WO2016136157A1 - Appareil de climatisation de véhicule - Google Patents

Appareil de climatisation de véhicule Download PDF

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Publication number
WO2016136157A1
WO2016136157A1 PCT/JP2016/000607 JP2016000607W WO2016136157A1 WO 2016136157 A1 WO2016136157 A1 WO 2016136157A1 JP 2016000607 W JP2016000607 W JP 2016000607W WO 2016136157 A1 WO2016136157 A1 WO 2016136157A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
heat
unit
evaporator
Prior art date
Application number
PCT/JP2016/000607
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English (en)
Japanese (ja)
Inventor
冬人 荒木
宏一郎 白井
Original Assignee
株式会社デンソー
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2016006141A external-priority patent/JP2016164062A/ja
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Priority to EP16754913.8A priority Critical patent/EP3263375B1/fr
Publication of WO2016136157A1 publication Critical patent/WO2016136157A1/fr

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    • 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
    • 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
    • B60H1/32—Cooling devices

Definitions

  • the present disclosure relates to a vehicle air conditioner including a heat-dissipating heat exchanger and an evaporator installed on the roof of the vehicle.
  • Patent Document 1 Conventionally, as this type of vehicle air conditioner, there is one described in Patent Document 1, for example.
  • the vehicle air conditioner described in Patent Document 1 includes a cooling unit portion and a condensing unit portion installed on a flat roof of a bus vehicle.
  • the vehicle air conditioner mounted on the bus vehicle requires a large heat exchanger for its use. Therefore, in the vehicle air conditioner of Patent Document 1, the condensing unit portion is configured to include a plurality of capacitors instead of a single capacitor. And the several capacitor
  • condenser namely, heat exchanger for thermal radiation is arrange
  • the cooling unit portion is configured to include an evaporator, and is disposed adjacent to the rear of the condensing unit portion in the front-rear direction of the vehicle. That is, the evaporator is disposed rearward with respect to any of the plurality of capacitors.
  • the vehicle air conditioner of Patent Document 1 includes a plurality of capacitors, that is, heat radiating heat exchangers, which ensures a large amount of heat exchange. It is advantageous.
  • the heat radiation of a vehicle air conditioner mounted on a vehicle type different from that of the bus vehicle or the like is also assumed.
  • a heat dissipating heat exchanger which is an outdoor heat exchanger, is arranged in the center of the vehicle air conditioner in the width direction of the vehicle. That is, the heat exchanger for heat dissipation is arranged between two evaporators that are indoor heat exchangers in the width direction.
  • the space that can be used to secure the air volume passing through the heat exchanger for heat dissipation has decreased.
  • the configuration in which the heat exchanger for heat radiation is disposed between the two evaporators in the width direction is a disadvantageous configuration from the viewpoint of improving the cooling performance of the vehicle air conditioner.
  • This indication aims at providing the air-conditioner for vehicles which can improve cooling performance in view of the above-mentioned point.
  • the vehicle air conditioner according to the first aspect of the present disclosure includes a condenser unit, a first evaporator unit, and a second evaporator unit.
  • the condenser unit is installed on the roof of the vehicle.
  • the first evaporator unit is installed on the roof.
  • a 2nd evaporator unit is installed in a roof, and is arrange
  • the condenser unit has a condensing unit and one or more cooling units.
  • the condensing unit condenses the refrigerant compressed by the compressor by heat exchange between the refrigerant and the outside air.
  • the supercooling unit cools the liquid-phase refrigerant condensed by the condensing unit by heat exchange between the liquid-phase refrigerant and outside air.
  • the condenser unit is disposed between the first evaporator unit and the second evaporator unit in the width direction of the vehicle.
  • Each of the first evaporator unit and the second evaporator unit evaporates the decompressed refrigerant by heat exchange between the decompressed refrigerant that has flowed out from one or more supercooling units and the air blown into the vehicle interior.
  • One of the one or two or more subcooling sections is arranged in the condenser unit so as to be biased forward in the traveling direction of the vehicle.
  • the vehicle air conditioner receives the ram pressure when the vehicle is traveling, so that the above-mentioned one error is arranged in the condenser unit biased forward in the traveling direction (that is, forward in the longitudinal direction of the vehicle).
  • the air volume passing through the cooling unit can be made larger than the rear air volume.
  • cooling of the refrigerant in the one supercooling unit is promoted, and the cooling performance of the vehicle air conditioner is improved as compared with a configuration in which the supercooling unit included in the condenser unit is biased backward, for example. It is possible to make it.
  • the vehicle air conditioner according to the second aspect of the present disclosure may include a first heat dissipation heat exchanger, a second heat dissipation heat exchanger, a first evaporator, and a second evaporator.
  • the first heat radiating heat exchanger is installed on the roof of the vehicle, and condenses the refrigerant compressed by the compressor by heat exchange between the refrigerant and the outside air.
  • the second heat radiating heat exchanger includes a condensing part that condenses the refrigerant compressed by the compressor by heat exchange between the refrigerant and the outside air, and a liquid condensed by the condensing part and the first heat radiating heat exchanger.
  • the first evaporator is installed on the roof.
  • the second evaporator is installed on the roof and arranged side by side in the vehicle width direction with respect to the first evaporator.
  • Each of the first evaporator and the second evaporator evaporates the decompressed refrigerant by heat exchange between the decompressed refrigerant flowing out of the supercooling section and the air blown into the passenger compartment.
  • the first heat dissipation heat exchanger and the second heat dissipation heat exchanger are disposed between the first evaporator and the second evaporator in the width direction of the vehicle.
  • the second heat dissipation heat exchanger is disposed in front of the traveling direction of the vehicle with respect to the first heat dissipation heat exchanger.
  • the vehicle air conditioner since the vehicle air conditioner receives ram pressure when the vehicle is traveling, the second heat dissipation disposed in front of the first heat dissipation heat exchanger in the traveling direction (that is, forward in the front-rear direction of the vehicle).
  • the amount of air passing through the heat exchanger can be made larger than the amount of air behind.
