JP2011190982A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger capable of preventing temperature unevenness of air taken out of the heat exchanger. <P>SOLUTION: The heat exchanger has a refrigerant condensing part 21 including a plurality of tubes 21a formed to extend in the vertical direction and radiation fins 21b joined to the tubes 21a for heat-exchanging with external gas by flowing a refrigerant body through the tubes 21a, and a refrigerant supercooling part 23 including a receiver tank 22 for gas-liquid separating the refrigerant body, and a deriving part 23c and an introducing part 23d of the refrigerant body in the vertical direction for heat-exchanging between the refrigerant body and the external gas. The refrigerant body flows through the refrigerant condensing part 21, the receiver tank 22, and the refrigerant supercooling part 23 in this order. The external gas flows around the refrigerant supercooling part 23 and then flows around the refrigerant condensing part 21. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a heat exchanger used in, for example, a vehicle air conditioner.

  Various types of air conditioners for vehicles have been proposed for fuel cell vehicles, electric vehicles, and the like with relatively little exhaust heat. In this type of vehicle air conditioner, it is required to improve the performance of the heat pump. For example, a technique of providing a supercooling part (subcooling part) downstream of a condenser (heater) has been proposed (Patent Document 1). reference).

JP-A-6-341736 (Claim 1, FIG. 1)

  However, in the technique described in Patent Document 1, the refrigerant is configured to flow in the order of the condenser and the supercooling unit in order to improve the heat pump capability. However, the temperature unevenness of the air taken out from the heat exchanger has never been so far. It has not been considered.

  This invention solves the said conventional problem, and makes it a subject to provide the heat exchanger which can prevent the temperature nonuniformity of the air taken out from a heat exchanger.

  The present invention includes a tube formed by extending a plurality of members in the vertical direction and a fin joined to the tube, and a refrigerant condensing unit that exchanges heat with an external gas by passing a refrigerant body through the tube; A gas-liquid separation unit that separates the refrigerant body from gas and liquid; a refrigerant subcooling unit that includes a derivation unit and an introduction unit of the refrigerant body in a vertical direction, and performs heat exchange between the refrigerant body and the gas from the outside; And the refrigerant body flows in the order of the refrigerant condensing unit, the gas-liquid separation unit, and the refrigerant subcooling unit, and after the gas from the outside flows through the refrigerant subcooling unit, the refrigerant It is configured to flow to the condensing part.

  According to this, the flow direction of the refrigerant flowing through the refrigerant condensing unit and the refrigerant subcooling unit are formed by extending the tube in the vertical direction and forming the lead-out unit and the introduction unit above and below the refrigerant subcooling unit. It is possible to oppose the flow direction of the refrigerant flowing through the heat exchanger, and the temperature of the gas taken out from the heat exchanger can be made uniform.

  That is, in the refrigerant condensing unit, the refrigerant flows from the upper side to the lower side, whereby the gas is cooled by the heat radiation of the refrigerant body, and the condensed refrigerant body (liquid refrigerant) is accumulated on the lower side. When the refrigerant body (liquid refrigerant) flows from the lower introduction part to the upper outlet part, the gas is further cooled by the heat radiation of the refrigerant body. As described above, the temperature of the refrigerant body decreases from the upper side to the lower side of the refrigerant condensing unit, and the temperature of the refrigerant body decreases from the lower side to the upper side of the refrigerant subcooling unit. It becomes possible to prevent temperature unevenness.

  In addition, an overheating region is disposed at the refrigerant inlet of the refrigerant condensing unit, a supercooling region is disposed at the refrigerant outlet of the refrigerant supercooling unit, and at least after gas from the outside flows through the supercooling region, A part flows into the overheating region.

  According to this, for example, a refrigerant body having a temperature higher than the condensing temperature flows in the superheated region of the refrigerant inlet portion, and a refrigerant body having a temperature lower than the condensing temperature flows in the supercooling region of the refrigerant outlet portion. The gas discharged from the exchanger is discharged at a temperature close to the intermediate condensation temperature. As described above, by arranging the overheating region and the overcooling region, it is possible to take out a gas having no temperature unevenness in the vertical direction of the heat exchanger. This makes it possible to obtain stable heat exchange performance.

  Further, the present invention is characterized in that a branch channel that branches a path leading to the gas-liquid separator and a path leading the refrigerant body to the outside is provided.

  According to this, by providing the branch flow path upstream of the gas-liquid separation unit, it is not necessary for the gas-liquid separation unit side when it is not necessary to flow the refrigerant through the gas-liquid separation unit and the refrigerant subcooling unit during the cooling operation. It is possible to prevent the refrigerant body from flowing through.

  ADVANTAGE OF THE INVENTION According to this invention, the heat exchanger which can prevent the temperature nonuniformity of the air taken out from a heat exchanger can be provided.

