WO2018229234A1 - Évaporateur à deux couches, en particulier pour circuit de climatisation de véhicule automobile, doté de tubes en u, et circuit de climatisation correspondant - Google Patents

Évaporateur à deux couches, en particulier pour circuit de climatisation de véhicule automobile, doté de tubes en u, et circuit de climatisation correspondant Download PDF

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Publication number
WO2018229234A1
WO2018229234A1 PCT/EP2018/065898 EP2018065898W WO2018229234A1 WO 2018229234 A1 WO2018229234 A1 WO 2018229234A1 EP 2018065898 W EP2018065898 W EP 2018065898W WO 2018229234 A1 WO2018229234 A1 WO 2018229234A1
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WIPO (PCT)
Prior art keywords
evaporator
pass
passes
refrigerating fluid
layer
Prior art date
Application number
PCT/EP2018/065898
Other languages
English (en)
Inventor
Bastien Jovet
Philippe DA SILVA
Original Assignee
Valeo Systemes Thermiques
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Publication date
Application filed by Valeo Systemes Thermiques filed Critical Valeo Systemes Thermiques
Publication of WO2018229234A1 publication Critical patent/WO2018229234A1/fr

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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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • F28D1/0341—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members with U-flow or serpentine-flow inside the conduits
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00321—Heat exchangers for air-conditioning devices
    • B60H1/00335—Heat exchangers for air-conditioning devices of the gas-air type
    • 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

