US20190120521A1 - Collecting tank of a heat exchanger - Google Patents
Collecting tank of a heat exchanger Download PDFInfo
- Publication number
- US20190120521A1 US20190120521A1 US16/166,059 US201816166059A US2019120521A1 US 20190120521 A1 US20190120521 A1 US 20190120521A1 US 201816166059 A US201816166059 A US 201816166059A US 2019120521 A1 US2019120521 A1 US 2019120521A1
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- United States
- Prior art keywords
- collecting pipe
- collecting
- heat exchanger
- respective bottom
- pipe
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/22—Means for preventing condensation or evacuating condensate
- F24F13/222—Means for preventing condensation or evacuating condensate for evacuating condensate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0085—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F2009/0285—Other particular headers or end plates
- F28F2009/0292—Other particular headers or end plates with fins
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0246—Arrangements for connecting header boxes with flow lines
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
- 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,
-
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. - An
air conditioning system 1, which can be used in avehicle 2, so as to climatize for example avehicle interior 3 of thevehicle 2, is illustrated inFIG. 1 in a highly simplified manner. Theair conditioning system 1 has acircuit 4, in which a coolant is driven by a conveyingdevice 5 and circulates. The coolant thereby flows through a capacitor 6, anexpander 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 isair 10, which flows through the evaporator 8 and is cooled thereby, wherein the cooledair 10 is supplied to thevehicle 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 theair 10 and the coolant can be attained in thatcorrugated 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 onecollecting tank 14, wherein a collectingtank 14 can be seen at an upper end of the heat exchanger 8 inFIG. 2 . At an opposite lower end, which is not shown, the heat exchanger 9 preferably has a furthersecond collecting tank 14, which is not shown. - As follows from a combined view of
FIG. 2 andFIG. 3 , in which thecorrugated fin 13 is suggested by a dashed line course and is illustrated in a transparent manner, the collectingtank 14 has two collectingpipes first collecting pipe 15, and asecond collecting pipe 16. On the side facing the heat exchanger pipes 11, therespective collecting pipe wall 18 of the corresponding collectingpipe hollow space 19 of the collectingpipe pipes longitudinal direction 20 and thus essentially in parallel and are arranged adjacent to one another in atransverse direction 21, which runs transversely to thelongitudinal direction 20, in particular so as to adjoin one another directly. Thewalls 18 of the collectingpipes central area 22 of the collectingtank 14 in thetransverse direction 21, and thus form acentral seam 23 of the collectingtank 14, which is arranged centrally in thetransverse direction 21 and which extends in thelongitudinal direction 20. In the bottom 17, therespective collecting pipe respective collecting pipe longitudinal direction 20 and in each case accommodate a heat exchanger pipe 11. In the shown example, the tank accommodations 24 of both collectingpipes longitudinal direction 20, wherein a tank accommodation 24 of thesecond collecting pipe 16 is arranged adjacent to the respective tank accommodation 24 of thefirst collecting pipe 15 in thetransverse 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 thetransverse direction 21 and that this arrangement repeats itself in thelongitudinal 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 thefirst collecting pipe 15 and are thus fluidically connected thereto, is supplied to thefirst collecting pipe 15 via aconnector assembly 25. The coolant flows through these heat exchanger pipes 11 and, in particular in the non-illustrated, opposite, lower orsecond collecting tank 14, respectively, is deflected into the heat exchanger pipes 11, which are accommodated in the tank accommodations 24 of thesecond collecting pipe 16, so that the coolant subsequently flows via these heat exchanger pipes 11 into thesecond collecting pipe 16, wherein the coolant is sucked from thesecond collecting pipe 16 via theconnector assembly 25. The coolant is thus pumped/injected into thefirst collecting pipe 15 with the help of the conveyingdevice 5, and is sucked/discharged from thesecond 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 air 10, theair 10 is cooled. As a result of the cooling of theair 10, condensate accumulates, which can in particular deposit on the bottom 17 of therespective collecting pipe FIGS. 3 and 4 , whereinFIG. 4 only shows the collectingtank 14 in cross section, the bottoms 17 of the collectingpipes 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 thetransverse direction 21, wherein saidangle 26 is formed by theouter 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 aninstallation position 29 oruse position 29, which is illustrated for example inFIGS. 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, theouter surfaces 27 of both bottoms 17 are inclined relative to the gravitational direction G in theinstallation position 29, so that condensate accumulating on the bottoms 17 can flow along theouter surface 27 in a simplified manner and can thus be discharged in a simplified manner. In the case of the example shown inFIGS. 