JP5364437B2 - Vehicle heat exchange module - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchange module for a vehicle reducing a fan noise caused by uneven flow rate distribution of air flow sucked by a fan via a fan shroud in a circumferential direction of an annular opening. <P>SOLUTION: In the heat exchange module for the vehicle including a rectangular heat exchanger, the fan shroud 4 enclosing the heat exchanger, having the annular opening 5 downstream of the heat exchanger and an axial fan arranged in the annular opening 5 of the fan shroud 4, a plurality of guide ribs 7 extending from a circumferential edge of the annular opening 5 to an outer circumference of the fan shroud 4, facilitating even flow rate distribution of the air flow in the circumferential direction sucked by the axial fan from a plurality of sucking areas 8 separated by the guide ribs, are arranged in an inner surface side of the fan shroud 4 facing the heat exchanger. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a heat exchanger module for a vehicle in which a radiator for an engine mounted on a vehicle and / or a condenser for an air conditioner and a fan are integrated.

  In the vehicle heat exchange module, a fan shroud is provided on the downstream side so as to surround the condenser and the radiator disposed in the front and rear in order to distribute air to the condenser for the air conditioner and the radiator for the engine, and the fan shroud. A configuration is adopted in which an axial fan such as a propeller fan is installed in an annular opening provided in the. Thereby, air is circulated through the condenser and the radiator, and heat exchange is performed with the refrigerant in the condenser and with the engine cooling water in the radiator.

  In such a vehicle heat exchange module, the fan shroud surrounds the entire circumference of a rectangular heat exchanger such as a condenser and a radiator, and the opening is only an annular opening provided with an axial fan. ing. For this reason, air is circulated only through the axial fan, and is circulated by the rotation of the fan during idling and by the ram pressure and the rotation of the fan during vehicle travel. However, since the fan shroud has a rectangular cross section, the axial fan is provided in the annular opening, so that the air flow sucked into the axial fan has a nonuniform flow velocity in the circumferential direction of the annular opening. It becomes a contracted flow with distribution and is sucked into the axial fan. This causes time fluctuations in the pressure distribution on the blade surface of the axial fan and causes fan noise.

  In Patent Document 1, the inner surface of the fan shroud facing the radiator is formed on the inner surface of the air guide portion, which becomes wider with the eccentricity of the annular opening. This shows a fan that reduces the rotational noise (primary component) of the fan by providing a rectifying plate that protrudes to the side and suppressing the air flow that flows into the annular opening along the wide air guide section. Has been. Further, in Patent Document 2, fan depressing members extending from the outer diameter side of the fan to the rotating shaft side with a predetermined distance from the fan on the inner surface side of the fan shroud are radially formed around the rotating shaft. A plurality of sheets are arranged so as to prevent the fan from interfering with the heat exchanger and to improve the air flow by its rectifying effect.

JP 2006-46113 A JP 2008-38776 A

  However, according to the above-mentioned patent documents 1 and 2, the circumferential flow velocity distribution of the air flow sucked into the axial fan provided in the annular opening from the suction area having a rectangular cross section on the inner surface of the fan shroud is annular. It does not correct the unevenness at the entrance of the opening. Therefore, these technologies cannot reduce the fan noise caused by the time variation of the pressure distribution on the blade surface of the axial flow fan that is sucked into the axial flow fan with a non-uniform flow velocity distribution. Such reduction of fan noise has been one of the problems in the heat exchange module for vehicles.

  The present invention has been made in view of such circumstances, and is caused by the fact that the flow velocity distribution in the circumferential direction of the annular opening of the air flow sucked into the fan via the fan shroud is uneven. An object of the present invention is to provide a vehicle heat exchange module that can reduce noise.