Definitions

  • Evaporator having two layers, in particular for a motor vehicle air conditioning circuit, comprising U-shaped tubes and a corresponding air conditioning circuit
  • the invention relates to an evaporator, in particular for a motor vehicle air conditioning installation.
  • evaporators having two superimposed layers each comprising a plurality of circulation conduits for a refrigerating fluid.
  • Evaporators comprise, on the one hand, a core which is generally constituted by two layers which are formed by a plurality of parallel conduits or channels for the circulation of a refrigerating fluid and, on the other hand, distribution means for the refrigerating fluid which are arranged at the two ends of the layers in order to ensure the distribution and collection of the refrigerating fluid in the different conduits of each of the layers.
  • the conduits are produced either from pairs of plates which are connected and which have a plurality of walls which define channels/passages for the circulation of the refrigerating fluid, or from tubes which are connected at the two ends thereof by collection boxes which allow the passage of the refrigerating fluid from one tube to another.
  • the internal structure of the conduits defines different zones which each form a circulation pass of the refrigerating fluid.
  • tube type evaporators In the case of tube type evaporators, they are internal walls which are provided in the collection boxes which define these passes.
  • the distribution means (configuration of the plates or internal partitioning of the collection boxes) are therefore configured to allow a circulation of the refrigerating fluid in a plurality of passes, with reversal of the direction of flow of the refrigerating fluid from one pass to the following pass.
  • each of the two layers of these evaporators has three or four passes.
  • a flow of air passes through the gaps between the fluid conduits and gives off heat to the refrigerating fluid which changes from the liquid state to the gaseous state.
  • the air flow which is cooled in this manner can particularly be used subsequently for air conditioning the passenger compartment of a vehicle.
  • Evaporators having two layers with a plurality of different fluid paths so as to define in portions of each layer, and/or from one layer to the next, a pathway of the fluid according to U-shaped circuits and/or with intersecting flows (that is to say, in opposite directions) are well-known to the person skilled in the art and are widely described in the prior art.
  • This improvement particularly involves maximising the useful surface- area for the heat exchange between the incident air and the refrigerating fluid.
  • each layer of the evaporator comprises in the lower portion thereof and in the upper portion thereof distribution means for the refrigerating fluid in the layers, also referred to as distributor means.
  • zones of the evaporator located in the region of these distribution means for the refrigerating fluid are not useful for the heat exchange because it is not possible to position at that location intermediate fins which are intended in known manner to be passed through by an air flow and to promote the heat exchange between the refrigerating fluid and the air to be cooled. This consequently limits the useful surface-area for heat exchange between the refrigerating fluid and the air to be cooled.
  • One of the objects of the invention is thus to configure an evaporator having two layers, the structure of which promotes the heat exchange between the refrigerating fluid and the air to be cooled.
  • Another object of the invention is to provide an evaporator having two layers, the structure of which defines for the refrigerating fluid a path which optimises the different circulation passes of the refrigerating fluid relative to each other and improves the evaporation process.
  • the invention proposes an evaporator, in particular for a motor vehicle air conditioning circuit, comprising a stack of planar circulation tubes for a refrigerating fluid forming two layers which extend in parallel planes and which each comprise at least three circulation passes for the refrigerating fluid, the planar tubes delimiting between them air passages so as to cool an incident air flow which flows via the passages through the successive layers of the evaporator.
  • the first layer comprises a first pass which is called an inlet pass of the refrigerating fluid in the evaporator and a last pass which is called an outlet pass of the refrigerating fluid of the evaporator, the inlet and outlet passes being adjacent and the first layer being located at the side of the incident air flow to be cooled.
  • the outlet pass of the heat exchange fluid is located at an edge of the first layer.
  • U-shaped planar tubes allows the refrigerant to be returned to the lower portion or the upper portion of the evaporator in accordance with the orientation of these tubes.
  • the U-shaped path extends in a plane parallel with the air flow to be cooled.
  • U-shaped planar tubes further allows a reduction of the pressure drop at the incident air flow because a portion of fin replaces a portion which beforehand did not allow the flow of the air.
