WO2020170651A1 - Échangeur de chaleur composé - Google Patents

Échangeur de chaleur composé Download PDF

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Publication number
WO2020170651A1
WO2020170651A1 PCT/JP2020/000822 JP2020000822W WO2020170651A1 WO 2020170651 A1 WO2020170651 A1 WO 2020170651A1 JP 2020000822 W JP2020000822 W JP 2020000822W WO 2020170651 A1 WO2020170651 A1 WO 2020170651A1
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WIPO (PCT)
Prior art keywords
heat exchanger
heat
fin
fins
tank
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PCT/JP2020/000822
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English (en)
Japanese (ja)
Inventor
隆一郎 稲垣
孝博 宇野
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株式会社デンソー
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Publication of WO2020170651A1 publication Critical patent/WO2020170651A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F1/24—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 and extending transversely
    • F28F1/30—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 and extending transversely the means being attachable to the element
    • 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
    • F28F1/24—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 and extending transversely
    • F28F1/32—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 and extending transversely the means having portions engaging further tubular elements

Definitions

  • the present disclosure relates to a combined heat exchanger.
  • the composite heat exchanger is a unit that combines multiple heat exchangers and is installed in a vehicle, for example. In each of the heat exchangers included in the combined heat exchanger, heat is exchanged between the air and the fluid.
  • Patent Document 1 describes a composite heat exchanger having a configuration in which a condenser for an air conditioner and a radiator for cooling an engine are combined. In the condenser, the refrigerant is cooled by heat exchange with air. In the radiator, the cooling water is cooled by heat exchange with air.
  • Each of the heat exchangers that compose the composite heat exchanger includes a tube through which the fluid passes, and fins arranged between the tubes adjacent to each other.
  • the fins provided in each heat exchanger are integrated to reduce the number of parts. In such a configuration, the fins of one heat exchanger and the fins of the other heat exchanger are connected to each other.
  • the temperature of the cooling water that flows into the radiator for engine cooling is often higher than the temperature of the refrigerant that flows into the condenser. Therefore, there is a concern that the heat from the radiator is transferred to the capacitor by heat conduction through the connection portion of the fins, and heat dissipation in the capacitor may not be sufficiently performed.
  • the inventors of the present invention are studying positively conducting heat conduction between the plurality of heat exchangers included in the composite heat exchanger via the fins. For example, when the temperature of the cooling water becomes lower than the temperature of the refrigerant, the heat from the condenser is transferred to the radiator by heat conduction through the fins so that the refrigerant is circulated. The operation load of the compressor can be reduced. As a result, it becomes possible to enhance the energy efficiency of the refrigeration cycle provided with the composite heat exchanger.
  • the fins have multiple louvers to promote heat exchange with air, specifically heat transfer.
  • louvers impede heat conduction, prioritizing heat conduction necessitates a reduction in the number of louvers, and as a result, heat transfer in the fins is reduced, and the heat exchanger of the entire combined heat exchanger is reduced. Performance will decrease.
  • the present disclosure aims to provide a composite heat exchanger capable of increasing energy efficiency by making both heat conduction and heat transfer between heat exchangers compatible.
  • a composite heat exchanger includes a first heat exchanger that performs heat exchange between a first fluid and air, and a second heat exchanger that performs heat exchange between a second fluid and air. , Is provided.
  • the first heat exchanger has a plurality of first tubes through which the first fluid passes and first fins arranged between the first tubes adjacent to each other.
  • the second heat exchanger has a plurality of second tubes through which the second fluid passes and second fins arranged between the second tubes adjacent to each other.
  • the first fin and the second fin are connected to each other via a connecting portion, and are configured as an integral fin as a whole.
  • a heat conduction promoting portion for promoting heat conduction between the first fin and the second fin is formed in the connection portion. When the direction in which the first heat exchanger and the second heat exchanger are arranged side by side is the air flow direction, the heat conduction promoting portion is at least one end of the connecting portion along the air flow direction. It is formed so as to extend to a certain position.
  • the first fins of the first heat exchanger and the second fins of the second heat exchanger are connected to each other through the connecting portion. Further, a heat conduction promoting portion is formed in the connecting portion, which promotes heat conduction between the first fin and the second fin.
