JP2007210550A - Air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve draining performance of condensed water when the quantity of air flow is low. <P>SOLUTION: This air conditioner is provided with an air blower 12 for blowing air; a cooling heat exchanger 13 arranged in the gravity direction inside an air passage where air flows and cooling the air; a movable member 15 arranged inside the air passage and operable in first operating positions A, D for concentrating an air flow at a lower part of the cooling heat exchanger 13 and second operating positions B, E for flowing air along an air inflow direction to inside of the air passage without changing the direction; and an operating mechanism 29 for operating the movable member 15. The operating mechanism 29 operates the movable member 15 in the second operating positions B, E when the air quantity of the air blower 12 exceeds predetermined air quantity, and operates the movable member 15 in the first operating positions A, D when the quantity of air flow is below the predetermined air quantity. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an air conditioner having a cooling heat exchanger that cools air blown from a blower, and is suitable for application to a vehicle air conditioner.

  A conventional vehicle air conditioner cools and dehumidifies air blown from a blower by a cooling heat exchanger disposed in an air conditioning case (see, for example, Patent Document 1).

  In Patent Document 1, a plurality of guide plates are fixedly arranged in the air conditioning case and on the air inflow side of the cooling heat exchanger. The plurality of guide plates uniformly distribute the blown air over the entire area of the cooling heat exchanger, thereby preventing the wind pressure of the blown air passing through the cooling heat exchanger from being locally increased.

This prevents the condensed water adhering to the heat exchange core surface of the cooling heat exchanger from being locally blown to the downstream side of the air flow by a large wind pressure, while cooling the condensed water with an appropriate wind pressure. It can be discharged to the downstream side of the air flow of the vessel.
JP-A-6-122320

  By the way, in recent years, air conditioners for vehicles have been commercialized to improve comfort by reducing the amount of air blown by the blower so that the amount of air blown from the air outlet is brought close to a state insensitive to passengers. ing.

  However, when the air volume by the blower becomes extremely small in this way, the wind pressure applied to the condensed water also becomes very small. For this reason, the condensed water moves down along the surface of the heat exchange core by gravity without being discharged to the downstream side of the air flow of the heat exchanger for cooling. Stay in large quantities.

  Thus, if the air volume of the blower is rapidly increased with a large amount of condensed water remaining in the lower part of the heat exchange core, there is a problem that a large amount of condensed water is blown to the downstream side of the air flow by the wind pressure.

  An object of this invention is to aim at the drainage improvement of the condensed water at the time of low air volume in view of the said point.

To achieve the above object, the present invention provides a blower (12) for blowing air,
A cooling heat exchanger (13) arranged in the direction of gravity in the air passage through which air flows to cool the air;
A first operation position (A, D) that is arranged in the air passage and concentrates the air flow in the lower part of the cooling heat exchanger (13), and the air flows as it is along the air inflow direction into the air passage. A movable member (15) operable to the second operation position (B, E);
An operation mechanism (29) for operating the movable member (15),
The operation mechanism (29) operates the movable member (15) to the second operation position (B, E) when the air volume of the blower (12) is larger than the predetermined air volume, and the movable member (15) when the air volume is less than the predetermined air volume. Is operated to the first operation position (A, D).

  According to this, when the air volume of the blower (12) is equal to or less than the predetermined air volume, the air flow is concentrated on the lower part of the cooling heat exchanger (13), so that the wind pressure at the lower part of the cooling heat exchanger (13) is increased. Can do.

  For this reason, since an appropriate wind pressure can be applied to the condensed water which is going to stay in the lower part of the cooling heat exchanger (13), the condensed water can be discharged well downstream of the air flow. As a result, when the air volume is rapidly increased, it is possible to avoid a large amount of condensed water being blown to the downstream side of the air flow.

  On the other hand, when the air volume of the blower (12) is larger than the predetermined air volume, the air flows as it is along the air inflow direction into the air passage without concentrating on the lower part of the cooling heat exchanger (13). The cooling performance can be exhibited in the entire area of the cooling heat exchanger (13).

  For this reason, the cooling performance of the cooling heat exchanger (13) can be exhibited without problems when the airflow is high and the cooling load is high.

  In addition, arrange | positioning the heat exchanger for cooling in this invention in a gravitational direction means arrange | positioning a heat exchanger for cooling so that the heat exchange core surface of the heat exchanger for cooling may extend in the direction of gravity. Here, the fact that the heat exchange core surface extends in the direction of gravity does not mean strictly extending in the direction of gravity but also includes extending in a direction slightly inclined with respect to the direction of gravity. .

In the present invention, specifically, the movable member (15) is arranged on the upstream side of the air flow of the cooling heat exchanger (13),
The movable member (15) operated to the first operation position (A) guides the air on the upstream side of the air flow to the lower part of the cooling heat exchanger (13).

  Thereby, the flow of air can be concentrated on the lower part of the cooling heat exchanger (13) by the movable member (15).

  In the present invention, more specifically, since the movable member (15) is composed of a rotatable member arranged in the direction of gravity, air is cooled by the movable member (15). 13) can be effectively guided to the lower part.