  • the air flows at the right and left outlets of the evaporator can thus be constantly balanced.
  • An evaporator according to the invention further has the advantage that the warmest passes are arranged at the side of the incident air flow and the coldest passes are arranged at the side of the outlet of the air flow of the evaporator.
  • the passes which are passed through last by the refrigerating fluid, that is to say, the coldest passes, are therefore arranged on the second layer.
  • This specific embodiment of the inlet and outlet passes of the evaporator allows optimisation of the homogeneity of the temperature of the cooled air at the outlet of the evaporator.
  • Such a configuration further allows an improvement of the heat exchanges between the evaporator and the air which passes through it because the temperature differential between the air flow passing through the evaporator and the temperature of the refrigerating fluid is maximised.
  • the fact of arranging the fluid outlet pass at an end of the first layer allows implementation of a conventional overheating phase of the refrigerating fluid so that the fluid evaporates completely before injection into the compressor of an air conditioning circuit, for example.
  • the tubes of the stack are stacked alternately with fins, which are also referred to as intermediate members, which are passed through by the incident air flow to be cooled.
  • each layer is constituted by a plurality of parallel conduits which are passed through by the refrigerating fluid, at least one lateral pass comprising more conduits than at least one central pass.
  • a "central pass” is not positioned at the edge of a layer.
  • the relative increase of the number of conduits of a lateral pass, in comparison with a central pass, allows an increase in the useful surface-area of heat exchange of the lateral pass while limiting the surface-area portions which are dedicated to the circulation of the refrigerant between the different passes.
  • the fins which are arranged between the tubes of the lateral passes are longer than the fins which are arranged between the tubes of at least one central pass which is located between the lateral passes.
  • the relative increase of the length of the fins of a lateral pass in comparison with a central pass also allows an increase of the useful surface-area for heat exchange of the lateral pass while limiting the surface-area portions which are dedicated to the circulation of the refrigerant between the different passes.
  • the evaporator comprises six circulation passes of the refrigerating fluid, the first and second layers each comprise three circulation passes of the refrigerating fluid.
  • the first layer successively comprises the last outlet pass, the first pass and a second circulation pass of the refrigerating fluid.
  • the second layer successively comprises a fifth circulation pass, a fourth circulation pass and a third circulation pass of the refrigerating fluid, which are arranged opposite the last outlet pass, the first pass and the second pass of the first layer, respectively.
  • the U-shaped tubes of the lateral passes of a first edge of the evaporator are positioned counter to the U-shaped tubes of the lateral passes of a second edge of the evaporator.
  • each layer is constituted by a plurality of parallel conduits through which the refrigerating fluid passes and which are defined by the tubes, the last pass and the fifth pass comprising between 20% and 40% of the conduits.
  • the last pass and fifth pass comprise approximately 40% of the conduits.
  • the first, second, third and fourth passes therefore comprise approximately 60% of the conduits of the evaporator, that is to say, approximately 30% each.
  • the last and fifth passes comprise approximately 30% of the conduits.
  • the first, second, third and fourth passes therefore comprise approximately 70% of the conduits of the evaporator, that is to say, approximately 35% each.
  • the evaporator comprises eight passes, the first and second layers each comprising four circulation passes of the refrigerating fluid.
  • each pass of the evaporator comprises between thirty and fifty conduits, in which the refrigerant circulates.
  • the invention also relates to an automotive air conditioning circuit comprising at least one evaporator as described above.
  • Figure 1 is a schematic top view of the configuration of the circulation passes of the refrigerating fluid in an evaporator according to a first embodiment of the invention
  • Figure 2 is a perspective view of the evaporator of Figure 1 showing the direction of flow of the fluid in the passes;
  • Figure 3 is a schematic side view of a U-shaped plate used in an evaporator according to the invention
  • Figure 4 is a schematic front view of an evaporator having two layers and two passes of the prior art comprising a stack of U-shaped plates
  • Figure 5 is a schematic front view of the so-called “useful” and “non-useful” front surface-areas of the evaporator according to the first embodiment of the invention
  • Figure 6 is a schematic top view of the configuration of the circulation passes of the refrigerating fluid in an evaporator according to a second embodiment of the invention.