  • the cooling of the refrigerant in the supercooling part is promoted, for example, compared with the configuration in which the supercooling part is biased rearward in the space occupied by the first and second heat radiating heat exchangers, It is possible to improve the cooling performance of the vehicle air conditioner.
  • FIG. 1 is a perspective view showing a vehicle 8 on which a vehicle air conditioner 100 (see FIG. 2) is mounted in the first embodiment.
  • the vehicle air conditioner 100 is mounted on a box-shaped vehicle 8, such as a bus vehicle.
  • FIG. 2 is a schematic configuration diagram showing the refrigeration cycle apparatus 10 included in the vehicle air conditioner 100 mounted on the vehicle 8 of FIG.
  • the arrows displayed along the refrigerant flow path in FIG. 2 indicate the direction of refrigerant flow, and this is the same in FIGS. 5 and 6 described later.
  • the vehicle air conditioner 100 performs air conditioning of the vehicle interior, and the refrigeration cycle device 10 of the vehicle air conditioner 100 constitutes a refrigeration cycle in which the refrigerant circulates and repeats heat absorption and heat dissipation. The air blown out is cooled by the refrigerant.
  • the vehicle air conditioner 100 includes, for example, a heater core, a blower, and a blower duct that use cooling water of a travel engine as a heat source, although not shown.
  • the refrigeration cycle apparatus 10 includes a roof installation unit 12 that is installed on the roof 9 (see FIG. 1) of the vehicle 8, and a compressor 14 that is arranged, for example, below the rear floor of the vehicle 8. And.
  • the roof installation unit 12 includes a first heat dissipation heat exchanger 16, a second heat dissipation heat exchanger 18, a receiver 20, a dryer 22, a first decompression device 24, a second decompression device 26, a first evaporator 28, And a second evaporator 30 and the like.
  • each arrow which shows the front-back direction DR1 and width direction DR3 displayed on FIG. 2 has shown the relative positional relationship of the heat exchangers 16 and 18 for heat radiation, and the evaporators 28 and 30, and this is mentioned later. The same applies to FIGS. 5 and 6.
  • the refrigerant discharged from the compressor 14 includes the compressor 14, the first heat dissipation heat exchanger 16, the condensing unit 181 of the second heat dissipation heat exchanger 18, and the receiver. 20, the supercooling section 182 of the second heat radiating heat exchanger 18 and the dryer 22 flow in this order, and are divided into two refrigerant paths downstream of the dryer 22. Then, the refrigerant flowing out of the dryer 22 flows in the order of the first decompression device 24, the first evaporator 28, and the compressor 14 in one of the two refrigerant paths, and the second decompression in the other refrigerant path. It flows in the order of the device 26, the second evaporator 30, and the compressor 14.
  • the compressor 14 has a refrigerant suction port 14a and a refrigerant discharge port 14b, compresses the refrigerant sucked from the refrigerant suction port 14a, and discharges the compressed refrigerant from the refrigerant discharge port 14b.
  • the compressor 14 is driven from a traveling engine (not shown) via an electromagnetic clutch.
  • the first heat radiation heat exchanger 16 is a condenser that condenses the refrigerant compressed by the compressor 14 by heat exchange between the refrigerant and the outside air.
  • the outside air heat-exchanged with the refrigerant is air outside the passenger compartment, specifically speaking, air including traveling wind blown from the front in the front-rear direction DR1. That is, the first heat radiating heat exchanger 16 is an outdoor heat exchanger that exchanges heat between air outside the passenger compartment and the refrigerant.
  • the first heat radiating heat exchanger 16 is a multi-flow heat exchanger, and is configured as shown in FIG.
  • FIG. 3 is a diagram showing a configuration of the first heat radiation heat exchanger 16 alone.
  • the first heat dissipation heat exchanger 16 includes a plurality of first refrigerant tubes 161, a plurality of second refrigerant tubes 162, a first inlet side tank portion 163a, and a second inlet side tank portion 163b.
  • An outlet side header tank 164 including a first outlet side tank portion 164a and a second outlet side tank portion 164b, and a plurality of corrugated fins 165.
  • the first refrigerant tube 161 and the second refrigerant tube 162 of the first heat radiating heat exchanger 16 have the same flat structure except for the connection destination, and the refrigerant flows in the refrigerant tubes 161 and 162. It has become.
  • the first refrigerant tube 161 is stacked in one direction, that is, in the tube stacking direction with an interval through which the outside air passes, and flows while allowing the refrigerant to exchange heat with the outside air.
  • the second refrigerant tubes 162 are also stacked in the tube stacking direction with an interval through which the outside air passes, and the refrigerant flows while exchanging heat with the outside air.
  • the first heat radiating heat exchanger 16 is arranged on the roof 9 of the vehicle 8 (see FIG. 1) so that the plurality of first refrigerant tubes 161 are aligned with one side in the width direction DR3 with respect to the plurality of second refrigerant tubes 162. Has been placed.
  • the tube stacking direction coincides with the width direction DR3.
  • the tube lamination direction may not coincide with the width direction DR3. The same applies to the fourth embodiment described later.
  • the inlet side header tank 163 has a separator 163c as a partition plate that divides the internal space of the inlet side header tank 163 into two.
  • the first inlet side tank portion 163a is one tank portion divided by the separator 163c
  • the second inlet side tank portion 163b is the other tank portion divided by the separator 163c.
  • the outlet side header tank 164 is divided in the same manner as the inlet side header tank 163. That is, the outlet side header tank 164 has a separator 164c that divides the internal space of the outlet side header tank 164 into two.
  • the first outlet side tank part 164a is one tank part divided by the separator 164c
  • the second outlet side tank part 164b is the other tank part divided by the separator 164c.
  • the first inlet side tank unit 163a is connected to one end of each of the plurality of first refrigerant tubes 161, and the first outlet side tank unit 164a is connected to each of the other ends of the plurality of first refrigerant tubes 161.
