which a refrigerant from a conveyor 5 is driven and circulated. The refrigerant flows through a capacitor in succession 6 , an expander 7 as well as an evaporator 8th , where the capacitor 6 and the evaporator 8th each as a heat exchanger 9 act. The respective heat exchanger 9 is passed through by the refrigerant and another fluid, such that it comes between the refrigerant and the other fluid to heat exchange. At the evaporator 8th is the other fluid air 10 which the evaporator 8th is flowed through and thereby cooled, with the cooled air 10 the vehicle interior 3 is supplied.

2 shows an isometric partial view of one of the heat exchanger 9 , in particular the evaporator 8th , The heat exchanger 9 has a plurality of heat exchanger tubes 11 on which flows through the refrigerant and are spaced from each other. In the example shown are the heat exchanger tubes 11 as flat tubes 12 educated. Due to the spaced arrangement of the heat exchanger tubes 11 can air 10 between the heat exchanger tubes 11 flow and this flow around and thereby heat with the through the heat exchanger tubes 11 exchange flowing refrigerant and thus cooled. An improved heat transfer between the air 10 and the refrigerant can be achieved that between adjacent heat exchanger tubes 11 flow-through corrugated ribs 13 be provided. The fluidic supply of the heat exchanger tubes 11 with the refrigerant takes place with the help of at least one header tank 14 , where in 2 a collection box 14 at an upper end of the heat exchanger 8th you can see. The heat exchanger 9 preferably has at an opposite, not shown lower end another, not shown second collection box 14 on.

As if from a synopsis of 2 and 3 in which the corrugated rib 13 indicated by a dashed line curve and is shown transparent, shows, the collection box 14 two manifolds 15 . 16 namely, a first manifold 15 and a second manifold 16 , on. The respective manifold 15 . 16 points to the heat exchanger tubes 11 facing side a flattened tube sheet 17 or short ground 17 on. On the respective floor 17 closes a wall 18 of the associated manifold 15 . 16 on that with the ground 17 a permeable cavity 19 of the manifold 15 . 16 limited. The headers 15 . 16 each extend in a longitudinal direction 20 and thus substantially parallel and are in a direction transverse to the longitudinal direction 20 extending transverse direction 21 adjacent to each other, in particular immediately adjacent to each other, arranged. The walls 18 the headers 14 . 15 meet in the transverse direction 21 in a middle area 22 of the collecting tank 14 and thus form one in the transverse direction 21 centrally arranged, in the longitudinal direction 20 extending middle seam 23 of the collecting tank 14 , The respective manifold 15 . 16 points in the ground 17 Recordings 24 for the heat exchanger tubes 11 on, which below as box recordings 24 be designated. The box picks 24 of the respective manifold 14 . 15 are in the longitudinal direction 20 spaced and each take a heat exchanger tube 11 on. In this case, in the example shown, the box recordings 24 both headers 14 . 15 longitudinal 20 arranged equidistant, with the respective box receptacle 24 of the first manifold 15 in the transverse direction 21 adjacent a box pickup 24 of the second manifold 16 is arranged such that in the transverse direction 21 in each case two mutually aligned and spaced heat exchanger tubes 11 are arranged and this arrangement in the longitudinal direction 20 repeated.

In the example shown, the first manifold 15 via a connection arrangement 25 supplied to the refrigerant, which in the first manifold 15 and in the heat exchanger tubes 11 which flows into the box receptacles 24 of the first manifold 15 arranged and thus fluidly connected thereto. The refrigerant flows through these heat exchanger tubes 11 and is, in particular in the opposite, lower, or second collection box, not shown 14 , in the heat exchanger tubes 11 redirected, which in the box shots 24 of the second manifold 16 are added, so that the refrigerant then through these heat exchanger tubes 11 in the second manifold 16 flows, the refrigerant via the connection arrangement 25 from the second manifold 16 is sucked. The refrigerant is thus using the conveyor 5 in the first manifold 15 pumped / sprayed and from the second manifold 16 sucked / discharged.