  • Figure 7 is a perspective view of the evaporator of Figure 3 showing the direction of flow of the fluid in the passes.
  • Figure 8 illustrates the pressure and temperature variation lines of the refrigerating fluid which flows in an evaporator.
  • the different embodiments according to the present invention are configured very particularly to optimise the pressure drops suffered by the refrigerating fluid during the different circulation passes in the evaporator, thereby leading to better control of the evaporation process and a better homogeneity of the temperature of the cooled air at the outlet of the evaporator in particular.
  • Figures 1 and 2 illustrate an evaporator 1 according to a first embodiment comprising an evaporator core 10 which is constituted by two adjacent layers 11, 12 which extend in parallel planes.
  • the first layer 11 of the evaporator 1 is located at the side of the inlet of the incident air flow or warm air flow 9A to be cooled while the second layer 12 is located behind the first layer 11, that is to say, at the side of the outlet of the air flow referred to as the cooled air flow 9B of the evaporator 1.
  • Each layer 11, 12 is formed by a plurality of parallel conduits 13 through which a refrigerating fluid passes so as to cool the air flow 9A which successively passes through the first layer 11 and second layer 12.
  • An inlet port 131 and an outlet port 132 for refrigerating fluid are arranged on a lateral face of the evaporator 1.
  • the evaporator 1 is constructed from a stack of planar tubes, each planar tube being formed by two sheet metal plates which are in contact with each other at the peripheral edges thereof so as to define with the internal walls thereof circulation conduits 13 of the refrigerating fluid.
  • conduits 13 are constructed from the individual plates which are connected to each other so as to define a predetermined circulation of the refrigerating fluid.
  • each planar tube There is left between each planar tube a space for the passage of an air flow to be cooled.
  • the plates are configured so as to define fluid distributor means to at least one of the two ends (upper and/or lower end) of the layers.
  • the plates of the evaporator 1 have openings at the upper end, the openings being bordered by collars so as to form an inlet collection space which is connected to the inlet port 131 and an outlet collection space which is connected to the outlet port 132 when the plates are stacked.
  • the evaporator core 10 is divided into six zones or passes which are uniformly distributed here between the two layers 11, 12.
  • circulation pass is intended to be understood to mean the path of the refrigerating fluid in one or more conduits 13 of a layer.
  • first layer 11 and the second layer 12 each comprise three passes.
  • the first layer 11 is divided into three zones in the direction of the length of the evaporator 1, defining from one edge to the other three circulation passes of the refrigerating fluid.
  • the first pass referred to as the inlet pass of the refrigerating fluid
  • the sixth pass 106 referred to as the outlet pass of the refrigerating fluid or last pass, of the evaporator 1 are arranged in the first layer 11 of the evaporator 1.
  • an object of the invention is to provide this inlet pass 101 and outlet pass 106 in an adjacent manner and to position the outlet pass 106 of the fluid at an edge of the first layer 11 (on the left in Figure 1) and therefore near a lateral face of the evaporator.
  • a second pass 102 is arranged in an adjacent manner to the inlet pass 101 of the fluid, at the other edge of the first layer 11 (on the right in Figure 1).
  • the inlet pass 101 is therefore arranged at the centre of the first layer 11, between the outlet pass 106 and a second pass 102.
  • the second layer 12 is also divided into three zones in the direction of the length of the evaporator 1, defining three circulation passes of the refrigerating fluid.
  • This second layer successively has (from right to left in Figure 1) a third pass 103, a fourth pass 104 and a fifth pass 105.
  • the third pass 103 is located at an edge of the second layer 12 (on the right in Figure 1) and is opposite the second pass 102 of the first layer 11.
  • the fifth pass 105 is located at the other edge of the second layer 12 (on the left in Figure 1) and is opposite the outlet pass 106 of the fluid of the first layer 11.
  • the fourth pass 104 which is located opposite the inlet pass 101 of the fluid, is arranged at the centre of the second layer 12, between the fifth pass 105 and the third pass 103.
  • the evaporator 1 comprises six successive passes 101, 102, 103, 104, 105, 106 which define a circulation circuit for the refrigerating fluid between the inlet 131 and the outlet 132 of the fluid of the evaporator 1, with a reversal of the direction of flow of the fluid in each successive pass, as illustrated in Figure 2.
  • the direction of flow of the passes (the passes 103 and 105, for example) adjacent to a given pass (the pass 104) is reversed in relation to the direction of flow of the fluid of this pass (the pass 104).
