JP2007024338A - Condenser cooling device for refrigerating cycle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve cooling performance without increasing air supply quantity in a condenser cooling device of a refrigerating cycle for cooling a condenser by a number of blower fans. <P>SOLUTION: This condenser cooling device is composed of a layered structure of a plurality of tubes 20 forming flow channels of a refrigerant and heat transfer fins 21 joined to the tubes 20, the condenser 10 exchanging heat between the refrigerant and the air, and the group of blower fans 13 composed of a number of blower fans for sending the air, the group of blower fans 13 is dispersed and mounted on the condenser 10 along the refrigerant flowing direction of the tube 20, and the blower fans in the group of blower fans 13 are successively operated from a refrigerant flow upstream side to a refrigerant flow downstream side, when the necessity of increasing heat radiating capacity of the condenser 10 is judged. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a condenser cooling device for a refrigeration cycle in which a condenser is cooled by a large number of blower fans, and is particularly suitable for use in a vehicle air conditioner.

  Conventionally, for example, an invention described in Patent Document 1 has been proposed as a condenser cooling device for a refrigeration cycle of a vehicle air conditioner. In this prior art, the condenser of the refrigeration cycle is arranged on the upstream side of the air flow of the engine cooling radiator, and two electric blower fans that generate cooling air are arranged side by side on the downstream side of the air flow of the condenser and the radiator. The refrigerant flowing in the condenser and the cooling water (hot water) flowing in the radiator are cooled by cooling air.

  These two blower fans are independently controlled to two kinds of air volumes, Hi level and Lo level, according to the high-pressure side pressure of the refrigeration cycle and the cooling load of the passenger compartment.

  For example, when the high-pressure side pressure is less than a predetermined value, the two blower fans are operated at the Lo level, which is a normal airflow level, and when the high-pressure side pressure reaches a predetermined value or more, the two blower fans are set to the maximum airflow Hi. It operates at the level to reduce the high pressure side pressure.

  Also, by determining the size of the cooling load from the amount of solar radiation, temperature, humidity, etc., and switching the air volume of the two blower fans independently according to the cooling load, the optimum airflow of the blower fan can be obtained. ing.

Thus, the amount of air passing through the condenser is finely adjusted to cool the condenser optimally.
Japanese Patent Laid-Open No. 9-76722

  By the way, in recent vehicles, the bumper phosphorus hose which is a vehicle structure tends to be disposed immediately before the air suction surface of the condenser as the engine room is reduced and overcrowded due to the expansion of the passenger compartment space.

  In such a vehicle, the bumper hose blocks the flow of the cooling air, so that a portion where the cooling air does not hit the condenser occurs. That is, since the air volume of the cooling air passing through the condenser is reduced, the cooling performance of the condenser is deteriorated in a vehicle-mounted state.

  This causes an increase in the high-pressure side pressure of the refrigeration cycle, so that the power for driving the compressor of the refrigeration cycle increases and the fuel consumption deteriorates.

  However, the prior art described in Patent Document 1 does not disclose any means for solving this problem. Moreover, if the air flow rate of the blower is simply increased to improve the cooling performance of the condenser, the power consumption of the blower will increase and the fuel efficiency will deteriorate.

  In view of the above points, an object of the present invention is to improve the cooling performance without increasing the air flow rate in a condenser cooling device for a refrigeration cycle in which the condenser is cooled by a large number of blower fans.

  In the present invention, technical means for achieving the above object are devised based on the following findings from experiments and research.

  Therefore, the knowledge of experiments and researches by the present inventor will be described first based on FIG. 11 to FIG. FIG. 11 is a schematic perspective view showing a state in which the condenser 10 is mounted on the vehicle, and FIG. 12 is a schematic front view of the condenser 10 in FIG. 11 viewed from the front of the vehicle. FIG. 13 is a heat dissipation characteristic diagram of the refrigerant when the entire surface of the condenser 10 in FIG. 11 is cooled with cooling air having a uniform airflow and temperature, and the distribution of the heat dissipation along the refrigerant flow path of the condenser 10. FIG.

  As is well known, the condenser 10 is connected to the refrigerant discharge side of the compressor 50 and the refrigerant inflow side of the decompression means (not shown) in the refrigeration cycle, and cools and condenses the discharged gas refrigerant of the compressor 50 with outside air. It is something to be made.

  As shown in FIG. 12, in the condenser 10, the heat exchange core portion 19 that performs heat exchange between the refrigerant and the blown air includes a plurality of tubes 20 in which the refrigerant flows and corrugated heat transfer fins 21. It is comprised by the laminated structure of.

  One end of the plurality of tubes 20 (the right end in FIG. 12 in this example) communicates with the first tank 22, and the other end (the left end in FIG. 12 in this example) communicates with the second tank 23. Both tanks 22 and 23 have a shape that extends in the direction in which the tubes 20 are stacked.

  The two tubes 20a and 22b arranged at predetermined intervals in the longitudinal direction in the first tank 22 and the one divider plate 23a arranged in the second tank 23 make the plurality of tubes 20 first to first. The 4th tube group 201-204 is comprised.

  Thereby, the gas refrigerant discharged from the compressor 50 flows in the condenser 10 while making a U-turn three times for each tube group, and flows out from the condenser 10 to the decompression means.

  In the condenser 10 having the above-described configuration, under the condition that the entire surface of the condenser 10 is irradiated with cooling air having a uniform air volume and temperature, the heat dissipation characteristics of the condenser 10 are as shown in FIG. It was found to have a distribution along.

  That is, the gas refrigerant flowing into the condenser is condensed and liquefied as it flows in the condenser 10 from the upstream side of the refrigerant flow to the downstream side of the refrigerant flow, but when the refrigerant is condensed and liquefied, the specific volume decreases. Compared with the flow rate, the refrigerant flow rate on the downstream side of the refrigerant flow decreases.

