JP2008069756A - Cooling system for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To restrain cooling capability from deteriorating by curbing the influence of a shielding body and of the thermal influence exerted from a front heat exchanger to a rear heat exchanger when the shielding body exists in the front of the heat exchanger and besides a plurality of the heat exchangers is horizontally mounted in contact with one another. <P>SOLUTION: A fin pitch in a shielding region (a section 3b) where a bumper lean force 6 exists in the front of a traveling direction of an intercoller 3 is made larger than that in an open region (sections 3a, 3c) where no bumper lean force 6 exists. Besides, a fin pitch of a radiator 4 in the rear of the shielding region is made smaller than that of the radiator 4 in the rear of the open region. Due to an increase in passing airflow in the rear of the shielding region of the radiator 4, the cooling capability of the radiator 4 can be augmented. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a cooling device for a vehicle having a plurality of types of heat exchangers.

  There has been proposed a structure in which a plurality of types of heat exchangers such as a radiator, an intercooler, and an oil cooler mounted on a vehicle are arranged so as to overlap each other in the traveling direction. Patent Document 1 discloses a cooling device in which an intercooler is disposed in front of a radiator, and the fin pitch of the radiator in the overlapping portion of both is larger than the fin pitch of the other portion. Patent Document 1 also discloses an apparatus for reducing the thickness of the radiator in the overlapping portion. In these apparatuses, there is an advantage that a reduction in cooling performance can be suppressed by increasing the amount of passing air by reducing the ventilation resistance of the overlapping portion.

  By the way, in recent vehicles, the arrangement of structures in the engine room has been increased in density, and there may be a shield against the circulation of outside air in the vicinity of the heat exchanger. In order to suppress a decrease in cooling performance due to a decrease in the air volume in such a case, an apparatus has been proposed in which the fin pitch of the part with a small air volume is made larger than that of the other part (Patent Document 2). In this device, the amount of air passing through the portion with the large fin pitch is increased, and the deterioration of the cooling performance can be suppressed.

Japanese Utility Model Publication No. 2-21550 Japanese Utility Model Publication No. 58-42323

  However, in the configuration of Patent Document 1, when a shielding object is present in front of a plurality of stacked heat exchangers, the cooling performance of the portion overlapping the shielding object is lowered. Moreover, in the structure of patent document 2, when the 2nd heat exchanger is arrange | positioned at the back of a heat exchanger, the cooling performance of the back side heat exchanger falls by the thermal influence from a front side heat exchanger. There is a risk.

  Therefore, an object of the present invention is to provide an effect of the shielding and the rear side of the heat exchanger on the front side when the shielding object exists in front of the heat exchanger and a plurality of heat exchangers are stacked on the front and back. It is in suppressing the thermal influence to a heat exchanger, and suppressing the fall of cooling performance.

  A cooling device for a vehicle according to the present invention is a cooling device for a vehicle which is arranged so that the second heat exchanger overlaps at least partially behind the first heat exchanger in the running direction. The ventilation resistance of the first heat exchanger in the shielding region where the shielding object exists in the traveling direction forward of the first heat exchanger is shielded in the traveling direction forward of the first heat exchanger. The ventilation resistance of the first heat exchanger in the open area where there is no object is smaller than the ventilation resistance of the second heat exchanger in the rear of the shielding area. It is characterized by being larger than the ventilation resistance of the second heat exchanger.

  In the present invention, the ventilation resistance of the first heat exchanger in the shielding area is set to be smaller than the ventilation resistance in the open area where there is no shielding object. The cooling performance of the exchanger can be promoted. In addition, the temperature behind the open area where the ventilation resistance is high in the first heat exchanger is relatively high because the air volume is relatively small, but the second heat exchanger is the first heat exchanger. The ventilation resistance of the second heat exchanger at the rear of the shielding area is larger than the ventilation resistance of the second heat exchanger at the rear of the open area. Therefore, the cooling performance of the second heat exchanger can be promoted by increasing the passing air volume.

  The ventilation resistance in each region of the first heat exchanger and / or the second heat exchanger can be controlled by changing the fin pitch and / or changing the fin ventilation path length. The larger the fin pitch and the smaller the ventilation path length of the fin, the smaller the ventilation resistance.

  Preferably, the first heat exchanger in the present invention is an intercooler for cooling the exhaust gas, and the second heat exchanger is a radiator for cooling the engine coolant.

  Embodiments of the present invention will be described below with reference to the drawings. 1 and 2, the vehicle 1 according to the first embodiment of the present invention includes an intercooler 3 for cooling exhaust gas from the engine 2 and a radiator 4 for cooling engine coolant. In front of the intercooler 3, a bumper lean force 6, which is a part of the vehicle body 5 and is a reinforcing body for a bumper (not shown), is arranged with the width direction of the vehicle body as a longitudinal direction. The bumper lean force 6 is located in front of the traveling direction of the intercooler 3 and the radiator 4 (in the direction of arrow A in FIG. 1) and shields a part of the front of both.