  • the circulation of the fluid is carried out downwards while for all the passes (the passes 106, 102 and 104) adjacent to this first pass 101, the circulation of the fluid is carried out upwards.
  • This characteristic may be applied to all the passes of the evaporator 1.
  • This specific configuration of the passes of the evaporator 1 is found to be optimum both for maximising the temperature difference between the incident air flow 9A and the cooled air flow 9B after passing through the evaporator 1 and for conserving good temperature homogeneity between the different regions (right/left, upper/lower) of the evaporator 1.
  • the inventors have chosen to arrange the fluid outlet pass 106 which has to be overheated on the first layer 11 of the evaporator 1, this first layer 11 being in contact with the incident air flow 9A (warm air).
  • the first pass 101 and second pass 102 which are also the hottest ones since they are located at the start of the circulation circuit of the fluid are also arranged on the first layer 11.
  • the fifth pass 105 which is the coldest pass since it is located at the end of the circulation circuit of the fluid is arranged counter to the hottest pass, in this instance the last outlet pass 106, on the second layer 12 of the evaporator 1.
  • the third pass 103 and fourth pass 104 of the second layer 12 which are also considered to be cold passes for the same reasons as the fifth pass 105 are also arranged on the second layer 12 counter to (or opposite) the second pass 102 and first pass 101 of the first layer 11.
  • the invention proposes a configuration in which the warmest passes (that is to say, the passes 101, 102 and 106) are arranged on the first layer 11 and the coldest passes (that is to say, the passes 103, 104 and 105) are arranged on the second layer 12 of the evaporator 1 so as to maximise the temperature difference between the incident air flow 9A and the cooled air flow 9B after passing through the evaporator 1.
  • this configuration of the passes in the evaporator 1 allows balancing of the temperature of the passes which are arranged opposite each other (the pass 106 with respect to the pass 105, the pass 101 with respect to the pass 104, the pass 102 with respect to the pass 103) in order to conserve good temperature homogeneity between the different regions of the evaporator 1.
  • the passes 102 and 103 and the passes 105 and 106 which are positioned at the edges of the evaporator 1 are formed from a plurality of planar tubes of a first type, referred to as U-shaped tubes.
  • the plates which form a U-shaped tube define a U-shaped circulation path of the refrigerating fluid within the tube.
  • Figure 3 is a front view of such a plate 2.
  • Such a U-shaped plate 2 is constituted by two longitudinal channels 2a and 2b which comprise at the upper end thereof an intake opening 21 and an outlet opening 23 of the refrigerating fluid, respectively, and, in the region of the lower end thereof, a return passage 22 which allows the refrigerating fluid to flow between the channels 2a and 2b of the U-shaped plate 2, in which it flows in opposite directions.
  • the orientation of the U-shaped plate 2 in Figure 3 is selected in a purely illustrative manner, such a U-shaped plate 2 being able to be positioned in one direction or the other, or in other words with the return passage 22 thereof orientated downwards or upwards.
  • a U-shaped tube is formed here by two U-shaped plates 2 which are arranged one counter to the other, the channels 2a, 2b of the two opposing plates forming conduits 13 which each belong to a pass.
  • Figure 5 is a schematic front view, at the side of the second layer 12, of the evaporator 1 according to the first embodiment of the invention.
  • the evaporator 1 comprises at each of the edges thereof a pair of passes 102 and 103 and 105 and 106 which are constituted by a plurality of parallel U-shaped tubes which connect the two layers 11 and 12 to each other.
  • the U-shaped tubes of these passes 102, 103, 105, 106 are obtained by assembling U-shaped plates identical to the one illustrated in Figure 3.
  • the U-shaped tubes which constitute the passes 102 and 103 are arranged so that the intake and outlet openings 21, 23 thereof for the refrigerant are positioned in the lower portion of the passes and the return passage 22 thereof is positioned in the upper portion.
  • the refrigerant is returned to the upper portion of the passes 102 and 103, which is included in the useful zone 3a of heat exchange between the refrigerant and the air which passes through the evaporator 1.
  • the U-shaped tubes which constitute the passes 105 and 106 are arranged in opposite directions in relation to the passes 102 and 103 at the other edge.
  • the U-shaped tubes of the passes 105 and 106 are arranged so that the intake and outlet openings 21, 23 thereof for the refrigerant are positioned in the upper portion of the passes and the return passage 22 thereof is positioned in the lower portion.
  • the refrigerant is returned to the lower portion of the passes 105 and 106, which is included in the useful zone 3a of heat exchange between the refrigerant and the air which passes through the evaporator 1.