  Accordingly, the heat transfer coefficient of the refrigerant on the downstream side of the refrigerant flow is reduced as compared with the heat transfer coefficient of the refrigerant on the upstream side of the refrigerant flow. Since the amount of heat released from the refrigerant is proportional to the heat transfer coefficient of the refrigerant, it has been found that the amount of heat released from the refrigerant decreases from the refrigerant inlet side to the refrigerant outlet side of the condenser.

  On the other hand, in the prior art, since the cooling fan control is not considered in consideration of the heat dissipation characteristics of the refrigerant, the refrigerant flow with a large amount of heat released from the refrigerant has a shortage of air flow to the upstream region. It was found that the amount of air flow to the downstream area of the refrigerant flow is excessive, and the cooling performance corresponding to the amount of air flow is not obtained.

In view of the above points, the present invention provides a condenser (10) for exchanging heat between refrigerant and air,
In the condenser cooling device of the refrigeration cycle, comprising a group of fan fans (13) consisting of a large number of fan fans for blowing air,
The blower fan group (13) is dispersedly arranged in the condenser (10) along the refrigerant flow direction of the tube (20).
When it is determined that there is a need to increase the heat dissipation capacity of the condenser (10), the first operation is to sequentially operate the blower fans in the blower fan group (13) from the refrigerant flow upstream side to the refrigerant flow downstream side. It is characterized by.

  Accordingly, in accordance with the heat dissipation characteristics of the refrigerant, it is possible to preferentially blow air to the upstream side of the refrigerant flow of the condenser (10) having a large amount of heat released from the refrigerant, and excessive air flow to the downstream side of the refrigerant flow having a small amount of heat released from the refrigerant. Therefore, the cooling performance can be improved without increasing the amount of air blown.

  Specifically, the present invention determines that there is a need to increase the heat dissipation capability of the condenser (10) when the high-pressure side pressure (Pc) of the refrigerant is equal to or greater than a predetermined value. In addition, the pressure of the refrigerant | coolant which flows out out of a condenser (10) is used for the high voltage | pressure side pressure (Pc) of a refrigerant | coolant.

Further, according to the present invention, a part of the condensing unit air blowing fans (1301 to 1316) in the air blowing fan group (13) is dispersedly arranged along the refrigerant flow direction of the tube (20) in the condensing unit (10a). The remaining supercooling section blower fans (1317 to 1320) are dispersedly arranged in the supercooling section (10b) along the refrigerant flow direction of the tube (20),
When it is determined that there is a need to increase the heat dissipation capacity of the condensing unit (10a), the condensing unit blower fans (1301 to 1316) are sequentially operated from the refrigerant flow upstream side to the refrigerant flow downstream side,
When the degree of supercooling (SC) of the refrigerant flowing out from the supercooling section (10b) is below a predetermined value, the supercooling section blower fans (1317 to 1320) are sequentially operated from the refrigerant flow upstream side to the refrigerant flow downstream side. Is the second feature.

  Here, the degree of supercooling (SC) is the temperature difference between the saturation temperature of the refrigerant and the actual refrigerant temperature.

  Thereby, in the condenser (10) provided with the condensing part (10a) and the supercooling part (10b), the air can be blown to the condensing part (10a) in accordance with the heat dissipation characteristic of the refrigerant, and also in accordance with the heat dissipation characteristic of the refrigerant Since the air can be blown to the supercooling part (10b), the cooling performance of both the condensing part (10a) and the supercooling part (10b) can be improved without increasing the blown amount.

  Note that, in the present invention, specifically, when the high-pressure side pressure (Pc) of the refrigerant is equal to or higher than a predetermined value, it is determined that there is a need to increase the heat dissipation capability of the condensing unit (10a). Here, as the high pressure side pressure (Pc) of the refrigerant, the pressure of the refrigerant flowing out from the condensing part (10a) may be used, or the pressure of the refrigerant flowing out from the supercooling part (10b) may be used.

  Further, in the present invention, specifically, the number of operating fans increases one by one, so the operating range of the fans can be finely controlled, and the amount of air blown is controlled in accordance with the heat dissipation characteristics of the refrigerant. it can.

Further, in the present invention, specifically, the plurality of tubes (20) constitutes a plurality of tube groups (201 to 205) in the stacking direction,
The refrigerant flows in a U-turn in the flow direction for each tube group,
You may make it the working number of ventilation fans increase per tube group.

  In the present invention, the blower fan group (13) may be arranged on the downstream side of the air flow of the condenser (10) to be a so-called suction type blower fan, or the blower fan group (13) may be a condenser ( It is good also as what is arrange | positioned in the air flow upstream of 10), and is what is called a pushing type ventilation fan.

  In addition, the code | symbol in the bracket | parenthesis of each means described in a claim and this column shows the correspondence with the specific means as described in embodiment mentioned later.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a plan view schematically showing an engine room of a vehicle on which a condenser cooling device for a refrigeration cycle for a vehicle according to this embodiment is mounted, and arrows in FIG. 1 indicate front-rear and left-right directions of the vehicle.

  The condenser 10 of the refrigeration cycle is arranged in line with the engine cooling radiator 12 in the vehicle left-right direction at the foremost part of an engine room 11 in which a vehicle engine (not shown) is mounted.

  Here, as is well known, the condenser 10 is a condenser for condensing and liquefying a high-temperature and high-pressure gas refrigerant discharged from a compressor (not shown) of a refrigeration cycle, and the outer shape of the condenser 10 is rectangular. Thin shape.

  A blower fan group 13 for blowing air (arrow a) passing through the inside of the condenser 10 is arranged on the downstream side (vehicle rear side) of the condenser 10. Here, the blower fan group 13 includes a large number of blower fans, details of which will be described later. Thereby, heat exchange is performed between the high-temperature gas refrigerant and the blown air, and the gas refrigerant is condensed and liquefied.

