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
  • F28D1/05391—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
  • 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
  • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
  • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
• • 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
  • F28F9/0253—Massive connectors, e.g. blocks; Plate-like connectors with multiple channels, e.g. with combined inflow and outflow channels
• • 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
  • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
  • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
• • 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
  • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
  • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
  • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins

Definitions

• the invention relates to a heat exchanger, in particular the heat exchanger for a motor vehicle.
• the new refrigerant such as R744 (carbon dioxide or CO 2 ) has been introduced.
• the R1234yf refrigerant has similar properties to R134a. However, its global warming potential or GWP is only 4, as opposed to 1430.
• the refrigerant R744 has been assigned a GWP value of 1 and functions as the reference gas.
• R744 Systems designed for use with R744 must withstand significantly higher pressures than those intended for R1234yf. In summer, the peak pressure is around 130 bar for conventional, R1234yf, whereas R744 has a peak pressure of 170 bar, which is above the critical pressure level (supercritical process). This makes controlling the system more difficult, but not problematic.
• the coefficient of performance or COP is the same in moderate climate conditions, but slightly poorer in hot, moist climate zones. The system can be designed to compensate for this, as the components are smaller because of the higher volumetric cooling capacity of R744.
• the R744 refrigerant is at a disadvantage as R744 absorbs slightly less energy per unit of flow in a refrigerant cycle.
• IHX Internal Heat exchanger
• An Internal Heat exchanger (IHX) is used to transfer heat between the low side pressure and the high pressure flow circuits. Its function is to improve system performance by further cooling the refrigerant being supplied to, for example, an evaporator through the refrigerant control device.
• Commonly used internal heat exchangers usually comprise, for example, a coaxial tube heat exchanger and a stacked heat exchanger.
• the coaxial heat exchanger is usually designed as a "tube in tube” structure.
• the outer tube is made of steel/copper, and the inner tube can be titanium, copper, copper-nickel depending on the requirements of working conditions.
• the coaxial heat exchanger usually conveys two fluids through separate circuits, wherein one circuit is conveyed in the opposite direction with respect to the other fluid.
• the stacked plate heat exchanger design is usually suited to transferring heat between medium- and low-pressure fluids.
• Welded, semi-welded and brazed heat exchangers are used for heat exchange between high-pressure fluids or where a more compact product is required.
• two alternating chambers usually thin in depth, separated at their largest surface by a corrugated metal plate.
• the plates used in a plate and frame heat exchanger are obtained by one piece pressing of metal plates.
• Stainless steel is a commonly used metal for the plates because of its ability to withstand high temperatures, its strength, and its corrosion resistance.
• both coaxial and plate heat exchangers are usually not suitable for high-pressure R744 refrigerant, unless thay are made of specific and expensive material.
• the heat exchangers such as coaxial tube heat exchanger require its components to be large enough to efficiently transfer the heat between the media. Consequently, the heat exchangers described above are inconvenient in terms of packaging, costs of production and weight reduction.
• the sub-components should preferably be made of inexpensive materials while maintaining high quality of the final product. Further, the production process of sub-components should be simple and efficient i.e. it would be desired to manufacture each sub-component using a method that does not require complicated production process.
• the object of the invention is, among others, a heat exchanger for a heat exchange between a first fluid and at least second fluid comprising: a first manifold comprising a first cover comprising at least a first channel extending along the axis of elongation of the first manifold, a second manifold spaced apart from the first manifold, wherein the second manifold comprises a second cover comprising at least a second channel extending along the axis of elongation of the second manifold, a plurality of tubes configured to provide a fluidal communication between the first manifold and the second manifold, wherein the tubes comprise a general axis of elongation being substantially orthogonal with respect to the axis of elongation of at least first manifold, wherein at least the first cover comprises first passages for the first fluid, wherein the first passages are configured to provide a fluidal communication between the first cover and the tubes, and the second cover comprises at least second passages for the second fluid, wherein the second passage
• the plurality of tubes comprises a first tube set and a second tube set, wherein the first tube set and the second tube set are arranged in at least first stack comprising a first stacking direction, wherein the first stacking direction is perpendicular with respect to the axis of elongation of the tubes.