Through the heat exchange between the through the heat exchanger tubes 11 and the headers 15 . 16 flowing refrigerant and the air 10 gets the air 10 cooled. By cooling the air 10 condensate accumulates, which in particular on the ground 17 of the respective manifold 15 . 16 can settle. As in particular the 3 and 4 it can be seen, where 4 only the collection box 14 in cross-section shows, the floors are running 17 the headers 15 . 16 in the manner of a saddle roof or an inverted gutter inclined to each other, so that they have a predetermined angle 26 , also referred to below as angle α, of unequal 180 °, in particular between 171 ° and 177 °, advantageously of about 174 ° form. Here is the respective floor 17 with respect to the transverse direction 21 inclined, said angle 26 through the heat exchanger tubes 11 facing outer surface 27 the floors 17 is formed, with the exception of the box shots 24 essentially flat and plate-shaped, so that the floors 17 each as a flat plate 28 are formed. In a mounting position 29 or position of use 29 which, for example, in the 3 and 4 is shown, are the floors 17 while also relative to the gravitational direction G inclined, such that they are in cross-section with the direction of gravity G form an angle of less than 90 °. In other words, in the installation position 29 are the outer surfaces 27 both floors 17 relative to the gravitational direction G inclined so on the floors 17 accumulating condensate along the outer surface 27 flows simplified and thus can be removed simplified. When in the 3 and 4 example shown are both floors 17 towards the associated cavity 19 inclined, leaving the floors 17 or the outer surfaces 27 on the cavities 19 facing or from the heat exchanger tubes 11 opposite side an angle 26 less than 180 °, in particular 174 °. The resulting condensate can thus reach the middle area 22 stream. This accumulating condensate can then in the middle range 22 or between the in the transverse direction 21 adjacent heat exchanger tubes 11 in the direction of the opposite, not shown lower header tank 14 stream and there from the middle area 22 this collecting tank in the transverse direction 21 flow to the outside, where the condensate can flow away and / or is discharged.

Especially in the 3 to 5 it can be seen that the box recordings 24 of the respective soil 17 or manifold 14 . 15 each through a passage 30 formed by tearing the associated soil 17 can be made. It can be seen that the passages 30 each from the associated cavity 19 are directed away and thus into the cavity 19 do not penetrate. This makes it possible in particular, the heat exchanger tubes 11 with a lower penetration depth into the headers 14 . 15 insert, so that the flow-through or usable volume of the cavity 19 is enlarged. In particular the 3 and 4 It can also be seen that the passages 30 from the associated cavity 19 groundbreaking faces 31 have, wherein the end faces 31 in the transverse direction 21 curved, in particular curved like a circle, extend. This is how it comes 3 can be seen, between the front side 31 and the adjacent corrugated rib 13 to a reduced contact area in the most projecting area of the front side 31 , Consequently, this volume can also be improved and made more efficient with the corrugated fins 13 be used.

As in particular from the 3 to 5 shows, is the collection box 14 in the example shown in one piece from a sheet metal part 32 , For example by reshaping of the sheet metal part 32 , manufactured. It can also be seen that the wall 18 of the respective manifold 15 . 16 one to the associated soil 17 opposite, circular segment-shaped circular section 33 as well as in the transverse direction 21 on both sides of the circle section 33 subsequent transitional sections 34 which is in the ground 17 pass over, with the circle section 33 and the Transition sections 34 a flow cross-section 35 of the associated manifold 15 . 16 or the associated cavity 19 define. Here is the flow cross section 35 preferably in the region of the circular section 33 and in the subsequent area of the associated transition sections 34 Ω-shaped or approximated to an Ω-shape. In the middle area 22 each lie a transition section 34 both headers 15 . 16 together and thus form the middle seam 23 ,

The respective manifold 15 . 16 points to the of the heat exchanger tubes 11 opposite side, especially in the area of the wall 18 , several beads 36 on, the below as stiffening beads 36 be designated. The stiffening beads 36 are each as outward impressions 37 educated. The stiffening beads 36 run in the transverse direction 21 and are longitudinal 20 spaced apart. In each case, a stiffening bead meet 36 of the first manifold 15 and a stiffening bead 36 of the second manifold 16 in the middle area 22 of the collecting tank 14 or in the middle seam area 23 in which the transition sections 34 the headers 15 . 16 abut each other. Thus, an improved mechanical stability of the entire header, even outside the beads 36 , Especially in a transverse to the longitudinal direction 20 and transverse to the transverse direction 21 extending height direction 47 , reached.