  The radiator 12 also has a rectangular thin shape, and a radiator-only fan 14 that blows air (arrow b) passing through the radiator 12 is provided on the downstream side (vehicle rear side) of the radiator 12. Has been placed. Thereby, the engine cooling water (hot water) sent from the vehicle engine is cooled by the blown air.

  The blower fan group 13 is fixed to the condenser 10 via a casing 16 that forms an air passage 15 extending from the condenser 10 to the blower fan group 13. Similarly, the radiator exclusive blower fan 14 is fixed to the radiator 12 via a casing 18 that forms an air passage 17 extending from the radiator 12 to the blower fan 14.

  FIG. 2 is a schematic front view of the condenser cooling device in FIG. 1 as viewed from the front of the vehicle. The illustration of the casing 16 is omitted, and some of the blower fans in the blower fan group 13 are illustrated. FIG. 3 is an enlarged view of a portion A in FIG.

  The condenser 10 includes a condensing unit 10a on the upstream side of the refrigerant flow and a supercooling unit 10b on the downstream side of the refrigerant flow. The gas-liquid two-phase refrigerant flowing out of the condensing unit 10a is gas-liquid separated by a gas-liquid separator (not shown). A so-called subcool type condenser is constructed in which the separated and gas-liquid separated liquid refrigerant is supercooled (subcooled) by the supercooling unit 10b to improve the cooling efficiency of the refrigeration cycle.

  Of the condenser 10, the heat exchange core portion 19 that performs heat exchange between the refrigerant and the blown air is configured by a laminated structure of a plurality of tubes 20 through which the refrigerant flows and corrugated heat transfer fins 21. . In this example, the tube 20 is a flat tube that is flat in the stacking direction (the vertical direction in FIG. 2 in this example).

  One end of the plurality of tubes 20 (the right end in FIG. 2 in this example) communicates with the first tank 22, and the other end (the left end in FIG. 2 in this example) communicates with the second tank 23. Both tanks 22 and 23 have a shape that extends in the direction in which the tubes 20 are stacked.

  In the first tank 22, a condensing part inlet space 24, an intermediate space 25, a condensing part outlet space 26, and a supercooling part inlet space 27 are provided by three partition plates 22 a to 22 c arranged at predetermined intervals in the longitudinal direction. It is formed.

  One end of the inlet side pipe 28 is connected to the condensing part inlet space 24 of the first tank 22, and the other end of the inlet side pipe 28 is connected to the discharge side of the compressor. The condensing unit outlet space 26 and the supercooling unit inlet space 27 communicate with each other via a communication pipe 29.

  In the second tank 23, a first intermediate space 30, a second intermediate space 31, and a supercooling portion outlet space 32 are formed by two partition plates 23a and 23b arranged at predetermined intervals in the longitudinal direction. One end of the outlet side pipe 33 is connected to the supercooling part outlet space 32 of the second tank 23, and the other end of the outlet side pipe 33 is connected to the refrigerant inlet side of the decompression means (not shown) of the refrigeration cycle. .

  Since the tanks 22 and 23 are partitioned into the spaces 23 to 26 and 29 to 31 by the partition plates 22a to 22c, 23a and 23b, the plurality of tubes 20 constitute the first to fifth tube groups 201 to 205. The refrigerant flowing in the condenser 10 makes a U-turn four times in the flow direction for each tube group. Here, the first to fifth tube groups 201 to 205 correspond to the tube groups in the present invention.

  In addition, side plates 34 that connect the tanks 22 and 23 and hold the rectangular outer shape of the condenser 10 are disposed in parallel with the tubes 20 at both longitudinal ends of the tanks 22 and 23.

  In addition, although illustration is abbreviate | omitted, the gas-liquid separator which isolate | separates the gas-liquid of a gas-liquid two-phase refrigerant | coolant is arrange | positioned in the connection piping 29 part.

  Thereby, the gas refrigerant discharged from the compressor is condensed in the condenser 10a on the upstream side of the refrigerant flow in the condenser 10 from the gas-liquid separator to become a gas-liquid two-phase refrigerant. This gas-liquid two-phase refrigerant is gas-liquid separated by the gas-liquid separator, and only the liquid refrigerant is sent to the supercooling unit 10b in the condenser 10 downstream of the refrigerant flow with respect to the gas-liquid separator. This liquid refrigerant is supercooled by the supercooling section 10b and sent to the decompression means.

  Each member such as the tube 20, the heat transfer fin 21, the first tank 22, the second tank 23, and the side plate 34 is formed of a metal such as aluminum, and after temporarily attaching these members to a predetermined assembly structure, The condenser 10 is assembled by brazing the assembled body integrally in a furnace.

  4 is a schematic front view of the condenser cooling device in FIG. 1 as viewed from the front of the vehicle, as in FIG. 2, and the illustration of the tubes 20 and the heat transfer fins 21 is omitted for convenience of explaining the arrangement of the blower fan group 13. And each boundary part of the 1st-5th tube groups 201-205 is shown with the dashed-two dotted line.

  On the downstream side of the air flow of the condenser 10 (the back side in the drawing of FIG. 4), the blower fan group 13 composed of a large number of blower fans is distributed along the refrigerant flow direction of the first to fifth tube groups 201 to 205. Be placed. Specifically, on the vehicle rear side of the first tube group 201, the first to fourth blower fans flow from the refrigerant flow upstream side (right side in FIG. 4) to the downstream side (left side in FIG. 4) of the first tube group 201. 1301 to 1304 are arranged side by side. On the vehicle rear side of the second tube group 202, fifth to eighth blowing fans 1305 to 1308 are provided from the refrigerant flow upstream side (left side in FIG. 4) to the downstream side (right side in FIG. 4). Arranged side by side.