• the first tube set comprises at least a primary tube and a secondary tub, wherein: the primary tube comprises a first flat section being parallel with respect to axis of elongation of the tubes, and first meandering sections arranged at the terminal ends of the first flat section.
• secondary tube comprises a second flat section being parallel with respect to axis of elongation of the tubes, and second meandering sections arranged at the terminal ends of the second flat section, wherein the primary tube and the secondary tube are juxtaposed with respect each other so that first meandering sections are in contact with second meandering sections forming a contact zone, so that the first tube set comprises a gap between the first flat section and the second flat section.
• the second tube set comprises at least one master tube, wherein the master tube comprises a third flat portion extending along the axis of elongation of the tubes through the entirety of the master tube.
• the first tube set comprises a first entry height measured in perpendicular to the axis of elongation of the tubes at the terminal ends of the first tube set where the contact zone of the meandering sections is formed.
• the second tube set comprises a second entry height measured in perpendicular to the axis of elongation of the tubes at the terminal ends of the second tube set.
• the first entry height is equal to the second entry height.
• the first tube set and the second tube set are arranged in a second stack comprising a second stacking direction being parallel to the first stacking direction, wherein the second stack is arranged next to the first stack so that the tubes forming each stack are at the same level, the level being determined in perpendicular to any of the stacking directions.
• the first manifold further comprises a first header comprising a plurality of slots configured to receive the tubes, and at least one first distribution plate arranged between the first header and first cover
• the second manifold further comprises a second header comprising a plurality of slots configured to receive the tubes and at least one second distribution plate arranged between the second header and the second cover.
• the primary tube and the secondary tube of the first tube set comprises a plurality of first micro-channels, wherein the first micro-channels are arranged evenly between the primary tube and a secondary tube.
• the master tube of the second tube set comprises plurality of second micro-channels, wherein the second micro-channels are arranged evenly within the master tube.
• the hydraulic diameter of all second micro-channels is greater than the hydraulic diameter of all first micro-channels.
• both first tube set and the second tube set comprise master tubes.
• the first tube set is configured to provide flow of the first fluid therein and the second tube set is configured to provide flow if the second fluid therein.
• the subject-matter of the invention is a heat exchanger 1. More precisely, the subject-matter of the invention is an internal heat exchanger (IHX) for a motor vehicle.
• the heat exchanger 1 may be suitable for a heat exchange between a first fluid HP and at least second fluid LP.
• the first fluid as suggested by the HP abbreviation, may be a high-pressure fluid.
• the first fluid may be a high-pressure R744.
• the second fluid may be a low-pressure fluid, such as low- pressure R744.
• low-pressure refers to the refrigerant circulating in the heat exchanger 1 under lower pressure compared to the first fluid HP.
• the heat exchanger 1 may further comprise a first manifold 10 which is suitable for distribution of the first fluid and/ or the second fluid. Analogically, the heat exchanger 1 may also comprise a second manifold 20 spaced apart from the first manifold 10.
• the manifolds 10, 20 may be fixed to the connection blocs 90, 91. In other words, at least one of the manifolds 10, 20 may comprise at least one connection block 90, 91.
• the connection blocks 90, 91 are adapted to provide a fluidal communication between the manifolds 10, 20 and the respective first fluid loop and the second fluid loop.
• the first manifold 10 may further comprise a first cover 11.
• the first cover 11 may further comprise at least a first channel 12 extending along the axis of elongation of the first manifold 10.
• the axis of elongation of the first manifold 10 is arranged parallel with respect to the axis of extension of its first channel 12, so that the distribution of the fluid is provided.
• the first manifold 10 may further comprise a first header 151 comprising a plurality of slots 40 configured to receive the tubes 30, and at least one first distribution plate 152 arranged between the first header 151 and first cover 11.
• the first distribution plate 152 distributes the first fluid and/ or the second fluid between the tubes 30 and the first cover 11.
• the heat exchanger 1 may further comprise the second manifold 20 spaced apart from the first manifold 10.
• the second manifold 20 may further comprise a second cover 21.
• the second cover may further comprise at least a second channel 22 extending along the axis of elongation of the second manifold 20.
• the axis of elongation of the second manifold 20 is arranged parallel with respect to the axis of extension of its second channel 22, so that the distribution of the fluid is provided.
• the second manifold 20 may further comprise a second header 161 comprising a plurality of slots 40 configured to receive the tubes 30 and at least one second distribution plate 162 arranged between the second header 161 and the second cover 21.
• the slots 40 for both first manifold 10 and the second manifold 20 use the same reference as they are substantially the same.
