JP2006015945A - Air-conditioning unit for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve strength of a unit case of an air-conditioning unit for a vehicle, and prevent turbulence and drift of air on a windward side of a cooling heat exchanger. <P>SOLUTION: An air flow path for sending air from a blower 4 to a cooling heat exchanger 5 has a ventilation path 21 extending from a boundary portion to a winding terminal end of a scroll part 20 to a bottom end of an air flow side windward face of a cooling heat exchanger 5 on the leeward side of the scroll part 20. The air flow path 21 has a relatively small expansion rate of a passage area on the windward side to a passage area of a terminal portion of the scroll part 20. One end of the windward face 22 is connected with a face of the scroll part 20, and the other end extends to the lower side of the cooling heat exchanger 5. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a unit case structure, in particular, of a vertically installed air conditioning unit mounted on a center console portion of a vehicle, for example.

The scroll fan air intake is placed on its side so that it opens opposite to the width direction of the vehicle, and the evaporator is located below the vertical direction of the vehicle and stored in the unit case. A vertical-type automotive air conditioner is already known (see, for example, Patent Document 1). If this is embodied in an air conditioning unit having the same basic configuration as the air conditioning unit according to the present application, it is as shown in FIG. In FIG. 13, 100 is an air conditioning unit, 101 is a unit body, 102 is a blower, 103 is a cooling heat exchanger, 104 is a unit case, 105 is a scroll portion, and 106 is a ventilation path portion. These configurations are substantially the same as those of the air conditioning unit 1 shown in FIG.
JP 2001-158217 A

  However, in the automotive air conditioner disclosed in Patent Document 1, the air flow path for guiding air from the discharge port of the fan to the heat exchanger for cooling is formed so as to face the inner surface having the bell mouth and scroll. The outer surface connected to the outer peripheral surface at the boundary between the scroll portion and the vicinity of the cooling heat exchanger in the ventilation path portion is more in the vehicle width direction than the outer peripheral wall surface with respect to the arc-shaped outer peripheral surface defining the portion. Spreading along. That is, the passage area of the ventilation path portion is rapidly expanded from the boundary portion.

  For this reason, the air guided to the scroll part from the air discharge port of the fan is, for example, in the process from the scroll part defined on the outer peripheral surface to the boundary part to the passage part defined on the outer surface. As shown by the arrow in FIG. 13B, turbulent flow is generated by rapid diffusion, which may cause noise and high ventilation resistance.

  Further, in the automotive air conditioner shown in Patent Document 1, the air sent from the scroll portion drifts to the lower side of the cooling heat exchanger, which is the farthest upstream side of the cooling heat exchanger. In the lower part of the cooling heat exchanger where the air velocity of the air passing through the cooling heat exchanger is not uniform and the ventilation rate is relatively fast, the water condensed and condensed on the surface of the cooling heat exchanger There is also a risk of flying to the side.

  Furthermore, since the inner side surface of the scroll portion has an opening for communicating with the air discharge port of the fan, the strength as a support body that supports the motor of the fan is not necessarily sufficient in structure. For this reason, the strength of the motor mounting surface on which the motor of the fan is mounted is also relatively insufficient, and there may be a problem such that the vibration of the motor increases and noise is generated.

  On the other hand, in Japanese Patent Application Laid-Open No. H10-228867, the foot passage duct is routed forward through the space in order to effectively use the space formed on both sides of the fan in the axial direction in FIG. Although examples are shown, the space secured on both sides of the fan in the axial direction is too small, and it is necessary to shift the tip of the foot passage duct to the left and right along the vehicle width direction. It cannot be said that it contributes sufficiently to the reduction of the required volume.

  In view of this, the present invention provides a vehicle air-conditioning unit that is devised in terms of the shape of the unit case, thereby preventing the occurrence of turbulent air flow and equalizing the distribution of air sent to the windward side of the cooling heat exchanger. The purpose is to prevent water from flowing downwind by equalizing the wind speed, to improve the strength of the unit case, and to secure sufficient space for passing ducts forward or backward in the vehicle traveling direction. It is.