Corresponding 2 as well as the 6 and 7 has the connection arrangement 25 a base plate 38 as well as an outer shell 39 on. The base plate 38 has a first plate opening 40 and a second plate opening 41 on. The base plate 38 lies on a front side 46 one from the heat exchanger tubes 11 and the at least one collection box 14 composite tube bundle 42 on. Here is the first plate opening 40 fluidic with a front or longitudinal end first manifold opening 43 of the first manifold 15 fluidly connected, whereas the second plate opening 41 with a front-side or longitudinal end second header opening 44 of the second manifold 16 is fluidically connected. The respective plate opening 40 . 41 is as a breakthrough 45 in the base plate 38 educated. The base plate 38 extends in the transverse direction 21 as well as in height direction 47 and lies on the front side 46 of the collecting tank 14 as well as on the adjacent, outer corrugated rib 13 on. Am from the gathering box 14 removed end of the base plate 38 stand by the corrugated rib 13 in the transverse direction 21 protruding a first Plattenausformung 48 and in the height direction 47 adjacent to and to the collection box 14 offset a second Plattenausformung 49 from. The outer shell 39 follows the course of the base plate 38 and has one of the first plate formation 48 opposite first shell formation 50 and one of the second plate formation 49 opposite second shell formation 51 on. The first plate formation 48 forms together with the first shell formation 50 a first tube recording 42 for a first supply pipe body 53 , whereas the second plate molding 49 with the second shell formation 51 one from the first tube recording 52 separate, in height direction 47 spaced second pipe receiving 54 for a second supply pipe body 55 the arrangement 25 forms. The respective supply pipe body 53 . 55 has a tubular adapter element 56 on which in the associated pipe receiving 52 . 54 is received and positively enclosed, such that the supply pipe body 53 . 55 mechanically stable in the associated pipe holder 52 . 54 is attached. Although the respective supply pipe body 53 . 55 in 6 from the associated adapter element 56 is shown spaced apart, the respective supply pipe body 53 . 55 and the associated adapter element 56 be made in one piece, in particular monolithic, so that no separate connection between the adapter element 56 and the associated supply body 53 . 55 necessary is.

The first supply pipe body 53 is about one at the first shot 52 subsequent first supply channel 57 fluidic with the first plate opening 40 and thus with the first manifold 15 connected. In contrast, the second supply pipe body 55 over the second pipe intake 54 and one from the first supply channel 57 separate second supply channel 58 fluidic with the second plate opening 41 and thus with the second manifold 16 connected. About the first supply pipe body 53 So is refrigerant in the first manifold 15 introduced, whereas on the second supply pipe body 55 Refrigerant from the second manifold 16 is sucked. The respective supply channel 57 . 58 closes to the associated pipe holder 52 . 54 and is through the base plate 38 and a channel section formed by a molding 59 the outer shell 39 educated.

In particular 6 can be taken, is the first plate opening 40 smaller, in particular, has a smaller cross section than the second plate opening 41 , It can also be seen that the second plate opening 41 one to the circle section 33 of the second manifold 16 in the region of the second manifold opening 44 adapted shape or adapted cross-section on. This means in particular that the cross section of the second plate opening 41 the cross section of the second header opening 44 is formed complementary. As a result, the refrigerant can be particularly effective and low pressure loss from the second manifold 16 suck.

8th shows a further embodiment of the base plate 38 in which the second plate opening 41 has a cross section which is the flow cross section 35 of the second manifold 16 in the 3 and 4 corresponds, preferably in the example shown, the flow cross-section 35 the second header opening 44 equivalent. In 8th It can also be seen that the plate openings 40 . 41 each in a way to the collection box 14 directed depression 60 are arranged, wherein the depressions 60 each slightly into the associated header opening 43 . 44 penetrate and one of the associated manifold opening 43 . 44 have filling shape. Here is the second plate opening 41 in the entire associated depression 60 formed, whereas the first plate opening 40 has a round shape and in the associated recess 60 is arranged approximately in the middle. It can also be seen that the depressions 60 the inclined course of the soil 17 consequences.

When in 8th the embodiment shown, the first Plattenausformung different 48 from the second plate formation 49 so that also the first tube recording 52 from the second tube intake 54 different. In this embodiment, therefore, the adapter element 56 of the first supply pipe body 53 and the adapter element 56 the second supply pipe body 55 designed differently. In contrast, in the 2 . 6 and 7 the respective pipe intake 52 . 54 the same design, so that the adapter elements 56 both supply pipe body 53 . 55 are the same. To recognize in 6 is further that the first supply pipe body 53 outside the associated adapter element 56 is smaller than the second supply pipe body 55 and having a correspondingly smaller flow cross-section.

Preferably, the base plate 38 , the outer shell 39 as well as the supply pipe body 53 . 55 , in particular the adapter elements 56 , joined together by a common method, wherein it is preferred if they are soldered together. For this, the outer shell 39 and the base plate 38 be soldered on at least one side. In this case, the respective adapter element 56 in the associated Plattenausformung 48 . 49 inserted and then the outer shell 39 with the base plate 38 be brought into contact and fixed to those in the 2 and 7 shown form of the connection arrangement 25 to reach, the arrangement 25 then joined cohesively, in particular soldered, is. It is also conceivable, the arrangement 25 together with other components of the heat exchanger 9 cohesive paste, in particular to be soldered. As a result, in addition to the production of the connection arrangement 25 at the same time also a connection of the connection arrangement 25 to the remaining heat exchanger 9 reached. In this case is on the of the outer shell 39 opposite side of the base plate 38 preferably as low as possible solder, in particular a Lotplattierung with a Lotanteil of less than 5%, attached to a burning or damage to the adjacent corrugated fin 13 to prevent or at least reduce.