  • the second inlet side tank portion 163b is connected to one end of each of the plurality of second refrigerant tubes 162, and the second outlet side tank portion 164b is connected to each of the other ends of the plurality of second refrigerant tubes 162.
  • the first inlet side tank portion 163a has a first refrigerant inlet 163d
  • the second inlet side tank portion 163b has a second refrigerant inlet 163e
  • the first outlet side tank portion 164a has a first refrigerant inlet 163d.
  • a first refrigerant outlet 164d for allowing the refrigerant to flow out from the outlet side tank part 164a is formed
  • a second refrigerant outlet 164e for allowing the refrigerant to flow out from the second outlet side tank part 164b is formed in the second outlet side tank part 164b.
  • the first refrigerant inlet 163d and the second refrigerant inlet 163e are provided in parallel with each other in the refrigerant flow in the first heat radiation heat exchanger 16, as shown in FIG. That is, the refrigerant compressed by the compressor 14 (see FIG. 2) flows from the first refrigerant inlet 163d into the first inlet side tank 163a as indicated by the arrow FL1in in FIG. 163a distributes and flows the inflowing refrigerant to the plurality of first refrigerant tubes 161, respectively. At the same time, the refrigerant compressed by the compressor 14 (see FIG. 2) flows from the second refrigerant inlet 163e into the second inlet side tank portion 163b as indicated by the arrow FL2in in FIG. The part 163b distributes and flows the inflowing refrigerant to the plurality of second refrigerant tubes 162, respectively.
  • the first refrigerant outlet 164d and the second refrigerant outlet 164e are also provided in parallel with each other in the refrigerant flow in the first heat-dissipating heat exchanger 16, as shown in FIG. That is, the first outlet side tank unit 164a collects the refrigerant that has flowed in from each of the plurality of first refrigerant tubes 161, and uses the refrigerant from the first refrigerant outlet 164d for the second heat dissipation as indicated by the arrow FL1out in FIG. The heat flows through the condenser 181 (see FIG. 2) of the heat exchanger 18 and the receiver 20 toward the supercooling unit 182 of the second heat radiating heat exchanger 18.
  • the second outlet side tank section 164b collects the refrigerant flowing in from each of the plurality of second refrigerant tubes 162, and the refrigerant is discharged from the second refrigerant outlet 164e to the second heat radiation as indicated by an arrow FL2out in FIG.
  • the heat flows through the condenser 181 and the receiver 20 of the heat exchanger 18 toward the supercooling unit 182 of the second heat radiating heat exchanger 18.
  • the first refrigerant inlet 163d is provided at a position closer to one side in the tube stacking direction in the first inlet-side tank portion 163a, and the first refrigerant outlet 164d is connected to the first outlet-side tank portion 164a. Of these, it is provided at a position on the other side opposite to the one in the tube stacking direction.
  • the second refrigerant inlet 163e is provided at a position closer to one side in the tube stacking direction in the second inlet side tank portion 163b, and the second refrigerant outlet 164e is in the tube stacking direction in the second outlet side tank portion 164b. Is provided at a position near the other side opposite to the above.
  • the corrugated fin 165 is formed into a corrugated shape from a thin strip material.
  • the corrugated fin 165 is interposed between the refrigerant tubes 161 and 162 and joined to the adjacent refrigerant tubes 161 and 162 by brazing or the like. Thereby, the corrugated fin 165 promotes heat exchange between the refrigerant flowing in the refrigerant tubes 161 and 162 and the outside air.
  • Such a first heat radiation heat exchanger 16 includes two condensing units 166 and 167 that condense the refrigerant compressed by the compressor 14 (see FIG. 2), that is, the first condensing unit 166 and the second condensing unit 167.
  • the first condensing unit 166 and the second condensing unit 167 are provided in parallel with each other in the refrigerant flow in the first heat radiating heat exchanger 16, and are arranged so as to be aligned in the width direction DR3.
  • the plurality of first refrigerant tubes 161, the first inlet side tank part 163 a, and the first outlet side tank part 164 a constitute the first condensing part 166.
  • the plurality of second refrigerant tubes 162, the second inlet side tank part 163b, and the second outlet side tank part 164b constitute a second condensing part 167.
  • the first condensing unit 166 and the second condensing unit 167 are heat exchange units having the same size. Specifically, the number of the plurality of first refrigerant tubes 161 included in the first condensing unit 166 is the same as the number of the plurality of second refrigerant tubes 162 included in the second condensing unit 167. That is, the total flow cross-sectional area of the plurality of first refrigerant tubes 161 included in the first condensing unit 166 is the same as the total flow cross-sectional area of the plurality of second refrigerant tubes 162 included in the second condensing unit 167. ing. Therefore, the refrigerant flow rate flowing from the compressor 14 (see FIG. 1) into the first condensing unit 166 is approximately the same as the refrigerant flow rate flowing from the compressor 14 into the second condensing unit 167.
  • the second heat radiation heat exchanger 18 is the same as the first heat radiation heat exchanger 16 described above in that the heat of the refrigerant compressed by the compressor 14 is radiated to the outside air. That is, the second heat radiating heat exchanger 18 is also an outdoor heat exchanger that exchanges heat between air outside the passenger compartment and the refrigerant. However, the second heat radiating heat exchanger 18 is provided on the downstream side of the refrigerant flow with respect to the first heat radiating heat exchanger 16.
  • the second heat dissipation heat exchanger 18 is, for example, a multiflow heat exchanger.
  • the second heat radiating heat exchanger 18 has two heat exchanging parts independent in the refrigerant flow by the same structure as the first heat radiating heat exchanger 16, that is, the structure in which the internal space of the header tank is divided by the separator. ing.
  • the second heat dissipation heat exchanger 18 includes a condensing unit 181 and a supercooling unit 182 as two heat exchanging units.
  • the condensing part 181 of the second heat radiating heat exchanger 18 is connected in series with the first heat radiating heat exchanger 16 in the refrigerant flow from the compressor 14 to the first evaporator 28 or the second evaporator 30.
