EP3872435B1 - A heat exchanger - Google Patents
A heat exchanger Download PDFInfo
- Publication number
- EP3872435B1 EP3872435B1 EP20461516.5A EP20461516A EP3872435B1 EP 3872435 B1 EP3872435 B1 EP 3872435B1 EP 20461516 A EP20461516 A EP 20461516A EP 3872435 B1 EP3872435 B1 EP 3872435B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- stack
- manifold
- tubes
- heat exchanger
- tube portion
- 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.)
- Active
Links
- 239000012530 fluid Substances 0.000 claims description 56
- 238000004891 communication Methods 0.000 claims description 8
- 239000003507 refrigerant Substances 0.000 description 9
- 239000006185 dispersion Substances 0.000 description 6
- 239000000463 material Substances 0.000 description 6
- 239000002826 coolant Substances 0.000 description 5
- 238000009826 distribution Methods 0.000 description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 5
- 238000007789 sealing Methods 0.000 description 4
- 238000005219 brazing Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 229910001092 metal group alloy Inorganic materials 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000004806 packaging method and process Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000009827 uniform distribution Methods 0.000 description 1
Images
Classifications
-
- 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
- F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
-
- 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
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
- F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
-
- 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
- F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
- F28F9/0221—Header boxes or end plates formed by stacked elements
-
- 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
- F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/06—Derivation channels, e.g. bypass
Definitions
- the invention relates to a heat exchanger, in particular the heat exchanger for a motor vehicle.
- a heat exchanger according to the preamble of claim 1 is known from document US 2019/10313 A1 .
- Heat exchangers commonly used in the industry may comprise means for redirecting the fluid inside the core in order to increase the distance traveled by the fluid and consequently to increase the overall performance of the heat exchanger.
- the fluid is transmitted between the neighboring sections to avoid complex solutions.
- creating several passes inside the core of the heat exchanger is problematic, because of increased pressure drop and limited packaging. Excessive pressure drop may also impact the performance in an indirect manner, due to increased power consumption by compressor.
- so-called “dead zones” can occur, wherein the flow of the heat exchange fluid is limited.
- One of the known solutions to promote the optimized and homogenous distribution of the fluid circulating through the heat exchanger is dividing heat exchanger into sections by blocking or limiting the flow of the fluid inside the manifolds.
- currently known solutions do not suggest providing homogeneity of the fluid distribution, what usually has a negative impact on efficiency of the whole heat exchanger.
- the fluid is not delivered to the tubes evenly, what may suggest the homogeneity problems particularly in that area. This concerns in particular the scenario in which cross section conducting fluid from first to second pass is much smaller which may result in significant pressure drops.
- the object of the invention is a heat exchanger according to claim 1.
- At least two tubes located on the terminal ends of the first stack are at the same level as at least two tubes located on the terminal ends of the second stack.
- the first stack and second stack are fluidly connected with the first manifold to provide at least one U-turn for the fluid, wherein the U-turn is formed between at least one tube of the first stack and the corresponding tube of the second stack.
- the first manifold is divided into an inlet channel and an outlet channel, wherein the inlet channel is fluidly connected with the inlet R in of the connection block and the primary pass of the first stack of tubes, and the outlet channel is fluidly connected with the outlet R out of the connection block and the primary pass of the second stack of tubes.
- the first tank comprises at least one dividing portion configured to block fluidal communication between the secondary pass, inlet channel and outlet channel.
- the tube portion and tube portion are fluidly connected with the inlet R in through the inlet channel.
- the tube portion P3 and tube portion P4 are fluidly connected with the outlet R out through the outlet channel.
- the tube portion P1 and tube portion P2 are fluidly isolated from tube portions P3 and P4 within the second manifold.
- the tube portion S1 is fluidly connected with tube portion S2 to form at least one U-turn within the first manifold.
- the tube portion S1 is adapted to collect the fluid from tube portions P1 and P2 within the second manifold.
- the tube portion S2 is adapted to distribute the fluid between the tube portions P3 and P4 within the second manifold.
- the first manifold comprises at least one hump configured to form at least one channel for the fluid inside the first tank.
- Invention relates to heat exchangers, wherein at least two media are guided through predetermined paths to exchange the heat between one another.
- the subject of the invention relates specifically to a heat exchanger 1 that may be applied in a motor vehicle comprising, for example, an internal combustion engine, an electric motor, or a combination of both those types.
- the heat exchanger may serve for example as an air cooled condenser (ACDS), a water cooled condenser (WCDS), an air gas cooler, or a chiller - a device for chilling the water and/or coolant fluid that has been heated while cooling down the batteries in electric vehicle.
- ACDS air cooled condenser
- WCDS water cooled condenser
- air gas cooler or a chiller - a device for chilling the water and/or coolant fluid that has been heated while cooling down the batteries in electric vehicle.
- Fig. 1 presents the heat exchanger 1 that may be used in a motor vehicle.
- Such heat exchangers usually comprise several key elements, inter alia, a first manifold 2 and a second manifold 3.
- the manifolds 2, 3 may be of different shapes and forms, but the most generic ones usually have a tubular or rectangular shape.
- the manifolds 2, 3 may comprise other elements, such as an inlet R in , an outlet R out , an integrated connection block 7, mounting brackets, so- called jumper lines, caps for closing the manifolds, baffles, and other.
- the first manifold 2 is not necessarily built the same way as the second manifold 3 as they may be optimized to increase the overall performance of heat exchanger 1.
- manifolds 2, 3 disclosed in the following embodiments of the invention, therefore the invention in not limited only to one particular type of sub-components forming the heat exchanger 1.
- the heat exchanger 1 further comprises a plurality of tubes 4 forming at least one stack deployed between the first manifold 2 and the second manifold 3.