Further, in the present invention, specifically, the movable member (15) is disposed on the downstream side of the air flow of the cooling heat exchanger (13),
The movable member (15) operated to the first operating position (D) prevents the flow of air passing through the upper part of the cooling heat exchanger (13).

  Even if the movable member (15) is configured in this manner, the air flow can be concentrated on the lower portion of the cooling heat exchanger (13) by the movable member (15).

  Further, the present invention specifically includes a control means (32) for controlling the blower (12) and the operation mechanism (29).

More specifically, in the present invention, when the control means (32) determines that the air volume needs to be decreased from the first air volume larger than the predetermined air volume to the second air volume equal to or less than the predetermined air volume, the air volume is calculated from the first air volume. After decreasing to the second air volume, the movable member (15) is operated from the second operation position (B, E) to the first operation position (A, D),
Further, when the control means (32) determines that the air volume needs to be increased from the second air volume to the first air volume, the movable member (15) is moved from the first operation position (A, D) to the second operation position (B , E), the air volume is increased from the second air volume to the first air volume.

  According to this, it is possible to avoid the flow of air from concentrating on the lower part of the cooling heat exchanger (13) during the first air volume with a large air volume, so that the wind pressure at the lower part of the cooling heat exchanger (13) becomes too high. You can avoid that. For this reason, it can avoid that the condensed water of the lower part of the heat exchanger (13) for cooling is skipped by the air flow downstream.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim 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 schematic cross-sectional view of the overall configuration of an indoor unit 10 of a vehicle air conditioner according to this embodiment. The indoor unit portion 10 is disposed at a substantially central portion in the vehicle width (left and right) direction inside an instrument panel (not shown) at the front of the vehicle interior. At that time, the indoor unit 10 is mounted as indicated by arrows in FIG. Therefore, the vehicle width direction is the direction perpendicular to the paper surface of FIG.

  The indoor unit portion 10 according to the present embodiment has an air conditioning case 11 that forms an air passage through which air flows toward the vehicle interior. The air-conditioning case 11 is actually formed as a plurality of divided case bodies for convenience in resin molding, assembly of built-in parts, and the like, and the plurality of divided case bodies are integrated by fastening means such as screws and clips. The air-conditioning case 11 is configured by fastening to.

  A blower 12 including a centrifugal blower fan 12a and an electric motor 12b that rotationally drives the blower fan 12a is disposed on the vehicle front side of the air conditioning case 11. And the evaporator 13 which makes the heat exchanger for cooling is arrange | positioned at the vehicle rear side of the air blower 12. As shown in FIG.

  An inside / outside air switching box (not shown) is connected to the suction port 12c side of the centrifugal blower fan 12a, and inside air (vehicle interior air) or outside air (vehicle interior air) sucked through the inside / outside air switching box is blown by the blower fan 12a. To do.

  Then, the blown air of the blower fan 12a flows from the front of the vehicle to the rear as shown by the arrow a and is blown to the front surface of the evaporator 13.

  The evaporator 13 is a substantially rectangular thin shape having substantially the same vehicle width direction dimensions as the air conditioning case 11, and is arranged in a substantially gravity direction (substantially up and down direction). Refrigerant fluid decompressed by decompression means of an air conditioning refrigeration cycle (not shown) is introduced into the evaporator 13, and the refrigerant fluid absorbs heat from the blown air and evaporates to cool the air.

  As is well known, the evaporator 13 has a heat exchange core portion 13a composed of a combination of a number of flat tubes (not shown) constituting the refrigerant passage and fins such as corrugated fins, and this heat exchange core portion. The tank portion 13b is arranged at both ends in the tube longitudinal direction (substantially gravitational direction) of 13a. Therefore, the heat exchange core surface of the heat exchange core portion 13a extends substantially in the direction of gravity.

  In the air conditioning case 11, the bottom surface portion located below the evaporator 13 constitutes a condensed water receiving portion, and a condensed water discharge pipe 14 is formed at the bottom. The condensed water discharged to the downstream side of the air flow of the evaporator 13 by the wind pressure of the blown air is collected on the bottom surface as indicated by an arrow w, and is discharged from the condensed water discharge pipe 14 to the outside of the vehicle compartment.

  One movable member 15 is provided on the front side (upstream side of the air flow) of the evaporator 13 to improve the condensate drainage by concentrating the flow of the blown air of the blower fan 12a at the lower part of the evaporator 13 when the air volume is low. Has been placed. In this example, the movable member 15 is constituted by a so-called butterfly door in which a rotation shaft 15b is arranged at the center of a main body 15a formed in a flat plate shape.

  The rotating shaft 15b of the movable member 15 is arranged in the air conditioning case 11 so as to extend in the center of the gravity direction so as to extend in the direction perpendicular to the sheet of FIG. 1 (vehicle width direction), and both ends of the rotating shaft 15b are side walls of the air conditioning case 11. It is rotatably supported by a bearing hole (not shown) of the part.

  In FIG. 1, the solid line position of the movable member 15 is a first operation position A for guiding the blown air (arrow a) to the lower part of the evaporator 13. In the first operation position A, the side close to the evaporator 13 in the flat plate-like main body portion 15a is inclined downward.

  On the other hand, the two-dot chain line position of the movable member 15 is the second operation position B where the blown air (arrow a) flows as it is without hitting the flat plate surface of the main body 15a. In the second operation position B, the main body portion 15a is horizontal.