  An air conditioning unit for a vehicle according to the present invention includes an air blower composed of a fan and a motor and a cooling heat exchanger, in the unit case so that the air blower is positioned relatively above the heat exchanger for cooling. And as an air flow path for sending air from the blower to the windward side of the cooling heat exchanger, cooling is performed from the boundary portion with the winding end portion of the scroll portion on the leeward side of the scroll portion. The ventilation path portion extends to the lower end of the upstream side of the ventilation side of the heat exchanger for cooling, and this ventilation path portion is located on the windward side of the cooling heat exchanger and the ventilation surface of the cooling heat exchanger. An upwind side surface disposed opposite to the upwind side surface and an air guide surface that is connected to the upwind side surface and guides air to the cooling heat exchanger side. The area of the passage in the vicinity of the upwind side of the ventilation path, It is characterized in being formed of magnification for the passage area of the winding terminal end portion of the roll unit to relatively small (claim 1). Here, the width of the upwind side surface of the ventilation path is substantially the same as the width of the scroll portion and the boundary portion thereof, and is configured so that there is no sudden expansion or reduction from the boundary portion over the entire ventilation path. (Claim 2). Further, the upwind side surface of the ventilation path has a portion extended in a substantially tangential direction of the winding of the scroll portion at a boundary portion with the winding end portion of the scroll portion. 3).

  The air passage section includes air direction changing means for changing the air direction of the air flowing in the air passage section in the middle of the air passage section to the upper side of the cooling heat exchanger (Claim 4). . Specifically, the wind direction changing means is configured by configuring the upwind side surface of the ventilation path portion with two divided surfaces arranged along the air flow, and connecting the two divided surfaces with a connecting surface, It is formed by providing a level | step difference in the middle of the ventilation path part (Claim 5).

  Further, the air passage section is characterized in that an air guide surface connected to the windward side surface is temporarily extended outward along the vehicle width direction as it approaches the cooling heat exchanger. 6). In this case, the air guide surface may be a flat plate or a curved surface that draws an arc recessed inward. Furthermore, the blower is arranged relatively close to the cooling heat exchanger (Claim 7).

  According to the present invention, there is almost no difference between the passage area of the windward side portion of the ventilation path portion and the passage area of the winding end portion of the scroll portion, and the expansion of the ventilation path portion in the vehicle width direction is relatively small. Since it has a structure, when the air flows from the scroll part into the ventilation path part, the air does not diffuse suddenly. For this reason, it is possible to suppress the occurrence of turbulence in the air, to avoid the generation of noise and high ventilation resistance, thereby suppressing the wind speed on the windward side of the cooling heat exchanger from becoming uneven, It is possible to prevent water from flowing down the cooling heat exchanger. In addition, the strength of the motor mounting surface to which the motor of the blower is mounted is relatively increased because the windward side surface of the ventilation path portion extends from the surface of the scroll portion to the lower portion of the cooling heat exchanger. Therefore, the vibration of the motor can be suppressed and the generation of noise can be reduced.

  In particular, according to the second aspect of the present invention, the air sent by the impeller of the blower forms a mainstream portion at the outer portion of the scroll portion by centrifugal force. As a result, when the air is blown from the winding terminal portion of the scroll portion to the ventilation path portion, a main flow portion is formed on the windward side surface, and the flow path width on the windward side surface is rapidly changed. However, in the invention according to claim 2, in the invention according to claim 2, by not abruptly changing the width of the windward side surface in the flow direction of the main flow portion, a sudden change in the channel width on the windward side surface is eliminated, A smoother flow can be ensured. In particular, according to the invention described in claim 3, since the boundary portion side of the airflow passage portion with the scroll portion is extended along the substantially tangential direction of the winding end portion of the scroll portion, the air is provided downstream. Can be sent smoothly.