- all types of the tubes 4 usually comprise open ends received in the manifolds 2, 3.
- the first manifold 2 usually comprises a plurality of slots configured to receive one end of the tubes 4, and the second manifold 3 also comprises plurality of slots configured to receive the other open ends of the corresponding tubes 4. This enables fluidal connection between the manifolds 2, 3 and the tubes 4.
- the tubes 4 may be in form of extruded tubes, folded tubes, the plates comprising micro channels and the channels for fluid formed by stamped plates.
- the path of the fluid flowing through the heat exchanger may be regarded as the sum of the passes between the inlet R in and the outlet R out of the heat exchanger 1 during its operational mode.
- the term "pass" is to be understood to mean a group or sub-group of tubes 4 in which the fluid follows one and the same direction in one and the same sense.
- the open ends of the tubes 4 are situated, in particular, in two opposite manifolds 2, 3. While moving from one pass to the another, the sense in which the fluid circulates may be reversed. Thus it is possible to lengthen the path of the fluid through the heat exchanger 1.
- the heat exchanger 1 may comprise at least two passes, wherein the primary pass 10 is defined by at least two tubes 4 located on the terminal ends of the particular stack. In other words, if at least one tube 4 is the top first tube of the particular stack and the other tube 4 is the bottom tube of the same stack, and in these tubes 4 the fluid follows one and the same direction in one and the same sense, then these tubes 4 form a primary pass 10. At least one secondary pass 20 is located between the tubes 4 forming the primary pass 10.
- a part of the primary section 10 is located in the vicinity of inlet R in , wherein the arrows indicate the direction of the flow.
- the primary pass 10 and the secondary pass 20 share the same first manifold 2 on one side and the second manifold 3 on the other.
- the fluid entering the heat exchanger 1 through the inlet R in is distributed across the primary pass 10 located on the top and the bottom of the stack by the first manifold 2.
- the top portion of the first manifold 2 may be fluidly connected with the bottom portion of the first manifold 2 by e.g. jumper line, as shown in Fig. 1 . This allows even distribution of the fluid across the first manifold 2, and consequently across the primary pass 10.
- the fluid travels along the primary pass 10 until it reaches the second manifold 3 wherein it is collected from the top and the bottom portion thereof, and it is further reversed to flow into the secondary pass 20.
- the heat exchanger 1 may comprise only one secondary pass 20, but in other examples it could comprise two or more secondary passes 20. Next, the fluid is collected and directed towards the outlet R out of the heat exchanger 1.
- Fig. 2 shows the schematic view of refrigerant flow arrangement in heat exchanger 1 comprising a first stack and a second stack of the tubes 4.
- the first stack is formed by tube portions P1, P2 and S1, wherein tube portion P1 and tube portion P2 form the primary pass 10 within the first stack, and tube portion S1 forms the secondary pass 20 for the first stack.
- the second stack is formed by secondary tube portions P3, P4 and S2, wherein tube portion P3 and tube portion P4 form the primary pass 10 for the second stack and tube portion S2 forms the secondary pass 20 for the second stack.
- the fluid enters the heat exchanger 1 though inlet R in and then enters primary pass 10 simultaneously through tube portion P1 and tube portion P2.
- the fluid enters tube portion S1 located between the tube portion P1 and tube portion P2, wherein P1, P2 and S1 are arranged in the first stack.
- the fluid performs a U-turn within the first stack, between the tube portion P1 and tube portion S1, and between the tube portion P2 and tube portion S1.
- the fluid flows through tube portion S1 of the first stack.
- the fluid performs a U-turn between the tube portion S1 and tube portion S2. It is to be noted that the U-turn is performed between the first stack and the second stack, yet within the tubes 4 forming the secondary pass 20.
- the fluid flows further through the tube section S2 and is splitted into two streams, wherein one stream performs a U-turn with respect to the tube portion S2 and it flows into tube portion P3, and the other stream also performs a U-turn with respect to tube portion S2, but it enters tube portion P4.
- the U-turns are preformed between the secondary section 20 and the primary section 10, within the second manifold 3.
- the fluid is directed towards an outlet R out in order to leave heat exchanger 1.
- Fig. 3 shows an exploded view of heat exchanger 1 suitable for cooling down one medium (e.g. coolant) using the other (e.g. R744 refrigerant), wherein both media are encapsulated in one device.
- This type of heat exchanger 1 involves two fluid circuits encapsulated within one housing 30.
- the coolant fluid delimited by a plastic housing 30 usually flows through and around the metallic core for refrigerant encapsulated within said housing 30.
- the refrigerant circuit of the heat exchanger 1 may comprise the connection block 7, the first manifold 2, the second manifold 3, and plurality of tubes in-between 4.
- connection block 7 may be made of a unitary block of material, e.g. the lightweight metal alloy such as aluminum.
- the shape of the connection block 7 usually corresponds to the shape of an opening 31 located on the housing 30, so that the connection block 7 may partially project from the housing 30.
- the connection block 7 is substantially rectangular.
- the connection block 7 comprises at least one inlet R in and at least one outlet R out , wherein the inlet R in is configured to introduce the first fluid into the first manifold 2 and the outlet R out is configured to collect the first fluid from the first manifold 2.
- the inlet R in and the outlet R out which usually penetrate through the body of the connection block 7 from its top portion towards the first manifold 2.
- connection block 7 may also comprise notches 8 that may serve to tightly connect the connector block 7 to the refrigerant circuit.
- the notches 8 may have different shape depending on desired connection type.
- the notches 8 presented in Fig 2 are cutouts in the connection block 7 material, however other shapes adapted to tightly connect the connector block 7 to the rest of the loop are also envisaged.