  • the heat dissipating heat exchanger 16 is provided on the downstream side. Therefore, the refrigerant compressed by the compressor 14 flows into the condensing unit 181 after passing through the first heat dissipation heat exchanger 16. And the condensation part 181 condenses the inflowing refrigerant
  • the condensing unit 181 causes the heat exchanged refrigerant to flow out to the receiver 20.
  • first heat radiating heat exchanger 16 does not have a heat exchanging portion corresponding to the supercooling portion 182 of the second heat radiating heat exchanger 18, as can be seen from FIG.
  • the entire amount of the refrigerant that has flowed out of the first heat radiation heat exchanger 16 flows into the condensing unit 181 of the exchanger 18.
  • the receiver 20 is a gas-liquid separator that separates the gas-liquid refrigerant flowing from the condensing unit 181 of the second heat radiating heat exchanger 18, and the separated liquid-phase refrigerant is supercooled by the second heat radiating heat exchanger 18. It flows out to the part 182.
  • the receiver 20 adjusts the amount of refrigerant circulating in the refrigeration cycle by storing a predetermined amount of refrigerant in the receiver.
  • the supercooling section 182 of the second heat radiating heat exchanger 18 includes a liquid phase refrigerant condensed by the first heat radiating heat exchanger 16 and the condensing section 181 of the second heat radiating heat exchanger 18. Liquid phase refrigerant flows in.
  • the supercooling unit 182 cools the inflowing liquid phase refrigerant by heat exchange between the liquid phase refrigerant and the outside air.
  • the supercooling unit 182 causes the cooled liquid phase refrigerant to flow out to the dryer 22.
  • the supercooling unit 182 since the volume flow rate of the refrigerant flowing into the supercooling unit 182 becomes smaller than the volume flow rate of the refrigerant flowing into the condensing unit 181 due to the condensation of the refrigerant, the supercooling unit 182 includes the condensing unit as shown in FIG. Compared to 181, it is a small heat exchange section. For example, the number of the plurality of refrigerant tubes included in the supercooling unit 182 is smaller than the number of the plurality of refrigerant tubes included in the condensing unit 181.
  • the total flow path cross-sectional area of the plurality of refrigerant tubes included in the supercooling unit 182 is smaller than the total flow path cross-sectional area of the plurality of refrigerant tubes included in the condensing unit 181.
  • the first heat radiation heat exchanger 16 and the second heat radiation heat exchanger 18 described above constitute a condenser unit 19 having a plurality of condenser parts 166, 167, 181 and one supercooling part 182 as a whole. Yes.
  • the condensing part 181 of the first heat radiating heat exchanger 16 and the second heat radiating heat exchanger 18 is a heat exchanging part that condenses the refrigerant, but the first heat radiating heat exchanger 16 is 2 It differs from the condensation part 181 of the heat exchanger 18 for heat dissipation in that the refrigerant flow is provided upstream of the condensation part 181. Therefore, the condensing part 181 of the 1st heat radiating heat exchanger 16 and the 2nd heat radiating heat exchanger 18 has a configuration adapted to the volume change due to the condensation of the refrigerant.
  • the first heat dissipation heat exchanger For example, if the refrigerant tubes 161 and 162 (see FIG. 3) included in the first heat dissipation heat exchanger 16 and the refrigerant tube included in the condensing unit 181 are the same, the first heat dissipation heat exchanger.
  • the number of 16 refrigerant tubes is larger than the number of refrigerant tubes of the condensing unit 181. That is, the total flow path cross-sectional area of the plurality of refrigerant tubes 161 and 162 included in the first heat dissipation heat exchanger 16 is larger than the total flow path cross-sectional area of the plurality of refrigerant tubes included in the condensing unit 181. .
  • the first heat-dissipating heat exchanger 16 is a large heat exchanging part as compared with the condensing part 181 of the second heat-dissipating heat exchanger 18, in other words, the heat exchanging capacity. Is getting bigger.
  • the dryer 22 contains a desiccant such as silica gel, absorbs intruding moisture that has entered the liquid-phase refrigerant flowing in from the supercooling portion 182 of the second heat radiating heat exchanger 18, and reduces the liquid-phase refrigerant to the first pressure reduction. It is made to flow out to device 24 and the 2nd decompression device 26, respectively.
  • a desiccant such as silica gel
  • Both the first pressure reducing device 24 and the second pressure reducing device 26 are temperature type expansion valves used in general vehicle air conditioners.
  • the first decompression device 24 decompresses the refrigerant flowing from the dryer 22 and then causes the refrigerant to flow out to the first evaporator 28.
  • the second decompression device 26 decompresses the refrigerant flowing from the dryer 22 and then causes the refrigerant to flow out to the second evaporator 30.
  • the first evaporator 28 evaporates the decompressed refrigerant and cools the air by heat exchange between the decompressed refrigerant and air blown into the passenger compartment (in other words, blown air).
  • the first evaporator 28 is an indoor heat exchanger that cools the air blown into the vehicle interior.
  • the second evaporator 30 is also an indoor heat exchanger that operates in the same manner as the first evaporator 28 described above. That is, the refrigerant that flows out from the supercooling part 182 of the second heat radiating heat exchanger 18 and is decompressed by the second decompression device 26 flows into the second evaporator 30. The second evaporator 30 evaporates the decompressed refrigerant and cools the air by heat exchange between the decompressed refrigerant and the air blown into the vehicle interior.
  • the refrigerant after heat exchange flowing out from the first evaporator 28 and the refrigerant after heat exchange flowing out from the second evaporator 30 are sucked into the refrigerant inlet 14a of the compressor 14.
  • FIG. 4 is a layout diagram in the roof installation unit 12 as viewed from above in the direction of arrow IV in FIG. 1, that is, the vertical direction DR2.
  • the decompression devices 24 and 26 are not shown, and the arrows indicating the front-rear direction DR1 and the width direction DR3 indicate the relative positional relationship between the constituent devices of the roof installation unit 12 and the roof installation unit 12. Indicates the direction.