  On the vehicle rear side of the evaporator 13, a wall portion 11 a protruding downward from the upper surface of the air conditioning case 11 is formed integrally with the air conditioning case 11. Further, on the vehicle rear side of the evaporator 13, the air conditioning case 11 forms a vertical wall surface 11b extending upward from the bottom surface portion. The vertical wall surface 11 b faces the lower part of the heat exchange core portion 13 a of the evaporator 13.

  In this example, a part of the wall portion 11a also faces the upper portion of the heat exchange core portion 13a of the evaporator 13, but the area of the portion of the wall portion 11a that faces the heat exchange core portion 13a is vertical. It is smaller than the area of the part of the wall surface 11b facing the heat exchange core part 13a.

  The cold air cooled by the evaporator 13 passes through a space formed between the lower end portion of the wall portion 11a and the upper end portion of the vertical wall surface 11b as indicated by an arrow d.

  In the air conditioning case 11, a heater core 16 is disposed on the rear side (the air flow downstream side) of the vertical wall surface 11b. The heater core 16 heats air using hot water (cooling water) from a vehicle engine (not shown) as a heat source. The heater core 16 has a heat exchange part composed of a laminated structure of a tube and a corrugated heat transfer fin between a lower hot water inlet tank part 16a and an upper hot water outlet tank part 16b arranged to face each other at a predetermined interval. 16c is arranged.

  The heater core 16 is disposed by inclining the hot water outlet tank portion 16b above the lower hot water inlet tank portion 16a toward the vehicle rear side. The plate-shaped air mix door 17 is disposed above the heater core 16, and the rotating shaft 17 a of the air mix door 17 is disposed near the upper end of the heater core 16.

  The rotary shaft 17a of the air mix door 17 is disposed so as to extend in the direction perpendicular to the plane of the drawing (vehicle width direction) in FIG. 1, and both ends of the rotary shaft 17a are formed by bearing holes (not shown) in the side wall portion of the air conditioning case 11. It is held rotatably.

  In the air conditioning case 11, a cold air bypass passage 18 is formed on the upper side of the heater core 16 (the vehicle rear side of the evaporator 13) to flow the cold air (arrow d) by bypassing the heater core 16 as indicated by an arrow e. On the other hand, in the air conditioning case 11, a hot air passage 19 through which the hot air heated by the heater core 16 flows as shown by an arrow f is formed in a portion from the rear side of the heater core 16 to the upper side.

  An air mixing section 20 that can mix hot air and cold air well is formed above the heater core 16 and downstream of the cold air bypass passage 18 and the hot air passage 19.

  In FIG. 1, the solid line position of the air mix door 17 is the maximum cooling position where the air passage of the heater core 16 is fully closed and the cold air bypass passage 18 is fully opened. The two-dot chain line position is a maximum heating position where the cold air bypass passage 18 is fully closed and the ventilation path of the heater core 16 is fully opened.

  As is well known, the air mix door 17 adjusts the air volume ratio between the warm air (arrow f) passing through the heat exchanging portion 16c of the heater core 16 and the cold air (arrow e) bypassing the heater core 16 and passing through the cold air bypass passage 18. Temperature adjusting means for adjusting the temperature of air blown into the passenger compartment. The air mixing unit 20 mixes the hot air (arrow f) and the cold air (arrow e) to obtain air having a desired temperature.

  On the other hand, a face opening 21 is opened on the vehicle rear side above the air conditioning case 11, and a defroster opening 22 is opened on the vehicle front side of the face opening 21. In the air conditioning case 11, a face passage 23 extending from the air mixing unit 20 toward the face opening 21 is formed.

  The face opening 21 blows out air toward the occupant's face through a face duct (not shown). A defroster duct (not shown) is connected to the defroster opening 22, and air is blown out from the defroster outlet at the tip of the defroster duct toward the inner surface of the vehicle front window glass.

  A defroster door 24 that switches between the defroster opening 22 and the face passage 23 is disposed above the air conditioning case 11. The defroster door 24 is a cantilever door in which a rotary shaft 24a is integrally disposed at one end in the door length direction.

  The rotating shaft 24 a of the defroster door 24 is arranged to extend in the direction perpendicular to the paper surface (vehicle width direction) in FIG. 1 on the rear side of the defroster opening 22, and both ends of the rotating shaft 24 a are the side walls of the air conditioning case 11. It is rotatably held by a bearing hole (not shown).

  In FIG. 1, the solid line position of the defroster door 24 indicates the position in the face mode, the bi-level mode, or the foot mode in which the defroster opening 22 is fully closed and the face passage 23 is fully opened. On the other hand, the two-dot chain line position of the defroster door 24 indicates a defroster mode position where the face passage 23 is fully closed and the defroster opening 22 is fully opened.

  Further, a foot passage 25 is formed in the air conditioning case 11 on the vehicle rear side of the warm air passage 19. The foot passage 25 is formed so as to hang downward from the face passage 23 side.

  Of the foot passage 25, the portion on the face passage 23 side opens almost entirely to the face passage 23 to form a foot opening 25 a.