- connection block 7 may also comprise a sealing region suitable for receiving sealing means, e.g. a synthetic gasket.
- the sealing region may be in a form of cutout along the perimeter of the connection block 7. The sealing region ought to be deployed in the vicinity of the opening 31 located on the housing body 7 to provide the fluid-tight connection.
- the tubes 4 are deployed between the first manifold 2 and the second manifold 3.
- the tubes 4 may be in a form of plates, and may comprise open ends introduced into the slots of respective headers 2b, 3b.
- the tubes 4 may comprise top and bottom sides and two lateral sides, wherein the top and bottom sides are have bigger surface than the lateral ones.
- the tubes 4 may further comprise a general plane that is parallel to the top and bottom sides thereof.
- the tubes 4 may be arranged in at least two parallel stacks, each of them comprising a top terminal tube and a bottom terminal tube wherein the top terminal tube and the bottom terminal tube are deployed on the terminal end of the same stack to form the primary pass 10.
- the term "parallel stacks" should be regarded as at least two stacks of tubes 4 arranged in parallel next to each other so that top and bottom sides are parallel to each other.
- the open ends of the tubes 4 forming each stack are connected to the first manifold 2 on one side and with the second manifold on the other side.
- tubes of each stack may be interlaced with heat dispersion portions 9, e.g. fins, turbulator fins, and other, wherein the stacks do not share the same set of dispersion portions 9. This allows the neighboring stacks to be materially separated, so that the gap between the stacks is created.
- the heat dispersion portions 9 may be interlaced between all tubes 4 forming the stack.
- the tubes 4 may comprise bended ends that allow forming pairs of tubes 4, which can be introduced into corresponding slots. This enables reducing the amount of connection areas between the tubes 4 and the manifolds 2, 3 which are mostly vulnerable to leakage. Moreover, it facilitates the coolant fluid flow between the tubes 4 and the first manifold 2.
- the tubes 4 may be straight; however, the quantity of slots in the first manifold 2 and the second manifold 3 ought to be increased accordingly.
- the first manifold 2 and the second manifold 3 may fluidly cooperate with each other in order to provide primary pass 10 and secondary pass 20 in the heat exchanger 1.
- the total number of tubes 4 forming primary pass 10 is equal to the total number of tubes 4 forming second pass 20. This provides moderately uniform distribution of the fluid between the passes 10, 20.
- the total number of the tubes 4 forming the primary pass 10 may be different than the total number of the tubes 4 forming the second pass 20.
- the number of tubes 4 forming the primary pass 10 could be greater than the number of tubes forming at least one secondary pass 20. It enables to further optimise the performance of the heat exchanger 1 in some applications.
- the heat exchanger 1 may comprise different types of tubes 4, depending on its type. As shown in Figs 2 and 3 , the manifolds 2, 3 receive the pair of tubes 4 in one slot, in particular two tubes 4 both having a specific shape. This facilitates the production process, increases the efficiency of the heat exchanger, and most importantly, it reduces the risk of leakage from the most vulnerable area i.e. the connection between the tube 4 and the slot of the manifold 2, 3.
- Fig. 4 shows in detail the sub-components forming the manifolds 2, 3.
- the connection block 7 may be fluidly connected with the first manifold 2, wherein the first manifold 2 participates in distribution and collection of the first fluid.
- the fluid is distributed by an inlet channel 21 which corresponds to the inlet R in in the connector 7, and it is collected by an outlet channel 22 which corresponds to the outlet R out of the connector 7.
- the first manifold 2 may comprise a first tank 2a and a first header 2b which are configured to determine the flow path to the tubes 4.
- the first tank 2a may be in a form of a unitary block of material comprising openings for fluid, which enable fluidal communication between the connection block 7 and the first manifold 2.
- the first tank 2a is closed on the bottom by e.g. end plate 2c.
- the first tank 2a is fluidly connected with the first header 2b which comprises several sub- components.
- the first header 2b may comprise a first plate comprising slots for receiving the tubes 4, e.g. the single slot of the first plate may receive a pair of tubes 4.
- the slots are configured to receive only one tube 4, so that the quantity of slots deployed on the first plate is equal to the quantity of tubes 4.
- the first header 2b is tightly connected, for example crimped, with the first tank 2a to ensure proper positioning of the first header 2b with respect to the first tank 2a and to facilitate creation of the fluid-tight connection after e.g. brazing one to the other.
- first header 2b comprises at least one second plate deployed between the first plate and the first tank 2a.
- the second plate may comprise at least one opening configured to enable fluidal communication between the adjacent stacks of tubes 4. This enables fluidal communication between the second passes 20 inside the first manifold 2.
- the first manifold 2 may further comprise at least one hump 6 which forms inlet channel 21 and outlet channel 22 for the fluid.
- the number of humps 6 may be equal to the number of channels 21, 22.
- the passes 10, 20 may be defined by the first manifold 2 which comprises at least one dividing portion 5 located on the first tank 2a.
- the dividing portion 5 is configured to guide the refrigerant fluid through the first header 2b into desired tubes 4 forming the primary pass 10.
- the dividing portion 5 may block the fluidal communication between the inlet channel 21 of the first tank 2a and the tubes 4 forming the secondary pass 20.
- the primary tank 2a is configured to collect the fluid and guide it towards the outlet R out of the connection block 7.
- the primary header 2b not only may fluidly connect first tank 2a and the tubes 4 forming the primary pass 10, but also fluidly connect the tubes 4 forming secondary passes 20 of neighboring stacks of tubes 4. Therefore, the first manifold 2 provides at least one U-turn for the refrigerant fluid.
- the dividing portions 5 may be in a form of leftover material from the process of forming the inlet channel 21 and/or outlet channel 22 in the first tank 2a.