  Similarly, the ninth to twelfth blower fans 1309 to 1312 are arranged on the vehicle rear side of the third tube group 203, and the thirteenth to sixteenth blower fans 1313 to 1316 are arranged on the vehicle rear side of the fourth tube group 204. The 17th to 20th blower fans 1317 to 1320 are arranged on the vehicle rear side of the fifth tube group 205 side by side from the upstream side to the downstream side of the refrigerant flow of each tube group.

  Here, the 1st-16th ventilation fans 1301-1316 arrange | positioned at the condensation part 10a of the condenser 10 correspond to the condensation part ventilation fan in this invention. Moreover, the 17th-20th ventilation fan 1317-1320 arrange | positioned at the supercooling part 10b of the condenser 10 corresponds to the supercooling part ventilation fan in this invention.

  The first to twentieth blower fans 1301 to 1320 are axial-flow fans, and each blower fan is independently driven to rotate by a motor (not shown) provided for each blower fan.

  In this example, the power consumption per motor is about 4 to 10 W. Thereby, the power consumption when driving all the blower fans of the blower fan group 13 is about the same as the power consumption when driving the conventional blower fan with the maximum air volume (about 80 to 200 W).

  By the way, the refrigerant | coolant pressure sensor 35 which detects the pressure Pc of the refrigerant | coolant which flows out out of the condensation part 10a is arrange | positioned at the communication piping 29 part of the condenser 10. FIG. A refrigerant temperature sensor 36 for detecting the temperature Tc of the refrigerant flowing out from the supercooling unit 10b is disposed in the outlet side pipe 33 part.

  Next, an outline of the electric control unit in the present embodiment will be described. FIG. 5 is a block diagram showing an outline of the electronic control unit of the condenser cooling device of the refrigeration cycle in the present embodiment. The air conditioning electronic control unit (ECU) 37 is a well-known microcomputer including a CPU, ROM, RAM, and the like. And its peripheral circuits.

  For the control of the blower fan group 13, detection signals are input to the air conditioning electronic control device 37 from the refrigerant pressure sensor 35 that detects the refrigerant pressure Pc and the refrigerant temperature sensor 36 that detects the refrigerant temperature Tc.

  Furthermore, an air conditioning operation panel (not shown) arranged around the instrument panel in the passenger compartment is provided with an air conditioner switch 38 that is manually operated by a passenger. An operation signal of the air conditioner switch 38 is also an electronic control unit 37 for air conditioning. Is input. Here, the air conditioner switch 38 generates an on / off signal of an electromagnetic clutch (not shown) for the compressor of the refrigeration cycle.

  The applied voltages of the fan driving motors of the first to twentieth fan fans 1301 to 1320 are intermittently interrupted by the motor driving circuits, and the rotations of the first to twentieth fan fans 1301 to 1320 are independently interrupted. Power is supplied to the air-conditioning electronic control unit 37 from a vehicle-mounted battery (not shown) via an ignition switch (not shown) of the vehicle engine.

  Next, the operation of this embodiment in the above configuration will be described. The flowchart of FIG. 6 shows an outline of control processing executed by the microcomputer of the air conditioning electronic control unit 37.

  The control routine of FIG. 6 starts when the air conditioner switch 38 of the air conditioning operation panel is turned on in a state where the ignition switch of the vehicle engine is turned on and power is supplied to the air conditioning electronic control unit 37.

  Here, in this example, the control routine of FIG. 6 is repeatedly executed at a period of about 10 to 15 seconds (a time period in which the refrigerant makes one cycle of the refrigeration cycle).

  Further, the first half (steps S100 to S210) of the control routine of FIG. 6 controls the condensing unit blowing fans 1301 to 1316, and the latter half (steps S220 to S330) is the supercooling unit blowing fans 1317 to 1320. Is to control.

  First, after initialization of flags, timers, etc., detection signals from the refrigerant pressure sensor 35 and the refrigerant temperature sensor 36 are read in step S100.

  Subsequently, in step S110, it is determined whether or not it is necessary to increase the heat dissipation capability of the condensing unit 10a. In this example, when the pressure Pc of the refrigerant flowing out from the condensing unit 10a is 1.5 MPa or more, it is determined that there is a need to increase the heat dissipation capability of the condensing unit 10a, and the process proceeds to step S120.

  In step S120, 1 is added to the first counter C1, and the process proceeds to step S130. In step S130, it is determined whether or not the value of the first counter C1 is 1. When the value of the first counter C1 is 1, the process proceeds to step S140.

  In step S140, a motor rotation signal is output to the motor drive circuit of the first blower fan 1301, and the rotation of the first blower fan 1301 is turned on. Thereby, it blows to the refrigerant | coolant flow most upstream part of the condensation part 10a.

  When the value of the first counter C1 is not 1 in step S130, that is, when the value of the first counter C1 is larger than 1, the process proceeds to step S150. In step S150, it is determined whether or not the value of the first counter C1 is 2. When the value of the first counter C1 is 2, the process proceeds to step S160.

  In step S160, motor rotation signals are output to the motor drive circuits of the first blower fan 1301 and the second blower fan 1302, and the rotation of the first blower fan 1301 and the second blower fan 1302 is turned on. Thereby, compared with the case where the value of the 1st counter C1 is 1, the range which ventilates is expanded to the refrigerant | coolant flow downstream of the condensation part 10a.

  Although not shown, when the value of the first counter C1 is not 2 in step S130, that is, when the value of the first counter C1 is greater than 2, is the value of the first counter C1 3? When the value of the first counter C1 is 3, the rotation of the first to third blower fans 1301 to 1303 is turned on.