  In particular, according to the inventions of the fourth and fifth aspects, the air direction changing means can prevent the air from drifting to the lower side of the cooling heat exchanger. The wind speed can be made uniform, and the water condensed and condensed on the surface of the cooling heat exchanger can be prevented from flying down to the cooling heat exchanger.

  In particular, according to the invention described in claim 6, by cutting the ventilation path portion, it is possible to suppress a rapid expansion of the passage area from the scroll portion to the ventilation path portion, and to reduce the cooling heat exchanger by the Coanda effect. The air that is about to flow to the lower side of the air can be supplied to the upper side of the heat exchanger for cooling along the air guide surface, so that the air volume distribution can be equalized and the air speed can be made uniform. According to the sixth aspect of the present invention, the ventilation passage portion is cut away from the portion corresponding to the ventilation flow area other than the mainstream portion, so that it is possible to reduce the required volume for mounting the air conditioning unit. Furthermore, according to the sixth aspect of the present invention, it is possible to pass a duct, a harness, or the like forward or backward in the vehicle traveling direction by using the space generated by reducing the ventilation path portion.

  In particular, according to the seventh aspect of the invention, the blower can be disposed immediately above the cooling heat exchanger, and the air conditioning unit can be reduced in size, while the scroll portion is wound. The distance from the end to the windward side of the cooling heat exchanger becomes relatively short, and a distance for enlarging the passage area of the ventilation passage portion cannot be taken for a while. In the present invention, even with such a short distance, The purpose can be fully achieved.

  Embodiments of the present invention will be described below with reference to the drawings.

  The air conditioning unit 1 shown in FIGS. 1, 2 and 3 is of a vertical full center placement type, for example, disposed at the center of the lower part of a vehicle instrument panel, and includes an intake box (not shown) and the unit main body 2. Basically composed. The intake box has a well-known open / close air switching door for appropriately selecting the air introduced from the inside air introduction port and the air introduced from the outside air introduction port. Is.

  As shown in FIGS. 2 and 3A, the unit main body 2 is a cooling device such as a blower 4 for sending air from the intake box to the downstream side, an evaporator for cooling the air sent by the blower 4, and the like. Heat exchanger 5, heating heat exchanger 6 such as a heater core that reheats the air cooled by cooling heat exchanger 5, and between cooling heat exchanger 5 and heating heat exchanger 6. An air mix door 7 that adjusts the ratio of the air that is arranged and sent to the heat exchanger 6 for heating and the air that is bypassed is housed in the unit case 8.

  In this embodiment, the blower 4 includes a fan 4A called a centrifugal multiblade fan (sirocco fan) and a motor 4B that drives the fan 4A, and is shown in FIG. Thus, the opening part opened in the vehicle left-right direction both sides with respect to the unit case 8 is provided, and it is inserted and arrange | positioned in this state so that the drive shaft of the motor 4B may follow along the vehicle left-right direction from this opening part. The cooling heat exchanger 5 is disposed at a position behind the blower 4 in the vehicle traveling direction and below the vehicle vertical direction, and in this embodiment, the heating heat exchanger 5 and the vehicle left-right direction. It is inclined to the front side. The blower 4 and the cooling heat exchanger 5 are relatively close to each other, and the blower 4 is disposed immediately above the cooling heat exchanger 5.

  Further, as shown in FIGS. 2 and 3, the unit main body 2 is disposed in the unit case 8 on the downstream side of the heating heat exchanger 6, in this embodiment, on the front side in the vehicle traveling direction. A hot air passage 9 through which the air reheated by the heating heat exchanger 6 passes is formed, and the vehicle traveling direction from the downstream side of the cooling heat exchanger 5 to the rotating shaft of the air mix door 7 A cool air passage 10 is formed slightly diagonally upward.

  Then, on the downstream side of the air mix chamber 11 where the hot air passage 9 and the cool air passage 10 of the unit main body 2 merge, as shown in FIGS. A blowing opening 13 and a foot blowing opening 14 are appropriately opened in the unit case 8. The foot blowing opening 14 is in an air flow path that continues from the air mix chamber 11 and extends in the vehicle lateral direction in the middle of the air flow path.