- the material forming the manifold is partially removed to provide fluidal communication between the first manifold 2 and one of the passages 10, 20. Consequently, the remaining material may form one or more dividing portions 5.
- the second manifold 3 may comprise a second tank 3a and a second header 3b, wherein the second manifold 3 plays role of refrigerant fluid distributor. In other words, the second manifold 3 receives the fluid from one portion of the tubes 4 and transfers it to the other portion of the tubes 4.
- the second header 3b may comprise at least one third plate comprising slots for receiving the tubes 4, e.g. the single slot of the third plate may receive a pair of tubes 4.
- the slots are configured to receive only one tube 4, so that the quantity of slots deployed on the third plate is equal to the quantity of tubes 4 received therein.
- the second header comprises two third plates.
- the second tank 3a comprises, inter alia, a cover plate which is substantially flat and provides closure of the second manifold 3 and at least one fourth plate configured to convey the first fluid from the top portion to the bottom portion of the second manifold 3.
- a cover plate which is substantially flat and provides closure of the second manifold 3 and at least one fourth plate configured to convey the first fluid from the top portion to the bottom portion of the second manifold 3.
- One of the ways to create the fourth plate may be forming a plate with a plurality of parallel openings extending from the top to the bottom portion thereof that will provide a fluidal communication with the sub-components of the second manifold 3.
- the second header 3b is tightly connected, for example crimped, with the second tank 3a to ensure proper positioning of the second header 3b with respect to the second tank 3a and to facilitate creation of the fluid-tight connection after e.g. brazing one to the other.
- each tube 4 is introduced into their respective manifolds 2, 3, so that they entirely penetrate the first plate and the third plate, and partially penetrate the second plate and the fourth plate.
- Fig. 4 further comprises exemplary location of primary pass 10 and secondary pass 20.
- the primary passes 10 will be fluidly connected to four slots of each stack, two of them located on the top and another two on the bottom portion of the headers 2b and 3b.
- the second pass 20 is formed from four slots deployed in-between the slots forming primary pass 10.
- two tubes 4 located on the top of each stack and two tubes 4 located on the bottom of each stack may be fixed (e.g. brazed) with six heat dispersion portions 9 interlaced in-between these tubes 4, whereas the top and the bottom tubes 4 may comprise the heat dispersion portions 9 fixed to the peripheral ends of the stack.
- four tubes 4 located in the middle of the stack may be fixed to five inner heat dispersion portions 9.
- air cooled condenser and air gas cooler comprise the top and the bottom tubes 4 which do not participate in fluid circulation, in water cooled condenser the first and the last passes are conducting coolant to improve resistance to high pressures which means, that the tubes 4 located on the top of the stack and the tubes 4 located on the bottom of the stack conduct refrigerant of greater heat exchange surface with second medium (e.g.) comparing to other passes.
- second medium e.g.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
- The invention relates to a heat exchanger, in particular the heat exchanger for a motor vehicle. A heat exchanger according to the preamble of
claim 1 is known from documentUS 2019/10313 A1 . - Heat exchangers commonly used in the industry may comprise means for redirecting the fluid inside the core in order to increase the distance traveled by the fluid and consequently to increase the overall performance of the heat exchanger. Sometimes, the fluid is transmitted between the neighboring sections to avoid complex solutions. Oftentimes, creating several passes inside the core of the heat exchanger is problematic, because of increased pressure drop and limited packaging. Excessive pressure drop may also impact the performance in an indirect manner, due to increased power consumption by compressor. In case of heat exchangers with two manifolds connected by heat exchange tubes, so-called "dead zones" can occur, wherein the flow of the heat exchange fluid is limited. Thus, it is problematic to provide a homogenous distribution of the fluid in the heat exchanger, including manifolds. One of the known solutions to promote the optimized and homogenous distribution of the fluid circulating through the heat exchanger is dividing heat exchanger into sections by blocking or limiting the flow of the fluid inside the manifolds. However, currently known solutions do not suggest providing homogeneity of the fluid distribution, what usually has a negative impact on efficiency of the whole heat exchanger. Sometimes the fluid is not delivered to the tubes evenly, what may suggest the homogeneity problems particularly in that area. This concerns in particular the scenario in which cross section conducting fluid from first to second pass is much smaller which may result in significant pressure drops.
- Therefore it would be desirable to provide a heat exchanger that would increase the efficiency and decrease the pressure drop.
- The object of the invention is a heat exchanger according to
claim 1. - Preferably, at least two tubes located on the terminal ends of the first stack are at the same level as at least two tubes located on the terminal ends of the second stack. Preferably, the first stack and second stack are fluidly connected with the first manifold to provide at least one U-turn for the fluid, wherein the U-turn is formed between at least one tube of the first stack and the corresponding tube of the second stack.
- Preferably, the first manifold is divided into an inlet channel and an outlet channel, wherein the inlet channel is fluidly connected with the inlet Rin of the connection block and the primary pass of the first stack of tubes, and the outlet channel is fluidly connected with the outlet Rout of the connection block and the primary pass of the second stack of tubes.
- Preferably, the first tank comprises at least one dividing portion configured to block fluidal communication between the secondary pass, inlet channel and outlet channel. Preferably, the tube portion and tube portion are fluidly connected with the inlet Rin through the inlet channel.
- Preferably, the tube portion P3 and tube portion P4 are fluidly connected with the outlet Rout through the outlet channel.
- Preferably, the tube portion P1 and tube portion P2 are fluidly isolated from tube portions P3 and P4 within the second manifold.
- Preferably, the tube portion S1 is fluidly connected with tube portion S2 to form at least one U-turn within the first manifold.
- Preferably, the tube portion S1 is adapted to collect the fluid from tube portions P1 and P2 within the second manifold.