In order to solve the above-described problems, the vehicle heat exchange module of the present invention employs the following means.
That is, the vehicle heat exchange module according to the present invention includes a rectangular heat exchanger, a fan shroud that surrounds the heat exchanger and has an annular opening provided downstream thereof, and the annular shape of the fan shroud. In a vehicle heat exchange module including an axial fan provided in an opening, on the inner surface side of the fan shroud facing the heat exchanger, from the periphery of the annular opening to the outer periphery of the fan shroud and extends, whereby a plurality of guide ribs are provided to equalize the flow velocity distribution in the circumferential direction of the air flow sucked from a plurality of suction areas in the axial fan partitioned, said guide ribs, and the axial flow fan center The fancy from the intersection point where a line segment connecting a plurality of points on the outer periphery of the fan shroud having a rectangular shape forms a peripheral edge of the annular opening. The guide rib is provided so as to extend to the outer periphery of the loudspeaker, and the guide rib is configured to increase a flow rate from the suction area where the flow rate of the air flow is reduced among a plurality of suction areas partitioned thereby. The installation angle of the guide rib is changed .

According to the present invention, the inner surface of the fan shroud that surrounds the heat exchanger and has an annular opening provided on the downstream side thereof faces the heat exchanger and extends from the periphery of the annular opening to the outer periphery of the fan shroud. Since a plurality of guide ribs are provided to equalize the flow velocity distribution in the circumferential direction of the airflow sucked into the axial fan from the plurality of suction areas partitioned thereby, the fan shroud passes through the rectangular heat exchanger Since the air flow circulated in the suction area having a rectangular cross section on the inner surface side is sucked into the axial fan provided in the annular opening, it is a contracted flow with a non-uniform flow velocity distribution in the circumferential direction. However, a plurality of guides provided so that the circumferential flow velocity distribution of the air flow sucked into the axial fan extends from the peripheral edge of the annular opening to the outer periphery of the fan shroud. Homogenized by blanking, it is possible to sucked into the axial fan. Therefore, it is possible to reduce the fluctuation of the pressure distribution on the blade surface of the axial fan and reduce the fan noise. In particular, the guide rib extends from the intersection where the line connecting the center of the axial fan and a plurality of points on the outer periphery of the rectangular fan shroud to the periphery of the annular opening extends to the outer periphery of the fan shroud. The installation angle of some guide ribs has been changed so as to increase the flow rate from the suction area where the flow rate of air flow is reduced among the multiple suction areas partitioned by the guide ribs. The suction area with a rectangular cross section on the inner surface side is divided into multiple suction areas by multiple guide ribs, and the size of the suction area in which the flow rate of air flow decreases is increased by changing the installation angle of the guide ribs. Increase the flow velocity distribution at the entrance of the annular opening of the airflow sucked into the axial fan through each suction area. It can be homogenized in. Accordingly, it is possible to improve fan noise caused by suction into the axial fan in a state where the air flow velocity distribution is not uniform.

  Furthermore, the vehicle heat exchange module according to the present invention is characterized in that, in any of the vehicle heat exchange modules described above, the guide rib is formed integrally with the fan shroud.

  According to the present invention, since the guide rib is integrally formed with the fan shroud, the guide rib can be simultaneously formed on the inner surface side of the fan shroud when the fan shroud is injection-molded with a resin material or the like. Therefore, guide ribs can be provided without increasing the number of processing steps or using additional parts, and the flow velocity distribution of the air flow sucked into the axial fan can be made uniform without extra cost and man-hours. Noise can be reduced.

  Furthermore, the vehicle heat exchange module according to the present invention is characterized in that, in any one of the vehicle heat exchange modules described above, the guide rib also serves as a reinforcing rib for the fan shroud.

  According to the present invention, since the guide rib is also configured to serve as a reinforcing rib for the fan shroud, the reinforcing rib provided for securing rigidity on the outer surface side of the fan shroud is omitted by sharing the guide rib. It becomes possible to do. Thereby, the reinforcing rib protruding outward from the outer surface side of the fan shroud can be eliminated, and the installation of the heat exchange module in the narrow engine room can be facilitated.

  Furthermore, in the vehicle heat exchange module according to the present invention, in any one of the vehicle heat exchange modules described above, the guide rib faces the rotational direction of the axial fan with respect to the air flow sucked into the axial fan. It is characterized by being curved so as to give a swirling flow in the direction of the movement.