  The blowing openings 12 and 13 are disposed on the periphery of the opening so that a blowing mode switching door 16 that opens and closes the openings 12 and 13 is swingable. In addition, a blow mode switching door 17 is slidably disposed on the flow path at a branching portion of the foot blow opening 14, and the air amount toward the foot blow opening 14 and the blow openings 12, 13 are arranged. It is possible to adjust the air amount toward

  By the way, of the air flow path in the case of the unit main body 2, the windward air flow path from the blower 4 to the cooling heat exchanger 5 is composed of a scroll portion 20 and a ventilation passage portion 21 continuous to the scroll portion 20. It is. Among these, the scroll part 20 is formed in the winding shape toward the outer side from the nose part 20a, and the ventilation path part 21 is continuous at the terminal portion of this winding.

  The ventilation path portion 21 is connected to the windward side surface 22 facing the windward ventilation surface of the cooling heat exchanger 5 and both side edges of the windward side surface 22 and is connected to the cooling heat exchanger from the windward side surface 22. A portion 21A extending from the winding end of the scroll portion 20 in a substantially tangential direction of the winding, and a cooling heat exchanger. The windward side surface 22 has one end continuous with the surface of the scroll portion 20 and the other end extending to the lower side of the cooling heat exchanger 5. Yes. And the width of this windward side surface 22 is substantially the same as the width in the boundary part with the winding termination | terminus part of the scroll part 20 with the cutting of the range shown by the oblique line of FIG. 3 (A) and (B), It is comprised so that there may be no rapid expansion or contraction over the ventilation path part 21 whole region from the said boundary part.

  Thereby, since the strength of the motor mounting surface of the unit case 8 to which the motor 4B of the blower 4 is mounted is also relatively improved by the upwind side surface 22 and the like, the vibration of the motor 4B can be suppressed and the generation of noise can be reduced. . Moreover, since air is smoothly sent to the downstream side by the portion 21A extending in the substantially tangential direction of the winding end portion of the scroll portion 20 in the ventilation path portion 21, the air resistance can be reduced.

  On the other hand, as shown in FIG. 4 (A), the windward side surface 22 is composed of a divided surface 22A and a divided surface 22B having different inclinations in accordance with the boundary between the two portions 21A and 21B of the ventilation path portion 21. On the other hand, when there is no step between the dividing surface 22A and the dividing surface 22B, most of the air that flows into the ventilation path portion 21 from the scroll portion 20 flows along the inner surface of the upwind side surface 22 as a cooling heat exchanger. As a result, the maximum ventilation resistance (total pressure) is about 523 Pa and the maximum wind speed is about 22.62 m / s, although the wind speed is not relatively fast, but the maximum ventilation resistance (total pressure) is It will be big. This is because, as shown in FIG. 4B, in the characteristic diagram showing the pressure distribution from the maximum value a to the minimum value j, the range of the maximum value a extends to the lower side of the cooling heat exchanger 5. It can be understood from the fact that it is relatively large.

  In order to eliminate such a problem, it is necessary to change a part of the wind direction to flow to the lower side of the cooling heat exchanger 5 so that air can also be sent to the upper side of the cooling heat exchanger 5. However, as such a wind direction changing means, while separating the lower end of the dividing surface 22A and the upper end of the dividing surface 22B, the step of colliding with air by passing the connecting surface 22C between them is passed through the air passage portion 21. It is adopted in the present invention to form the following.