  The foot passage 25 is formed so as to extend over the entire length in the vehicle width direction inside the case. Side opening portions 25b are opened at the left and right end portions of the foot passage 25 in the vehicle width direction, that is, the left and right side portions of the air conditioning case 11, which are the end portions (upper end portions) on the foot opening portion 25a side of the foot passage 25. Yes. A foot duct (not shown) that hangs downward is connected to each of the left and right side opening portions 25b, and air is blown from the foot outlet at the lower end of the foot duct to the feet of the front seat occupant. It has become.

  A rear foot opening 25c is opened at the downstream end (lower end) of the air passage 25 in the air flow direction. A rear foot duct (not shown) extending rearward of the vehicle is connected to the rear foot opening 25c, and air is blown from the rear foot outlet at the front end of the rear foot duct to the feet of the rear seat occupant. Yes.

  A face door 26 that switches between the face opening 21 and the foot opening 25a is disposed above and behind the air conditioning case 11. The face door 26 is a cantilever door in which a rotary shaft 26a is integrally disposed at one end in the door length direction.

  The rotary shaft 26 a of the face door 26 is arranged to extend in the direction perpendicular to the plane of FIG. 1 (vehicle width direction) on the rear side of the face opening 21, and both ends of the rotary shaft 26 a are the side wall portions of the air conditioning case 11. It is rotatably held by a bearing hole (not shown).

  In FIG. 1, the solid line position of the face door 26 indicates the position in the face mode in which the foot opening 25a of the foot passage 25 is fully closed and the face passage 23 is fully opened. On the other hand, the two-dot chain line position of the face door 26 indicates a foot mode position where the face passage 23 is fully closed and the foot opening 25a of the foot passage 25 is fully opened.

  The defroster door 24 and the face door 26 constitute a blow mode switching door, and the rotating shafts 24 a and 26 a of both the doors 24 and 26 are servoed via a link mechanism 27 outside the air conditioning case 11. It is connected to an electric drive device 28 composed of a motor, and the electric drive device 28 rotates both doors 24 and 26 to a predetermined position in conjunction with each other.

  Further, the rotating shaft 15b of the movable member 15 and the rotating shaft 17a of the air mix door 17 are also connected to the electric drive devices 29 and 30 each consisting of a servo motor outside the air conditioning case 11, respectively. The rotational positions (openings) of the movable member 15 and the air mix door 17 are adjusted. The electric drive device 29 corresponds to the operation mechanism in the present invention.

  The blower fan driving electric motor 12b of the blower 12 is controlled in applied voltage by the blower drive circuit 31, and the rotational speed of the blower 12 is adjusted by controlling the motor applied voltage.

  The air mix door 17, the defroster door 24, and the face door 26 may be rotated by a manual operation mechanism that uses the manual operation force of the passenger.

  Next, the principal part of the electric control part in this embodiment is demonstrated based on FIG. As is well known, the air conditioning electronic control device 32 is composed of a well-known microcomputer comprising a CPU, ROM, RAM, etc. and its peripheral circuits, and corresponds to the control means in the present invention.

  Various setting signals set by an occupant are input to the air-conditioning electronic control device 32 through operation members of an air-conditioning operation panel 33 arranged around the instrument panel in the passenger compartment.

  Specifically, the air conditioning operation panel 33 includes a temperature setting switch 34 that generates a temperature setting signal Tset, an auto switch 35 that outputs a command signal of an air conditioning automatic control state, and an inside / outside air switching switch that generates an inside / outside air switching signal. There are provided operation members such as an air volume switch for generating an air volume switching signal for the blower 12, a blow mode switch for generating a blow mode signal, and an air conditioner switch for generating an operation signal for a compressor (not shown) in a refrigeration cycle.

  The air conditioning electronic control device 32 receives detection signals from the sensor groups 36 to 38 that detect the internal air temperature Tr, the external air temperature Tam, the solar radiation amount Ts, and the like for air conditioning control.

  The air-conditioning electronic control device 32 is based on the detection signals from the sensor groups 36 to 38 and various setting signals from the operation members of the air-conditioning operation panel 33, and the electric drive devices 28 and movable members of the defroster door 24 and the face door 26. 15, the electric drive device 29 of the air mix door 17, the blower drive circuit 31 of the electric motor 12 b for driving the blower fan of the electric blower 12, the compressor of the refrigeration cycle, and the like. Yes.

  Next, the operation of this embodiment will be described based on the above configuration. In FIG. 1, when the electric motor 12b of the blower unit 12 is energized and the centrifugal blower fan 12a is rotationally driven, the inside air or the outside air is sucked from an inside / outside air switching box (not shown), and this sucked air is blown by the blower fan 12a. The vehicle front side region in the air conditioning case 11 flows from the front to the rear as indicated by the arrow a and is blown to the front surface of the evaporator 13.

  By the way, the cold air d that passes through the heat exchange core portion 13a of the evaporator 13 to the vehicle rear side and is cooled and flows to the vehicle rear side is adjusted by the electric drive device 30 as shown in FIG. According to the opening of 17, the cool air e passing through the cool air bypass passage 18 and the warm air f passing through the heater core 16 are distributed, and the cool air e and the warm air f are mixed in the vicinity of the air mixing unit 20. Therefore, by adjusting the air volume ratio of the cold air e and the hot air f by the air mix door 17, air having a desired temperature can be obtained in the air mixing unit 20.