  According to the present invention, since the guide rib is curved so that a swirl flow in a direction opposite to the rotational direction of the axial fan is given to the air flow sucked into the axial fan, the axial flow is caused by the guide rib. While making the flow velocity distribution of the air flow sucked into the fan uniform, a swirl flow in a direction opposite to the rotational direction of the axial fan can be given to the air flow by the curved portion. As a result, the suction efficiency of the axial fan can be increased, and as a result, the fan rotation speed can be reduced and the fan noise can be further reduced with the same air volume comparison.

  Furthermore, in the vehicle heat exchange module according to the present invention, in any one of the vehicle heat exchange modules described above, the annular opening and the axial fan are provided eccentrically from a central portion of the heat exchanger, and the guide rib is provided on the guide rib. Is characterized in that a through hole is provided for correcting the flow rate imbalance of the air flow caused by the eccentric opening and the axial fan being provided eccentrically.

  According to the present invention, the annular opening and the axial flow fan are provided eccentrically from the central portion of the heat exchanger, and the flow unbalance of the air flow caused by the eccentric opening and the axial flow fan provided on the guide rib is corrected. As a result, it is difficult to place the axial fan in the center of the heat exchanger due to over-concentration in the engine room, and the annular opening of the fan shroud and the axial fan are located in the center of the heat exchanger. Even if it is provided eccentrically from the part, if the air flow between specific guide ribs increases and the static pressure in the suction area rises, the distance between the adjacent guide ribs through the through holes provided in the guide ribs Part of it will be distributed to the suction area. As a result, the influence of flow rate imbalance caused by the eccentricity of the axial fan can be reduced, and it can be effectively applied to a heat exchange module having a specification in which the axial fan is eccentric with respect to the heat exchanger. Will be able to.

  Furthermore, in the vehicle heat exchange module according to the present invention, in any one of the vehicle heat exchange modules described above, the annular opening and the axial fan are provided eccentrically from a central portion of the heat exchanger, and the guide rib is The annular opening and the axial fan are provided eccentric so as to protrude toward the suction area where the flow rate of the air flow increases.

  According to the present invention, the annular opening and the axial flow fan are provided eccentrically from the central portion of the heat exchanger, and the guide rib is provided with the annular opening and the axial flow fan eccentrically provided to increase the air flow rate. Due to overhanging on the area side, it becomes difficult to place the axial fan in the center of the heat exchanger due to overcrowding in the engine room, and the fan shroud annular opening and the axial fan exchange heat Even if it is provided eccentric from the center of the vessel, the air flow rate in the suction area can be reduced by projecting the guide rib toward the suction area side where the flow rate of the air flow increases (the area increases) However, by increasing the air flow rate in the suction area adjacent to it, the flow rate balance of the air flow flowing into the plurality of suction areas between the guide ribs can be adjusted. Can. As a result, the influence of flow rate imbalance caused by the eccentricity of the axial fan can be reduced, and it can be effectively applied to a heat exchange module having a specification in which the axial fan is eccentric with respect to the heat exchanger. Will be able to.

  Furthermore, in the vehicle heat exchange module according to the present invention, in any one of the vehicle heat exchange modules described above, the heat exchanger is a radiator for an engine mounted on the vehicle and / or a capacitor for an air conditioner. It is characterized by.

  According to the present invention, since the heat exchanger is a radiator for an engine and / or a condenser for an air conditioner mounted on the vehicle, the heat for the vehicle in which the heat exchanger is a radiator for the engine. In any of a vehicle heat exchange module (CRFM) in which a condenser and a radiator are arranged at the front and rear as a vehicle heat exchange module or a heat exchanger in which the exchange module or the heat exchanger is a condenser for an air conditioner, The circumferential flow velocity distribution of the air flow sucked into the axial fan is made uniform by a plurality of guide ribs provided so as to extend from the peripheral edge of the annular opening to the outer periphery of the fan shroud, and sucked into the axial fan. Can do. Therefore, fluctuations in pressure distribution on the blade surface of the axial fan can be reduced, and fan noise can be reduced.