It is a disassembled perspective view which shows the heat exchanger of 1st Embodiment. It is an external appearance perspective view which shows the heat exchanger of 1st Embodiment. (A) is sectional drawing which shows an upper header, (b) is sectional drawing which shows a lower header. It is sectional drawing which shows the connection part of a receiver tank and a refrigerant | coolant supercooling part. It is a whole block diagram which shows the flow of the refrigerant body at the time of heating operation at the time of applying the heat exchanger of this embodiment to a vehicle air conditioner. It is a whole block diagram which shows the flow of the refrigerant body at the time of air_conditionaing | cooling operation at the time of applying the heat exchanger of this embodiment to a vehicle air conditioner. It is explanatory drawing which shows typically the effect in the heat exchanger of this embodiment, (a) is this embodiment, (b) is a comparative example. The heat exchanger of 2nd Embodiment is shown, (a) is a partially-omission perspective view, (b) is XX sectional drawing of (a), (c) is YY sectional drawing of (a). It is. The heat exchanger of 3rd Embodiment is shown, (a) is a longitudinal cross-sectional view, (b) is a perspective view which shows the structure of a tube. It is sectional drawing which shows the structure of the connection part of a refrigerant | coolant condensing part and a refrigerant | coolant supercooling part, and a receiver tank, (a) is a modification, (b) is another modification. (A) And (b) is a modification of the internal structure of a tube, (c)-(f) is a modification of the cross-sectional structure of a header.

Hereinafter, embodiments according to the present invention will be described with reference to the drawings.
As shown in FIGS. 1 and 2, the heat exchanger 20 of the first embodiment includes a refrigerant condensing unit 21, a receiver tank (gas-liquid separating unit) 22, and a refrigerant subcooling unit 23. A refrigerant supercooling unit 23 is stacked on the refrigerant condensing unit 21.

  In the refrigerant condensing unit 21, a plurality of tubes 21a, 21a,... Extending in the vertical direction (vertical direction) are arranged at equal intervals, and corrugated heat radiation fins (fins) 21b are provided between the tubes 21a, 21a. It is provided and configured. The tubes 21a and the heat radiating fins 21b are formed of a metal material (aluminum, copper, etc.) having high thermal conductivity (heat dissipation).

  The refrigerant condensing unit 21 includes an upper header 21c that distributes the refrigerant discharged from the compressor 10 described later to each tube 21a, and a lower header 21d in which the refrigerant passing through each tube 21a gathers at the lower part, It has. Details of the upper header 21c and the lower header 21d will be described later.

  The receiver tank 22 is disposed on the sides of the refrigerant condensing unit 21 and the refrigerant subcooling unit 23 (see FIG. 2), and the refrigerant body (liquid refrigerant) liquefied by the refrigerant condensing unit 21 and the refrigerant body (liquid refrigerant) that has not been liquefied ( (Gas refrigerant).

  That is, the receiver tank 22 has a vertically long cylindrical shape, and has a tank portion 22a that separates and stores liquid refrigerant and gas refrigerant. In addition, about the refrigerant | coolant body introduce | transduced into the tank part 22a, the moisture contained in it may be removed. In the present embodiment, for example, a desiccant is filled in the bottom of the tank portion 22a to enable moisture removal.

  The refrigerant subcooling section 23 performs heat exchange between the liquid refrigerant derived from the receiver tank 22 and air-conditioning air (gas from the outside) A, and further cools the liquid refrigerant to make it a complete liquid refrigerant. is there.

  Moreover, the refrigerant | coolant supercooling part 23 is comprised by the tube 23a formed with the material similar to the refrigerant | coolant condensing part 21, and the radiation fin 23b which covers this tube 23a.

  The tube 23a is formed to extend in the horizontal direction, and has a meandering shape from the lower side to the upper side while being folded back in a U shape at positions corresponding to both ends of the refrigerant condensing unit 21.

  The heat radiating fins 23b are of a plate type, and a plurality of vertically long fins are arranged in parallel so as to cover the periphery of the meandering tube 21a.

  In addition, each shape of the radiation fin 21b of the refrigerant | coolant condensing part 21 and the radiation fin 23b of the refrigerant | coolant subcooling part 23 is as follows. There is no particular limitation as long as both of them can be passed between them, and for example, both can be appropriately changed to a corrugated type.

  As shown in FIG. 3 (a), the upper header 21c has a space in which the refrigerant flows in the horizontal direction, and the upper end of each tube 21a is a through hole formed in the bottom surface of the upper header 21c. The upper header 21c and each tube 21a are joined to each other. As a result, the refrigerant introduced from the compressor 10 into the upper header 21c is distributed and introduced into the respective tubes 21a as indicated by arrows, and flows downward.

  As shown in FIG. 3B, the lower header 21d has a space through which the refrigerant flows in the horizontal direction, and the lower end of each tube 21a is formed on the upper surface of the lower header 21d. Each tube 21a and the lower header 21d are joined by being inserted into the through hole 21d1.

  The lower header 21d is connected to the receiver tank 22 via a pipe 22b. The pipe 22b extends from the bottom of the tank portion 22a through the tank portion 22a upward to a predetermined length. The predetermined length is preferably set at a position where the liquid refrigerant does not exceed the tip (upper end) of the pipe 22b when the liquid refrigerant accumulates. FIG. 3A shows a state where the predetermined length is shorter than the actual length for convenience of explanation.