As in particular the 2 . 6 and 7 it can be seen, has the outer shell 39 in the area of the plate openings 40 . 41 an edge protruding, the shape of the collecting tank 41 and the base plate 38 following grip section 61 on top of the base plate 38 surmounted on the edge. The grip section 61 surrounds the front 46 of the collecting tank 14 at the edge and is arranged over several, distributed connecting elements 62 , which with on the walls 18 the headers 15 . 16 provided counter-connecting elements 63 interact positively with the collecting box 14 mechanically connected. As a result, the manifold openings 43 . 44 and the base plate 38 at the edge of the handle section 61 embraced because of the handle section 61 on the wall 18 of the respective manifold 15 . 16 on the outside. This stabilizes the connection between the collection box 14 and the connection arrangement 25 and leads to lower pressure losses in the refrigerant or a better sealing of the flow path of the refrigerant. The connecting elements 62 and counter-connecting elements 63 can also be used to the arrangement 25 before a cohesive joining with the rest of the heat exchanger 9 relative to fix.

In the examples shown, both tube recordings extend 52 . 54 along the base plate 38 so that they are related to the plate opening 40 . 41 are oriented vertically or so that the tube recordings 52 . 54 each in a direction perpendicular to the associated plate opening 40 . 41 can be flowed through the plane running. The respective supply channel 57 . 58 runs in this case, in particular by 90 °, curved.

The collection box 14 points as in 3 shown one in height direction 47 running box height 65 which may 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 the passages 30 , below draft height 66 may be less than 3 mm, preferably less than 2.5 mm and 2.2 mm, most preferably 2 mm.

One in height direction 47 running height 76 one from the heat exchanger tubes 11 and corrugated ribs 13 composing network 75 of the heat exchanger 9 , also network height 76 called (see also 7 ), is preferably less than 45 mm, in particular less than 42 mm. The net height 76 is advantageously between 39 mm and 40 mm, in particular between 39.4 mm and 40 mm.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• CA 2123368 A1 [0003]
• US 7971636 B2 [0004]
• US 7231966 B2 [0004]
• DE 112005000423 T5 [0005]

Claims (13)

Collecting box (14) of a heat exchanger (9), in particular of an evaporator (8) of an air conditioning system (1), with a first collecting pipe (15) and a second collecting pipe (16) adjacent to the first collecting pipe (15) for receiving heat exchanger pipes (11) the heat exchanger (9), wherein the manifolds (15, 16) each have a flow-through cavity (19), - wherein the respective manifold (15, 16) has a flattened bottom (17), - spaced in the respective bottom (17) Box receptacles (24) for receiving the heat exchanger tubes (11) are formed, characterized in that the bottoms (17) α at a predetermined angle (26) of not equal to 180 ° .. Collection box after Claim 1 , characterized in that the bottoms (17) form a predetermined angle (26) α of between 177 ° and 171 °, in particular of 174 °. Collecting box according to one of Claims 1 or 2 , characterized in that the bottoms (17) are each formed as a flat plate (28) with box receivers (24). Collecting box according to one of Claims 1 to 3 , characterized in that the bottoms (17) are inclined towards the associated cavity (19). Collecting box according to one of Claims 1 , or 3, characterized in that the bottoms (17) by their course form a predetermined angle (26) α greater than 180 ° and are inclined away from the associated cavity (19). Collecting box according to one of Claims 1 to 5 , characterized in that at least one of the manifolds (15, 16) has a bottom (17) adjoining wall (18) which forms a flow cross-section (35) of the collecting tube (15, 16) with the bottom (17). Collection box after Claim 6 , characterized in that the wall (18) has a bottom (17) opposite circular segment-shaped circular section (33) and on both sides subsequent transition sections (34), which pass into the bottom (17). Collecting box according to one of Claims 1 to 7 , characterized in that the box receivers (24) of at least one of the headers (15, 16) are formed by passages (30) directed away from the associated cavity (19). Collection box after Claim 8 , characterized in that at least one of the passages (30) protrudes by less than 3 mm from the associated bottom (17). Collection box after Claim 8 or 9 , characterized in that at least one of the passages (30) has a curved passage end face (31). Collecting box according to one of Claims 1 to 10 , characterized in that - the collecting tubes (15, 16) each comprise beads (36) on the side opposite the associated base (17), - that in each case a bead (36) of the first collecting tube (15) and a bead (36) of the second manifold (16) in a region (22) between the two manifolds (15, 16) are in mechanical contact. Collecting box according to one of Claims 1 to 11 , characterized in that the collecting tubes (15, 16) are made together from a sheet metal part (32). Heat exchanger (9), in particular evaporator (8) of an air conditioner (1), with at least one collecting box (14) according to one of Claims 1 to 12 and with a plurality of heat exchanger tubes (11) which are received in the box receptacles (24) of the floors (17).

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