  Similarly, as the value of the first counter C1 increases, the number of operating fans increases one by one from the refrigerant flow upstream side of the condensing unit 10a to the refrigerant flow downstream side, and the air blowing range to the condensing unit 10a Is expanded from the refrigerant flow upstream side to the refrigerant flow downstream side.

  As shown in steps S170 and S180, when the value of the first counter C1 is 15, the rotations of the first to fifteenth blower fans 1301 to 1315 are turned on.

  When the value of the first counter C1 is not 15 in step S170, that is, when the value of the first counter C1 is larger than 15, the process proceeds to step S190, and the rotation of the first to sixteenth blower fans 1301 to 1316 is turned on. Is done. Thereby, since it ventilates to the whole range of the condensation part 10a, the condensation part 10a will be in a maximum cooling state.

  By the way, when the refrigerant pressure Pc is not 1.5 MPa or more in Step S110, that is, when the refrigerant pressure Pc is less than 1.5 MPa, the process proceeds to Step S200, and the first counter C1 is reset. That is, the value of the first counter C1 becomes zero.

  In step S210, the rotations of the first to sixteenth blower fans 1301 to 1316 are turned off. That is, when the refrigerant pressure Pc is less than 1.5 MPa, there is no need to increase the heat dissipation capacity of the condensing unit 10a, and therefore all the condensing unit blower fans 1301 to 1316 are stopped.

  When it is determined by the control of the first half part (steps S100 to S210) that it is necessary to increase the heat dissipation capacity of the condensing unit 10a, the condensing unit blower fans 1301 to 1316 are moved from the refrigerant flow upstream side to the refrigerant flow downstream side. It can be operated sequentially.

  Thereby, according to the heat dissipation characteristic of a refrigerant | coolant, while being able to ventilate preferentially to the refrigerant | coolant flow upstream of the condensation part 10a with much heat dissipation, it suppresses the excessive ventilation | bath to the refrigerant | coolant flow downstream of the condensation part 10a with little heat dissipation. Therefore, the cooling performance in the condensing part 10a can be improved without increasing the blowing rate.

  Next, control of the supercooling section blower fans 1317 to 1320, which is the latter half of the control routine of FIG. 6 (steps S220 to S330), will be described.

  First, in step S220, the degree of supercooling SC is calculated based on the refrigerant pressure Pc and the refrigerant temperature Tc detected by the refrigerant temperature sensor 36. Here, the supercooling degree SC is a temperature difference between the saturation temperature of the refrigerant flowing out from the supercooling unit 10b and the actual refrigerant temperature.

  Specifically, the refrigerant pressure Pc flowing out of the condensing unit 10a is regarded as the pressure of the refrigerant flowing out of the supercooling unit 10b, the refrigerant saturation temperature Ts at the refrigerant pressure Pc is calculated, and the refrigerant saturation temperature Ts and the refrigerant temperature Tc are calculated. From this, the degree of supercooling SC (SC = Ts−Tc) is calculated.

  That is, as the degree of supercooling SC is larger, it means that the liquid refrigerant is supercooled in the supercooling section 10b. Note that the pressure Pc of the refrigerant flowing out of the condenser 10a is regarded as the pressure of the refrigerant flowing out of the supercooling unit 10b because the pressure of the refrigerant flowing out of the supercooling unit 10b of the condenser 10 flows out of the condensing unit 10a. This is because the pressure is approximately the same as the refrigerant pressure Pc.

  Next, in step S230, it is determined whether or not the supercooling degree SC of the refrigerant flowing out from the supercooling unit 10b is equal to or less than a predetermined value. In this example, when the degree of supercooling SC is 10 ° C. or less, it is determined that the degree of supercooling SC is less than a predetermined value, and the process proceeds to step S240.

  In step S240, 1 is added to the second counter C2, and the process proceeds to step S250. In step S250, it is determined whether or not the value of the second counter C2 is 1. When the value of the second counter C2 is 1, the process proceeds to step S260.

  In step S260, the rotation of the seventeenth blower fan 1317 is turned on. Thereby, it blows to the refrigerant | coolant flow most upstream part of the supercooling part 10b.

  When the value of the second counter C2 is not 1 in step S250, that is, when the value of the second counter C2 is larger than 1, the process proceeds to step S270. In step S270, it is determined whether or not the value of the second counter C2 is 2. When the value of the second counter C2 is 2, the process proceeds to step S280.

  In step S280, the rotations of the seventeenth and eighteenth blower fans 1317 and 1318 are turned on. Thereby, compared with when the value of the 2nd counter C2 is 1, the range which ventilates is expanded to the refrigerant | coolant flow downstream of the supercooling part 10b.

  When the value of the second counter C2 is not 2 in step S250, that is, when the value of the second counter C2 is larger than 2, it is determined whether or not the value of the second counter C2 is 3 in step S290. When the value of the second counter C2 is 3, the process proceeds to step S300, and the rotations of the first to third blower fans 1301 to 1303 are turned on.

  When the value of the second counter C2 is not 3 in step S300, that is, when the value of the second counter C2 is larger than 3, the process proceeds to step S310, and the rotation of the 17th to 20th blower fans 1317 to 1320 is performed. Is turned on. Thereby, since it ventilates to the whole range of the supercooling part 10b, the supercooling part 10b of the condenser 10 will be in a maximum cooling state.

  By the way, when the degree of supercooling SC is not less than 10 ° C. in step S230, that is, when the degree of supercooling SC is greater than 10 ° C., the process proceeds to step S320, and the second counter C2 is reset. That is, the value of the second counter C2 becomes zero. In step S330, the rotations of the seventeenth to twentieth blower fans 1317 to 1320 are turned off.

  That is, when the degree of supercooling SC is greater than 10 ° C., the liquid refrigerant is sufficiently subcooled in the subcooling section 10b, so that all the subcooling section blower fans 1317 to 1320 are stopped.