3 and 4 , both bottoms 17 are thereby inclined to the correspondinghollow space 19, so that the bottoms 17 or theouter surfaces 27, respectively, form anangle 26 of smaller than 180°, in particular of 174°, on the side facing thehollow spaces 19 or facing away from the heat exchanger pipes 11, respectively. The accumulating condensate can thus flow all the way to thecentral area 22. This accumulating condensate can then flow in thecentral area 22 or between the heat exchanger pipes 11, which are adjacent in thetransverse 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 thecentral area 22 of this collecting tank in thetransverse 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 collectingpipe hollow space 19 and thus do not penetrate into thehollow space 19. It is in particular possible hereby to insert the heat exchanger pipes 11 into the collectingpipes hollow space 19, which can be flown through or which can be used, respectively, is increased. It can furthermore be gathered in particular fromFIGS. 3 and 4 that the passages 30 havefront sides 31, which face away from the correspondinghollow space 19, wherein thefront sides 31 run in a curved manner in thetransverse direction 21, in particular curved in the shape of a circular segment. As can be gathered fromFIG. 3 , a reduced contact area results between thefront side 31 and the adjacentcorrugated fin 13 at the area of thefront side 31, which protrudes the most. This volume can thus also be improved and can be used more efficiently for providing with thecorrugated fins 13. - As follows in particular from
FIGS. 3 to 5 , the collectingtank 14 in the shown example is produced integrally from onesheet metal part 32 or by forming thesheet metal part 32, respectively. It can further be seen that thewall 18 of therespective collecting pipe circular section 33 in the shape of a circular segment located opposite the corresponding bottom 17, as well astransition sections 34, which connect to thecircular section 33 on both sides and which transition into the bottom 17, wherein thecircular section 33 and thetransition sections 34 define aflow cross section 35 of the corresponding collectingpipe hollow space 19, respectively. Theflow cross section 35 is thereby preferably Ω-shaped or is close to an Ω-shape, respectively, in the area of thecircular section 33 and in the adjacent area of thecorresponding transition sections 34. In thecentral area 22, atransition section 34 each of both collectingpipes central seam 23. - On the side facing away from the heat exchanger pipes 11, in particular in the area of the
wall 18, therespective collecting pipe transverse direction 21 and are spaced apart from one another in thelongitudinal direction 20. A reinforcing bead 36 of thefirst collecting pipe 15 and a reinforcing bead 36 of thesecond collecting pipe 16 thereby each meet in thecentral area 22 of the collectingtank 14 or in the area of thecentral seam 23, respectively, in which thetransition sections 34 of the collectingpipes height direction 47, which runs transversely to thelongitudinal direction 20 and transversely to thetransverse direction 21. - According to
FIG. 2 as well asFIGS. 6 and 7 , theconnector assembly 25 has abase plate 38 as well as anouter shell 39. Thebase plate 38 has a first plate opening 40 and a second plate opening 41. Thebase plate 38 abuts on afront side 46 of apipe bundle 42, which consists of the heat exchanger pipes 11 and the at least onecollecting 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 thefirst 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 thesecond collecting pipe 16. The respective plate opening 40, 41 is embodied as an aperture 45 in thebase plate 38. Thebase plate 38 extends in thetransverse direction 21 as well as in theheight direction 47 and abuts on thefront side 46 of the collectingtank 14 as well as on the adjacent, outercorrugated fin 13. On the end of thebase plate 38, which is spaced apart from the collectingtank 14, afirst plate molding 48 protrudes from thecorrugated fin 13 in thetransverse direction 21, and a second plate molding 49 adjacent thereto in theheight direction 48 and offset to the collectingtank 14. Theouter shell 39 follows the course of thebase plate 38 and has afirst shell molding 50 located opposite thefirst plate molding 48, and a second shell molding 51 located opposite thesecond plate molding 49. Thefirst plate molding 48, together with thefirst shell molding 50, forms afirst pipe accommodation 42 for a firstsupply pipe body 53, whereas the second plate molding 49 forms, with thesecond shell molding 51, asecond pipe accommodation 54, which is separate from thefirst pipe accommodation 52 and is spaced apart in theheight direction 47, for a secondsupply pipe body 55 of theassembly 25. The respectivesupply pipe body adapter element 56, which is accommodated in thecorresponding pipe accommodation supply pipe body corresponding pipe accommodation supply pipe body adapter element 56 inFIG. 6 , the respectivesupply pipe body adapter element 56 can be made integrally, in particular monolithically, so that no separate connection between theadapter element 56 and thecorresponding supply body - The first