  • the configuration of the composite heat exchanger as described above can be applied not only to the composite heat exchanger in which the radiator and the condenser are combined, but also to other composite heat exchangers.
  • it can be applied to a composite heat exchanger in which a radiator for cooling the motor generator and a heat exchanger for cooling the battery are combined.
  • a composite heat exchanger capable of increasing energy efficiency by making both heat conduction and heat transfer between heat exchangers compatible.
  • FIG. 1 is a diagram showing an overall configuration of a composite heat exchanger according to the first embodiment.
  • FIG. 2 is an enlarged view of the portion A of FIG.
  • FIG. 3 is a diagram showing a configuration of fins included in the composite heat exchanger of FIG. 1.
  • FIG. 4 is a diagram schematically showing a part of the AA cross section and a part of the BB cross section of FIG. 3, respectively.
  • FIG. 5 is a figure for demonstrating the effect of having formed the heat conduction promotion part in the fin.
  • FIG. 6 is a diagram for explaining the relationship between the shape of the fin and the heat radiation amount.
  • FIG. 7 is a figure which shows the structure of the fin with which the composite-type heat exchanger which concerns on the modification of 1st Embodiment is equipped.
  • FIG. 7 is a figure which shows the structure of the fin with which the composite-type heat exchanger which concerns on the modification of 1st Embodiment is equipped.
  • FIG. 8 is a figure which shows the structure of the fin with which the composite-type heat exchanger which concerns on 2nd Embodiment is provided.
  • FIG. 9 is a figure which shows the structure of the fin with which the composite-type heat exchanger which concerns on 3rd Embodiment is provided.
  • FIG. 10 is a figure which shows the structure of the fin with which the composite-type heat exchanger which concerns on 4th Embodiment is provided.
  • FIG. 11 is a figure which shows the structure of the fin with which the composite-type heat exchanger which concerns on 5th Embodiment is equipped.
  • the composite heat exchanger 10 is mounted on a vehicle (not shown) and is for adjusting the temperature of various fluids circulating in the vehicle.
  • the vehicle in which the combined heat exchanger 10 is mounted is an electric vehicle that travels by the driving force of the motor generator.
  • the composite heat exchanger 10 includes a radiator 100 and a condenser 200.
  • the composite heat exchanger 10 is configured by combining these two heat exchangers and integrating them.
  • the radiator 100 is a heat exchanger for exchanging heat between cooling water and air.
  • the cooling water circulates between the radiator 100 and vehicle-mounted electric devices such as a motor generator, an inverter, and a battery.
  • vehicle-mounted electric devices such as a motor generator, an inverter, and a battery.
  • the cooling water that has passed through the vehicle-mounted electric device and has become high temperature is cooled by air when passing through the radiator 100, and the temperature thereof is lowered.
  • a cooling water pump (not shown) is provided on the way of the circulation path of the cooling water.
  • the cooling water pump operates by electric power supplied from a battery mounted on the vehicle.
  • the radiator 100 is one of the heat exchangers included in the composite heat exchanger 10 as described above, and corresponds to the “first heat exchanger” in the present embodiment.
  • the cooling water used for heat exchange in the radiator 100 corresponds to the "first fluid" in the present embodiment.
  • the condenser 200 is a heat exchanger for exchanging heat between the refrigerant and the air.
  • the condenser 200 is a part of an air conditioner mounted on the vehicle, and is provided as a part of a heat pump system constituting the air conditioner. When the air conditioner cools the vehicle interior, the condenser 200 radiates heat from the refrigerant to the air.
  • a refrigerant compressor (not shown) is provided on the way of the refrigerant circulation path. The refrigerant compressor operates by electric power supplied from a battery mounted on the vehicle.
  • the condenser 200 is one of the heat exchangers included in the composite heat exchanger 10 as described above, and corresponds to the “second heat exchanger” in the present embodiment.
  • the refrigerant used for heat exchange in the condenser 200 corresponds to the "second fluid" in this embodiment.
  • the radiator 100 includes tanks 110 and 120, a tube 130, and fins 310.