- Preferably, the tube portion S2 is adapted to distribute the fluid between the tube portions P3 and P4 within the second manifold.
- Preferably, the first manifold comprises at least one hump configured to form at least one channel for the fluid inside the first tank.
- Examples of the invention will be apparent from and described in detail with reference to the accompanying drawings, in which:
-
Fig. 1 shows flow arrangement through the heat exchanger in the first example not according to the invention, -
Fig. 2 shows the schematic view of flow arrangement in the heat exchanger according to the invention, -
Fig. 3 shows the exploded view of the heat exchanger in the second example, -
Fig. 4 shows the first manifold assembly and the second manifold assembly in the second example. - Invention relates to heat exchangers, wherein at least two media are guided through predetermined paths to exchange the heat between one another. The subject of the invention relates specifically to a
heat exchanger 1 that may be applied in a motor vehicle comprising, for example, an internal combustion engine, an electric motor, or a combination of both those types. - The heat exchanger may serve for example as an air cooled condenser (ACDS), a water cooled condenser (WCDS), an air gas cooler, or a chiller - a device for chilling the water and/or coolant fluid that has been heated while cooling down the batteries in electric vehicle.
-
Fig. 1 presents theheat exchanger 1 that may be used in a motor vehicle. Such heat exchangers usually comprise several key elements, inter alia, afirst manifold 2 and asecond manifold 3. Themanifolds heat exchanger 1, themanifolds connection block 7, mounting brackets, so- called jumper lines, caps for closing the manifolds, baffles, and other. Furthermore, thefirst manifold 2 is not necessarily built the same way as thesecond manifold 3 as they may be optimized to increase the overall performance ofheat exchanger 1. There may be different types ofmanifolds heat exchanger 1. - The
heat exchanger 1 further comprises a plurality oftubes 4 forming at least one stack deployed between thefirst manifold 2 and thesecond manifold 3. Despite the fact that thetubes 4 may be of different form and shape depending on the type of theheat exchanger 1, all types of thetubes 4 usually comprise open ends received in themanifolds first manifold 2 usually comprises a plurality of slots configured to receive one end of thetubes 4, and thesecond manifold 3 also comprises plurality of slots configured to receive the other open ends of thecorresponding tubes 4. This enables fluidal connection between themanifolds tubes 4. Thetubes 4 may be in form of extruded tubes, folded tubes, the plates comprising micro channels and the channels for fluid formed by stamped plates. - One of the ways to optimize the efficiency of the
heat exchanger 1 is to force the fluid to flow through an organized, predetermined path. The path of the fluid flowing through the heat exchanger may be regarded as the sum of the passes between the inlet Rin and the outlet Rout of theheat exchanger 1 during its operational mode. The term "pass" is to be understood to mean a group or sub-group oftubes 4 in which the fluid follows one and the same direction in one and the same sense. In thetubes 4 of one and the same pass, the open ends of thetubes 4 are situated, in particular, in twoopposite manifolds heat exchanger 1. - The
heat exchanger 1 may comprise at least two passes, wherein theprimary pass 10 is defined by at least twotubes 4 located on the terminal ends of the particular stack. In other words, if at least onetube 4 is the top first tube of the particular stack and theother tube 4 is the bottom tube of the same stack, and in thesetubes 4 the fluid follows one and the same direction in one and the same sense, then thesetubes 4 form aprimary pass 10. At least onesecondary pass 20 is located between thetubes 4 forming theprimary pass 10. - As shown in
Fig. 1 , a part of theprimary section 10 is located in the vicinity of inlet Rin, wherein the arrows indicate the direction of the flow. In this example, theprimary pass 10 and thesecondary pass 20 share the samefirst manifold 2 on one side and thesecond manifold 3 on the other. The fluid entering theheat exchanger 1 through the inlet Rin is distributed across theprimary pass 10 located on the top and the bottom of the stack by thefirst manifold 2. The top portion of thefirst manifold 2 may be fluidly connected with the bottom portion of thefirst manifold 2 by e.g. jumper line, as shown inFig. 1 . This allows even distribution of the fluid across thefirst manifold 2, and consequently across theprimary pass 10. The fluid travels along theprimary pass 10 until it reaches thesecond manifold 3 wherein it is collected from the top and the bottom portion thereof, and it is further reversed to flow into thesecondary pass 20. Theheat exchanger 1 may comprise only onesecondary pass 20, but in other examples it could comprise two or moresecondary passes 20. Next, the fluid is collected and directed towards the outlet Rout of theheat exchanger 1. -
Fig. 2 shows the schematic view of refrigerant flow arrangement inheat exchanger 1 comprising a first stack and a second stack of thetubes 4. - The first stack is formed by tube portions P1, P2 and S1, wherein tube portion P1 and tube portion P2 form the
primary pass 10 within the first stack, and tube portion S1 forms thesecondary pass 20 for the first stack. Analogically, the second stack is formed by secondary tube portions P3, P4 and S2, wherein tube portion P3 and tube portion P4 form theprimary pass 10 for the second stack and tube portion S2 forms thesecondary pass 20 for the second stack. - The fluid enters the