  • the surface-area portions of the evaporator 1 which are located in the region of the distribution means and collection means of the refrigerant in the passes do not allow a satisfactory heat exchange and therefore form non-useful zones 3b of heat exchange.
  • Such a configuration of the evaporator 1 allows permanent balancing of the air flows in the region of the right and left outlets of the air conditioning circuit because of the central symmetry observed in the arrangement of the evaporator 1.
  • the tubes are not U-shaped unlike the lateral passes and have at the upper and lower ends thereof inlet and outlet openings for the refrigerating fluid.
  • the non-useful zones 3b of heat exchange extend for these central passes 101, 104 at the upper and lower ends of the bundle.
  • Figure 4 is a schematic view of an evaporator which has two layers and two passes (that is to say, one pass per layer, the passes being in opposite directions) of the prior art and which is constituted by a stack of U-shaped plates which are identical to the one illustrated in Figure 3.
  • the U-shaped tubes which are formed from these plates allow the refrigerant to be returned to the lower portion of the passes.
  • a "non-useful" surface-area portion 3b is located at the upper end of the passes in the region of the distribution and collection means of the refrigerating fluid.
  • This surface-area portion 3b of the front surface-area of the evaporator is used for the circulation of the refrigerating fluid and is therefore not useful for the heat exchange between the air and the refrigerant, which reduces the thermal power level of the evaporator.
  • the front surface-area dedicated to the circulation of refrigerating fluid is 15%.
  • Fins or intermediate members which extend as far as the bottom of the passes can be arranged between the U-shaped tubes in order to promote the heat exchange between the air and the refrigerant.
  • these fins cannot extend into the upper portion of the passes.
  • the surface-area portion which is covered by these fins is therefore described as a "useful surface-area portion" 3a for heat exchange between the air passing through the fins and the refrigerating fluid.
  • the extent of the useful surface-area portion of the evaporator 1 of the first embodiment is increased by 5%.
  • this useful surface- area portion is increased by 6%.
  • the evaporator 1 has a central symmetry so that the air flows passing through the right and left portions of the evaporator are balanced.
  • the front surface-area of heat exchange between the air and the refrigerant which flows in the evaporator 1 is increased in comparison with the known evaporators having two layers which allows the heat exchange to be improved.
  • first layer 11 and second layer 12 have identical dimensions.
  • the six zones which define the six passes of the evaporator 1 have such dimensions that the sixth pass 106 and fifth pass 105 together comprise between 20% and 40% of the total conduits of the evaporator 1.
  • the zones which define the different passes of the evaporator 1 have dimensions such that the sixth pass 106 and the fifth pass 105 together comprise approximately 40% of the total conduits of the evaporator 1, that is to say, approximately 20% each. Approximately 60% of the remaining conduits are included in the first pass 101, second pass 102, third pass 103 and fourth pass 104, that is to say, approximately 15% of the total conduits of the evaporator 1 per pass.
  • the zones which define the different passes of the evaporator have such dimensions that the sixth and fifth passes 106, 105 together comprise approximately 30% of the total conduits of the evaporator 1, that is to say, approximately 15% each.
  • the first pass 101, second pass 102, third pass 103 and fourth pass 104 therefore comprise approximately 70% of the remaining conduits, that is to say, approximately 17.5% each of the total conduits of the evaporator 1.
  • each pass of the evaporator 1 comprises between thirty and fifty conduits 13.
  • At least one lateral pass comprises more parallel conduits than at least one central pass.
  • the relative increase of the number of conduits of a lateral pass in comparison with a central pass allows an increase of the useful surface-area for heat exchange of the lateral pass while limiting the surface-area portions which are dedicated to the circulation of the refrigerant between the different passes.
  • the fins of at least one lateral pass are longer than the fins of at least one central pass.
  • the relative increase of the length of the fins of a lateral pass, in comparison with a central pass, also allows an increase of the useful surface-area for heat exchange of the lateral pass while limiting the surface-area portions which are dedicated to the circulation of the refrigerant between the different passes.
  • the non-useful zones 3b for the heat exchange are covered with an anti- corrosion coating.
  • Figures 6 and 7 illustrate an evaporator 100 according to a second embodiment of the invention.
  • the evaporator 100 comprises an evaporator core 10 which is constituted by two adjacent layers 11, 12 which extend in parallel planes.
  • the first layer 11 of the evaporator 1 is located at the side of the inlet of the incident air flow 9A which is intended to be cooled while the second layer 12 is located behind the first layer 11, that is to say, at the side of the outlet of the cooled air flow 9B of the evaporator 1.
