Patent Application
20190120521
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.
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.
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.
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.
In each case schematically,
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
As follows from a combined view of
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
It can in particular be seen in
As follows in particular from
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
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
In the case of the exemplary embodiment shown in
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
As can in particular be gathered from
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
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
| Number | Date | Country | Kind |
|---|---|---|---|
| 102017218810.3 | Oct 2017 | DE | national |