heat exchanger 1 though inlet Rin and then entersprimary pass 10 simultaneously through tube portion P1 and tube portion P2. Next, the fluid enters tube portion S1 located between the tube portion P1 and tube portion P2, wherein P1, P2 and S1 are arranged in the first stack. The fluid performs a U-turn within the first stack, between the tube portion P1 and tube portion S1, and between the tube portion P2 and tube portion S1. Next, the fluid flows through tube portion S1 of the first stack. The fluid performs a U-turn between the tube portion S1 and tube portion S2. It is to be noted that the U-turn is performed between the first stack and the second stack, yet within thetubes 4 forming thesecondary pass 20. The fluid flows further through the tube section S2 and is splitted into two streams, wherein one stream performs a U-turn with respect to the tube portion S2 and it flows into tube portion P3, and the other stream also performs a U-turn with respect to tube portion S2, but it enters tube portion P4. It is to be noted that the U-turns are preformed between thesecondary section 20 and theprimary section 10, within thesecond manifold 3. Finally, the fluid is directed towards an outlet Rout in order to leaveheat exchanger 1. -
Fig. 3 shows an exploded view ofheat exchanger 1 suitable for cooling down one medium (e.g. coolant) using the other (e.g. R744 refrigerant), wherein both media are encapsulated in one device. This type ofheat exchanger 1 involves two fluid circuits encapsulated within onehousing 30. In this type ofheat exchanger 1, the coolant fluid delimited by aplastic housing 30 usually flows through and around the metallic core for refrigerant encapsulated within saidhousing 30. - The refrigerant circuit of the
heat exchanger 1 may comprise theconnection block 7, thefirst manifold 2, thesecond manifold 3, and plurality of tubes in-between 4. - The
connection block 7 may be made of a unitary block of material, e.g. the lightweight metal alloy such as aluminum. The shape of theconnection block 7 usually corresponds to the shape of anopening 31 located on thehousing 30, so that theconnection block 7 may partially project from thehousing 30. Preferably, theconnection block 7 is substantially rectangular. Further, theconnection block 7 comprises at least one inlet Rin and at least one outlet Rout, wherein the inlet Rin is configured to introduce the first fluid into thefirst manifold 2 and the outlet Rout is configured to collect the first fluid from thefirst manifold 2. The inlet Rin and the outlet Rout, which usually penetrate through the body of theconnection block 7 from its top portion towards thefirst manifold 2. The inlet Rin and the outlet Rout may have a circular cross-section. Theconnection block 7 may also comprisenotches 8 that may serve to tightly connect theconnector block 7 to the refrigerant circuit. Thenotches 8 may have different shape depending on desired connection type. Thenotches 8 presented inFig 2 are cutouts in theconnection block 7 material, however other shapes adapted to tightly connect theconnector block 7 to the rest of the loop are also envisaged. - The
connection block 7 may also comprise a sealing region suitable for receiving sealing means, e.g. a synthetic gasket. The sealing region may be in a form of cutout along the perimeter of theconnection block 7. The sealing region ought to be deployed in the vicinity of theopening 31 located on thehousing body 7 to provide the fluid-tight connection. - As
Fig.3 shows, thetubes 4 are deployed between thefirst manifold 2 and thesecond manifold 3. Thetubes 4 may be in a form of plates, and may comprise open ends introduced into the slots ofrespective headers tubes 4 may comprise top and bottom sides and two lateral sides, wherein the top and bottom sides are have bigger surface than the lateral ones. Thetubes 4 may further comprise a general plane that is parallel to the top and bottom sides thereof. Thetubes 4 may be arranged in at least two parallel stacks, each of them comprising a top terminal tube and a bottom terminal tube wherein the top terminal tube and the bottom terminal tube are deployed on the terminal end of the same stack to form theprimary pass 10. The term "parallel stacks" should be regarded as at least two stacks oftubes 4 arranged in parallel next to each other so that top and bottom sides are parallel to each other. - The open ends of the
tubes 4 forming each stack are connected to thefirst manifold 2 on one side and with the second manifold on the other side. Further, tubes of each stack may be interlaced withheat dispersion portions 9, e.g. fins, turbulator fins, and other, wherein the stacks do not share the same set ofdispersion portions 9. This allows the neighboring stacks to be materially separated, so that the gap between the stacks is created. Theheat dispersion portions 9 may be interlaced between alltubes 4 forming the stack. Further, thetubes 4 may comprise bended ends that allow forming pairs oftubes 4, which can be introduced into corresponding slots. This enables reducing the amount of connection areas between thetubes 4 and themanifolds tubes 4 and thefirst manifold 2. Alternatively, thetubes 4 may be straight; however, the quantity of slots in thefirst manifold 2 and thesecond manifold 3 ought to be increased accordingly. - The
first manifold 2 and thesecond manifold 3 may fluidly cooperate with each other in order to provideprimary pass 10 andsecondary pass 20 in theheat exchanger 1. - In the basic embodiment of an invention the total number of
tubes 4 formingprimary pass 10 is equal to the total number oftubes 4 formingsecond pass 20. This provides moderately uniform distribution of the fluid between thepasses tubes 4 forming theprimary pass 10 may be different than the total number of thetubes 4 forming thesecond pass 20. For example, the number oftubes 4 forming theprimary pass 10 could be greater than the number of tubes forming at least onesecondary pass 20. It enables to further optimise the performance of theheat exchanger 1 in some applications. - As mentioned in the previous paragraphs, the
heat exchanger 1 may comprise different types oftubes 4, depending on its type. As shown inFigs 2 and3 , themanifolds tubes 4 in one slot, in particular twotubes 4 both having a specific shape. This facilitates the production process, increases the efficiency of the heat exchanger, and most importantly, it reduces the risk of leakage from the most vulnerable area i.e. the connection between thetube 4 and the slot of themanifold -