  The lower header 21d is connected to a pipe a2 (see FIG. 6) flowing toward the capacitor 30 described later on the side opposite to the receiver tank 22. In the present embodiment, the lower header 21d constitutes a branch channel.

  As shown in FIG. 4, the refrigerant supercooling unit 23 is connected to the receiver tank 22 via a pipe 22c. That is, the pipe 22 c is formed extending downward from the bottom of the receiver tank 22 and is connected to the inlet 23 a 1 (introduction portion 23 c) of the tube 23 a of the refrigerant supercooling portion 23.

  The heat exchanger 20 configured as described above is used as a vehicle air conditioner 1A for a vehicle V such as an electric vehicle (EV), a fuel cell vehicle (FCV), and a hybrid vehicle (HEV). Can be used.

  As shown in FIGS. 5 and 6, the vehicle air conditioner 1 </ b> A includes a compressor 10, a heat exchanger 20, a condenser 30, an automatic expansion valve 40, a first evaporator 50, a second evaporator 60, The switching means 70 and an ECU (control device) 80 are included.

  The compressor 10 is driven by a motor (or engine) or the like, sucks and compresses a refrigerant body, and discharges a high-temperature and high-pressure refrigerant body toward the heat exchanger 20.

  The condenser 30 includes a condensing unit 31 and a receiver tank 32. The condenser 30 is disposed in a space in the hood at the front end of the vehicle V, and the refrigerant flowing through the condensing unit 31 is introduced from the front of the vehicle V and heat. Replacement (heat dissipation) is performed. The condensing unit 31 includes a plurality of tubes (not shown) extending in the left-right direction, radiating fins (not shown), and the like.

  The receiver tank 32 is disposed on the side of the condensing unit 31 and is formed in a cylindrical shape like the receiver tank 22 and has a function of separating the liquid refrigerant and the gas refrigerant in the condensing unit 31 during the cooling operation (gas-liquid separation). Function).

  The automatic expansion valve 40 can change the opening degree according to the temperature of the refrigerant body, and is means for detecting the temperature and pressure of the refrigerant body flowing out from the first evaporator 50 (or the second evaporator 60) described later (non- The opening of the automatic expansion valve 40 can be changed according to the temperature and pressure of the refrigerant flowing out from the first evaporator (or the second evaporator 60), and the flow rate of the refrigerant can be changed. .

  The first evaporator 50 exchanges heat with the air-conditioning air A (heat source) discharged from the passenger compartment C through the refrigerant flowing through the interior, and is used for air-conditioning such as the cargo compartment D (trunk room) of the vehicle V. The air A is disposed at the rear part of the vehicle V from which the air A is discharged outside the vehicle. That is, in the 1st evaporator 50, heat is taken in from the air-conditioning air A (heat source) discharged | emitted from the vehicle interior C of the vehicle V outside a vehicle via a refrigerant body at the time of heating operation. The heat source is not limited to the air-conditioning air A exhausted from the vehicle interior C, and exhaust heat from a drive portion (such as a motor) of the vehicle V may be used.

  The second evaporator 60 is disposed in the passenger compartment C and performs heat exchange between the refrigerant body and the air conditioning air A, and is located upstream of the heat exchanger 20 with respect to the flow of the air conditioning air A. Has been placed.

  The refrigerant outlet 10b of the compressor 10 is connected to the refrigerant inlet 21a1 of the refrigerant condensing unit 21 via a pipe a1, and the refrigerant outlet 21a2 of the refrigerant condensing part 21 is a pipe a2 provided with an electromagnetic valve V1. Is connected to the inlet 30a of the refrigerant body of the capacitor 30. The solenoid valve V1 constitutes a capacitor shut-off means that shuts off the flow of the refrigerant to the capacitor 30 by closing the solenoid valve V1.

  The outlet 30b of the refrigerant body of the condenser 30 is connected to the inlet 40a on the pressure reducing side of the automatic expansion valve 40 via a pipe a3 provided with a check valve V2. The outlet 40b on the pressure reducing side of the automatic expansion valve 40 is connected to the refrigerant inlet 50a of the first evaporator 50 via a pipe a4. The check valve V <b> 2 is a valve that allows only the flow of the refrigerant from the capacitor 30 to the automatic expansion valve 40.

  The refrigerant body outlet 50b of the first evaporator 50 is connected to the refrigerant body inlet 60a of the second evaporator 60 via a pipe a5. The outlet 60b of the refrigerant body of the second evaporator 60 is connected to the temperature detection side inlet 40c of the automatic expansion valve 40 via a pipe a6. An outlet 40d on the temperature detection side of the automatic expansion valve 40 is connected to a refrigerant inlet 10a of the compressor 10 via a pipe a7.