  In order to know the optimum value of the step width, the step width L1 as shown in FIG. 5A is 10 mm, the step width L2 as shown in FIG. 6A is 15 mm, and FIG. When the three steps of the step width L3 as shown in FIG. 7 were analyzed, the worst condition was when the step shown in FIG. 7A was 20 mm, and the maximum ventilation resistance (total pressure) was about 526 Pa, The maximum wind speed was about 22.86 m / s. Next, when the level difference L2 shown in FIG. 6A was 15 mm, the maximum ventilation resistance (total pressure) was about 503 Pa and the maximum wind speed was about 24.97 m / s. The best conditions were when the step width L1 shown in FIG. 5A was 10 mm, the maximum ventilation resistance (total pressure) was about 504 Pa, and the maximum wind speed was about 23.34 m / s. The order of these conditions is shown in FIG. 5 (B) to FIG. 7 (B), in the characteristic diagram showing the pressure distribution in the stage from the maximum value a to the minimum value j. It can be understood from the characteristic diagram of FIG. 7 (B), which is the widest, the characteristic diagram of FIG. 6 (B), and the smallest in the characteristic diagram of FIG. 5 (B).

  From this analysis result, in relation to the inner shape of the ventilation path portion 21 according to the present invention, in order to reduce the airflow resistance, the step size L is preferably 0 <L <20 mm. The width is optimally set to L1 (10 mm) in FIG.

  Next, when the air moves from the scroll part 20 into the ventilation path part 21, the ventilation path part 21 has a structure that rapidly expands with respect to the scroll part 20 as shown in FIG. In order to eliminate the problem of the turbulent flow of the air that has flowed into 21 other than the main flow, the increase ratio of the passage area of the ventilation passage portion 21 is not so much larger than the passage area of the winding end portion of the scroll portion 20. In addition, reducing the passage area of the ventilation passage 21 is also adopted in the present invention.

  Focusing only on reducing the passage area of the ventilation path portion 21 in this regard, for example, as shown in FIG. 8A, a portion 21A that extends from the scroll portion 20 in the same direction is 20 is composed of a cube-shaped portion extending as it is from the winding end portion with the opening width, and a hem-spreading portion extending from the end of the cubic-shaped portion toward the cooling heat exchanger. The portion 21B along the windward ventilation surface cuts the ventilation path portion 21 to the maximum so that the flared portion extends to the lower side of the cooling heat exchanger 5 as it is. In this case, the width of the portion 21A extending in the same direction as it is from the scroll portion 20 and the portion 21B along the ventilation surface on the windward side of the cooling heat exchanger 5 is relatively narrow, The flow is throttled, the maximum ventilation resistance (total pressure) is about 503 Pa, and the maximum wind speed is about 25.75 m / s, which are substantially the same values as in the case where the ventilation path portion 21 in FIG. 4 is not cut. The fact that the performance does not change can be understood from the fact that the range of the maximum numerical value a in the characteristic diagram of the ventilation resistance in FIG. 10B is not so different from the characteristic diagram in FIG.

  On the other hand, in FIG. 9 (A), about the part 21A extended in the same direction as it is from the scroll part of the ventilation path part 21, the both-sides part is cut diagonally in the shape of a straight line. The structure which also cuts the thickness along the vehicle advancing direction of the site | part 21B along the ventilation surface of the windward side of the exchanger 5 is shown. In the structure of the ventilation path portion 21, a part of the air that has flowed into the ventilation path portion 21 from the scroll portion 20 flows along the inner surface of the air guide surface 23 due to the Coanda effect. However, the maximum ventilation resistance (total pressure) is about 462 Pa, the maximum wind speed is about 21.14 m / s, and the air passage portion 21 in FIG. 5 (A) is not cut. Both figures are excellent compared to the case. This is also indicated by the fact that the range of the maximum value “a” disappears in the characteristic diagram of the ventilation resistance in FIG. 9B.