  • the tank 110 is a container for receiving cooling water supplied from the outside and distributing the cooling water to the tubes 130.
  • the tank 110 is configured as an elongated rod-shaped container extending in the vertical direction.
  • a separator (not shown) is arranged at a position substantially in the center along the vertical direction.
  • the internal space of the tank 110 is divided into two upper and lower spaces by the separator.
  • a separator 410 similar to this is also arranged in the internal space of the tank 120.
  • the shape of the separator arranged inside the tank 110 is the same as the shape of the separator 410 shown in FIG.
  • a supply port 141 is provided in a portion of the tank 110 above the separator. Further, a supply port 143 is provided in a portion of the tank 110 below the separator.
  • the supply ports 141 and 143 are both inlets for cooling water supplied from the outside.
  • the tank 120 is a container for receiving the cooling water that has passed through the tube 130 and discharging the cooling water to the outside. Like the tank 110, the tank 120 is configured as an elongated rod-shaped container extending along the vertical direction. 1 and 2, in order to show the internal structure of the tank 120, a state in which the tank 120 is disassembled together with a tank 220 described later is shown.
  • a separator 410 is arranged inside the tank 120 at a position substantially in the center along the vertical direction.
  • the internal space of the tank 120 is divided into two upper and lower spaces by the separator 410.
  • the separator 410 is arranged at the same height as the separator arranged inside the tank 110.
  • a discharge port 142 is provided in a portion of the tank 120 above the separator 420. Further, a discharge port 144 is provided in a portion of the tank 120 below the separator 420. Each of the discharge ports 142 and 144 is an outlet of the cooling water discharged from the tank 120 to the outside.
  • the tube 130 is a tubular member in which a flow path for cooling water is formed.
  • the tube 130 has a flat shape in a cross section perpendicular to its longitudinal direction.
  • the tube 130 is arranged between the tank 110 and the tank 120 in a state where the normal direction of the main surface is along the vertical direction.
  • a plurality of tubes 130 are provided, and they are arranged so as to be lined up along the longitudinal direction of the tank 110.
  • Each tube 130 has one end along the longitudinal direction connected to the tank 110 and the other end connected to the tank 120.
  • the inner space of the tank 110 and the inner space of the tank 120 are communicated with each other by the tubes 130.
  • the tube 130 is a tube through which the cooling water that is the first fluid passes, and corresponds to the “first tube” in the present embodiment.
  • the fins 310 are corrugated fins formed by bending a metal plate in a wavy shape. As shown in FIG. 2, the fins 310 are arranged at positions between the tubes 130 adjacent to each other. That is, in the radiator 100, the tubes 130 and the fins 310 are arranged so as to be alternately arranged in the vertical direction. The fins 310 are not shown in FIG.
  • the fins 310 have their peaks and valleys apex brazed to the adjacent tube 130. By providing the fins 310, the contact area with the air is increased, and the efficiency of heat exchange in the radiator 100 is improved.
  • the fin 310 corresponds to the “first fin” in this embodiment. The specific configuration of the fin 310 will be described later.
  • the cooling water supplied from the supply port 141 to the tank 110 is distributed to the tubes 130 located above the separator in the tank 110. After passing through each tube 130, the cooling water flows into a space above the separator 410 in the tank 120, and is discharged to the outside from the discharge port 142.
  • the cooling water is cooled by heat exchange with the air passing outside when passing through the inside of each tube 130 above the separator.
  • the air is sent by a fan (not shown) arranged near the composite heat exchanger 10.
  • the direction in which air passes through the composite heat exchanger 10 is a direction perpendicular to both the longitudinal direction of the tank 110 and the longitudinal direction of the tube 130, and in FIG. It is the direction to go.
  • the cooling water supplied from the supply port 143 to the tank 110 is distributed to the tubes 130 below the separator in the tank 110. After passing through each tube 130, the cooling water flows into the space inside the tank 120 below the separator 410, and is discharged from the discharge port 144 to the outside.
  • the cooling water is cooled by heat exchange with the air passing outside when passing through the inside of each tube 130 below the separator.