  The outlet 23a2 of the refrigerant supercooling section 23 of the heat exchanger 20 is connected to the check valve V2 and the automatic expansion valve 40 via a pipe a8 including an electromagnetic valve V3, an intermediate throttle S, and a check valve V4 in order from the upstream side. It connects so that it may join to the piping a3 between. The check valve V4 is a valve that allows only the flow of the refrigerant from the refrigerant subcooling section 23 to the automatic expansion valve 40. Moreover, the electromagnetic valve V3 constitutes a supercooling portion bypassing means that closes the solenoid valve V3 and flows the coolant bypassing the refrigerant supercooling portion 23.

  A pipe a3 between the outlet 30b of the capacitor 30 and the check valve V2 is connected so as to join the pipe a7 via a pipe a9 having an electromagnetic valve V5 and a check valve V6 in order from the upstream side. Yes. The check valve V6 is a valve that allows only the flow of the refrigerant from the pipe a3 side to the pipe a7 side.

  Between the pipe a4 and the pipe a5, a pipe a10 provided with an electromagnetic valve V7 that functions as a first evaporator bypass means is connected.

  Between the pipe a5 and the pipe a6, a pipe a11 including an electromagnetic valve V8 that functions as a second evaporator bypass means is connected.

  The cooling / heating switching means 70 switches between the flow of the refrigerant body and air-conditioning air A during the heating operation and the flow of the refrigerant body and air-conditioning air A during the cooling operation, and the first evaporator bypass means and the second evaporator. The air damper 71 is configured together with the bypass means, the condenser cutoff means, and the supercooling portion bypass means.

  The air damper 71 is disposed in a space between the heat exchanger 20 and the second evaporator 60. During the heating operation, the air damper 71 is opened, and the air-conditioning air A introduced from the outside of the vehicle into the vehicle interior C is the second. The flow is controlled so as to pass through the evaporator and through the heat exchanger 20 (see FIG. 5). On the other hand, during the cooling operation, the air damper 71 is closed, and the flow is controlled so that the air conditioning air A introduced into the vehicle interior C passes through the second evaporator 60 and does not pass through the heat exchanger 20. (See FIG. 6).

  The ECU 80 controls opening and closing of the electromagnetic valves V1, V3, V5, V7, and V8, and also controls the opening and closing of the air damper 71 so that the flow of the refrigerant and the air conditioning air A during the heating operation and the cooling operation are performed. To control the flow.

  Next, the operation of the vehicle air conditioner 1A will be described. The vehicle V shown in FIG. 5 shows the heating operation, and the electromagnetic valves V1 and V7 are closed. The vehicle V shown in FIG. 6 shows the cooling operation, and the electromagnetic valves V3, V5, and V8 are closed.

(Operation during heating operation)
As shown in FIG. 5, during the heating operation, when the compressor 10 is driven, the refrigerant body sucked from the suction port 10a of the compressor 10 and discharged from the discharge port 10b is transferred to the heat exchanger 20 via the pipe a1. Supplied. As a result, a high-temperature and high-pressure refrigerant (gas) is supplied to the heat exchanger 20.

  The refrigerant body supplied from the compressor 10 is introduced into the refrigerant condensing unit 21 of the heat exchanger 20, and flows from the outside of the vehicle to the vehicle interior C when flowing in the refrigerant condensing unit 21 from the upper side to the lower side (see FIG. 1). Heat exchange is performed with the air-conditioning air A to be introduced. That is, the refrigerant body is condensed by being cooled by the air-conditioning air A (cold outside air), and becomes a low-temperature liquid refrigerant from a high-temperature gas refrigerant. On the other hand, the air-conditioning air A is heated by heat released when it is condensed.

  The refrigerant body (liquid refrigerant) derived from the refrigerant condensing unit 21 is introduced into the receiver tank 22 via the pipe 22b. In the receiver tank 22, the refrigerant body is gas-liquid separated, that is, the liquid refrigerant is accumulated in the lower part of the tank part 22a (see FIG. 1), and the gas refrigerant that has not been liquefied in the refrigerant condensing part 21 is accumulated in the upper part of the tank part 22a. . The liquid refrigerant separated from the gas and liquid in the receiver tank 22 is introduced from the bottom of the receiver tank 22 into the refrigerant supercooling unit 23 via the pipe 22c.

  The refrigerant body (liquid refrigerant) introduced into the introduction part 23c provided at the lower end of the refrigerant supercooling part 23 exchanges heat with air-conditioning air A (cold outside air) introduced into the vehicle interior C. Since the refrigerant subcooling unit 23 is located upstream (upward) of the refrigerant condensing unit 21 with respect to the flow of the air conditioning air A, the refrigerant body is further cooled by the air conditioning air A and the condensation temperature is increased. It becomes a lower temperature liquid refrigerant. This processing is a so-called subcool region.

  The liquid refrigerant led out from the lead-out part 23d provided at the upper end of the refrigerant subcooling part 23 passes through the intermediate throttle S, so that the liquid refrigerant is decompressed.

  The liquid refrigerant decompressed by the intermediate throttle S is introduced into the automatic expansion valve 40 via the pipe a3. The liquid refrigerant decompressed by the automatic expansion valve 40 is changed to a refrigerant body in which liquid and gas are mixed and introduced into the first evaporator 50.