  The air at the desired temperature is blown into the vehicle compartment from a predetermined outlet by opening and closing the blow mode switching door by the blow mode operation mechanism including the link mechanism 27 and the electric drive device 28 according to the set blow mode. The

  When the face mode is set, the face door 26 is operated to the solid line position where the face opening 21 is fully opened and the foot opening 25a is fully closed by the blowing mode operation mechanism. At the same time, the defroster door 24 is operated to the solid line position by the blowing mode operation mechanism, and the defroster opening 22 is fully closed and the face passage 23 is fully opened.

  Therefore, the conditioned air adjusted to a desired temperature by the air mix door 17 (face mode is mainly cool air) passes through the face passage 23 from the air mixing unit 20 and flows into the face opening 21, and this face opening 21 To the passenger's face side to cool the passenger compartment.

  Next, when the bi-level mode is set, the face door 26 is operated to the intermediate opening position and the defroster door 24 is operated to the solid line position in FIG. Both of the foot openings 25a are simultaneously opened to the same extent.

  Therefore, a part of the conditioned air whose temperature is adjusted by the air mix door 17 passes through the face passage 23 from the air mixing unit 20 and blows out from the face opening 21 to the occupant's face side, and at the same time, the remaining conditioned air is air. It flows into the foot opening 25 a and the foot passage 25 from the mixing unit 20. Further, the air flows from the foot passage 25 to the side opening 25b located on the left and right side surfaces of the air conditioning case 11 and the rear foot opening 25c located at the lower end of the foot passage 25. The side opening 25b and the rear foot opening 25c Air conditioned air blows out to the feet of the front and rear passengers.

  Next, when the foot mode is set, the face door 26 is in the position indicated by the two-dot chain line in FIG. 1, and the face door 26 fully opens the foot opening 25a and fully closes the face opening 21. For this reason, the air whose temperature has been adjusted by the air mixing unit 20 is blown out only to the feet of the front and rear passengers through the face passage 23, the foot opening 25a, the foot passage 25, the side opening 25b, and the rear foot opening 25c. .

  Next, when the foot defroster mode is set, the face door 26 is in the position indicated by the two-dot chain line in FIG. 1, and the foot opening 25a is fully opened and the face opening 21 is fully closed. Moreover, the defroster door 24 becomes an intermediate opening position, and both the defroster opening 22 and the face passage 23 are simultaneously opened to the same extent. As a result, the air whose temperature has been adjusted by the air mixing unit 20 is blown out toward the vehicle window through the defroster opening 22 to prevent the vehicle window from being fogged. At the same time, the air whose temperature has been adjusted by the air mixing unit 20 is blown out to the feet of the front and rear passengers through the face passage 23, the foot opening 25a, the foot passage 25, the side opening 25b, and the rear foot opening 25c. To heat the passenger feet.

  Next, when the defroster mode is set, the defroster door 24 is positioned at the two-dot chain line in FIG. 1, the face opening 21 is fully closed, and the defroster opening 22 is fully opened. As a result, the entire amount of the air whose temperature has been adjusted by the air mixing unit 20 is blown out to the vehicle window glass side through the defroster opening 22, thereby preventing the vehicle window glass from being fogged.

  Next, a control process that is a main part of the operation of the present embodiment will be described with reference to FIG. The flowchart of FIG. 3 shows an outline of the control processing executed by the microcomputer of the air conditioning electronic control device 32. The control routine of FIG. 3 is an electronic control for air conditioning when an ignition switch (not shown) of the vehicle engine is turned on. This is executed when the auto switch 35 of the air conditioning operation panel 33 is turned on in a state where power is supplied to the device 32.

  First, after initialization of a timer, a flag, etc., in step S100, an operation signal from the temperature setting switch 34 of the air conditioning operation panel 33 and detection signals from the sensor groups 36 to 38 are read.

  Subsequently, in step S200, a target blowing temperature TAO of the conditioned air blown into the vehicle interior is calculated based on the following formula (1). This target blowing temperature TAO is a blowing temperature necessary for maintaining the passenger compartment at the set temperature Tset of the temperature setting switch 34.

TAO = Kset × Tset−Kr × Tr−Kam × Tam−Ks × Ts + C (1)
Here, Tr is the inside air temperature detected by the inside air temperature sensor 36, Tam is the outside air temperature detected by the outside air temperature sensor 37, Ts is the amount of solar radiation detected by the solar radiation sensor 38, and Kset, Kr, Kam, and Ks are controlled. Gain and C are correction constants.

  In step S300, the blower voltage BLW to be applied to the blower fan driving electric motor 12b of the blower 12 is determined using the TAO and the characteristic diagram shown in FIG.

  In the characteristic diagram shown in FIG. 4, when TAO is in the intermediate region, the blower voltage BLW is set to be the lowest value, and as the TAO gradually increases from the intermediate region, the blower voltage BLW gradually approaches the highest value. The blower voltage BLW is set to gradually approach the maximum value as TAO gradually decreases from the intermediate region.

  Here, the blower voltage BLW and the air volume by the blower 12 are in a one-to-one relationship, and as the blower voltage BLW increases, the air volume by the blower 12 increases, and as the blower voltage BLW decreases, by the blower 12 The air volume is decreasing.