  According to the present invention, the circumferential flow velocity distribution of the air flow sucked into the axial fan is made uniform by the plurality of guide ribs provided so as to extend from the peripheral edge of the annular opening to the outer periphery of the fan shroud. Since it can be sucked into the flow fan, the fluctuation of the pressure distribution on the blade surface of the axial fan can be reduced and the fan noise can be reduced.

It is a longitudinal section of the heat exchange module for vehicles concerning a 1st embodiment of the present invention. It is an aa cross-section equivalent figure of the heat exchange module for vehicles shown in FIG. FIG. 2 is a graph (A) showing the uniformization of the passing wind speed in the vehicle heat exchange module shown in FIG. 1 and a display diagram (B) showing the passing wind speed and the angular position. It is an aa cross-section equivalent figure in Drawing 1 of a heat exchange module for vehicles concerning a 2nd embodiment of the present invention. It is an aa section equivalent figure in Drawing 1 of a heat exchange module for vehicles concerning a 3rd embodiment of the present invention. It is an aa section equivalent figure in Drawing 1 of a heat exchange module for vehicles concerning a 4th embodiment of the present invention.

Embodiments according to the present invention will be described below with reference to the drawings.
[First Embodiment]
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. 1 to 3.
FIG. 1 shows a longitudinal sectional view of a vehicle heat exchange module 1 according to the first embodiment of the present invention. The vehicle heat exchange module 1 here is a vehicle heat exchange module 1 called CRFM, in which a condenser 2 for an air conditioner and a radiator 3 for an engine are arranged in front and back.

  The condenser (heat exchanger) 2 constitutes the refrigeration cycle of the vehicle air conditioner, and is used for heat exchange between the refrigerant and air to condense the refrigerant, and a horizontally long rectangular heat exchanger is used. The radiator (heat exchanger) 3 is provided in the cooling water path of the vehicle travel engine, and cools the engine cooling water by exchanging heat between the engine cooling water and the air. A shaped heat exchanger is used. The capacitor 2 and the radiator 3 are arranged at the front and rear with the capacitor 2 arranged upstream in the air flow direction.

  A fan shroud 4 that guides the airflow to the axial fan 6 is provided downstream of the condenser 2 and the radiator 3 so as to surround the entire circumference of the condenser 2 and the radiator 3. The fan shroud 4 is made of resin and is integrally formed by injection molding or the like. As shown in FIG. 2, the cross section of the fan shroud 4 is a horizontally long rectangular shape similar to the capacitor 2 and the radiator 3, and a ring is formed at the center thereof. An opening 5 in the form of a bell mouth is provided. An axial flow fan 6 such as a propeller fan is installed in the annular opening 5 via a support stay (not shown). As the axial fan 6, a hub in which a thin electric motor is integrally provided in the hub is used.

  On the inner surface side of the fan shroud 4 facing the radiator 3, as shown in FIG. 2, a plurality of guide ribs 7 are provided by integral molding. The guide rib 7 is extended from the intersection C where the line segment connecting the center Φ of the axial fan 6 and a plurality of representative points O on the outer periphery of the fan shroud 4 to the periphery of the annular opening 5 to the outer periphery of the fan shroud 4. Is provided. The plurality of representative points O on the outer periphery of the fan shroud 4 are, for example, vertical and horizontal lines passing through four vertices of the fan shroud 4 and the center Φ of the axial fan 6 when the representative point O is eight. And four points of intersection with each side of the fan shroud 4.

  When the guide rib 7 is provided so as to extend from the intersection C where the line segment forms the peripheral edge of the annular opening 5 to the outer periphery of the fan shroud 4, the guide rib 7 flows axially from the plurality of suction areas 8 partitioned by the plurality of guide ribs 7. It is provided so that the flow velocity distribution in the circumferential direction of the air flow sucked into the fan 6, that is, the annular opening 5, is made uniform. That is, the guide ribs 7 are not all provided radially as shown by broken lines toward the representative point O, but flow rate from the suction area 8A located on both sides of the long side where the flow rate of air flow is relatively small. The installation angle of some of the guide ribs 7 is adjusted so as to increase the flow rate so that the circumferential flow velocity distribution of the air flow at the entrance of the annular opening 5 is made uniform.