  In the first evaporator 50, heat is exchanged between the air for air A discharged from the passenger compartment C to the cargo compartment D (see FIG. 5) and the refrigerant body. That is, when the refrigerant body passes through the first evaporator 50, the refrigerant body evaporates by absorbing the heat of the air-conditioning air A. Thereby, the heat of the vehicle interior C can be utilized effectively.

  The refrigerant derived from the first evaporator 50 passes through the pipe a11 that bypasses the second evaporator 60, and returns to the compressor 10 through the pipe a6, the automatic expansion valve 40, and the pipe a7.

  In the vehicle air conditioner 1 </ b> A during the heating operation, the air damper 71 is fully opened by the ECU 80, so that the air conditioning air A taken from outside the vehicle passes through both the second evaporator 60 and the heat exchanger 20. In the second evaporator 60, since the refrigerant bypasses, heat exchange is not performed, and in the heat exchanger 20, the air-conditioning air A is heated by the high-temperature / high-pressure refrigerant due to the heat radiation in the refrigerant condensing unit 21, and the warm air is It is introduced into the passenger compartment C.

  During the heating operation, the solenoid valve V5 is opened by the ECU 80, so that the condenser 30 and the suction port 10a of the compressor 10 communicate with each other via the pipe a9. Thereby, the refrigerant body (liquid refrigerant) remaining in the capacitor 30 such as the receiver tank 32 is sucked through the pipe a9 by the suction force (negative pressure) generated at the suction port 10a when the compressor 10 is operated. Therefore, the refrigerant body can be used effectively.

(Operation during cooling operation)
As shown in FIG. 6, during the cooling operation, when the compressor 10 is driven, the refrigerant body compressed by the compressor 10 is supplied to the heat exchanger 20 via the pipe a1. As a result, a high-temperature and high-pressure refrigerant (gas) is supplied to the heat exchanger 20.

  The refrigerant body supplied from the compressor 10 is introduced into the refrigerant condensing unit 21 of the heat exchanger 20. However, since the air damper 71 is controlled to be fully closed, the refrigerant body flows through the refrigerant condensing unit 21. Heat exchange with the air-conditioning air A is not performed. Therefore, the air-conditioning air A is not heated by the high-temperature / high-pressure refrigerant body. Further, since the electromagnetic valve V1 is opened and the electromagnetic valve V3 is closed by the ECU 80, the refrigerant body that has passed through the refrigerant condensing unit 21 does not flow to the receiver tank 22 and the refrigerant subcooling unit 23, but via the pipe a2. Are introduced into the capacitor 30.

  The refrigerant introduced into the condenser 30 is cooled by exchanging heat with the outside air when passing through the condenser 31. The refrigerant body after heat exchange is gas-liquid separated in the receiver tank 32, and the liquid refrigerant is separated from the refrigerant body. The liquid refrigerant in the receiver tank 32 is introduced into the automatic expansion valve 40 through the pipe a3.

  The liquid refrigerant introduced into the automatic expansion valve 40 is depressurized, and the liquid refrigerant and the gas refrigerant are mixed. The refrigerant body that has passed through the automatic expansion valve 40 is introduced into the second evaporator 60 through the pipe a10 that bypasses the first evaporator 50.

  In the second evaporator 60, heat exchange between the air-conditioning air A introduced into the passenger compartment C and the refrigerant body, that is, when the refrigerant body passes through the second evaporator 60, the low-temperature refrigerant body cooled by the capacitor 30 is By absorbing the heat of the air conditioning air A, the air conditioning air A is cooled and introduced into the passenger compartment C.

  The refrigerant body derived from the second evaporator 60 returns to the compressor 10 via the pipe a6, the automatic expansion valve 40, and the pipe a7.

  In the vehicle air conditioner 1A during the cooling operation, since the air damper 71 is controlled to be fully closed, the air-conditioning air A cooled by the second evaporator 60 is not heated by the heat exchanger 20, and cold air is It is introduced into the room C.

  Note that during the dehumidifying heating operation, the ECU 80 is further controlled to close the electromagnetic valve V8 so that the refrigerant passes through the second evaporator 60 with respect to the state during the heating operation. In addition, description is abbreviate | omitted about the part which overlaps with the operation | movement at the time of heating operation.

  That is, the refrigerant introduced from the first evaporator 50 to the second evaporator 60 absorbs the heat of the air-conditioning air A, and the air-conditioning air A is cooled. And the refrigerant body derived | led-out from the 2nd evaporator 60 returns to the compressor 10 via the piping a6, the automatic expansion valve 40, and the piping a7.

  As described above, when the refrigerant derived from the first evaporator 50 and the second evaporator 60 that exchanges heat with the air-conditioning air A are provided, the refrigerant flowing into the second evaporator 60 during the dehumidifying heating operation is provided. Since air-conditioning air A is cooled by heat absorption, water vapor contained in air (air-conditioning air A) taken from outside air is removed, and dehumidification is performed.