  Next, it progresses to step S400 and it is determined whether the blower voltage BLW is larger than a predetermined value. The predetermined value of the blower voltage BLW can be arbitrarily set, but is set as follows in this embodiment.

  That is, when the air volume of the blower fan 12a is large, the condensed water of the evaporator 13 is quickly discharged to the downstream side of the air flow of the evaporator 13 by the wind pressure. On the other hand, when the air volume of the blower fan 12a is small, the wind pressure applied to the condensed water is small, so the drainage of the condensed water is lowered and the amount of condensed water retained in the evaporator 13 is increased.

  Therefore, in the present embodiment, the value of the blower voltage BLW that generates the air volume when the retained water amount of the condensed water in the evaporator 13 becomes a predetermined amount is set as the predetermined value. It should be noted that “the air volume when the amount of condensed water retained in the evaporator 13 becomes a predetermined amount” and “the value of the blower voltage BLW that generates the air amount when the amount of retained water in the evaporator 13 reaches a predetermined amount”. Is previously determined by experiment.

  When it is determined in step S400 that the blower voltage BLW is greater than the predetermined value, the process proceeds to step S500, and the movable member 15 is rotated to the second operation position B indicated by the two-dot chain line in FIG. At the second operation position B, the blown air (arrow a) of the blower fan 12a flows without hitting the flat plate surface of the main body portion 15a, so that the air flow is not changed by the movable member 15.

  In step S600, the blower voltage BLW is applied to the blower fan driving electric motor 12b of the blower 12 to adjust the air volume by the blower 12. At this time, the condensed water in the evaporator 13 is quickly discharged to the downstream side of the air flow of the evaporator 13 by the wind pressure.

  On the other hand, when it is determined in step S400 that the blower voltage BLW is equal to or lower than the predetermined value, the process proceeds to step S700, and the blower voltage BLW is applied to the blower fan driving electric motor 12b of the blower 12 to adjust the air volume by the blower 12. After that, in step S800, the movable member 15 is rotated to the first operation position A shown by the solid line in FIG. Thereby, the condensate drainage property at the time of the low air volume in which the blower voltage BLW is below a predetermined value is improved.

  Specifically, when the movable member 15 is rotated to the first operation position A, the flow of air that hits the flat plate surface of the main body 15a in the blown air (arrow a) of the blower fan 12a is indicated by the arrow b in FIG. Thus, it is guided to the lower part of the evaporator 13. As a result, the blown air is concentrated in the lower part of the evaporator 13.

  FIG. 5 shows the passing wind speed distribution of the evaporator 13 at this time. As can be seen from FIG. 5, when the movable member 15 is rotated to the first operation position A, the flow of the blown air is concentrated at the lower part of the evaporator 13. The passing wind speed at the lower part of 13 can be increased.

  On the other hand, FIG. 6 is a comparative example, and shows a passing air speed distribution of the evaporator 13 in a state where the movable member 15 is rotated to the second operation position B with the same air volume as in FIG. As can be seen from FIG. 6, when the movable member 15 is rotated to the second operation position B, the passing wind speed at both ends in the gravity direction of the evaporator 13 becomes small.

  In this comparative example, the passing wind speed at the lower part of the evaporator 13 is particularly small. This is because the vertical wall surface 11b of the air conditioning case 11 faces the lower part of the heat exchange core portion 13a of the evaporator 13 on the downstream side of the air flow of the evaporator 13 (the vehicle rear side). This is because the flow of air passing through the lower portion of the exchange core portion 13a is blocked.

  Since the wind pressure applied to the condensed water is low when the blower voltage BLW is below a predetermined value, the condensed water is not drained to the downstream side of the air flow of the evaporator 13, and the heat exchange core is caused by gravity as indicated by an arrow g. It falls down along the surface of the part 13a. In this comparative example, since the passing wind speed is particularly low in the lower part of the evaporator 13, the drainage performance is significantly reduced in the lower part of the evaporator 13. For this reason, the condensed water which falls along the surface of the heat exchange core part 13a will stay in large quantities in the lower part of the heat exchange core part 13a.

  In this way, if the amount of air is rapidly increased with a large amount of condensed water remaining in the lower part of the heat exchange core portion 13a, a large amount of condensed water is blown to the downstream side of the air flow.

  On the other hand, in the present embodiment shown in FIG. 5, the passing air speed at the lower part of the evaporator 13 can be increased, so that an appropriate wind pressure can be applied to the condensed water collected at the lower part of the evaporator 13. . For this reason, since condensed water can be discharged | emitted favorably to the air flow downstream of the evaporator 13 also at the time of low air volume, it can avoid that condensed water accumulates in the lower part of the heat exchange core part 13a.

  By the way, if the movable member 15 is rotated to the first operation position A when the blower voltage BLW is higher than a predetermined value, the passing wind speed and the wind pressure at the lower part of the evaporator 13 become too high, and the evaporator 13 Condensed water in the lower part is blown to the downstream side of the air flow.

  In this regard, in this embodiment, if it is determined in step S400 that the blower voltage BLW is greater than the predetermined value, the movable member 15 is rotated from the first operation position A to the second operation position B in step S500. In step S600, the air volume of the blower 12 is increased.