  In FIG. 2, the intercooler 3 and the radiator 4 are arranged between a plurality of water tubes 12 that are in fluid communication with each other between the hollow heads 11 arranged on both sides, and between the water tubes 12. The corrugated fins 13 are fixed. The fins 13 are fixed to the water tubes 12 adjacent to each other at the top and bottom at the top and the bottom at the bottom by brazing. An inlet pipe is connected to the upper part of one head 11 and an outlet pipe is connected to the lower part of the other head 11, and high-temperature fluid is introduced in the direction of arrow B in FIG. 2 and discharged in the direction of C. The high temperature fluid introduced into the intercooler is exhaust gas from an exhaust passage (not shown), and the high temperature fluid introduced into the radiator 4 is engine coolant from the engine 2.

  As shown in FIG. 1, the intercooler 3 and the radiator 4 are divided into a shielded area where the bumper lean force 6 exists in front of the traveling direction and an open area where the shield is not substantially present. The intercooler 3 has sections 3a, 3b, and 3c. The sections 3a and 3c are open areas, and the section 3b is a shielding area. As shown in FIG. 2, the fin pitch of the section 3b that is the shielding area of the intercooler, that is, the interval between a certain peak of the fin 13 and the peak adjacent to the fin 13 is set to P2. The fin pitch of the sections 3a and 3c, which are open areas, is set to P1. The fin pitch P2 in the shielding area is larger than the fin pitch P1 in the open area. Further, the interval between the water tubes 12 in the section 3b that is the shielding area is set larger than that in the sections 3a and 3c that are the open areas. As described above, the ventilation resistance in the shielding area of the intercooler 3 is set to be smaller than the ventilation resistance in the open area.

  The radiator 4 has sections 4a, 4b, and 4c, and the fin pitch P3 of the section 4b that is behind the shielding area is smaller than the fin pitch P4 of the sections 4a and 4c that is behind the open area. The fin pitches P3 and P4 of the radiator 4 may be equal to or different from the fin pitches P1 and P2 of the intercooler 3, respectively. The interval between the water tubes 12 of the radiator 4 is also smaller in the section 3b than in the sections 3a and 3c. As described above, the ventilation resistance behind the shielding area of the radiator 4 is made larger than the ventilation resistance behind the open area.

  In the present embodiment configured as described above, traveling wind is introduced into the engine room from left to right in FIG. 1 as the vehicle 1 travels in the direction of arrow A in FIG. Here, in the present embodiment, outside air is supplied to the intercooler 3 in the direction of the arrow a that is substantially parallel to and opposite to the traveling direction in an open region where there is no shield in front of the traveling direction. Moreover, in the shielding area where the bumper lean force 6 that is a shielding object is present in the front, outside air that has circulated from the front opening toward the section 3b is introduced in the direction of the arrow b. In addition, the air that has passed through the sections 3a and 3c of the intercooler 3 basically goes straight in the direction opposite to and parallel to the traveling direction toward the radiator sections 4a and 4c (arrow c), but has passed through the section 3b. The air is supplied in the direction of the arrow d toward the radiator sections 4a and 4c due to the difference in fluid resistance from the section 4b.

  As described above, in the present embodiment, the ventilation resistance of the intercooler 3 in the shielding region where the bumper lean force 6 that is the shielding object exists in front of the traveling direction of the intercooler 3 that is the first heat exchanger is the bumper lean. Since the ventilation resistance in the open area where the force 6 does not exist is smaller, the cooling performance of the intercooler 3 can be promoted by increasing the amount of passing air in the shielding area.

  Further, in the space 7 between the intercooler 3 and the radiator 4, the sections 7a and 7c that are behind the open area where the fin pitch P2 is small in the intercooler 3 are more than the section 7b that is behind the shielding area. Since the air volume is relatively small, the temperature is relatively high. However, in this embodiment, the ventilation resistance of the radiator 4 behind the shielding area is smaller than the ventilation resistance of the radiator 4 behind the opening area. The cooling performance of the radiator 4 can be promoted by increasing the passing air volume at the rear of the region.

  Next, a second embodiment of the present invention will be described. In FIG. 3, in the cooling device in the vehicle 101 according to the second embodiment, the depths, that is, the substantial thicknesses of the fins 113a, 113b, 113c of the intercooler 103 are different from each other, and the ventilation path of the fin 113b in the shielding region The length is smaller than the ventilation path length of the fins 113a and 113c of the intercooler 103 in the open region. As described above, the ventilation resistance in the shielding area of the intercooler 103 is set to be smaller than the ventilation resistance in the open area.

  The ventilation path length of the fins 114b of the radiator 104 at the rear of the shielding area is set to be longer than the ventilation path lengths of the fins 114a and 114c of the radiator 104 at the rear of the open area. As described above, the ventilation resistance in the shielding area of the radiator 104 is set larger than the ventilation resistance in the open area.