  As described above, according to the heat exchanger 20 of the first embodiment, the tube 21a is formed by extending in the vertical direction, the flow direction of the refrigerant flowing through the refrigerant condensing unit 21 is directed downward, and the refrigerant is supercooled. In the refrigerant condensing unit, the temperature of the refrigerant body is changed from the top to the bottom by forming the refrigerant body introduction part on the lower side of the part 23 and forming the refrigerant body outlet part on the upper side so that the flow direction of the refrigerant body is upward. Since the temperature of the refrigerant body decreases from the bottom to the top in the refrigerant subcooling section, the temperature of the gas exiting from the refrigerant condensing section can be made uniform.

  Further, according to the heat exchanger 20 of the first embodiment, the superheat region R1 is arranged at the refrigerant inlet portion Q1 (see FIG. 3A) of the refrigerant condensing portion 21, and the refrigerant outlet portion Q2 of the refrigerant subcooling portion 23 is disposed. By arranging the supercooling region R2 (see FIG. 1) and flowing the air-conditioning air A to the supercooling region R2, the following effects are obtained.

  That is, as shown in FIG. 7A, when cold air-conditioning air A is introduced into the refrigerant subcooling section 23 from the outside of the vehicle, in the supercooling region R2, the condensation temperature cooled by the refrigerant subcooling section 23 is higher. A refrigerant body having a low temperature flows, and in the superheat region R1, a refrigerant gas having a temperature higher than the condensation temperature from the compressor 10 flows. Therefore, the refrigerant condensing unit is located at a height position of the supercooling region R2 and the superheat region R1. The air-conditioning air A taken out from 21 becomes wind (gas) at a certain warm temperature (for example, Ta). By the way, in the region R3 on the refrigerant inlet side of the refrigerant subcooling portion 23, a refrigerant body close to the condensation temperature just introduced into the refrigerant subcooling portion 23 flows, and in the region R4 on the refrigerant outlet portion side of the refrigerant condensing portion 21, Since the refrigerant body close to the condensation temperature radiated by the refrigerant condensing unit 21 flows, the air-conditioning air A taken out from the refrigerant condensing unit 21 at the height positions of the regions R3 and R4 is a warm air having a temperature Ta similar to the above ( Gas).

  Incidentally, as a comparative example, as shown in FIG. 7B, when the air-conditioning air A is allowed to pass only through the refrigerant condensing unit 21, the refrigerant body having a temperature higher than the condensing temperature in the region R10 on the refrigerant inlet side. Therefore, the conditioned air A taken out from the refrigerant condensing part 21 becomes hot, and in the region R20 on the refrigerant outlet side, a refrigerant body close to the condensing temperature flows, so the air conditioned air A taken out from the refrigerant condensing part 21 becomes warm. . For this reason, temperature unevenness occurs above and below the refrigerant condenser 21.

  In this way, the same air conditioning air A is applied to the superheating region R1 of the refrigerant condensing unit 21 arranged at the refrigerant inlet Q1 and the supercooling region R2 of the refrigerant subcooling unit 23 arranged at the refrigerant outlet Q2. By setting so as to flow, it is possible to prevent variations in temperature in other regions, and to obtain stable heat exchange performance. Note that the same air-conditioning air A flows means that the air-conditioning air A heat-exchanged by the refrigerant flowing in the supercooling region R2 is heat-exchanged by the refrigerant flowing in the superheating region R1.

  Moreover, according to the heat exchanger 20 of 1st Embodiment, as shown in FIG.3 (b), since the lower header 21d of the refrigerant | coolant condensing part 21 was comprised as a branch flow path, at the time of air_conditionaing | cooling operation, electromagnetic valve V3 ( By closing (see FIG. 6), the refrigerant body that has passed through the tube 21 a flows into the capacitor 30 without flowing into the receiver tank 22. On the other hand, at the time of heating operation, by closing the electromagnetic valve V1 (see FIG. 5), the refrigerant body that has passed through the tube 21a flows to the receiver tank 22 without going to the capacitor 30, and further passes through the refrigerant subcooling section 23. It is introduced into the automatic expansion valve 40. As described above, during the cooling operation, the refrigerant body can be prevented from flowing unnecessarily to the receiver tank 22 and the refrigerant supercooling unit 23.

  8A and 8B show a heat exchanger according to the second embodiment, in which FIG. 8A is a partially omitted perspective view, FIG. 8B is a sectional view taken along line XX of FIG. 8A, and FIG. 8C is YY of FIG. It is line sectional drawing. In the heat exchanger 200 of the second embodiment, a tube constituting the refrigerant condensing unit and a tube constituting the refrigerant subcooling unit are integrally formed.

  That is, as shown in FIG. 8A, the heat exchanger 200 includes a plurality of tubes 210 extending in the vertical direction, radiating fins 220 disposed between the tubes 210, an upper header 230, and a lower header 240. Yes. Since the receiver tank 22 is the same as that of the first embodiment, the same reference numerals are given and description thereof is omitted.