  • the air is sent by the fan (not shown) as described above.
  • the upper part and the lower part of the radiator function as separate heat exchangers. For example, if the cooling water after passing through the motor generator is supplied from the supply port 141 and the cooling water after passing through the battery is supplied from the supply port 143, the respective cooling targets are maintained at different temperatures. It becomes possible to do.
  • the direction in which air passes through the radiator 100 is the x direction, and the x axis is set along the same direction.
  • the direction perpendicular to the x direction and extending from the tank 110 to the tank 120 is the y direction, and the y axis is set along the same direction.
  • a direction that is perpendicular to both the x direction and the y direction and that goes from the lower side to the upper side along the longitudinal direction of the tank 110 is the z direction, and the z axis is set along the same direction. doing.
  • description will be made using the x direction, the y direction, and the z direction defined as above.
  • the condenser 200 includes tanks 210 and 220, a tube 230, and a fin 320.
  • the tank 210 is a container for receiving the refrigerant flowing from one of the tubes 230 and distributing the refrigerant to another tube 230.
  • the tank 210 is configured as an elongated rod-shaped container extending along the z direction.
  • the tank 210 is arranged at a position adjacent to the tank 110 of the radiator 100 on the x direction side.
  • the tank 210 and the tank 110 are integrated with each other.
  • the tank 220 is a container for receiving the refrigerant supplied from the outside and distributing the refrigerant to the tubes 230.
  • the tank 220 also functions as a container for receiving the refrigerant that has passed through the tubes 230 and discharging the refrigerant to the outside.
  • the tank 220 is configured as an elongated rod-shaped container extending along the z direction.
  • the tank 220 is arranged at a position adjacent to the tank 120 of the radiator 100 on the x direction side.
  • the tank 220 and the tank 120 are integrated with each other.
  • a separator 420 is arranged inside the tank 220 at a position below the center along the vertical direction.
  • the internal space of the tank 220 is divided into two upper and lower spaces by the separator 420.
  • a supply port 241 is provided in a portion of the tank 220 above the separator 420.
  • the supply port 241 is an inlet for the refrigerant supplied from the outside.
  • a discharge port 242 is provided in a portion of the tank 220 below the separator 420.
  • the discharge port 242 is an outlet for the refrigerant discharged from the tank 220 to the outside.
  • the tube 230 is a tubular member having a flow passage formed therein through which a refrigerant flows.
  • the tube 230 has a flat shape in a cross section perpendicular to its longitudinal direction.
  • the tube 230 is arranged between the tank 210 and the tank 220 in a state where the normal line direction of the main surface is along the vertical direction.
  • a plurality of tubes 230 are provided, and they are arranged so as to be lined up along the longitudinal direction of the tank 210.
  • Each tube 230 has one end along the longitudinal direction connected to the tank 210 and the other end connected to the tank 220.
  • the inner space of the tank 210 and the inner space of the tank 220 are connected to each other by respective tubes 230.
  • the tube 230 is a tube through which the refrigerant that is the second fluid passes, and corresponds to the “second tube” in the present embodiment.
  • the number of tubes 230 is the same as the number of tubes 130. Further, the height of the position where each tube 230 is arranged is the same as the height of the position where each tube 130 is arranged.
  • the fin 320 is a corrugated fin formed by bending a metal plate in a wavy shape. As shown in FIG. 3, the fins 320 are arranged at positions between the tubes 230 adjacent to each other. That is, in the capacitor 200, the tubes 230 and the fins 320 are arranged so as to be alternately arranged in the vertical direction.
  • the fins 320 have their peaks and valleys apex welded to the adjacent tube 230. Since the fins 320 are provided, the contact area with the air is increased, and the efficiency of heat exchange in the condenser 200 is improved.
  • the fin 320 corresponds to the “second fin” in this embodiment. The specific configuration of the fin 320 will be described later.
  • the refrigerant supplied from the supply port 241 to the tank 220 is distributed to each tube 230 above the separator 420 in the tank 220.
  • the refrigerant is supplied to the tank 210 through each tube 230.
  • the refrigerant supplied to the tank 210 is distributed to the tubes 230 below the separator 420 in the tank 220.