  • the first heat dissipation heat exchanger 16 and the second heat dissipation heat exchanger 18 are arranged side by side along the traveling direction of the vehicle. More specifically, the second heat radiation heat exchanger 18 is disposed in front of the first heat radiation heat exchanger 16 in the traveling direction. That is, paying attention to the layout of the supercooling part 182 of the second heat radiating heat exchanger 18, the supercooling part 182 is arranged in the condenser unit 19 so as to be biased forward in the traveling direction.
  • the traveling direction of the vehicle is a direction facing the front of the front-rear direction DR1 as shown in FIG.
  • the roof installation unit 12 includes a unit case 121 as an outer shell.
  • the unit case 121 is configured such that traveling air, which is outside air blown from the front, is introduced into the unit case 121, and the traveling air flows from the front to the second heat dissipation heat exchanger 18 and the first heat dissipation heat exchange. Flows to vessel 16.
  • the first heat-dissipating heat exchanger 16 and the second heat-dissipating heat exchanger 18 have the same amount of outside air (running wind) passing through the second heat-dissipating heat exchanger 18. 1 It is provided so that it may become larger than the air volume of the external air (running wind) which passes the heat exchanger 16 for thermal radiation.
  • the first evaporator 28 is disposed on one side (specifically, on the right side) in the width direction DR3 with respect to the first heat radiation heat exchanger 16 and the second heat radiation heat exchanger 18 arranged in the front-rear direction DR1. ing. That is, the 1st evaporator 28 comprises the 1st evaporator unit which is one of the two evaporator units which the vehicle air conditioner 100 has.
  • the second evaporator 30 is disposed on the other side (specifically, on the left side) of the width direction DR3 with respect to the first heat dissipation heat exchanger 16 and the second heat dissipation heat exchanger 18. That is, the second evaporator 30 constitutes a second evaporator unit that is the other of the two evaporator units. And the 2nd evaporator unit is arrange
  • the first heat dissipation heat exchanger 16 and the second heat dissipation heat exchanger 18 are arranged in the front-rear direction DR1 between the two evaporators 28, 30 arranged in the width direction DR3. Is arranged in.
  • the condenser unit 19 composed of the first heat-dissipating heat exchanger 16 and the second heat-dissipating heat exchanger 18 includes the first evaporator unit having the first evaporator 28 and the second evaporation in the width direction DR3. It is arranged between the second evaporator unit having the evaporator 30.
  • the first heat dissipation heat exchanger 16 and the second heat dissipation heat exchanger 18 are the same as the first evaporator 28 or the second evaporator 30.
  • it is arranged on one side in the width direction DR3.
  • the first heat dissipation heat exchanger 16 and the second heat dissipation heat exchanger 18 are connected to the first evaporator 28 or the second evaporator 30 in the width direction DR3.
  • the first evaporator 28 or the second evaporator 30 is arranged such that the distance between the first evaporator 28 and the second evaporator 30 is shorter than the distance between the other one of the first evaporator 28 and the second evaporator 30.
  • the length and the length of the second evaporator 30 are longer than both the length of the first heat radiating heat exchanger 16 and the length of the second heat radiating heat exchanger 18.
  • the first heat dissipation heat exchanger 16 and the second heat dissipation heat exchanger 18 are both within the range occupied by the first evaporator 28 and the second evaporator 30 in the front-rear direction DR1. Further, the receiver 20 and the dryer 22 are also within the range occupied by the first evaporator 28 and the second evaporator 30 in the front-rear direction DR1.
  • the second heat dissipation heat exchanger 18 is arranged such that the condensing unit 181 is aligned with the subcooling unit 182 in the width direction DR3. Specifically, in the second heat dissipation heat exchanger 18, the condensing unit 181 is disposed on the second evaporator 30 side, and the supercooling unit 182 is disposed on the first evaporator 28 side.
  • the receiver 20 is disposed between the second heat radiation heat exchanger 18 and the second evaporator 30 in the width direction DR3, and the dryer 22 is disposed in the second heat radiation heat exchanger 18 and the first evaporator in the width direction DR3. 28.
  • the first heat dissipation heat exchanger 16 and the second heat dissipation heat exchanger 18 are arranged side by side along the traveling direction.
  • the first evaporator 28 or the second evaporator 30 is arranged on one side in the width direction DR3.
  • the first heat-dissipating heat exchanger 16 and the second heat-dissipating heat exchanger 18 are arranged side by side in the front-rear direction DR1 between the two evaporators 28, 30 arranged in the width direction DR3.
  • the first and second heat-dissipating functions in the front-rear direction DR1 can be shortened. Specifically, by reducing the length of the roof installation unit 12 in the front-rear direction DR1 while suppressing the dimension in the width direction DR3 of the roof installation unit 12 within a predetermined width dimension not exceeding the width of the roof 9, The layout of the roof installation unit 12 can be improved.
  • the first heat dissipation heat exchanger 16 does not include a heat exchanging portion corresponding to the subcooling portion 182 of the second heat dissipating heat exchanger 18, and the second heat dissipating heat exchanger 16.
  • the total amount of the refrigerant that has flowed out of the first heat radiation heat exchanger 16 flows into the condensing unit 181 of the vessel 18. Therefore, as shown in FIG. 2, the refrigerant flow path from the compressor 14 to the evaporators 28 and 30 can be simply configured.
  • the second heat dissipation heat exchanger 18 is disposed in front of the first heat dissipation heat exchanger 16 in the front-rear direction DR1.
  • the traveling wind flows from the front to the second heat dissipation heat exchanger 18 and the first heat dissipation heat exchanger 16. Therefore, the air volume of the outside air passing through the second heat radiating heat exchanger 18 is larger than the air volume of the outside air passing through the first heat radiating heat exchanger 16.
  • the outside air absorbs heat and rises in temperature as heat is exchanged with the refrigerant in each heat dissipation heat exchanger 16, 18. Outside air before the first heat radiating heat exchanger 16 absorbs heat flows through the supercooling portion 182 of the second heat radiating heat exchanger 18.