  By controlling the latter half (steps S220 to S330), when the degree of supercooling SC is equal to or less than a predetermined value, the supercooling section blower fans 1317 to 1320 can be sequentially operated from the refrigerant flow upstream side to the refrigerant flow downstream side. .

  Thereby, according to the heat dissipation characteristic of the refrigerant, the air can be preferentially blown to the upstream side of the refrigerant flow of the supercooling portion 10b having a large heat release amount, and the excessive airflow to the downstream side of the refrigerant flow of the supercooling portion 10b having a small heat release amount. Therefore, it is possible to improve the cooling performance in the supercooling portion 10b without increasing the air flow rate.

  As a result of the above operation, in the condenser cooling device of the refrigeration cycle, it is possible to improve the cooling performance without increasing the air flow rate.

(Second Embodiment)
In the first embodiment, the operating number of the condensing unit blowing fans 1301 to 1316 and the operating number of the supercooling unit blowing fans 1317 to 1320 are increased by one. In the second embodiment, the condensing unit blowing fan is increased. The number of operating units 1301 to 1316 and the number of operating subcooling section blower fans 1317 to 1320 are increased in units of tube groups.

  The configurations of the condenser 10, the blower fan group 13, and the electric control unit in the present embodiment are the same as those in the first embodiment.

  The flowchart in FIG. 7 shows the outline of the control processing in the present embodiment, and this control routine is about 10 to 15 seconds (the time for which the refrigerant makes one cycle of the refrigeration cycle), as in the first embodiment. It is repeatedly executed in the cycle.

  In addition, the first half (steps S100 to S210) of the control routine of FIG. Is to control.

  In the present embodiment, when 1 is added to the first counter C1, the operating number of the condenser air blowing fans 1301 to 1316 increases in units of tube groups. That is, when the value of the first counter C1 is 1, the rotation of the first to fourth blower fans 1301 to 1304 arranged in the first tube group 201 is turned on in step S140A. As a result, the first tube group 201 is blown.

  When the value of the first counter C1 is 2, the rotation of the first to eighth blowing fans 1301 to 1308 is turned on in step S160A. Thereby, since it blows to the 1st tube group 201 and the 2nd tube group 202, compared with the time of the value of the 1st counter C1 being 1, the range which ventilates expands to the refrigerant | coolant flow downstream of the condensation part 10a. Is done.

  When the value of the first counter C1 is 3, the rotation of the first to third blower fans 1301 to 1303 is turned on in step S180A, so that the first to third tube groups 201 to 203 are blown.

  When the value of the first counter C1 is greater than 3, the rotation of the first to sixteenth blower fans 1301 to 1316 is turned on in step S190A. Thereby, since it ventilates to the whole range of the condensation part 10a, the condensation part 10a will be in a maximum cooling state.

  Thereby, the working number of the condensation part ventilation fans 1301-1316 can be increased per tube group.

  In this embodiment, when 1 is added to the second counter C2, the rotation of the 17th to 20th blower fans 1317 to 1320 arranged in the fifth tube group 205 is turned on in step S260A. Thereby, since it blows to the whole range of the supercooling part 10b, the supercooling part 10b will be in a maximum cooling state.

  Thereby, the operating number of the supercooling part ventilation fans 1317-1320 can be increased per tube group.

  Even if it does in this way, since it can ventilate according to the thermal radiation characteristic of a refrigerant | coolant with respect to the condensation part 10a similarly to 1st Embodiment, the cooling performance of the condensation part 10a can be improved. Moreover, the air flow with respect to the supercooling part 10b can be adjusted independently of the condensing part 10a, and appropriate air flow to the supercooling part 10b can be performed.

  Thereby, when the air flow rate with respect to the supercooling part 10b cannot be adjusted independently of the condensing part 10a, for example, since the same fan blows air to the supercooling part 10b and the condensing part 10a, the air flow rate with respect to the supercooling part 10b is reduced to the condensing part. The cooling performance of the supercooling unit 10b can be improved as compared with the case where the air flow is linked to 10a.

(Third embodiment)
In each of the above embodiments, the present invention is applied to the subcooled condenser 10 including the condensing unit 10a and the supercooling unit 10b. However, in the present embodiment, only the condensing unit 10a that does not have the supercooling unit 10b. The present invention is applied to a condenser 10 constituted by:

  FIG. 8 is a schematic front view of the condenser cooling device according to the present embodiment as viewed from the front of the vehicle, and is a view in which the tubes 20 and the heat transfer fins 21 are not shown. The condenser 10 in the present embodiment has only a condensing unit 10a in which the supercooling unit 10b is omitted from the condenser 10 in the first embodiment.

  That is, in the first tank 22, a condensing unit inlet space 24, an intermediate space 25, and a condensing unit outlet space 26 are formed by two partition plates 22a and 22b. In the second tank 23, one partition plate 23a A first intermediate space 30 and a second intermediate space 31 are formed.

  In addition, one end of the outlet side pipe 33 is connected to the condenser outlet space 26 of the first tank 22. A refrigerant pressure sensor 35 for detecting the pressure Pc of the refrigerant flowing out from the condensing unit 10a is disposed in the outlet side pipe 33 part.

  Thereby, the some tube 20 comprises the 1st-4th tube group 201-204, and the refrigerant | coolant which flows through the inside of the condenser 10 carries out the U-turn 3 times for each tube group.

  Moreover, the ventilation fan group 13 in this embodiment becomes a structure which excluded the supercooling part ventilation fans 1317-1320 from the ventilation fan group 13 in 1st Embodiment.

  The flowchart of FIG. 9 shows the outline of the control processing in the present embodiment. From the control routine (FIG. 6) in the first embodiment, the control part of the subcooling section blower fans 1317 to 1320, that is, the latter half part (step S220). To S330) are omitted.