  • the refrigerant passes through these tubes 230, flows into the space below the separator 420 in the tank 220, and is then discharged from the discharge port 242 to the outside.
  • the refrigerant When passing through the inside of each tube 230 above the separator 420, the refrigerant is cooled by heat exchange with the air passing through the outside, and changes from a gas phase to a liquid phase.
  • the air is the air after passing through the radiator 100.
  • the direction in which the radiator 100 and the condenser 200 are lined up is the x direction, that is, the air flow direction.
  • the refrigerant that has changed to the liquid phase due to the above heat exchange is cooled again by heat exchange with the air when passing through the inside of each tube 230 below the separator 420. Thereby, the degree of supercooling of the refrigerant is increased.
  • a portion of the radiator 100 below the separator 420 functions as a so-called “subcool portion”.
  • FIG. 3 illustrates a state in which a pair of fins 310 and fins 320 arranged at the same height as each other are viewed along the y direction. Further, in FIG. 3, a pair of upper and lower tubes 130 to which the fins 310 are joined and a pair of upper and lower tubes 230 to which the fins 320 are joined are also drawn.
  • the fins 310 and the fins 320 arranged at the same height are connected to each other via a connecting portion 330, and the whole is configured as an integral fin 300.
  • the configuration is the same for all the fins 310 and the fins 320. That is, in the composite heat exchanger 10, the fins 300 are shared between the radiator 100 and the condenser 200.
  • the boundary between the portion of the fin 300 that is joined to the tube 130 and the portion that is not joined along the x direction is indicated by a dotted line DL21.
  • the boundary between the portion of the fin 300 joined to the tube 230 and the portion not joined to the tube 230 along the x direction is indicated by a dotted line DL22.
  • the connecting portion 330 is a portion of the fin 300 between the dotted lines DL21 and DL22. In FIG. 3, the range of such a connecting portion 330 is indicated by an arrow AR2.
  • FIG. 4(A) schematically shows a part of the AA cross section of FIG.
  • FIG. 4B a part of the BB cross section of FIG. 3 is schematically shown.
  • the fin 300 is formed with a plurality of louvers 341 and 342.
  • the louvers 341 and 342 are formed by forming a plurality of cut CTs in the z direction on the fin 300, and then twisting and deforming strip-shaped portions between the cut CTs adjacent to each other in the fin 300.
  • the heat transfer coefficient is improved by disturbing the flow of the passing air, and heat transfer with the air is promoted.
  • the dimension of the louvers 341 and 342 along the z direction is also referred to as “louver length” below.
  • the z direction is a direction in which a plurality of tubes 130 or tubes 230 are arranged.
  • the above louver length can be said to be the dimension of the louvers 341 and 342 along the stacking direction.
  • the louver length of the fin 300 is shorter in the connection portion 330 and its vicinity than in other portions.
  • the louvers shortened in this way are indicated as “louvers 342”, and the other louvers are indicated as “louvers 341”.
  • the position of the end portion on the ⁇ x direction side in the range where the louver 342 is formed is indicated by a dotted line DL11. Further, the position of the end portion on the x direction side in the range where the louver 342 is formed is indicated by the dotted line DL12.
  • heat conduction promoting section 350 the portion between the dotted line DL11 and the dotted line DL12 is also referred to as “heat conduction promoting section 350” below.
  • the range of such a heat conduction promoting unit 350 is indicated by an arrow AR1.
  • the heat conduction promoting unit 350 is formed to promote heat conduction between the fin 310 that is the first fin and the fin 320 that is the second fin. As described above, the louver length of the heat conduction promoting portion 350 is shorter than that of the other portions, so that heat conduction between the fins 310 and 320 is promoted.
  • FIG. 5(A) schematically shows the configuration of the composite heat exchanger 10 according to the comparative example.
  • the vehicle on which the composite heat exchanger 10 is mounted is not the electric vehicle as in the present embodiment but a vehicle equipped with an engine. Therefore, in this comparative example, the high-temperature cooling water that has passed through the engine is supplied to the radiator 100. As a result, the temperature of the cooling water flowing into the radiator 100 is significantly higher than the temperature of the refrigerant flowing into the condenser 200.