Fig. 4 shows in detail the sub-components forming themanifolds connection block 7 may be fluidly connected with thefirst manifold 2, wherein thefirst manifold 2 participates in distribution and collection of the first fluid. The fluid is distributed by an inlet channel 21 which corresponds to the inlet Rin in theconnector 7, and it is collected by an outlet channel 22 which corresponds to the outlet Rout of theconnector 7. Thefirst manifold 2 may comprise afirst tank 2a and afirst header 2b which are configured to determine the flow path to thetubes 4. Thefirst tank 2a may be in a form of a unitary block of material comprising openings for fluid, which enable fluidal communication between theconnection block 7 and thefirst manifold 2. Naturally, thefirst tank 2a is closed on the bottom by e.g.end plate 2c. Thefirst tank 2a is fluidly connected with thefirst header 2b which comprises several sub- components. Thefirst header 2b may comprise a first plate comprising slots for receiving thetubes 4, e.g. the single slot of the first plate may receive a pair oftubes 4. Alternatively, the slots are configured to receive only onetube 4, so that the quantity of slots deployed on the first plate is equal to the quantity oftubes 4. Thefirst header 2b is tightly connected, for example crimped, with thefirst tank 2a to ensure proper positioning of thefirst header 2b with respect to thefirst tank 2a and to facilitate creation of the fluid-tight connection after e.g. brazing one to the other. Further, thefirst header 2b comprises at least one second plate deployed between the first plate and thefirst tank 2a. The second plate may comprise at least one opening configured to enable fluidal communication between the adjacent stacks oftubes 4. This enables fluidal communication between the second passes 20 inside thefirst manifold 2. - The
first manifold 2 may further comprise at least onehump 6 which forms inlet channel 21 and outlet channel 22 for the fluid. The number ofhumps 6 may be equal to the number of channels 21, 22. - The passes 10, 20 may be defined by the
first manifold 2 which comprises at least one dividingportion 5 located on thefirst tank 2a. The dividingportion 5 is configured to guide the refrigerant fluid through thefirst header 2b into desiredtubes 4 forming theprimary pass 10. The dividingportion 5 may block the fluidal communication between the inlet channel 21 of thefirst tank 2a and thetubes 4 forming thesecondary pass 20. Further, theprimary tank 2a is configured to collect the fluid and guide it towards the outlet Rout of theconnection block 7. Theprimary header 2b not only may fluidly connectfirst tank 2a and thetubes 4 forming theprimary pass 10, but also fluidly connect thetubes 4 formingsecondary passes 20 of neighboring stacks oftubes 4. Therefore, thefirst manifold 2 provides at least one U-turn for the refrigerant fluid. - The dividing
portions 5 may be in a form of leftover material from the process of forming the inlet channel 21 and/or outlet channel 22 in thefirst tank 2a. The material forming the manifold is partially removed to provide fluidal communication between thefirst manifold 2 and one of thepassages more dividing portions 5. - The
second manifold 3 may comprise asecond tank 3a and asecond header 3b, wherein thesecond manifold 3 plays role of refrigerant fluid distributor. In other words, thesecond manifold 3 receives the fluid from one portion of thetubes 4 and transfers it to the other portion of thetubes 4. - The
second header 3b may comprise at least one third plate comprising slots for receiving thetubes 4, e.g. the single slot of the third plate may receive a pair oftubes 4. Alternatively, the slots are configured to receive only onetube 4, so that the quantity of slots deployed on the third plate is equal to the quantity oftubes 4 received therein. As shown inFig. 4 , the second header comprises two third plates. - The
second tank 3a comprises, inter alia, a cover plate which is substantially flat and provides closure of thesecond manifold 3 and at least one fourth plate configured to convey the first fluid from the top portion to the bottom portion of thesecond manifold 3. One of the ways to create the fourth plate may be forming a plate with a plurality of parallel openings extending from the top to the bottom portion thereof that will provide a fluidal communication with the sub-components of thesecond manifold 3. - The
second header 3b is tightly connected, for example crimped, with thesecond tank 3a to ensure proper positioning of thesecond header 3b with respect to thesecond tank 3a and to facilitate creation of the fluid-tight connection after e.g. brazing one to the other. - To provide a fluid-tight and rigid connection between the
tubes 4 and themanifolds tube 4 are introduced into theirrespective manifolds -
Fig. 4 further comprises exemplary location ofprimary pass 10 andsecondary pass 20. In particular, the primary passes 10 will be fluidly connected to four slots of each stack, two of them located on the top and another two on the bottom portion of theheaders second pass 20 is formed from four slots deployed in-between the slots formingprimary pass 10. - In one example, two
tubes 4 located on the top of each stack and twotubes 4 located on the bottom of each stack may be fixed (e.g. brazed) with sixheat dispersion portions 9 interlaced in-between thesetubes 4, whereas the top and thebottom tubes 4 may comprise theheat dispersion portions 9 fixed to the peripheral ends of the stack. Further, fourtubes 4 located in the middle of the stack may be fixed to five innerheat dispersion portions 9. The features mentioned above does apply in particular to water chiller heat exchanger, but other types of heat exchangers are also envisaged, as they obey the same principles as the water chiller. For instance, air cooled condenser and air gas cooler comprise the top and thebottom tubes 4 which do not participate in fluid circulation, in water cooled condenser the first and the last passes are conducting coolant to improve resistance to high pressures which means, that thetubes 4 located on the top of the stack and thetubes 4 located on the bottom of the stack conduct refrigerant of greater heat exchange surface with second medium (e.g.) comparing to other passes.