  Thereby, also in the condenser 10 comprised only by the condensation part 10a which does not have the supercooling part 10b, the cooling performance of the condenser 10 can be improved, without increasing ventilation volume.

(Fourth embodiment)
In each said embodiment, the 1st-4th tube groups 201-204 are comprised in the condensation part 10a of the condenser 10, and the flow direction of a refrigerant | coolant makes the U-turn 3 times for every tube group in the condensation part 10a. However, in this embodiment, only the 1st tube group 201 is comprised in the condensation part 10a, and a refrigerant | coolant flows in one direction, without making a U-turn in the condensation part 10a.

  FIG. 10 is a schematic front view of the condenser cooling device according to the present embodiment as viewed from the front of the vehicle, and is a view in which illustration of the tubes 20 and the heat transfer fins 21 is omitted. In the condenser 10 according to the present embodiment, only the first tube group 201 is configured in the condensing unit 10a.

  That is, in the first tank 22, a condensing part inlet space 24 and a supercooling part outlet space 32 are formed by one partition plate 22a, and in the second tank 23, a condensing part outlet space is formed by one partition plate 23a. 26, a supercooling portion inlet space 27 is formed.

  A communication pipe 29 is disposed between the condenser outlet space 26 and the supercooling inlet space 27. One end of the outlet side pipe 33 is connected to the subcooling section outlet space 32 of the first tank 22.

  Thereby, the some tube 20 comprises the 1st, 5th tube group 201,205, and the refrigerant | coolant which flows through the inside of the condenser 10 makes a U-turn once in the flow direction. In addition, although illustration is abbreviate | omitted, the gas-liquid separator which isolate | separates the gas-liquid of a gas-liquid two-phase refrigerant | coolant is arrange | positioned in the connection piping 29 part.

  Thereby, the gas refrigerant discharged from the compressor flows through the first tube group 201 of the condensing unit 10a in one direction (in this example, the left direction in FIG. 10), and is condensed to become a gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is gas-liquid separated by a gas-liquid separator, and only the liquid refrigerant is sent to the supercooling unit 10b.

  In addition, the blower fan group 13 is dispersedly arranged along the refrigerant flow direction of the condenser 10 on the downstream side of the air flow of the condenser 10 (the back side of the drawing in FIG. 10).

  Specifically, on the vehicle rear side of the first tube group 201, the first to fourth blower fans from the refrigerant flow upstream side (right side in FIG. 10) to the downstream side (left side in FIG. 10) of the first tube group 201. 1301 to 1304 are arranged side by side. On the vehicle rear side of the fifth tube group 205, seventeenth to twentieth blower fans 1317 to 1320 are directed from the refrigerant flow upstream side (left side in FIG. 10) to the downstream side (right side in FIG. 10) of the fifth tube group 205. Arranged side by side.

  In this example, the output per one motor that rotationally drives the first to fourth blower fans 1301 to 1304 is about 16 to 40 W, and the output per motor that rotationally drives the seventeenth to twentieth blower fans 1317 to 1320. The output is about 4-10W. Thereby, the power consumption when driving all the blower fans of the blower fan group 13 is about the same as that of the first embodiment (about 80 to 200 W).

  Next, the operation of this embodiment in the above configuration will be described. Similarly to the first embodiment, when the refrigerant pressure Pc is 1.5 MPa or more, 1 is added to the first counter C1.

  When the value of the first counter C1 is 1, the rotation of the first blower fan 1301 is turned on. When the value of the first counter C1 is 2, the rotation of the first blower fan 1301 and the second blower fan 1302 is turned on.

  When the value of the first counter C1 is 3, the rotation of the first to third blower fans 1301 to 1303 is turned on. When the value of the first counter C1 is greater than 3, the rotation of the first to fourth blower fans 1301 to 1304 is turned on.

  By the way, when the refrigerant pressure Pc is less than 1.5 MPa, the first counter C1 is reset, and the rotation of the first to fourth blower fans 1301 to 1304 is turned off.

  In the condenser 10 in which the refrigerant flows in one direction in the condensing unit 10a by the above operation, when it is determined that there is a need to increase the heat dissipation capacity of the condensing unit 10a, the condensing unit blower fans 1301 to 1304 are flown upstream. It can be operated sequentially from the side to the refrigerant flow downstream side.

  Thereby, the cooling performance in the condensing part 10a can be improved, without increasing blast volume. In addition, control of the supercooling part ventilation fans 1317-1320 is the same as that of 1st Embodiment.

(Other embodiments)
(1) In the first embodiment, the condenser 10 includes five tube groups, that is, the first to fifth tube groups 201 to 205, and the refrigerant flows in the condenser 10 a total of four times U. However, the number of tube groups of the condenser 10 may be increased or decreased to increase or decrease the number of U-turns in the refrigerant flow direction in the condenser 10.

  In this embodiment, the refrigerant is not limited to flow in one direction in the supercooling unit 10b, and the refrigerant may flow in a U-turn in the supercooling unit 10b.

  Further, as the number of tube groups increases or decreases, the number of blower fans also increases or decreases as appropriate. And according to increase / decrease in the number of ventilation fans, the power consumption of the drive motor of each ventilation fan is set suitably. Specifically, the power consumption of the motor for driving each blower fan is set so that the power consumption when driving all the blower fans is approximately the same as in the first embodiment.

  (2) In each of the above embodiments, four fan fans are arranged for each tube group. However, the present invention is not limited to this, and the number of fan fans arranged for each tube group is other than four. The number may be increased or decreased, and the number of blower fans arranged may be changed depending on the tube group.

  (3) In the first, third and fourth embodiments, the operating number of the blower fans is increased by one, but the operating number of the blower fans may be increased by a predetermined number other than one. For example, the number of operating fans may be increased by two.