  • the heat from the radiator 100 may be transferred to the capacitor 200 by heat conduction via the connection portion 330 of the fin 300, and the heat dissipation in the capacitor 200 may not be sufficiently performed. Therefore, in this comparative example, the width dimension of the connecting portion 330 along the z direction is reduced by forming the cut 390 in the fin 300. This suppresses heat conduction through the connecting portion 330 and prevents the above problems from occurring.
  • FIG. 5B schematically shows the structure of the composite heat exchanger 10 according to this embodiment.
  • the temperature of the cooling water supplied to the radiator 100 is low because the combined heat exchanger 10 is mounted on the electric vehicle.
  • the cooling of the refrigerant in the condenser 200 is performed more efficiently. As a result, it becomes possible to reduce the operation load of the refrigerant compressor provided in the refrigeration cycle.
  • the heat conduction promoting section 350 is formed in the connection section 330.
  • the amount of heat transfer between the radiator 100 and the condenser 200 is increased, and the operating load of the refrigerant compressor is reduced as described above.
  • the condenser 200 which is an outdoor unit
  • heat is transferred from the radiator 100 to the condenser 200 via the heat conduction promoting unit 350.
  • frost attached to the tubes 230 and the fins 320 that have become low temperature can be removed by the heat transfer from the radiator 100.
  • the heat conduction promoting portion 350 in the present embodiment is formed not only in the connecting portion 330 but also in a range extending outside the connecting portion 330.
  • the heat conduction promoting portion 350 is formed so as to extend along the x direction, which is the air flow direction, to the portion of the fin 300 that is joined to the tube 130 or the tube 230.
  • the portion joined to the tube 130 is a portion on the ⁇ x direction side of the dotted line DL21 in FIG.
  • the portion joined to the tube 230 is a portion on the x direction side of the dotted line DL22 in FIG.
  • heat conduction promoting portion 350 is formed in the above range.
  • L shown on the horizontal axis of FIG. 6A is the distance along the x-axis from the dotted line DL22 to the dotted line DL12, as shown in FIG. FIG. 6A shows how the amount of heat transferred from the capacitor 200 to the radiator 100 by heat conduction changes when the above L is changed.
  • heat conduction amount the amount of heat will be referred to as “heat conduction amount”.
  • heat conduction amount As shown in FIG. 6(A), as L becomes larger, the heat conduction in the fins 300 is less likely to be hindered, so the amount of heat conduction becomes larger.
  • FIG. 6B shows how the amount of heat transferred from the condenser 200 to the air via the fins 300 changes when the above L is changed.
  • the heat quantity will be referred to as "heat transfer quantity”.
  • heat transfer quantity As shown in FIG. 6(B), as L becomes larger, the effect of improving the heat transfer rate by the louvers 342 and the like becomes smaller, so the heat transfer amount becomes smaller.
  • FIG. 6C shows how the total value of the heat conduction amount and the heat transfer amount changes when the above L is changed.
  • the total value will be referred to as “heat dissipation amount”.
  • the amount of heat radiation increases as L increases, but decreases as L further increases. For this reason, the amount of heat radiation is maximum in the range where the value of L is approximately 0 to x1. According to what the present inventors have confirmed by experiments and the like, the value of x1 is about 3 mm.
  • the amount of heat radiation from the capacitor 200 is maximized by setting the value of L to 3 mm. This further reduces the operating load of the refrigerant compressor.
  • the value of L may be appropriately adjusted within the range of 0 mm to 3 mm.
  • the range of the heat conduction promoting part 350 matches the range of the connecting part 330.
  • the range of the heat conduction promoting part 350 may be narrower than the range of the connecting part 330.
  • the heat conduction promoting unit 350 extends to the position of the end of the connecting unit 330 along the air flow direction. It is preferable that the heat conduction promoting portion 350 is formed so as to extend to the position of at least one end of the connecting portion 330 along the air flow direction. That is, the condition that the x-direction side end of the heat conduction promoting part 350 extends to the position of the dotted line DL22 or the position further to the x direction side, and the end part of the heat conduction promoting part 350 on the ⁇ x direction side. It is preferable that either or both of the condition that the line extends to the position of the dotted line DL21 or the position further to the ⁇ x direction side is satisfied.