  Since the flow rate of the airflow flowing through the suction area 8 is determined by the configuration of the condenser 2 and the radiator 3 provided on the upstream side, the flow rate is calculated for each condenser 2 and radiator 3 used, and the inlet portion of the annular opening 5 is obtained. What is necessary is just to design the installation angle etc. of the several guide rib 7 so that the flow velocity distribution in this may become uniform. Further, the guide rib 7 may be configured to serve as a reinforcing rib for the fan shroud 4 by making the guide rib 7 thicker in order to ensure the rigidity of the fan shroud 4.

With the configuration described above, according to the present embodiment, the following operational effects can be obtained.
By rotating the axial fan 6, air is circulated through the condenser 2 and the radiator 3, and the refrigerant in the condenser 2 and the engine coolant in the radiator 3 are cooled by heat exchange with the air. The air that has passed through the condenser 2 and the radiator 3 is guided to the inner surface side of the fan shroud 4 and is guided to the axial fan 6 provided in the annular opening 5 through the fan shroud 4. This air flow is sucked into the axial fan 6 and then discharged to the downstream side by its rotation.

At this time, if there is variation in the flow velocity distribution in the circumferential direction of the air flow sucked into the axial fan 6, the fan noise of the primary component is deteriorated, but in the present embodiment, an annular shape is formed on the inner surface side of the fan shroud 4. A plurality of guide ribs 7 extending from the peripheral edge of the opening 5 to the outer periphery of the fan shroud 4 are provided, and by changing the installation angle of the guide ribs 7 , the annular airflow sucked into the axial fan 6 from the plurality of suction areas 8 The flow velocity distribution in the circumferential direction at the entrance of the opening 5 is made uniform.

That is, the air flow that has passed through the condenser 2 and the radiator 3 and is circulated into the suction area in which the cross section on the inner surface side of the fan shroud 4 has a rectangular shape is sucked into the axial flow fan 6 provided in the annular opening 5. Therefore, the flow contracts with a non-uniform flow velocity distribution in the circumferential direction. As described above, the line segment connecting the center Φ of the axial fan 6 and the plurality of representative points O on the outer periphery of the fan shroud 4 is circular. Guide ribs 7 extending from the intersection C forming the periphery of the opening 5 to the outer periphery of the fan shroud 4 are provided , and the flow rate from the suction area 8A located on both sides of the long side where the flow rate of the air flow is relatively small increases. as to change the installation angle of the part of the guide ribs 7, since the adjustment to increase the flow rate of the area, the circumferential direction of the flow of the air stream which is sucked into the axial fan 6 via the guide rib 7 It distributed equalized, it is possible to sucked into the axial fan 6.

  Therefore, the fluctuation of the pressure distribution on the blade surface of the axial fan 6 can be reduced, and the primary component fan noise can be reduced. FIG. 3 shows a comparison diagram of flow velocity distributions with and without the guide rib 7. The broken line in the figure indicates the flow velocity distribution when the guide rib 7 is not present, and the solid line indicates the flow velocity distribution when the guide rib 7 is present. As shown in FIG. 3 (B), the passing wind speed on the vertical axis in FIG. 3 (A) is the wind speed near the entrance of the annular opening 5, and the angle θ on the horizontal axis is from the axial fan center Φ. An angle from an upwardly extending vertical line (a 180 ° range is shown for symmetry) is shown. Also from FIG. 3, it can be understood that the flow velocity distribution in the circumferential direction of the air flow sucked into the axial fan 6 is made uniform, and the above effect can be expected.

  In addition, according to the present embodiment, the guide rib 7 is formed integrally with the resin fan shroud 4 by injection molding or the like, so without increasing the number of processing steps or using additional parts, Guide ribs 7 can be installed. Accordingly, the flow velocity distribution of the air flow sucked into the axial fan 6 can be made uniform without extra costs and man-hours, and the fan noise can be reduced. Furthermore, by using the guide rib 7 also as a reinforcing rib for the fan shroud 4, it is possible to eliminate the reinforcing rib provided for securing rigidity on the outer surface side of the fan shroud 4. For this reason, the reinforcement rib which protrudes outward from the outer surface side of the fan shroud 4 can be eliminated, and the installation of the heat exchange module 1 in a narrow engine room can be facilitated.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG.
This embodiment differs from the first embodiment described above in that the guide rib 7A is curved. Since other points are the same as those in the first embodiment, description thereof will be omitted.
In the present embodiment, as shown in FIG. 4, the guide rib 7 </ b> A is curved and a swirling flow in a direction opposite to the rotational direction N of the axial fan 6 is generated with respect to the air flow sucked into the axial fan 6. The configuration is given.