  10A, both sides of the part 21A extending in the same direction as the scroll part 20 of the ventilation path part 21 are cut into an arc (for example, R80) obliquely, and the cooling is performed accordingly. The structure which also cuts the thickness along the vehicle advancing direction of the site | part 21B along the ventilation surface of the windward side of the heat exchanger 5 for a vehicle is shown. According to the configuration of the ventilation path portion 21, the Coanda effect is further exhibited, so that a part of the air flowing into the ventilation path portion 21 from the scroll portion 20 is further cooled along the inner surface of the air guide surface 23. Because the air flows in a wide area in the vehicle width direction with respect to the upper side ventilation surface of the heat exchanger 5, the maximum ventilation resistance (total pressure) is about 446 Pa, the maximum wind speed is about 23.82 m / s, and the maximum ventilation resistance (Total pressure) is further reduced. This is also shown by the fact that not only the maximum value “a” but also the range of “b” having the next highest value disappear in the characteristic diagram of the ventilation resistance in FIG.

  From this analysis result, as shown in FIG. 8 (A), in order to achieve uniform ventilation resistance and uniform wind speed in relation to the inner shape of the air passage section 21 according to the present invention. It is preferable to cut the ventilation path portion 21 so that the air guide surface 23 becomes an inclined surface, in particular, an arc-shaped inclined surface (for example, R80), not the maximum cut of the ventilation path portion 21.

  Then, as shown in FIGS. 3A and 3B, a space is created by cutting the ventilation path portion 21 so that the air guide surfaces 23 and 23 become inclined surfaces. As described above, the unit case 8 is provided with a side foot blowing opening, a duct 30 connected to the side foot blowing opening is disposed, and the duct 30 is connected to the ventilation space 4 from the space on both sides in the axial direction. The space generated by cutting the road portion 21 can be passed substantially linearly and routed forward or backward in the vehicle traveling direction.

  Further, as shown in FIG. 12, a steering member stay 32 is provided from both sides of the air conditioning unit 1 to a steering member 31 extending close to the air conditioning unit 1 along the width direction of the vehicle. Can be extended along the airspace generated by cutting the ventilation path 21 while avoiding the air intake of the blower 4.

  However, the air space generated by cutting the ventilation path portion 21 is not limited to the installation location of the duct 30 and the steering member stay 32, and can be used in various ways such as the installation location for the side vent duct. It is.

  Moreover, the shape of the ventilation path part 21 may not be left-right symmetric when viewed from the vehicle traveling direction depending on the temperature distribution of the cooling heat exchanger 5 and the performance of the air conditioning unit 1.

FIG. 1 is an external view of a unit main body of a vehicle air conditioning unit according to the present invention. FIG. 2 is a cross-sectional view of the unit main body of the above vehicle air conditioning unit. FIG. 3A is a cross-sectional view of the unit main body of the vehicle air conditioning unit showing the position of the air passage of the vehicle air conditioning unit same as above, and FIG. 3B shows the flow of air in the air passage. It is explanatory drawing shown. FIG. 4 (A) is a schematic diagram showing the structure of the ventilation path when there are two sides of the side facing the heat exchanger for cooling, but there are no steps on the side, and FIG. It is a characteristic line figure which shows the ventilation resistance in the ventilation path part of the structure of FIG. 4 (A). FIG. 5 (A) is a schematic diagram showing the configuration of the ventilation path when the side facing the cooling heat exchanger has two surfaces and the level difference between the surfaces is L1, FIG. 5 (B) FIG. 6 is a characteristic diagram showing ventilation resistance in the ventilation path portion having the configuration of FIG. FIG. 6 (A) is a schematic diagram showing the configuration of the ventilation path when the side facing the heat exchanger for cooling is two surfaces and the step between the surfaces is L2, FIG. 6 (B) FIG. 7 is a characteristic diagram showing ventilation resistance in the ventilation path portion having the configuration of FIG. FIG. 7 (A) is a schematic diagram showing the configuration of the ventilation path when the side face facing the heat exchanger for cooling is two faces and the level difference between the faces is L3. FIG. FIG. 8 is a characteristic diagram showing ventilation resistance in the ventilation path portion having the configuration of FIG. FIG. 8A is a schematic diagram showing the structure of the ventilation path portion cut to the maximum so that only the region where the mainstream flows is almost, and FIG. 8B is the ventilation of the structure of FIG. It is a characteristic line figure which shows the ventilation resistance in a road part. FIG. 9 (A) is a schematic view showing the structure of the ventilation path section that is cut obliquely so that the side surface extending from the side facing the cooling heat exchanger toward the cooling heat exchanger becomes a flat slope. FIG. 9B is a characteristic diagram showing the ventilation resistance in the ventilation path portion having the configuration shown in FIG. FIG. 10 (A) is a schematic diagram showing the structure of the ventilation path section that is obliquely cut so that the side surface extending from the side facing the cooling heat exchanger toward the cooling heat exchanger becomes an arcuate slope, FIG. 10B is a characteristic diagram showing the ventilation resistance in the ventilation path portion having the configuration of FIG. FIG. 11 is a reference diagram showing an example in which an area generated by the adoption of the unit case of the vehicle air conditioning unit is used for installing a duct. FIG. 12 is a reference diagram showing an example in which the region generated by the adoption of the unit case of the vehicle air conditioning unit is used for installing the steering member. FIG. 13 (A) is an explanatory diagram showing the configuration described in Patent Document 1 in a configuration that is substantially in common with the vehicle air conditioning unit according to the present application, and FIG. 13 (B) is the vehicle air conditioning of FIG. 13 (A). It is explanatory drawing which showed the flow of the air in the ventilation path in a unit.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Vehicle air-conditioning unit 2 Unit main body 4 Blower 4A Fan 4B Motor 5 Cooling heat exchanger 8 Unit case 20 Scroll part 21 Ventilation path part 22 Upwind side surface 22A Split surface 22B Split surface 22C Connecting surface 23 Wind guide surface 30 Duct 31 Steering member 32 Steering member stay