  • each louver 342 formed in the heat conduction promoting portion 350 is formed in the fin 300 at a central position along the stacking direction.
  • a portion on the z direction side of the louver 342 and a portion on the ⁇ z direction side of the louver 342 are secured widely.
  • a wide heat conduction path is secured in the fin 300 at a position in the vicinity of the tubes 130 and 230, so that heat conduction via the fin 300 can be further promoted. Has become.
  • a modified example of the first embodiment will be described with reference to FIG. 7.
  • the composite heat exchanger 10 according to the present modification differs from the first embodiment only in the arrangement of the louvers 342 and the like formed on the fins 300.
  • points different from those of the first embodiment will be mainly described, and descriptions of points common to the first embodiment will be appropriately omitted.
  • the position of the end portion on the ⁇ x direction side in the range where the heat conduction promoting portion 350 is formed that is, the position indicated by the dotted line DL11 is the position on the x direction side compared to the case of the first embodiment.
  • the position of the end portion on the x direction side in the range where the louvers 342 are formed that is, the position indicated by the dotted line DL12 is the same as in the case of the first embodiment.
  • the heat conduction promoting portion 350 of the present embodiment is formed so as to extend only to the portion on the fin 320 side to the portion joined to the tube 230 along the x direction. Even in such a mode, the same effect as that described in the first embodiment can be obtained.
  • the second embodiment will be described with reference to FIG.
  • the composite heat exchanger 10 according to the present modification differs from the first embodiment only in the aspect of the heat conduction promoting unit 350.
  • points different from those of the first embodiment will be mainly described, and descriptions of points common to the first embodiment will be appropriately omitted.
  • the louvers 341 are formed on the entire fins 310, and the louvers 341 are also formed on the entire fins 320.
  • neither the louver 341 nor the louver 342 is formed in the connecting portion 330.
  • the connecting portion 330 of the present embodiment is a flat plate-like portion as a whole, and no cut CT is formed therein.
  • connection portion 330 At the connecting portion 330, heat conduction along the x direction is not impeded by the louvers 341, etc., so it can be said that heat conduction is maximized at that portion.
  • the entire connection portion 330 shown by the arrow AR2 is the heat conduction promoting portion 350. Even in such a mode, the same effect as that described in the first embodiment can be obtained. If heat transfer is sufficiently performed even if the louvers 341 and louvers 342 are not formed in the connection portion 330, heat transfer and heat transfer between the heat exchangers can be made compatible even with such a configuration. ..
  • the third embodiment will be described with reference to FIG.
  • the composite heat exchanger 10 according to the present modification differs from the second embodiment only in the aspect of the connecting portion 330.
  • points different from the second embodiment will be mainly described, and description of points common to the second embodiment will be appropriately omitted.
  • connection portion 330 is the heat conduction promoting portion 350.
  • the dimples 360 are further formed on a part of the connecting portion 330.
  • the dimple 360 is formed by deforming a part of the connecting portion 330 so as to project in the y direction side or the ⁇ y direction side.
  • the dimple 360 corresponds to a “heat transfer promotion section” for promoting heat transfer with the air.
  • an effect that heat transfer with the air is promoted can be obtained.
  • the fourth embodiment will be described with reference to FIG.
  • the composite heat exchanger 10 according to the present modification is different from the third embodiment only in the aspect of the heat transfer promoting portion formed in the connecting portion 330.
  • points different from those of the third embodiment will be mainly described, and descriptions of points common to the third embodiment will be appropriately omitted.
  • a protrusion 370 is formed instead of the dimple 360 shown in FIG.
  • the projecting portion 370 is formed by forming the cut CT1 of FIG. 10 in the connecting portion 330, and then bending the inner portion of CT1 toward the y direction side along the dotted line DL3 so as to project obliquely.
  • the protruding portion 370 corresponds to the “heat transfer promoting portion” in this embodiment. Even in such a configuration, the same effect as that described in the third embodiment can be obtained.