  As shown in FIG. 8C, the tube 210 includes a substantially elliptical cylindrical body 211 and a partition wall 212 that divides the space inside the cylindrical body 211 into two. The partition wall 212 is arranged so as to extend from the substantially upper end to the lower end of the tube 210 in the vertical direction so as to divide the space in the tube 210 into two. In addition, concave notches 214 and 214 are formed in the upper end portion 213 of the cylindrical body 211 at positions corresponding to the partition walls 212. Note that a concave notch 216 is similarly formed at the position corresponding to the partition wall 212 at the lower end portion 215 of the cylindrical body 211 (see FIG. 8B).

  The heat radiating fins 220 are corrugated fins, and are disposed over the entire side surfaces of the tube 210 (see FIG. 8A).

  As shown in FIG. 8 (b), the upper header 230 has a substantially mountain-shaped cross section when viewed from the flow direction of the refrigerant, and includes a base 231 to which each tube 210 is connected and an upper portion of the base 231. The cover 232 for covering and a partition plate 233 for partitioning the space of the upper header 230 at a position corresponding to the partition wall 212 are configured.

  The base 231 has a substantially plate shape extending in the arrangement direction of the tubes 210, and through holes 231 a into which the upper end portions 213 of the tubes 210 are inserted are formed at positions corresponding to the tubes 210. The cover 232 has a convex shape and is configured to close the upper portion of the base 231 and one end on the receiver tank 22 side. The partition plate 233 is formed to extend in the direction in which the tubes 210 are arranged, and is arranged so that the lower end edge of the tube 210 abuts the notch 214.

  The base 231, the cover 232, and the partition plate 233 formed in this way are joined by welding or the like. Note that the cross section of the flow path S10 of the tube 210 located on the leeward side of the air-conditioning air A is formed to be larger than the cross section of the flow path S20 of the tube 210 located on the upwind side. . Further, the upper header 230 is formed such that the cross section of the flow path S1 on the side corresponding to the flow path S10 is larger than the cross section of the flow path S3 on the side corresponding to the flow path S20. Similarly, in the lower header 240, the flow path cross section of the flow path S2 on the side corresponding to the flow path S10 is formed to be larger than the flow path cross section of the flow path S4 on the side corresponding to the flow path S20. Has been.

  The lower header 240 is configured in the same manner as the upper header 230 by a base 241 having a through-hole 241a into which the lower end portion 215 of the tube 210 is inserted, a cover 242 that covers the base 241 and a partition plate 243. A pipe 22b that communicates with the flow path S2 and a pipe 22c that communicates with the flow path S4 are connected to one end surface 240a of the lower header 240 on the receiver tank 22 side.

  In the heat exchanger 200 configured as described above, during the heating operation, the refrigerant introduced from the compressor 10 passes through the flow path S1 of the upper header 230, the flow path S10 of the tube 210, and the flow path S2 of the lower header 240. Thus, the air-conditioning air A is warmed. The refrigerant body heat-exchanged with the air-conditioning air A is introduced into the receiver tank 22 through the pipe 22b and separated into gas and liquid, and is introduced into the flow path S4 of the lower header 240 through the pipe 22c. Thereafter, the gas is introduced into the automatic expansion valve 40 (intermediate throttle S) through the flow path S20 of the tube 210 and the flow path S3 of the upper header 230.

  That is, in the heat exchanger 200 of the second embodiment, the refrigerant condensing unit is configured by the flow path S10 of the tube 210, the heat radiation fin 220, the flow path S1 of the upper header 230, and the flow path S2 of the lower header 240. Moreover, in 2nd Embodiment, the refrigerant | coolant supercooling part is comprised by the flow path S20 of the tube 210, the thermal radiation fin 220, the flow path S3 of the upper header 230, and the flow path S4 of the lower header 240.

  According to the heat exchanger 200 of the second embodiment configured as described above, as shown in FIG. 8 (b), the superheat region R1 of the refrigerant condensing part arranged in the refrigerant inlet part Q1, and the refrigerant outlet part Q2 Since the same air-conditioning air A flows to the supercooling region R2 of the refrigerant supercooling unit disposed in the air-conditioning system, the air-conditioning air A having the same temperature can be taken out in other regions. Stable heat exchange performance can be obtained without causing unevenness.

  In addition, according to the second embodiment, the lower header 240 configures the flow path S2 (branch flow path) that branches into the flow path that flows to the receiver tank 22 and the flow path that flows to the capacitor 30. During operation, the refrigerant body can be prevented from flowing unnecessarily to the receiver tank 22 and the refrigerant subcooling section.

  FIG. 9 shows a heat exchanger according to the third embodiment, in which (a) is a longitudinal sectional view and (b) is a perspective view showing a configuration of a tube. In the heat exchanger 300 of the third embodiment, the tube 310 constituting the refrigerant condensing part and the tube 320 constituting the refrigerant subcooling part are constituted by separate tubes.

  That is, the heat exchanger 300 includes a plurality of tubes 310 and 320 extending in the vertical direction, radiating fins 330 disposed between the tubes 310 and 320, an upper header 340, and a lower header 350.