supply pipe body 53 is fluidically connected to the first plate opening 40 and thus to thefirst collecting pipe 15 via afirst supply duct 57 connected to thefirst accommodation 52. In contrast, the secondsupply pipe body 55 is fluidically connected to the second plate opening 41 and thus to thesecond collecting pipe 16 via thesecond pipe accommodation 54 and asecond supply duct 58, which is separated from thefirst supply duct 57. Coolant is thus introduced into the first accumulatingpipe 15 via the firstsupply pipe body 53, whereas coolant is sucked from thesecond collecting pipe 16 via the secondsupply pipe body 55. Therespective supply duct corresponding pipe accommodation base plate 38 as well as a duct section 59 of theouter 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 thecircular section 33 of thesecond collecting pipe 16 in the area of the secondcollecting 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 secondcollecting pipe opening 44. The coolant can thereby be sucked from thesecond collecting pipe 16 particularly effectively and with little loss of pressure. -
FIG. 8 shows a further exemplary embodiment of thebase plate 38, in the case of which the second plate opening 41 has a cross section, which corresponds to theflow cross section 35 of thesecond collecting pipe 16 inFIGS. 3 and 4 , which, in the case of the shown example, preferably also corresponds to theflow cross section 35 of the secondcollecting pipe opening 44. It can further be seen inFIG. 8 that the plate openings 40, 41 are each arranged in adepression 60, which is directed towards the collectingtank 14, wherein thedepressions 60 each slightly penetrate into the correspondingcollecting pipe opening opening depression 60, whereas the first plate opening 40 has a round form and is arranged approximately in the center in the correspondingdepression 60. It can also be seen that thedepressions 60 follow the inclined course of the bottoms 17. - In the case of the exemplary embodiment shown in
FIG. 8 , thefirst plate molding 48 differs from the second plate molding 49, so that thefirst pipe accommodation 52 also differs from thesecond pipe accommodation 54. Theadapter element 56 of the firstsupply pipe body 53 and theadapter element 56 of the secondsupply pipe body 55 are thus embodied differently in this exemplary embodiment. In contrast, therespective pipe accommodation FIGS. 2, 6 and 7 , so that theadapter elements 56 of bothsupply pipe bodies FIG. 6 that the firstsupply pipe body 53 outside of the correspondingadapter element 56 is smaller than the secondsupply pipe body 55 and has a correspondingly smaller flow cross section. - The
base plate 38, theouter shell 39 as well as thesupply pipe bodies 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, theouter shell 39 and thebase plate 38 can be solder-plated at least on one side. Therespective adapter element 56 can thereby be placed in thecorresponding plate molding outer shell 39 can subsequently be brought into contact with thebase plate 38, and can be fixed thereto so as to attain the form of theconnector assembly 25 shown inFIGS. 2 and 7 , wherein theassembly 25 is joined integrally subsequently, in particular soldered. It is also conceivable to join theassembly 25 integrally, in particular to weld it, together with further parts of the heat exchanger 9. In addition to the production of theconnector assembly 25, a connection of theconnector 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 thebase plate 38 facing away from theouter 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 adjacentcorrugated fin 13. - As can in particular be gathered from
FIGS. 2, 6 and 7 , theouter shell 39 has, in the area of the plate openings 40, 41, ahandle section 61, which protrudes on the edge side, follows the form of the collecting tank 41 and of thebase plate 38, and which protrudes beyond thebase plate 38 on the edge side. Thehandle section 61 encompasses thefront side 46 of the collectingtank 14 on the edge side and is mechanically connected to the collectingtank 14 via a plurality of connectingelements 62, which are arranged so as to be distributed and which interact in a positive manner withmating connecting elements 63 provided on thewalls 18 of the collectingpipes pipe openings base plate 38 are thereby encompassed by thehandle section 61 on the edge side, because thehandle section 61 abuts on the outer side of thewall 18 of therespective collecting pipe tank 14 and theconnector 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 connectingelements 62 andmating connecting elements 63 can further be used to fix theassembly 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 base plate 38, so that they are oriented perpendicularly to the corresponding plate opening 40, 41 or so that thepipe accommodations respective supply duct - As shown in
FIG. 3 , the collectingtank 14 has atank height 65, which runs in theheight 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 correspondingheight 66 of the passages 30, hereinafter referred to aspassage 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 theheight direction 47, of a net 75, which consists of the heat exchanger pipes 11 andcorrugated fins 13, of the heat exchanger 9, also referred to as net height 76 (see alsoFIG. 7 ) is preferably less than 45 mm, in particular less than 42 mm. Advantageously, thenet height 76 is between 39 mm and 40 mm, in particular between 39.4 mm and 40 mm.