Claims (12)
- A heat exchanger (1), in particular for a motor vehicle, comprising:- a first manifold (2) comprising a first tank (2a) and a first header (2b),- a second manifold (3), comprising a second tank (3a) and a second header (3b),- a connection block (7) comprising an inlet Rin and an outlet Rout for a fluid, wherein the connection block (7) is fluidly connected with the first manifold (2),- a plurality of tubes (4) forming at least one stack deployed between the first manifold (2) and the second manifold (3), the tubes (4) comprising open ends received in the manifolds (2, 3),wherein the first manifold (2) and the second manifold (3) are fluidly connected with each other forming a primary pass (10) and a secondary pass (20) for a fluid, characterised in that the primary pass (10) is defined by at least two tubes (4) located on the terminal ends of the stack and the secondary pass (20) is located between the tubes (4) forming the primary pass (10), wherein the tubes (4) are arranged in a first stack comprising a first stacking direction, a second stack comprising a second stacking direction being parallel to the first stacking direction, wherein the second stack is distanced from the first stack in a third direction being perpendicular to the first stacking direction and the second stacking direction, wherein the first stack comprises tube portions (P1), (P2) and (S1), wherein tube portion (P1) and tube portion (P2) form the primary pass (10) within the first stack and tube portion (S1) forms the secondary pass (20) for the first stack, wherein the second stack comprises secondary tube portions (P3), (P4) and (S2), wherein tube portion (P3) and tube portion (P4) form the primary pass (10) for the second stack and tube portion (S2) forms the secondary pass (20) for the second stack, wherein the tube portion (S2) is located between the tube portions (P3), (P4) forming the primary pass (10).
- The heat exchanger (1) according to claim 1, wherein at least two tubes (4) located on the terminal ends of the first stack are at the same level as at least two tubes (4) located on the terminal ends of the second stack.
- The heat exchanger (1) according to any of the preceding claims, wherein the first stack and second stack are fluidly connected with the first manifold (2) to provide at least one U-turn for the fluid, wherein the U-turn is formed between at least one tube (4) of the first stack and the corresponding tube (4) of the second stack.
- The heat exchanger (1) according to any of the preceding claims, wherein the first manifold (2) is divided into an inlet channel (21) and an outlet channel (22), wherein the inlet channel (21) is fluidly connected with the inlet Rin of the connection block (7) and the primary pass (10) of the first stack of tubes (4), and the outlet channel (22) is fluidly connected with the outlet Rout of the connection block (7) and the primary pass (10) of the second stack of tubes (4).
- The heat exchanger (1) according to claim 4, wherein the first tank (2a) comprises at least one dividing portion (5) configured to block fluidal communication between the secondary pass (20), inlet channel (21) and outlet channel (22).
- The heat exchanger (1) according to any of the preceding claims, wherein the tube portion (P1) and tube portion (P2) are fluidly connected with the inlet Rin through the inlet channel (21).
- The heat exchanger (1) according to any of the preceding claims, wherein the tube portion (P3) and tube portion (P4) are fluidly connected with the outlet Rout through the outlet channel (22).
- The heat exchanger (1) according to any of the preceding claims, wherein the tube portion (P1) and tube portion (P2) are fluidly isolated from tube portions (P3) and (P4) within the second manifold (3).
- The heat exchanger (1) according to any of the preceding claims, wherein the tube portion (S1) is fluidly connected with tube portion (S2) to form at least one U-turn within the first manifold (2).
- The heat exchanger (1) according to any of the preceding claims, wherein the tube portion (S1) is adapted to collect the fluid from tube portions (P1) and (P2) within the second manifold (2).
- The heat exchanger (1) according to any of the preceding claims, wherein the tube portion (S2) is adapted to distribute the fluid between the tube portions (P3) and (P4) within the second manifold (3).
- The heat exchanger (1) according to any of the preceding claims, wherein the first manifold (2) comprises at least one hump (6) configured to form at least one channel (21, 22) for the fluid inside the first tank (2a).
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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EP20461516.5A EP3872435B1 (en) | 2020-02-28 | 2020-02-28 | A heat exchanger |
PCT/EP2021/053631 WO2021170438A1 (en) | 2020-02-28 | 2021-02-15 | A heat exchanger |
CN202180016817.6A CN115176120A (en) | 2020-02-28 | 2021-02-15 | Heat exchanger |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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EP20461516.5A EP3872435B1 (en) | 2020-02-28 | 2020-02-28 | A heat exchanger |
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EP3872435A1 EP3872435A1 (en) | 2021-09-01 |
EP3872435B1 true EP3872435B1 (en) | 2023-08-23 |
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EP20461516.5A Active EP3872435B1 (en) | 2020-02-28 | 2020-02-28 | A heat exchanger |
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EP (1) | EP3872435B1 (en) |
CN (1) | CN115176120A (en) |
WO (1) | WO2021170438A1 (en) |
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EP4194787A1 (en) * | 2021-12-10 | 2023-06-14 | Valeo Autosystemy SP. Z.O.O. | A heat exchanger |
EP4382843A1 (en) * | 2022-12-05 | 2024-06-12 | Valeo Systemes Thermiques | A water chiller |
EP4382846A1 (en) * | 2022-12-05 | 2024-06-12 | Valeo Systemes Thermiques | A heat exchanger for vehicles |
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JP3982379B2 (en) * | 2002-10-15 | 2007-09-26 | 株式会社デンソー | Heat exchanger |
US7703282B1 (en) * | 2007-12-10 | 2010-04-27 | Iea, Inc. | Heat exchanger with horizontal flowing charge air cooler |
ES2689931T3 (en) * | 2008-05-05 | 2018-11-16 | Carrier Corporation | Heat exchanger with microchannels that includes multiple fluid circuits |
JP5920175B2 (en) * | 2012-11-13 | 2016-05-18 | 株式会社デンソー | Heat exchanger |
US10184703B2 (en) * | 2014-08-19 | 2019-01-22 | Carrier Corporation | Multipass microchannel heat exchanger |
-
2020
- 2020-02-28 EP EP20461516.5A patent/EP3872435B1/en active Active
-
2021
- 2021-02-15 WO PCT/EP2021/053631 patent/WO2021170438A1/en active Application Filing
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CN115176120A (en) | 2022-10-11 |
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