  As shown in FIG. 9B, the tube 310 has a semi-track shape in the flow path, and the tube 320 has a semi-elliptical shape in the flow path. Further, the flat wall surface of the tube 310 and the flat wall surface of the tube 320 face each other, and the gap 360 is formed.

  The difference between the upper header 340 and the upper header 230 of the second embodiment is that, as shown in FIG. 9 (a9), through holes 341a, through which the upper ends of the tube 310 and the tube 320 are inserted into the base 341, 341b is also formed in the lower header 350. The lower header 350 is the second only in that through holes 351a and 351b into which the upper ends of the tubes 310 and 320 are inserted are formed in the base 351. It differs from the lower header 240 of the embodiment.

  Further, in the third embodiment, the refrigerant condensing unit is configured by the tube 310, the heat radiation fin 220, the flow path S1 of the upper header 340 and the flow path S2 of the lower header 350. In the third embodiment, the refrigerant supercooling section is configured by the tube 320, the heat radiation fin 220, the flow path S3 of the upper header 340, and the flow path S4 of the lower header 350.

  According to the heat exchanger 300 of the third embodiment configured as described above, a stable heat exchange performance can be obtained without causing temperature unevenness, as in the first and second embodiments. During the cooling operation, the refrigerant body can be prevented from flowing unnecessarily to the receiver tank 22 and the refrigerant subcooling section.

  In the two embodiments described above, the lower header 240 and the receiver tank 22 are connected using the pipes 22b and 22c. However, the present invention is not limited to this, and as shown in FIG. Inside, a block-shaped member 400 having a flow path 401 connecting the flow path S2 of the lower header 240 and the receiver tank 22 and a flow path 402 connecting the flow path S4 of the lower header 240 and the receiver tank 22 is provided. It may be used. 10B, the lower header 240 is formed to extend to the bottom side of the receiver tank 22, and the pipe 22b in the receiver tank 22 is connected to the communication hole 245 that opens on the upper surface of the receiver tank 22. And you may make it connect the opening part of the exit of the receiver tank 22 to the communicating hole 246 opened to an upper surface. The configuration shown in FIG. 10 may be applied to the first embodiment and the third embodiment.

  Moreover, the tubes 21a, 23a, 210, 310, and 320 shown in the embodiments of the present invention are not limited to simple cylinders. For example, as shown in FIGS. 11 (a) and 11 (b), A plurality of flow paths may be formed in the tube 210A, 310A, 320A by incorporating a plurality of partition walls s. Further, the partition wall 212 shown in FIG. 8C may be shared with the partition wall s of the tube 210A in FIG.

  Further, the headers 230 and 240 shown in FIG. 8 and the headers 340 and 350 shown in FIG. 9 may be formed integrally with a partition plate and a cover, as indicated by reference numeral 230A in FIG. 11C. In FIG. 11D, as shown by reference numeral 230B, the cover, the base, and the partition plate may be integrally formed. Moreover, in FIG.11 (e), as shown to the code | symbol 230C, the two headers which consist of the peak-shaped header h1 formed in the refrigerant | coolant condensing part side and the peak-shaped header h2 formed in the refrigerant | coolant subcooling part side are shown. A part of the partition plate may be formed on the surface where the headers h1 and h2 are in contact with each other by connecting on the opposite side surfaces. Further, in FIG. 11 (f), as shown by reference numeral 230D, a seal member t may be provided at a contact portion.

20, 200, 300 Heat exchanger 21 Refrigerant condensing part 21a Tube 21b Radiation fin (fin)
21c Upper header 21d Lower header (branch channel)
22 Receiver tank (gas-liquid separator)
23 Refrigerant supercooling part 23c Introducing part 23d Deriving part Q1 Refrigerant inlet part Q2 Refrigerant outlet part R1 Superheated area R2 Supercooled area

Claims (3)

A refrigerant condensing part that includes a tube formed by extending a plurality of members in the vertical direction and fins joined to the tube, and exchanges heat with gas from the outside by passing a refrigerant body through the tube;
A gas-liquid separator for gas-liquid separation of the refrigerant body;
A refrigerant supercooling section that includes an outlet portion and an introduction portion of the refrigerant body in a vertical direction, and performs heat exchange between the refrigerant body and the gas from the outside;
The refrigerant body flows in the order of the refrigerant condensing unit, the gas-liquid separating unit, and the refrigerant subcooling unit, and after the gas from the outside flows through the refrigerant subcooling unit, it flows into the refrigerant condensing unit A heat exchanger configured as described above. An overheating region is disposed at the refrigerant inlet of the refrigerant condensing unit,
A supercooling region is disposed at the refrigerant outlet of the refrigerant supercooling unit;
2. The heat exchanger according to claim 1, wherein at least a part of the gas from the outside flows in the superheating region after the gas from the outside flows in the supercooling region.   The said refrigerant | coolant condensing part was equipped with the branch flow path which branches the path | route derived | led-out to the said gas-liquid separation part, and the path | route which derive | leads-out a refrigerant | coolant body to the exterior. Heat exchanger.

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