  Further, the number of operating fans is not limited to increase by the same number each time. For example, when the value of the first counter C1 is 1, the number of operating fan fans may be increased by one, and when the value of the first counter C1 is 2, the operating number of fan fans may be increased by two.

  (4) In each of the above embodiments, the operating number of the condensing unit blowing fans 1301 to 1316 and the operating number of the supercooling unit blowing fans 1317 to 1320 are increased by the same number, but the present invention is not limited to this. .

  For example, the operating number of the condensing unit blowing fans 1301 to 1316 may be increased in units of tube groups, while the operating number of the subcooling unit blowing fans 1317 to 1320 may be increased one by one.

  (5) In the first, second and fourth embodiments, the refrigerant pressure sensor 35 is disposed in the connecting pipe 29 and the refrigerant pressure Pc flowing out from the condenser 10a is detected. 35 may be disposed in the outlet side pipe 33 to detect the pressure of the refrigerant flowing out of the supercooling unit 10b.

  (6) In each said embodiment, although the ventilation fan group 13 is arrange | positioned in the air flow downstream (vehicle rear side) of the condenser 10 and it is set as what is called a suction type ventilation fan, the ventilation fan group 13 is set to the condenser 10. It may be arranged on the upstream side of the air flow (front side of the vehicle) so as to be a so-called push-type blower fan.

  (7) In each of the above embodiments, the condenser 10 and the radiator 12 are arranged side by side in the vehicle left-right direction, but the condenser 10 and the radiator 12 may be arranged side by side in the vehicle vertical direction.

It is the top view which showed typically the engine room of the vehicle carrying the condenser cooling device of the refrigerating cycle which concerns on 1st Embodiment of this invention. It is a schematic front view of the condenser cooling device in FIG. It is the A section enlarged view in FIG. FIG. 2 is a schematic front view of the condenser cooling device in FIG. 1, in which a tube and a heat transfer fin are not shown. It is a block diagram which shows the outline | summary of the electronic control part of 1st Embodiment of this invention. It is a flowchart which shows the flow of the control processing performed by the air-conditioning control apparatus of 1st Embodiment of this invention. It is a flowchart which shows the flow of the control processing performed by the air-conditioning control apparatus of 2nd Embodiment of this invention. It is a schematic front view of the condenser cooling device in 3rd Embodiment of this invention, and is a figure which abbreviate | omitted illustration of the tube and the heat-transfer fin. It is a flowchart which shows the flow of the control processing performed by the air-conditioning control apparatus of 3rd Embodiment of this invention. It is a schematic front view of the condenser cooling device in 4th Embodiment of this invention, and is a figure which abbreviate | omitted illustration of the tube and the heat-transfer fin. It is a schematic perspective view of a recent vehicle equipped with a condenser. It is a schematic front view of the condenser in FIG. FIG. 12 is a heat dissipation characteristic diagram of the refrigerant in the condenser of FIG. 11.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Condenser, 10a ... Condensing part, 10b ... Supercooling part, 13 ... Blower fan group,
20 ... Tube, 21 ... Heat transfer fin,
201-205 ... 1st-5th tube group (tube group),
1301 to 1316... Condensing section blower fan, 1317 to 1320.

Claims (5)

A condenser (10) having a laminated structure of a plurality of tubes (20) forming a refrigerant flow path and heat transfer fins (21) joined to the tubes (20) and exchanging heat between the refrigerant and air. )When,
In the condenser cooling device of the refrigeration cycle, comprising a group of fan fans (13) consisting of a plurality of fan fans for blowing the air,
The blower fan group (13) is dispersedly arranged in the condenser (10) along the refrigerant flow direction of the tube (20),
When it is determined that there is a need to increase the heat dissipation capability of the condenser (10), the blower fans in the blower fan group (13) are sequentially operated from the refrigerant flow upstream side to the refrigerant flow downstream side. A condenser cooling device for a refrigeration cycle. A condenser (10) having a laminated structure of a plurality of tubes (20) forming a refrigerant flow path and heat transfer fins (21) joined to the tubes (20) and exchanging heat between the refrigerant and air. )When,
A blower fan group (13) comprising a plurality of blower fans for blowing the air,
In the condenser cooling device for a refrigeration cycle, the condenser (10) is provided with a condenser section (10a) on the upstream side of the refrigerant flow and a supercooling section (10b) on the downstream side of the refrigerant flow.
A part of the condenser fan fans (1301 to 1316) in the fan fan group (13) is dispersedly arranged along the refrigerant flow direction of the tube (20) in the condenser part (10a), and the residual excess. Cooling unit blower fans (1317 to 1320) are distributed and arranged along the refrigerant flow direction of the tube (20) in the supercooling unit (10b),
When it is determined that there is a need to increase the heat dissipation capacity of the condensing unit (10a), the condensing unit blower fans (1301 to 1316) are sequentially operated from the refrigerant flow upstream side to the refrigerant flow downstream side,
When the degree of supercooling (SC) of the refrigerant flowing out from the supercooling section (10b) is below a predetermined value, the supercooling section blower fans (1317 to 1320) are sequentially operated from the refrigerant flow upstream side to the refrigerant flow downstream side. A condenser cooling device for a refrigeration cycle. The condenser cooling device for a refrigeration cycle according to claim 2, wherein the necessity is determined when the high-pressure side pressure (Pc) of the refrigerant is equal to or higher than a predetermined value. The condenser cooling device for a refrigeration cycle according to any one of claims 1 to 3, wherein the number of operating blow fans increases by one. The plurality of tubes (20) constitutes a plurality of tube groups (201 to 205) in the stacking direction,
The refrigerant flows in a U-turn in the flow direction for each tube group,
The condenser cooling device for a refrigeration cycle according to any one of claims 1 to 3, wherein the number of operating fans is increased in units of the tube group.

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