  Further, when it is determined in step S400 that the blower voltage BLW is equal to or less than the predetermined value, the air volume of the blower 12 is reduced in step S700, and then the movable member 15 is moved from the first operation position A to the second operation position in step S600. Rotate to B.

  For this reason, since the movable member 15 is always in the second operating position B when the blower voltage BLW is higher than the predetermined value, it is possible to avoid excessive increase in the passing wind speed and the wind pressure in the lower part of the evaporator 13. As a result, it is possible to avoid the condensed water in the lower part of the evaporator 13 from being blown to the downstream side of the air flow.

  Further, if the flow of the blown air is concentrated in the lower part of the evaporator 13, the cooling performance cannot be sufficiently exhibited in the upper part of the evaporator 13, so that the cooling performance of the evaporator 13 is deteriorated, but at the time of low airflow with a low cooling load. Such a decrease in cooling performance is not a problem.

  On the other hand, when the cooling load is high and the air volume is high, the movable member 15 is rotated to the second operation position B to avoid the flow of the blown air from concentrating on the lower part of the evaporator 13, thereby reducing the cooling performance. In addition, the cooling performance can be exhibited in the entire region of the evaporator 13 without any problem.

  Moreover, in this embodiment, since the drainage of the condensed water at the time of a low air volume can be improved, the condensed water retention amount of the evaporator 13 can be reduced. For this reason, generation | occurrence | production of the frost (frosted) phenomenon in the evaporator 13 can be suppressed.

(Second Embodiment)
In the first embodiment, only one movable member 15 is arranged. However, in the second embodiment, as shown in FIG. 7, a plurality of movable members 15 are arranged side by side in the direction of gravity.

  In the present embodiment, each of the plurality of movable members 15 is configured as a so-called cantilever door in which a rotation shaft 15b is disposed at one end portion in the length direction of the main body portion 15a. The rotating shafts 15 b of the plurality of movable members 15 are connected to the electric drive device 29 via the link mechanism 40 outside the air conditioning case 11.

  The electric drive device 29 rotates the plurality of movable members 15 to a predetermined position in conjunction with each other. Note that the plurality of movable members 15 may be individually rotated by the plurality of electric drive devices 29.

  In FIG. 7, the solid line position of the movable member 15 is a first operation position A for guiding the blown air (arrow a) to the lower part of the evaporator 13. In the first operation position A, the rotation tip of the main body 15 a faces the lower part of the evaporator 13. That is, the main body portion 15a is inclined downward on the rotating front end side.

  On the other hand, the two-dot chain line position of the movable member 15 is the second operation position B where the blown air (arrow a) flows as it is without hitting the flat plate surface of the main body 15a. In the second operation position B, the rotation tip of the main body portion 15a faces the rear of the vehicle. That is, the main body portion 15a is horizontal.

  In the present embodiment, the blown air (arrow a) can be effectively guided to the lower part of the evaporator 13 by the plurality of movable members 15. For this reason, at the time of a low air volume, condensed water can be discharged | emitted more favorably to the air flow downstream of the evaporator 13. FIG.

(Third embodiment)
In the said 1st Embodiment, although the movable member 15 is arrange | positioned in the air-conditioning case 11 in the approximate center of the gravity direction, in this 3rd Embodiment, as shown in FIG. Arranged at the top of the.

  In the present embodiment, the movable member 15 is a cantilever door. The rotating shaft 15 b of the movable member 15 is disposed close to the upper surface portion of the air conditioning case 11.

  In FIG. 8, the solid line position of the movable member 15 is the first operation position A for guiding the blown air (arrow a) to the lower part of the evaporator 13. In the first operation position A, the rotation tip of the main body 15 a faces the lower part of the evaporator 13. That is, the main body portion 15a is inclined downward on the rotating front end side.

  On the other hand, the two-dot chain line position of the movable member 15 is the second operation position B where the blown air (arrow a) flows as it is without hitting the flat plate surface of the main body 15a. In the second operation position B, the rotating front end portion of the main body portion 15 a faces the upper portion of the evaporator 13. That is, the main body portion 15 a is substantially parallel to the upper surface of the air conditioning case 11.

  Even if the movable member 15 is configured in this manner, the same effects as those of the first embodiment can be obtained.

(Fourth embodiment)
In the first embodiment, the movable member 15 is arranged on the upstream side of the air flow of the evaporator 13. However, in the fourth embodiment, as shown in FIG. It is arranged on the downstream flow side.

  In the present embodiment, the movable member 15 is a cantilever door. The rotating shaft 15 b of the movable member 15 is disposed close to the upper surface portion of the air conditioning case 11.

  In FIG. 9, the solid line position of the movable member 15 is a first operation position D that obstructs the air flow passing through the upper portion of the heat exchange core portion 13 a of the evaporator 13. In the first operation position D, the rotation tip of the main body portion 15a faces downward. That is, the flat plate surface of the main body portion 15 a faces the upper portion of the heat exchange core portion 13 a of the evaporator 13.