Claims (20)
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.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102017218810.3A DE102017218810A1 (en) | 2017-10-20 | 2017-10-20 | Collection box of a heat exchanger |
DE102017218810.3 | 2017-10-20 |
Publications (1)
Publication Number | Publication Date |
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US20190120521A1 true US20190120521A1 (en) | 2019-04-25 |
Family
ID=65996073
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/166,059 Abandoned US20190120521A1 (en) | 2017-10-20 | 2018-10-19 | Collecting tank of a heat exchanger |
Country Status (3)
Country | Link |
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US (1) | US20190120521A1 (en) |
CN (1) | CN109696076A (en) |
DE (1) | DE102017218810A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP4317895A1 (en) * | 2022-08-02 | 2024-02-07 | Valeo Systemes Thermiques | A tank assembly |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112240714B (en) * | 2019-07-19 | 2022-04-26 | 广州汽车集团股份有限公司 | Evaporator |
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WO2001067010A1 (en) * | 2000-03-10 | 2001-09-13 | Zexel Valeo Climate Control Corporation | Heat exchanger for cooling |
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US20120199332A1 (en) * | 2011-02-04 | 2012-08-09 | Ken Cornell | Heat exchanger header plate |
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JPH01114697A (en) * | 1987-10-29 | 1989-05-08 | Nippon Denso Co Ltd | Heat exchanger |
JP3287100B2 (en) | 1993-05-19 | 2002-05-27 | 株式会社デンソー | Cooling unit and drain case for air conditioner |
JP4026277B2 (en) * | 1999-05-25 | 2007-12-26 | 株式会社デンソー | Heat exchanger |
DE60010377T2 (en) * | 1999-07-02 | 2004-09-16 | Denso Corp., Kariya | Refrigerant evaporator with refrigerant distribution |
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JP4193741B2 (en) | 2004-03-30 | 2008-12-10 | 株式会社デンソー | Refrigerant evaporator |
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KR101396437B1 (en) * | 2008-01-22 | 2014-05-19 | 한라비스테온공조 주식회사 | Evaporator And Air conditioner for an Automobile equipped with same |
DE102011086605A1 (en) * | 2011-11-17 | 2013-05-23 | Behr Gmbh & Co. Kg | Method for closing a collecting box |
FR3015016B1 (en) * | 2013-12-13 | 2019-05-17 | Valeo Systemes Thermiques | COLLECTOR BOX AND THERMAL EXCHANGER CORRESPONDING |
CN203772102U (en) * | 2014-04-09 | 2014-08-13 | 泰安鼎鑫冷却器有限公司 | High-strength oil chamber of oil radiator |
-
2017
- 2017-10-20 DE DE102017218810.3A patent/DE102017218810A1/en active Pending
-
2018
- 2018-09-29 CN CN201811145810.0A patent/CN109696076A/en active Pending
- 2018-10-19 US US16/166,059 patent/US20190120521A1/en not_active Abandoned
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JPH0579791A (en) * | 1991-09-17 | 1993-03-30 | Calsonic Corp | Heat exchanger for recovering heat from exhaust |
WO2001067010A1 (en) * | 2000-03-10 | 2001-09-13 | Zexel Valeo Climate Control Corporation | Heat exchanger for cooling |
US20020066553A1 (en) * | 2000-11-07 | 2002-06-06 | Ewald Fischer | Heat exchanger and method for producing a heat exchanger |
JP2002147992A (en) * | 2000-11-09 | 2002-05-22 | Zexel Valeo Climate Control Corp | Heat exchanger |
US20120199332A1 (en) * | 2011-02-04 | 2012-08-09 | Ken Cornell | Heat exchanger header plate |
US20150292816A1 (en) * | 2014-04-15 | 2015-10-15 | Trane International Inc. | Coil support pad having condensate drainage functionality |
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EP4317895A1 (en) * | 2022-08-02 | 2024-02-07 | Valeo Systemes Thermiques | A tank assembly |
WO2024028068A1 (en) * | 2022-08-02 | 2024-02-08 | Valeo Systemes Thermiques | A tank assembly |
Also Published As
Publication number | Publication date |
---|---|
CN109696076A (en) | 2019-04-30 |
DE102017218810A1 (en) | 2019-04-25 |
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