  • the cooling of the refrigerant in the supercooling unit 182 is promoted in the condenser unit 19.
  • the cooling performance of the vehicle air conditioner 100 can be improved as compared with a configuration in which the supercooling unit 182 included in the condenser unit 19 is disposed rearward in the front-rear direction DR1.
  • the first heat dissipation heat exchanger 16 has the first condensing unit 166 and the second condensing unit 167 that condense the refrigerant discharged from the compressor 14. is doing.
  • the first condensing unit 166 and the second condensing unit 167 are provided in parallel with each other in the refrigerant flow in the first heat dissipation heat exchanger 16.
  • the first heat dissipation heat exchanger 16 is not divided into the two condensing parts 166 and 167, and compared with a configuration including a single condensing part, the first heat dissipating heat exchanger 16 is enlarged,
  • the refrigerant distribution in the first heat radiating heat exchanger 16 is suppressed and the distribution of the refrigerant can be made close to a uniform distribution. That is, it is possible to improve the distribution of the refrigerant in the first heat radiation heat exchanger 16, in other words, the distribution of the refrigerant to the refrigerant tubes 161 and 162.
  • the first heat dissipation heat exchanger 16 is arranged such that the first condensing unit 166 is aligned with the second condensing unit 167 in the width direction DR3. .
  • the traveling airflow is evenly distributed from the front to the first condensing unit 166 and the second condensing unit 167, and the bias of the heat exchange capacity between the first condensing unit 166 and the second condensing unit 167 is suppressed. Is possible.
  • FIG. 5 is a refrigerant circuit diagram illustrating the compressor circuit from the compressor 14 to the upstream side of the dryer 22 in the refrigerant circuit of the refrigeration cycle apparatus 10 according to the present embodiment.
  • the vehicle air conditioner 100 according to the present embodiment includes a refrigerant flow path from the refrigerant discharge port 14 b of the compressor 14 to the dryer 22 and a first heat dissipation heat exchanger 16 in the first embodiment ( Different from FIG. In the present embodiment, the refrigerant flow path from the dryer 22 to the refrigerant suction port 14a of the compressor 14 is the same as that shown in FIG. 2, and is not shown in FIG.
  • the first heat dissipation heat exchanger 16 of the first embodiment has two condensing parts 166 and 167 as shown in FIG. 2, but the first heat dissipation heat exchanger of the present embodiment. 16 has one condensing part 168 and one supercooling part 169 as shown in FIG.
  • the condensing unit 168 has the same function as the condensing units 166 and 167 of the first embodiment. That is, the condensing unit 168 of the first heat radiation heat exchanger 16 shown in FIG. 5 condenses the refrigerant compressed by the compressor 14 by heat exchange between the refrigerant and the outside air.
  • the supercooling unit 169 of the first heat dissipation heat exchanger 16 has the same function as the supercooling unit 182 of the second heat dissipation heat exchanger 18. That is, the subcooling portion 169 of the first heat dissipation heat exchanger 16 is a liquid phase condensed by the condensing portion 168 of the first heat dissipation heat exchanger 16 and the condensing portion 181 of the second heat dissipation heat exchanger 18. The refrigerant is cooled by heat exchange between the liquid phase refrigerant and the outside air.
  • the refrigerant discharged from the compressor 14 is the condensing part 168 of the first heat radiating heat exchanger 16 and the condensing part 181 of the second heat radiating heat exchanger 18. And then condensed in the respective condensing sections 168 and 181 and then flow into the receiver 20.
  • the liquid-phase refrigerant from the receiver 20 flows into the supercooling unit 169 of the first heat dissipation heat exchanger 16 and the subcooling unit 182 of the second heat dissipation heat exchanger 18, and the respective subcooling units 169 and 182. After being cooled, the air flows into the dryer 22 (see FIG. 2).
  • the condensing part 168 of the first heat radiating heat exchanger 16 and the condensing part 181 of the second heat radiating heat exchanger 18 are connected in parallel to each other. ing. And the supercooling part 169 of the 1st heat radiation heat exchanger 16 and the supercooling part 182 of the 2nd heat radiation heat exchanger 18 are also mutually connected in parallel. In short, the first heat radiating heat exchanger 16 and the second heat radiating heat exchanger 18 are connected in parallel to each other.
  • the condenser unit 19 includes a plurality of supercooling units 169 and 182. And the supercooling part 182 of the 2nd heat radiating heat exchanger 18 which is one supercooling part among the plurality of supercooling parts 169 and 182 is biased forward in the running direction in the condenser unit 19. Has been placed.
  • the condensing unit 168 of the first heat radiating heat exchanger 16 is parallel to the condensing unit 181 of the second heat radiating heat exchanger 18. It is connected.
  • the condensing units 166 and 167 of the first heat radiating heat exchanger 16 are both connected in series to the condensing unit 181 of the second heat radiating heat exchanger 18. Due to such differences, as can be seen by comparing FIG. 2 and FIG. 5, the piping circuit in the roof installation unit 12 is simplified in the first embodiment compared to the second embodiment. It is possible to improve the layout of the constituent devices of the installation unit 12.
  • FIG. 6 is a schematic configuration diagram showing the refrigeration cycle apparatus 10 of the present embodiment, and corresponds to FIG. 2 of the first embodiment.
  • the vehicle air conditioner 100 of the present embodiment is different from the first embodiment (see FIG. 2) in the direction of the second heat dissipation heat exchanger 18.
  • the second heat dissipation heat exchanger 18 is arranged such that the supercooling portion 182 is arranged in front of the condensing portion 181 in the traveling direction.
  • this embodiment is a modification based on 1st Embodiment, it is also possible to combine this embodiment with the above-mentioned 2nd Embodiment.
  • FIG. 7 is a diagram showing a configuration of the first heat radiation heat exchanger 16 alone in the present embodiment, and corresponds to FIG. 3 of the first embodiment.
  • the structure of the first heat radiating heat exchanger 16 is different from that of the first embodiment (see FIG. 3).