• the first manifold 10 may comprise both first channel 12 and the second channel 22, and the second manifold 20 may comprise the second channel 22 and the first channel 11. Consequently, the first cover 11 may comprise both first passages 111 and the second passages 222, and the second cover 22 may comprise the second passages 222 and the first passages 111. It should be noted that such configuration is dependent on the type of fluid (first fluid or second fluid) which may flow through the first manifold 10 and second manifold. Usually the first manifold 10 may be configured for ingress of the first fluid and the egress of the second fluid, whereas the second manifold 20 may be configured for the egress of the first fluid and the ingress of the second fluid.
• the object of the invention i.e. the heat exchanger 1, herewith comprises the second manifold 20 spaced apart from the firs manifold 10, wherein the first cover 11 comprises one first channel 12 and one second channel 22, and the second manifold 20 comprises one second channel 22 and one first channel 12.
• the channels 12, 22 are fluidly connected with respective blocks 90, 91.
• the other configurations (i.e. location and number) of the channels 12, 22 are also envisaged.
• the first cover 11, and the second cover 21 may be made, for example, out of unitary block of metallic material which was created in process of machining.
• the heat exchanger 1 may further comprise a plurality of tubes 30 configured to provide a fluidal communication between the first manifold 10 and the second manifold 20.
• the intended flow direction of the first fluid HP and the second fluid LP is indicated in the drawings by the respective arrows.
• the tubes 30 may comprise a general axis of elongation which is substantially orthogonal with respect to the axis of elongation of at least first manifold 10.
• the word substantially orthogonal suggests that the angles close to 90 degrees are also envisaged. A small angular position between the axis of extension of the tubes 30 and the axis of extension of the manifolds 10, 20 is thus possible.
• the first cover 11 comprises first passages 111 for the first fluid HP.
• the second cover 21 comprises at least second passages 222 for the second fluid LP, wherein the second passages 222 are configured to provide a fluidal communication between the first cover 11 and the tubes 30.
• the first and the second passages 111, 222 may be in the form of openings configured for optimized flow of the fluid.
• the first and the second passages 111, 222 may have a shaped of an oblong or oval, so that the pressure drop in the heat exchanger is not increased therefore allowing the heat exchanger 1 to operate at desired efficiency.
• the first passages 111 and second passages 222 are fluidly insulated from each other. It means that the first passages 111 are devoid of fluidal communication with the second channel 22 whereas the second passaged are devoid of fluidal communication with the first channel 12.
• the first passages 111 are arranged alternately with the second passages 222, so that first passages 111 are arranged at the different level than the second passages 222.
• the respective level of the first passages 111 and the second passages 222 may be parallel to the main axis of extension of the tubes 30.
• the level of the first passages 111 and the second passages 222 may be determined with respect to the plane which extends in perpendicular with respect to the axis of extension of the first manifold 10 and/ or the plane which extends in perpendicular with respect to the axis of extension of the second manifold 20.
• the plurality of tubes 30 comprises a first tube set 30A and a second tube set 30B.
• the plurality of tubes 30 may be divided according to its function.
• the first tube set 30A and the second tube set 30B are arranged in at least first stack S1 comprising a first stacking direction, wherein the first stacking direction is perpendicular with respect to the axis of elongation of the tubes 30.
• tube set 30A may configured to provide flow of the first fluid HP therein and the second tube set 30B may be configured to provide flow if the second fluid LP therein.
• the first tube set 30A may be regarded a pair of juxtaposed tubes 30, whereas the second tube set 30B may be regarded as a singular tube 30. Therefore, the term tube set shall be interpreted broadly, as the second tube set 30B may comprise singular tube.
• the heat exchanger comprising only one first tube set 30A and only one second tube set 30B may be regarded as the simplest embodiment, yet its performance may be far from required, thus it remain just an example.
• the first stack S1 may comprises several tubes 30 of the first tube set 30A interlaced with the tubes 30 of the second tube set 30B.
• the first tube set 30A may comprise at least a primary tube 31 and a secondary tube 32.
• the primary tube 31 may comprise a first flat section 31A being parallel with respect to axis of elongation of the tubes 30. Further, each primary tube 31 may comprise meandering sections 31B arranged at the terminal ends of the first flat section 31A.
• the meandering sections 31B shall face the same direction. It means that the meandering section 31B shall be so arranged, that the open ends of the primary tube 31 are at the same level, wherein said level is a plane parallel with respect to the first flat section 31A.
• the secondary tube 32 may comprise a second flat section 32A being parallel with respect to axis of elongation of the tubes 30, and second meandering sections 32B arranged at the terminal ends of the second flat section 32A.
• first tube set 30A comprises a gap between the first flat section 31A and the second flat section 32A.
• This gap may be filled with a wavy, metallic structure such as fin 95, so that the heat dissipation is increased.
• the first tube set 30A bears its name also due the fact, that the open ends of the primary tube 31 and the secondary tube 32 may be accommodated in the same, respective slot.