Claims (7)

A blower configured with a fan and a motor and a cooling heat exchanger are housed in a unit case so that the blower is positioned relatively above the cooling heat exchanger, and
As an air flow path for sending air from the blower to the windward side of the cooling heat exchanger, the airflow side of the cooling heat exchanger from the boundary portion with the winding end of the scroll part on the leeward side of the scroll part It has a ventilation path that extends to the lower end of the upstream surface,
The ventilation path section is located on the windward side of the cooling heat exchanger, facing the ventilation surface of the cooling heat exchanger, and connected to the windward side surface for the cooling heat exchange. And a wind guide surface for guiding air to the vessel side,
The air guide surface is formed so that an enlargement ratio of a passage area in a portion near the windward side of the ventilation path with respect to a passage area of a winding end portion of the scroll portion is relatively small. Air conditioning unit for vehicles. The width of the windward side surface of the ventilation path is substantially the same as the width of the scroll portion and the boundary portion thereof, and is configured so that there is no sudden expansion or contraction over the entire ventilation path from the boundary portion. The vehicle air conditioning unit according to claim 1, wherein The windward side surface of the ventilation path has a portion extending in a substantially tangential direction of winding of the scroll portion at a boundary portion with a winding end portion of the scroll portion. The air conditioning unit for vehicles described in 1. The said ventilation path part has a wind direction change means for changing the wind direction of the air which flows in the said ventilation path part in the middle to the upper part side of the said heat exchanger for cooling. The air conditioning unit for vehicles described in 1. The wind direction changing means is configured such that the upwind side surface of the ventilation path portion is constituted by two divided surfaces arranged along the air flow, and the two divided surfaces are connected by a connecting surface, so that the middle of the ventilation path portion is formed. The vehicle air conditioning unit according to claim 4, wherein the vehicle air conditioning unit is formed by providing a step on the surface. The air passage surface connected to the windward side surface of the ventilation path portion is temporarily extended outward along the vehicle width direction as it approaches the cooling heat exchanger. The vehicle air conditioning unit according to 3, 4, or 5. The vehicle air conditioning unit according to claim 1, 2, 3, 4, 5, or 6, wherein the blower is disposed relatively close to the cooling heat exchanger.

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