  • the first heat dissipation heat exchanger 16 of the present embodiment is different from the first embodiment in that both header tanks 163 and 164 do not have separators 163c and 164c (see FIG. 3).
  • the first heat dissipation heat exchanger 16 includes a plurality of refrigerant tubes 160, an inlet-side header tank 163, an outlet-side header tank 164, and a plurality of corrugated fins 165. ing.
  • the refrigerant tube 160 of the present embodiment is the same tube as the refrigerant tubes 161 and 162 of the first embodiment.
  • the refrigerant tubes 160 are stacked in the tube stacking direction with an interval through which the outside air passes, and exchange heat between the refrigerant flowing inside the refrigerant tubes 160 and the outside air.
  • the inlet side header tank 163 does not have the separator 163c (see FIG. 3), it forms a single internal space. Similarly to the inlet side header tank 163, the outlet side header tank 164 forms a single internal space.
  • the inlet side header tank 163 is connected to one end of each of the plurality of refrigerant tubes 160, and the outlet side header tank 164 is connected to each of the other ends of the plurality of refrigerant tubes 160.
  • the inlet side header tank 163 is formed with a first refrigerant inlet 163f and a second refrigerant inlet 163g.
  • the first refrigerant inlet 163f and the second refrigerant inlet 163g are provided in parallel with each other in the refrigerant flow in the first heat dissipation heat exchanger 16, like the refrigerant inlets 163d and 163e of the first embodiment. That is, the refrigerant compressed by the compressor 14 (see FIG. 2) flows in parallel to the first refrigerant inlet 163f and the second refrigerant inlet 163g as indicated by arrows FL1in and FL2in in FIG. And the inlet side header tank 163 distributes and flows the inflowing refrigerant to the plurality of refrigerant tubes 160.
  • the outlet-side header tank 164 is formed with a refrigerant outlet 164f through which the refrigerant flows out from the outlet-side header tank 164.
  • the outlet-side header tank 164 collects the refrigerant flowing in from each of the plurality of refrigerant tubes 160, and the refrigerant is condensed from the refrigerant outlet 164f to the condensing part 181 of the second heat radiating heat exchanger 18 as indicated by an arrow FLout in FIG. (Refer to FIG. 2) and the receiver 20 and flow toward the supercooling part 182 of the second heat radiating heat exchanger 18.
  • the first refrigerant inlet 163f is provided at one end portion 163h of the inlet side header tank 163 in the tube stacking direction
  • the second refrigerant inlet 163g is the other end of the inlet side header tank 163 in the tube stacking direction.
  • the portion 163i is provided.
  • the second refrigerant inlet 163g is provided at a position shifted from the first refrigerant inlet 163f in the tube stacking direction.
  • the refrigerant outlet 164f is disposed between the first refrigerant inlet 163f and the second refrigerant inlet 163g in the tube stacking direction. In detail, it arrange
  • the first refrigerant inlet 163f is provided at one end portion 163h of the inlet-side header tank 163 in the tube stacking direction, and the second refrigerant inlet 163g is tube stacked.
  • the other end portion 163i of the inlet side header tank 163 in the direction is provided. Therefore, for example, as compared with the configuration having only one refrigerant inlet, the first heat radiation heat exchanger 16 is enlarged, and the refrigerant distribution in the first heat radiation heat exchanger 16 is suppressed and the distribution of the refrigerant is uniform. There is an advantage that it is easy to approach the distribution. That is, it is possible to improve the distribution of the refrigerant in the first heat radiation heat exchanger 16, in other words, the distribution to each refrigerant tube 160.
  • the refrigerant outlet 164f is disposed between the first refrigerant inlet 163f and the second refrigerant inlet 163g in the tube stacking direction, it is possible to further improve the distribution of the refrigerant to each refrigerant tube 160. is there.
  • this embodiment is a modification based on 1st Embodiment, it is also possible to combine this embodiment with the above-mentioned 3rd Embodiment.
  • the vehicle air conditioner 100 is mounted on, for example, a bus vehicle.
  • the vehicle on which the vehicle air conditioner 100 is mounted is not limited to a bus vehicle or the like.
  • the outlet side header tank 164 shown in FIG. 3 may have a structure in which the internal space is not divided like the outlet side header tank 164 shown in FIG.
  • the vehicle air conditioner 100 includes two evaporators 28 and 30.
  • the number of the evaporators 28 and 30 is not limited, and the vehicle air conditioner 100 may include one evaporator or three or more evaporators.
  • the first evaporator unit of the vehicle air conditioner 100 includes the first evaporator 28, and the second evaporator unit includes the second evaporator 30.
  • the first evaporator unit and the second evaporator unit are not limited to having one evaporator.
  • one or both of the first evaporator unit and the second evaporator unit may have a plurality of small evaporators.
  • the condenser unit 19 includes the first heat radiation heat exchanger 16 and the second heat radiation heat exchanger 18.
  • the condenser unit 19 may have one or three or more heat dissipation heat exchangers.
  • the condenser unit includes a condensing unit and one or more subcooling units. And the condenser unit is arrange
  • the first heat dissipation heat exchanger and the second heat dissipation heat exchanger are arranged between the first evaporator and the second evaporator in the width direction of the vehicle.
  • the 2nd heat dissipation heat exchanger which has a supercooling part is arranged ahead of a run direction to the 1st heat dissipation heat exchanger.
  • the first heat dissipation heat exchanger includes a condensing part of the second heat dissipation heat exchanger in the refrigerant flow from the compressor to one of the first evaporator and the second evaporator. It is connected in series and provided upstream of the condensing part. And the whole quantity of the refrigerant
  • the amount of outside air passing through the second heat dissipation heat exchanger passes through the first heat dissipation heat exchanger. It is provided to be larger than the air volume of the outside air. Therefore, it is possible to promote cooling of the refrigerant in the supercooling portion of the second heat dissipation heat exchanger, among the first heat dissipation heat exchanger and the second heat dissipation heat exchanger. And it is possible to improve the air_conditioning
  • the refrigerant tubes of the first heat-dissipating heat exchanger are stacked in one direction, and the second refrigerant inlet is provided at a position shifted from the first refrigerant inlet in the one direction. ing. Therefore, it is possible to improve the distribution of the refrigerant in the first heat radiating heat exchanger, in other words, the distribution of the refrigerant to each refrigerant tube.