  • Each layer 11, 12 is formed by a plurality of parallel conduits 13 through which a refrigerating fluid passes so as to cool the incident air flow 9A which successively passes through the first layer 11 and second layer 12.
  • the evaporator core 10 is divided into eight zones, or passes, which are distributed uniformly here over the two layers 11, 12.
  • the first layer 11 and the second layer 12 each comprise four passes.
  • the configuration of the eight passes of the evaporator 100 is substantially similar to that of the evaporator 1 described above.
  • the evaporator 100 comprises eight successive passes 111, 112, 113, 114, 115, 116, 117, 118 which define a circulation circuit of the refrigerating fluid between the inlet 131 and the outlet 132 of the fluid of the evaporator 100 with reversal of the direction of flow of the fluid for each successive pass, as illustrated in Figure 4.
  • the inlet 131 and the outlet 132 of the refrigerating fluid are arranged in the first layer 11 of the evaporator 100.
  • the first layer 11 therefore comprises the first pass 111, referred to as the inlet pass of the fluid, and the eighth pass 118, referred to as the last pass or outlet pass of the fluid, of the evaporator 1.
  • the invention proposes the provision of these passes 111, 118 in an adjacent manner and the placement of the last pass 118 at an edge of the first layer 11 (on the left in Figure 3).
  • This specific configuration of the passes of the evaporator is found to be optimum both for maximising the temperature difference between the incident air flow 9A and the cooled air flow 9B after passing through the evaporator 100 and for conserving good temperature homogeneity between the different regions (right/left, upper/lower) of the evaporator 100.
  • the first pass 111, second pass 112 and third pass 113 which are also the warmest because they are located at the start of the circulation circuit of the fluid are also arranged on the first layer 11.
  • the seventh pass 117 which is the coldest pass because it is located at the end of the circulation circuit of the fluid is arranged counter to the warmest pass, that is to say, the eighth and last pass 118, on the second layer 12 of the evaporator 100.
  • the fourth pass 114, fifth pass 115 and sixth pass 116 which are also considered to be cold passes for the same reasons as the seventh pass 117 are also arranged on the second layer 12 counter to the third pass 113, second pass 112 and first pass 111, respectively.
  • the invention proposes a configuration in which the warmest passes (the passes 111, 112, 113 and 118 in this instance) are arranged on the first layer 11 and the coldest passes (the passes 114, 115, 116 and 117 in this instance) are arranged on the second layer 12 of the evaporator 100 so as to maximise the temperature difference between the incident air flow 9A and the cooled air flow 9B after passing through the evaporator 100.
  • this configuration of the passes in the evaporator 100 allows balancing of the temperature of the passes which are arranged opposite each other (the pass 117 with respect to the pass 118, the pass 116 with respect to the pass 111, the pass 115 with respect to the pass 112 and the pass 114 with respect to the pass 113) in order to conserve good temperature homogeneity between the different regions of the evaporator 100.
  • the circulation of the fluid is carried out downwards while for all the passes (the passes 118, 112 and 116) adjacent to this first pass 111, the circulation of the fluid is carried out upwards.
  • This feature can be applied to all the other passes of the evaporator 100.
  • the passes 113 and 114 and the passes 117 and 118 which are positioned at the edges of the evaporator 1 are constituted by a plurality of parallel U-shaped tubes which connect the two layers 11 and 12 to each other.
  • edge or lateral passes have the same technical advantages as those set out in the context of an evaporator 10 according to the first embodiment, as described above.
  • the U-shaped tubes which constitute the passes 117 and 118 are arranged so that the intake and outlet openings 21, 23 thereof for the refrigerant are positioned in the upper portion of the passes and the return passage 22 is positioned in the lower portion.
  • the U-shaped tubes which constitute the passes 113 and 114 are arranged so that the intake and outlet openings 21, 23 thereof for the refrigerant are positioned in the upper portion of the passes and the return passage 22 is positioned in the lower portion.
  • the two embodiments described above relate to evaporators having two layers with three and four circulation passes per layer, respectively.
  • the evaporator according to the invention may be implemented in HVAC housings (Heating, Ventilation and/or Air Conditioning) of motor vehicles.
  • HVAC housings Heating, Ventilation and/or Air Conditioning
  • the evaporator can be fixed in the container by means of a connection of the slide type, in which the upper and lower portions of the evaporator slide in corresponding grooves which are arranged in the container.