  When the guide rib 7A is installed, the rib angle of the guide rib 7A on the annular opening 5 is set such that the angle formed by the tangent of the circle at the intersection C on the annular opening 5 and the guide rib 7A is constant. Needless to say, the guide rib 7 </ b> A is bent so that the air flow direction is opposite to the rotational direction N of the axial fan 6. Further, the curve of the guide rib 7A may be a monotonous curve or a broken line. Further, the curved guide rib 7A has the same flow rate ratio as that of the first embodiment in which the guide ribs 7 are provided in a straight line in the flow ratio of the air flow passing through the plurality of suction areas 8 between the guide ribs 7A. Of course, it is set as follows.

  In this way, the guide rib 7A is curved so that a swirl flow in a direction opposite to the rotational direction N of the axial fan 6 is given to the air flow sucked into the axial fan 6. The curved portion can impart a swirl flow in a counter direction opposite to the rotational direction N of the axial fan 6 to the air stream while equalizing the flow velocity distribution of the air flow sucked into the axial fan 6 by the guide rib 7A. The suction efficiency of the axial fan 6 can be increased. As a result, with the same air volume comparison, it is possible to reduce the fan rotation speed and further reduce fan noise.

[Third Embodiment]
Next, a third embodiment of the present invention will be described with reference to FIG.
This embodiment is different from the first embodiment described above in that the guide rib 7B is provided with an appropriate number of through holes 9. Since other points are the same as those in the first embodiment, description thereof will be omitted.
In the present embodiment, the annular opening 5 provided in the fan shroud 4 and the axial fan 6 installed in the annular opening 5 are provided at positions eccentric from the center portions of the condenser 2 and the radiator 3. Such a configuration is employed when the engine room is overcrowded and it is difficult to place the axial fan 6 at the center of the condenser 2 or the radiator 3.

  As described above, since the axial fan 6 is provided eccentrically, the flow rate balance of the airflow flowing through the plurality of suction areas 8 between the guide ribs 7B is lost, but in order to reduce the influence, in the present embodiment, As shown in FIG. 5, the guide rib 7B is provided with an appropriate number of through holes 9 through which airflow can pass along the extending direction of the guide rib 7B.

  As described above, by providing an appropriate number of through holes 9 in the guide rib 7B, when the air flow rate between the specific guide ribs 7B increases and the static pressure in the suction area 8 increases, the through holes provided in the guide rib 7B. A part of the suction area 8 is distributed between the adjacent guide ribs 7 </ b> B through the holes 9. For this reason, it is possible to reduce the influence of flow rate imbalance due to the eccentricity of the axial fan 6. Therefore, the present invention can be effectively applied to the heat exchange module 1 having a specification in which the axial fan 6 is eccentric with respect to the condenser 2 and the radiator 3.

[Fourth Embodiment]
Next, a fourth embodiment of the present invention will be described with reference to FIG.
This embodiment is related to the heat exchange module 1 having a specification in which the axial flow fan 6 is eccentric as in the third embodiment described above, but the configuration of the guide rib 7C is different. Since other points are the same as those in the first and third embodiments, description thereof will be omitted.
In the present embodiment, a part of the plurality of guide ribs 7C is provided such that the annular opening 5 of the fan shroud 4 and the axial flow fan 6 are provided eccentrically from the central portions of the condenser 2 and the radiator 3, thereby increasing the flow rate of the air flow ( It is provided so as to project to the suction area 8B side.