• the slots 40 in the headers receive respective pairs of the primary tubes 31 and the secondary tubes 32, thus the tubes 30 of the first tube set 30A.
• the first tube set 30A may comprise plurality of first micro-channels 50A, wherein the first micro-channels 50A are arranged evenly between the primary tube 31 and a secondary tube 32.
• the second tube set 30B may comprise at least one master tube 33. Therefore the first tube set 30A differs from the second tube set 30B in that said first tube set 30A comprises two juxtaposed tubular portions with meandering sections the first tube set 30A where the contact zone C of the meandering sections 31B, 32B, whereas the second tube set 30B comprises straight tubular portion or portions.
• the master tube 33 may comprise a third flat portion 33A extending along the axis of elongation of the tubes 30 through the entirety of the master tube 33.
• the master tube 33 is substantially flat, in contrast to the primary tube 31 and the secondary tube 32 of the first tube set 30A.
• the hydraulic diameter of the second tube set 30B i.e. the total hydraulic diameter of all the second micro-channels 50B in the cross-section of the master tube 33, may be the same as the hydraulic diameter of the first tube set 30A, i.e. the total hydraulic diameter of all the first micro-channels 50A in the cross-section of the primary tube 31 and the secondary tube 32.
• the hydraulic diameter of the second tube set 30B may be greater than the hydraulic diameter of the first tube set 30A.
• the hydraulic diameter of the second tube set 30B may be smaller than the hydraulic diameter of the first tube set 30A.
• the master tube 33 may comprise a first master tube 33A and a second master tube 33B. Both master tubes 33A, 33B may be substantially flat tube portions which are in contact with each other.
• Fig. 4 wherein the master tube 33 being singular is shown at the upper half of the figure, and the master tube 33 comprising an assembly of first master tube 33A and second master tube 33B is shown in the lower half of the figure. Consequently each of the master tube 33A, 33B may comprise its individual second micro-channels 50B which in total contribute to the hydraulic diameter of the master tube 33.
• the second entry height H2 is defined as the total height of the first master tube 33A and the second master tube 33B, as shown in Fig.4 .
• the master tube 33 of the second tube set 30B may comprise plurality of second micro-channels 50B, wherein the second micro-channels 50B are arranged evenly within the master tube 33.
• the first tube set 30A may comprise the fins interlaced between the primary tube 31 and the secondary tube 32.
• the fin provides a reinforcement and partially allows the heat dissipation.
• the fluid flowing through the housing would rinse the fins and flow past the terminal ends of the first tube set, allowing the heat transfer.
• the housing might comprise at least one inlet and at least one outlet for the fluid.
• I-flow through the housing may be envisaged.
• at least one U-flow through the housing may also be provided.
• a tri-fluid heat exchanger is envisaged.
• the heat exchanger 1 comprises plurality of slots 40 which receive the first tube set 30A and the second tube set 30B, respectively.
• the first tube set 30A may comprise a first entry height H1.
• the first entry height H1 is measured in perpendicular to the axis of elongation of the tubes 30, at the terminal ends of the first tube set 30A where the contact zone C of the meandering sections 31B, 32B is formed.
• the first entry height H1 is smaller than the opening of the slot, so that the tight connection between the two may be formed.
• the second tube set 30B may comprise a second entry height H2 measured in perpendicular to the axis of elongation of the tubes 30 at the terminal ends of the second tube set 30B, i.e. at the terminal ends of the master tube 33.
• the second entry height H2 is smaller than the opening of the slot, so that the tight connection between the two may be formed.
• first entry height H1 is equal to the second entry height H2. This allows forming the slots 40 of one size, without the necessity to adapt the manifolds 10, 20. This also provides liberal approach when it comes to the arrangement of the first tube set 30A and the second tube set 30B within the stack S1.
• the first entry height H1 may be different than the second entry height H2. This however would require adaptation of the slots 40.
• the slots 40 which receive the first tube set 30A need to be bigger compared to the slots 40 receiving the second tube set 30B.
• the change of the first entry height H1 may be substantiated, or rather be the consequence of increasing the hydraulic diameter of the tubes 30 forming the first tube set 30A. Consequently, the hydraulic diameter of the first tube set 30A may be greater than the hydraulic diameter of the second tube set 30B, and so will be its first entry height H1.
• first tube set 30A and the second tube set 30B may be further arranged in a second stack S2 comprising a second stacking direction being parallel to the first stacking direction, wherein the second stack S2 is arranged next to the first stack S1.
• the tubes 30 forming each of the stacks S1, S2 are at the same level, i.e. next to each other and facing the same direction.
• the term "level" may determined in perpendicular to any of the stacking directions S1 or S2. It is preferred that the heat exchanger 1 comprises the first stack S1 and the second stack S2 for optimal performance.

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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)

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Citations (5)

• 2024
  • 2024-08-27 EP EP24196679.5A patent/EP4703665A1/fr active Pending

Patent Citations (5)

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