Landscapes

  • 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)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'invention concerne un évaporateur à deux couches, en particulier pour un circuit de climatisation d'un véhicule automobile, comprenant des tubes en U, et un circuit de climatisation correspondant.L'évaporateur (1), destiné en particulier à un circuit de climatisation d'un véhicule automobile, comprend un empilement de tubes de circulation plats pour un fluide frigorigène, les tubes plats formant deux couches (11, 12) s'étendant dans des plans parallèles et comprenant chacun au moins trois passages de circulation pour le fluide frigorigène, les tubes plats délimitant entre eux des passages d'air de manière à refroidir un écoulement d'air incident (9A) s'écoulant par l'intermédiaire des passages à travers les couches successives de l'évaporateur (1).Selon l'invention, la première couche (11) comprend un passage d'entrée (101) et un passage de sortie (106) du fluide frigorigène de l'évaporateur (1), le passage d'entrée et le passage de sortie (101, 106) étant adjacents, les tubes plats formant les passages latéraux de l'évaporateur définissant un circuit de circulation en U du fluide frigorigène dans une direction parallèle à l'écoulement d'air incident (9A) à refroidir.
PCT/EP2018/065898 2017-06-14 2018-06-14 Évaporateur à deux couches, en particulier pour circuit de climatisation de véhicule automobile, doté de tubes en u, et circuit de climatisation correspondant WO2018229234A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1755383A FR3067797B1 (fr) 2017-06-14 2017-06-14 Evaporateur a deux nappes, notamment pour circuit de climatisation de vehicule automobile, comprenant des tubes en "u" et circuit de climatisation correspondant
FR1755383 2017-06-14

Publications (1)

Publication Number Publication Date
WO2018229234A1 true WO2018229234A1 (fr) 2018-12-20

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Application Number Title Priority Date Filing Date
PCT/EP2018/065898 WO2018229234A1 (fr) 2017-06-14 2018-06-14 Évaporateur à deux couches, en particulier pour circuit de climatisation de véhicule automobile, doté de tubes en u, et circuit de climatisation correspondant

Country Status (2)

Country Link
FR (1) FR3067797B1 (fr)
WO (1) WO2018229234A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114475154A (zh) * 2022-02-11 2022-05-13 浙江创立汽车空调有限公司 一种车载空调用高效稳定的一体化冷暖蒸发器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5024269A (en) * 1989-08-24 1991-06-18 Zexel Corporation Laminated heat exchanger
JPH11159990A (ja) * 1997-09-24 1999-06-15 Showa Alum Corp 蒸発器
US20020000309A1 (en) * 2000-06-30 2002-01-03 Kim Jae Hoon Heat exchanger having superheated coolant bypass passage
US20030070797A1 (en) * 2000-09-27 2003-04-17 Calsonic Kansei Corporation Stacked-type evaporator

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5024269A (en) * 1989-08-24 1991-06-18 Zexel Corporation Laminated heat exchanger
JPH11159990A (ja) * 1997-09-24 1999-06-15 Showa Alum Corp 蒸発器
US20020000309A1 (en) * 2000-06-30 2002-01-03 Kim Jae Hoon Heat exchanger having superheated coolant bypass passage
US20030070797A1 (en) * 2000-09-27 2003-04-17 Calsonic Kansei Corporation Stacked-type evaporator

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114475154A (zh) * 2022-02-11 2022-05-13 浙江创立汽车空调有限公司 一种车载空调用高效稳定的一体化冷暖蒸发器
CN114475154B (zh) * 2022-02-11 2023-06-23 浙江创立汽车空调有限公司 一种车载空调用高效稳定的一体化冷暖蒸发器

Also Published As

Publication number Publication date
FR3067797A1 (fr) 2018-12-21
FR3067797B1 (fr) 2020-06-12

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