On the other hand, the two-dot chain line position of the movable member 15 is the second operation position E where the blown air (arrow a) flows as it is without hitting the flat plate surface of the main body 15a. In the second operation position E, the main body portion 15a is substantially parallel to the upper surface of the air conditioning case 11. In this embodiment, when the movable member 15 is rotated to the second operation position E, the main body portion 15a is moved to the evaporator 13. Since the air flow passing through the heat exchange core portion 13a is not hindered, the blown air passes through the heat exchange core portion 13a as it is.

  On the other hand, when the movable member 15 is rotated to the first operation position D, the air flow passing through the upper portion of the heat exchange core portion 13a is obstructed by the flat plate surface of the main body portion 15a. , Mainly flows through the lower part of the heat exchange core part 13a and flows to the air mix door 17 side.

  For this reason, since the flow of blowing air can be concentrated in the lower part of the evaporator 13, the condensed water of the evaporator 13 can be discharged | emitted favorably downstream of an air flow at the time of low air volume.

(Other embodiments)
In each of the above-described embodiments, the present invention is applied to a so-called automatic air conditioner that performs automatic control so as to maintain a desired temperature when the occupant sets a desired temperature, but the occupant manually adjusts the temperature, the air volume, etc. The present invention may be applied to an air conditioner. That is, when the air volume set by the occupant is less than or equal to the predetermined air volume, the movable member 15 is rotated to a position where the blown air is concentrated at the lower part of the evaporator 13, while when the air volume set by the occupant is larger than the predetermined air volume, The movable member 15 may be rotated to a position where the flow does not change.

  In this case, the rotating operation of the movable member 15 is not necessarily performed by the electric drive device 29 including the air-conditioning electronic control device 32 and the servo motor, and the driving means of the movable member 15 may be configured by a manual operation mechanism. . That is, the air volume switching of the blower 12 is performed by an air volume switching lever operated by an occupant, and the air flow switching lever is connected to the movable member 15 via a link mechanism or the like, whereby the blower 12 and the movable member 15 are connected. May be operated in conjunction with each other.

  Further, in each of the above embodiments, the movable member 15 is constituted by a revolving door that can rotate around the rotation shaft 15b. However, the movable member 15 can be slid in the vehicle width direction (left-right direction) or the gravity direction. You may comprise.

  In each of the above embodiments, the present invention is applied to a vehicle air conditioner. However, the present invention is not limited to a vehicle and can be generally applied to an air conditioner as long as it matches the gist of the present invention.

It is a schematic sectional drawing of the indoor unit part in 1st Embodiment of this invention. It is a block diagram which shows the principal part of the electric control part in 1st Embodiment of this invention. It is a flowchart which shows the principal part of the action | operation of 1st Embodiment of this invention. It is an air volume control characteristic figure in a 1st embodiment of the present invention. It is a passing wind speed distribution map of the evaporator in a 1st embodiment of the present invention. It is a passing wind speed distribution map of the evaporator in a comparative example. It is principal part sectional drawing of the indoor unit part in 2nd Embodiment of this invention. It is principal part sectional drawing of the indoor unit part in 3rd Embodiment of this invention. It is principal part sectional drawing of the indoor unit part in 4th Embodiment of this invention.

Explanation of symbols

12 ... Blower, 13 ... Evaporator (cooling heat exchanger), 15 ... Movable member,
29 ... Electric drive device (operation mechanism), A ... First operation position, B ... Second operation position.

Claims (6)

A blower (12) for blowing air;
A cooling heat exchanger (13) arranged in the direction of gravity in an air passage through which the air flows, and cooling the air;
A first operating position (A, D) that is disposed in the air passage and concentrates the air flow at a lower portion of the cooling heat exchanger (13), and along an air inflow direction into the air passage. A movable member (15) operable to a second operation position (B, E) for flowing the air as it is;
An operation mechanism (29) for operating the movable member (15),
The operation mechanism (29) operates the movable member (15) to the second operation position (B, E) when the air volume of the blower (12) is larger than a predetermined air volume, and the air volume is less than the predetermined air volume. An air conditioner characterized in that the movable member (15) is sometimes operated to the first operation position (A, D). The movable member (15) is disposed on the upstream side of the air flow of the cooling heat exchanger (13);
The movable member (15) operated to the first operating position (A) guides air on the upstream side of the air flow to a lower portion of the cooling heat exchanger (13). The air conditioner according to claim 1. The air conditioner according to claim 2, wherein the movable member (15) is constituted by a rotatable member arranged in the gravity direction. The movable member (15) is disposed on the downstream side of the air flow of the cooling heat exchanger (13),
The movable member (15) operated to the first operating position (D) prevents the flow of air passing through the upper part of the cooling heat exchanger (13). The air conditioner according to claim 1. The air conditioner according to any one of claims 1 to 4, further comprising control means (32) for controlling the blower (12) and the operation mechanism (29). When the control means (32) determines that the air volume needs to be reduced from the first air volume larger than the predetermined air volume to the second air volume below the predetermined air volume, the air volume is changed from the first air volume to the second air volume. The movable member (15) is moved from the second operation position (B, E) to the first operation position (A, D),
Further, when the control means (32) determines that the air volume needs to be increased from the second air volume to the first air volume, the movable member (15) is moved from the first operation position (A, D). The air conditioner according to claim 5, wherein the air volume is increased from the second air volume to the first air volume after being operated to the second operation position (B, E).

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