  That is, when the annular opening 5 and the axial fan 6 are decentered from the center of the condenser 2 and the radiator 3, the areas of the plurality of suction areas 8 partitioned by the guide rib 7C may be significantly unbalanced. In this case, since the flow rate balance of the air flow is lost, as shown in FIG. 6, for example, the flow rate of the air flow increases in the vertical guide rib 7C passing through the center Φ of the axial fan 6 (the area increases). The structure is provided so as to project to the suction area 8B side.

  As described above, the axial flow fan 6 is provided eccentric so that the flow rate of the air flow is increased (the area is increased), and the guide rib 7C is provided on the suction area 8B side so that the air flow rate in the suction area 8B is increased. The flow rate balance of the airflow flowing into the plurality of suction areas 8 between the guide ribs 7C can be adjusted by reducing the flow rate of the adjacent suction areas 8 and increasing the air flow rate of the adjacent suction areas 8. Accordingly, even with such a configuration, the influence of the flow rate imbalance caused by the eccentricity of the axial fan 6 can be reduced, and the heat of the specification in which the axial fan 6 is eccentric with respect to the condenser 2 and the radiator 3 can be reduced. It can be effectively applied to the exchange module 1 as well.

  In addition, this invention is not limited to the invention concerning the said embodiment, In the range which does not deviate from the summary, it can change suitably. For example, in the above-described embodiment, a so-called CRFM in which a condenser 2 for an air conditioner and a radiator 3 for an engine are provided as front and rear as a heat exchanger has been described, but either the condenser 2 or the radiator 3 is provided. Needless to say, the present invention can be similarly applied to a vehicle heat exchange module. Of course, the axial fan 6 is not limited to the propeller fan.

1 Vehicle heat exchange module 2 Capacitor (heat exchanger)
3 Radiator (heat exchanger)
4 Fan shroud 5 Annular opening 6 Axial fans 7, 7A, 7B, 7C Guide ribs 8, 8A, 8B Suction area 9 Through hole Φ Axial fan center O Representative point C Intersection N Direction of rotation of axial fan

Claims (7)

A rectangular heat exchanger, a fan shroud that surrounds the heat exchanger and has an annular opening provided downstream thereof, and an axial fan provided in the annular opening of the fan shroud. In the vehicle heat exchange module
Air flow sucked into the axial fan from a plurality of suction areas partitioned from a peripheral edge of the annular opening to an outer periphery of the fan shroud on an inner surface facing the heat exchanger of the fan shroud. A plurality of guide ribs that equalize the flow velocity distribution in the circumferential direction are provided ,
The guide rib extends from an intersection where a line segment connecting a center of the axial fan and a plurality of points on the outer periphery of the fan shroud having a rectangular shape forms a peripheral edge of the annular opening to the outer periphery of the fan shroud. Provided to be
The guide rib is characterized in that the installation angle of some of the guide ribs is changed so as to increase the flow rate from the suction area where the flow rate of the air flow is reduced among the plurality of suction areas partitioned thereby. The vehicle heat exchange module. The vehicle heat exchange module according to claim 1 , wherein the guide rib is formed integrally with the fan shroud. The guide ribs, the heat exchange module for a vehicle according to claim 1 or 2, characterized in that there is a configuration in which also serves as a reinforcing rib of the fan shroud. The said guide rib is curved so that the swirl | flow may be given to the direction opposite to the rotation direction of the said axial flow fan with respect to the air flow sucked in the said axial flow fan. 3 heat exchange module for a vehicle according to any one of. The annular opening and the axial fan are provided eccentrically from the center of the heat exchanger, and the flow rate unbalance of air flow caused by the annular opening and the axial fan being provided eccentrically on the guide rib is provided. The vehicle heat exchange module according to any one of claims 1 to 4 , wherein a through hole for correction is provided. The annular opening and the axial flow fan are provided eccentrically from the center of the heat exchanger, and the guide rib is provided with the annular opening and the axial flow fan eccentrically to increase the air flow rate. heat exchange module for a vehicle according to any one of claims 1 to 4, characterized in that provided by overhang the suction area side. The vehicle heat exchange module according to any one of claims 1 to 6 , wherein the heat exchanger is a radiator for an engine and / or a condenser for an air conditioner mounted on the vehicle.

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