  • the first refrigerant inlet is provided at one end portion of the inlet-side header tank in the one direction, and the second refrigerant inlet is the inlet side in the one direction. It is provided at the other end portion of the header tank. Therefore, it is possible to improve the distribution of the refrigerant in the first heat radiating heat exchanger, in other words, the distribution of the refrigerant to each refrigerant tube.
  • the refrigerant outlet is disposed between the first refrigerant inlet and the second refrigerant inlet in the one direction. Therefore, this configuration can also improve the distribution of the refrigerant to each refrigerant tube.
  • the first heat-dissipating heat exchanger has a first condensing part and a second condensing part provided in parallel with each other in the refrigerant flow in the first heat-dissipating heat exchanger. is doing. Therefore, compared with the case where the 1st condensation part and the 2nd condensation part are connected in series, for example, it is possible to make the two condensation parts exhibit the same degree of condensation ability.
  • the first heat-dissipating heat exchanger is arranged such that the first condensing part is aligned with the second condensing part in the width direction of the vehicle. Therefore, it is possible for the outside air to flow evenly from the front to the first condensing unit and the second condensing unit, and to suppress the unevenness of the heat exchange capacity between the first condensing unit and the second condensing unit.
  • the outlet-side header tank of the first heat-dissipating heat exchanger collects the refrigerant flowing in from each of the plurality of first refrigerant tubes and the plurality of second refrigerant tubes and performs second heat dissipation. Flow toward the supercooling section of the heat exchanger. Therefore, piping for collecting the refrigerant flowing in from the plurality of first refrigerant tubes and the refrigerant flowing in from the plurality of second refrigerant tubes is unnecessary, and the first heat dissipation heat exchanger and the second heat dissipation heat exchanger are unnecessary. It is possible to simply configure the refrigerant pipe connecting the two.
  • the plurality of first refrigerant tubes are arranged so as to be aligned in the width direction of the vehicle with respect to the plurality of second refrigerant tubes. Therefore, it is possible for the outside air to circulate evenly from the front to the first refrigerant tube and the second refrigerant tube, and to suppress the unevenness of the heat exchange capability between the first refrigerant tube and the second refrigerant tube.
  • the second heat radiating heat exchanger is arranged such that the condensing part is aligned with the supercooling part in the width direction of the vehicle. Therefore, it is possible to introduce the outside air from the front to the condensing part of the second heat radiating heat exchanger with the same air volume as the supercooling part. As a result, for example, it is easy to reduce the size of the condensing unit in the second heat radiating heat exchanger.
  • the second heat radiating heat exchanger is arranged such that the supercooling portion is arranged in front of the condensing portion in the traveling direction. Therefore, it is easy to increase the air volume of the outside air flowing to the supercooling part of the second heat radiating heat exchanger.

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

Abstract

L'invention concerne un appareil de climatisation de véhicule qui comprend : une unité de condenseur (19) ; une première unité d'évaporateur (28) ; et une seconde unité d'évaporateur (30). La seconde unité d'évaporateur est disposée parallèlement à la première unité d'évaporateur dans la direction de largeur (DR3) d'un véhicule (8). L'unité de condenseur comporte des parties de condensation (166, 167, 168, 181) qui réalisent un échange de chaleur entre l'air extérieur et un réfrigérant comprimé par un compresseur (14), ce qui permet de condenser le réfrigérant ; et une ou plusieurs parties de surfusion (169, 182) qui réalisent un échange de chaleur entre l'air extérieur et le réfrigérant en phase liquide condensé par les parties de condensation, ce qui permet de refroidir le réfrigérant en phase liquide. La première unité d'évaporateur et la seconde unité d'évaporateur réalisent chacune un échange de chaleur entre le réfrigérant décomprimé s'écoulant depuis la ou les parties de surfusion et l'air envoyé à l'intérieur du véhicule, ce qui permet d'évaporer le réfrigérant décomprimé. Une partie de surfusion (182) d'une ou plusieurs parties de surfusion est disposée dans l'unité de condenseur de façon à être déviée vers l'avant dans la direction de déplacement de véhicule.
PCT/JP2016/000607 2015-02-27 2016-02-05 Appareil de climatisation de véhicule WO2016136157A1 (fr)

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Application Number Priority Date Filing Date Title
EP16754913.8A EP3263375B1 (fr) 2015-02-27 2016-02-05 Appareil de climatisation de véhicule

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JP2015-038650 2015-02-27
JP2015038650 2015-02-27
JP2016-006141 2016-01-15
JP2016006141A JP2016164062A (ja) 2015-02-27 2016-01-15 車両用空調装置

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109353187A (zh) * 2018-11-27 2019-02-19 珠海格力电器股份有限公司 空调系统及具有其的车辆

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62411U (fr) * 1985-06-20 1987-01-06
JPS62244711A (ja) * 1986-04-17 1987-10-26 Mitsubishi Electric Corp 車両用空気調和装置
JPH09216512A (ja) * 1995-01-12 1997-08-19 Denso Corp 車両用屋上装着型冷房装置
JP4110906B2 (ja) * 2002-02-28 2008-07-02 株式会社デンソー 車両用空調装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62411U (fr) * 1985-06-20 1987-01-06
JPS62244711A (ja) * 1986-04-17 1987-10-26 Mitsubishi Electric Corp 車両用空気調和装置
JPH09216512A (ja) * 1995-01-12 1997-08-19 Denso Corp 車両用屋上装着型冷房装置
JP4110906B2 (ja) * 2002-02-28 2008-07-02 株式会社デンソー 車両用空調装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109353187A (zh) * 2018-11-27 2019-02-19 珠海格力电器股份有限公司 空调系统及具有其的车辆

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