  • the fifth embodiment will be described with reference to FIG.
  • the composite heat exchanger 10 according to the present modification differs from the second embodiment of FIG. 8 only in the aspect of the connecting portion 330.
  • points different from the second embodiment will be mainly described, and description of points common to the second embodiment will be appropriately omitted.
  • a plurality of drainage holes 380 that are openings are formed at the position that is the end portion on the ⁇ z direction side of the connection portion 330.
  • the drain holes 380 are for discharging the water attached to the fins 300 to the outside.
  • the structure of the composite heat exchanger 10 is not limited to this.
  • a heat exchanger for cooling the battery mounted on the vehicle may be used instead of the condenser 200.
  • a coolant such as cooling water cooled by the cooler may directly or indirectly cool the battery. Since the battery generates a relatively large amount of heat, the effect of adopting the configurations of the above-described embodiments is further enhanced.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'objectif de la présente invention est de fournir un échangeur de chaleur composé qui est capable d'augmenter l'efficacité énergétique en réalisant à la fois une conduction de chaleur et une transmission de chaleur entre des échangeurs de chaleur. Un échangeur de chaleur composé (10) comporte : un premier échangeur de chaleur (100) qui réalise un échange de chaleur entre un premier fluide et de l'air ; et un second échangeur de chaleur (200) qui réalise un échange de chaleur entre un second fluide et de l'air. Une première ailette du premier échangeur de chaleur et une seconde ailette du second échangeur de chaleur sont raccordées l'une à l'autre par l'intermédiaire d'une partie de raccordement (330) et conçues pour être une ailette intégrée (300) dans son ensemble. La partie de raccordement présente une partie favorisant la conduction de chaleur (350) destinée à favoriser une conduction de chaleur entre la première ailette et la seconde ailette. La partie favorisant la conduction de chaleur est formée de manière à s'étendre jusqu'à au moins une position qui sert d'extrémité latérale le long d'une direction d'écoulement d'air dans la partie de raccordement.
PCT/JP2020/000822 2019-02-18 2020-01-14 Échangeur de chaleur composé WO2020170651A1 (fr)

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JP2019026846A JP2020133991A (ja) 2019-02-18 2019-02-18 複合型熱交換器
JP2019-026846 2019-02-18

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WO2020170651A1 true WO2020170651A1 (fr) 2020-08-27

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4325139A4 (fr) * 2021-04-13 2024-06-05 Mitsubishi Electric Corporation Échangeur de chaleur et dispositif à cycle de réfrigération

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023203640A1 (fr) * 2022-04-19 2023-10-26 三菱電機株式会社 Échangeur de chaleur et climatiseur

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11294984A (ja) * 1998-04-09 1999-10-29 Zexel:Kk 並設一体型熱交換器
JP2002350077A (ja) * 2001-05-21 2002-12-04 Calsonic Kansei Corp 一体型熱交換器のコア部構造
WO2004090448A2 (fr) * 2003-03-31 2004-10-21 Valeo Thermique Moteur Module d’echange de chaleur, notamment pour vehicule automobile
JP2006162136A (ja) * 2004-12-06 2006-06-22 Denso Corp 複合式熱交換器
JP2018035802A (ja) * 2016-08-26 2018-03-08 株式会社デンソー 複合型熱交換器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11294984A (ja) * 1998-04-09 1999-10-29 Zexel:Kk 並設一体型熱交換器
JP2002350077A (ja) * 2001-05-21 2002-12-04 Calsonic Kansei Corp 一体型熱交換器のコア部構造
WO2004090448A2 (fr) * 2003-03-31 2004-10-21 Valeo Thermique Moteur Module d’echange de chaleur, notamment pour vehicule automobile
JP2006162136A (ja) * 2004-12-06 2006-06-22 Denso Corp 複合式熱交換器
JP2018035802A (ja) * 2016-08-26 2018-03-08 株式会社デンソー 複合型熱交換器

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4325139A4 (fr) * 2021-04-13 2024-06-05 Mitsubishi Electric Corporation Échangeur de chaleur et dispositif à cycle de réfrigération

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