  In the present embodiment configured as described above, traveling wind is introduced into the engine room from left to right in FIG. 3 as the vehicle 101 travels in the direction of arrow A in FIG. Here, in the present embodiment, outside air is supplied to the intercooler 103 in the direction of the arrow a that is substantially parallel to and opposite to the traveling direction in an open region where there is no shielding object ahead in the traveling direction. Moreover, in the shielding area where the bumper lean force 6 that is a shielding object is present in the front, outside air that has circulated from the front opening toward the section 3b is introduced in the direction of the arrow b. In addition, the air that has passed through the sections 103a and 103c of the intercooler 103 basically goes straight to the radiator sections 104a and 104c in a direction substantially parallel to and opposite to the traveling direction (arrow c), but has passed through the section 103b. The air is supplied in the direction of the arrow d toward the radiator sections 104a and 104c due to the difference in fluid resistance from the section 104b.

  As described above, in the present embodiment, the ventilation resistance of the intercooler 103 in the shielding area where the bumper lean force 6 that is the shielding object exists in front of the traveling direction of the intercooler 103 that is the first heat exchanger is the bumper lean. Since the ventilation resistance in the open area where the force 6 does not exist is smaller, the cooling performance of the intercooler 103 can be promoted by increasing the amount of passing air in the shielding area.

  Further, in the space 7 between the intercooler 103 and the radiator 104, the sections 7a and 7c that are behind the open area where the fin pitch P2 is small in the intercooler 103 are more than the sections 7b that are behind the shielding area. Since the air volume is relatively small, the temperature is relatively high. However, in this embodiment, the ventilation resistance of the radiator 104 at the rear of the shielding area is smaller than the ventilation resistance of the radiator 104 at the rear of the opening area. The cooling performance of the radiator 104 can be promoted by increasing the passing air volume at the rear of the region.

  In the above embodiments, the present invention has been described with a certain degree of concreteness, but various modifications and changes can be made to the present invention without departing from the spirit and scope of the invention described in the claims. It must be understood that it is possible. That is, the present invention includes modifications and changes included in the scope and spirit of the claims and their equivalents. For example, in each of the above embodiments, the first heat exchanger in the present invention is an intercooler for cooling exhaust gas, and the second heat exchanger is a radiator for cooling engine coolant. The combination of the first and second heat exchangers in the present invention may include other types, or may be the same type.

  In each of the above embodiments, the front projection areas of the first and second heat exchangers are equal, and both are arranged so as to overlap with each other in the traveling direction. May be different from each other, and the first and second heat exchangers may be arranged so as to overlap each other.

  In the first embodiment, the airflow resistance in each region is controlled by the fin pitch of the first and second heat exchangers, and in the second embodiment, the airflow path lengths of the first and second heat exchangers are used. Although the ventilation resistance of the area was controlled, the means for controlling the ventilation resistance in each heat exchanger can be selected arbitrarily and independently of each other, including by changing the interval of the water tubes. Further, the ventilation resistance may be controlled by changing both the fin pitch and the ventilation path length in a single heat exchanger, and such application also belongs to the category of the present invention.

It is a side view showing a schematic structure of a cooling device for vehicles concerning a 1st embodiment of the present invention. It is a disassembled perspective view which shows an intercooler and a radiator. It is a side view which shows schematic structure of the cooling device for vehicles which concerns on 2nd Embodiment of this invention.

Explanation of symbols

1,101 Vehicle 2 Engine 3,103 Intercooler 4,104 Radiator 6 Bumper Reinforce 11 Head 12 Water tube 13, 103a, 103b, 103c, 104a, 104b, 104c Fin

Claims (6)

A cooling device for a vehicle arranged such that the second heat exchanger overlaps at least partially with a predetermined interval behind the first heat exchanger in the running direction,
The ventilation resistance of the first heat exchanger in the shielding region where the shielding object is present in the traveling direction of the first heat exchanger is not present, and the shielding object is not present in the traveling direction of the first heat exchanger. The ventilation resistance of the first heat exchanger in the open area is smaller than
Ventilation resistance of the second heat exchanger in the rear of the shielding area is made larger than the ventilation resistance of the second heat exchanger in the rear of the open area. apparatus. The vehicle cooling device according to claim 1,
The cooling device for a vehicle according to claim 1, wherein a fin pitch of the first heat exchanger in the shielding region is larger than a fin pitch of the first heat exchanger in the open region. A cooling device for a vehicle according to claim 1 or 2,
The cooling for a vehicle, wherein a fin pitch of the second heat exchanger behind the shielding area is smaller than a fin pitch of the second heat exchanger behind the open area. apparatus. A cooling device for a vehicle according to any one of claims 1 to 3,
Ventilation path length of the fins of the first heat exchanger in the shielding area is made shorter than a ventilation path length of the fins of the first heat exchanger in the open area. Cooling system. A cooling device for a vehicle according to any one of claims 1 to 4,
The ventilation path length of the fins of the second heat exchanger in the rear of the shielding area is larger than the ventilation path length of the fins of the second heat exchanger in the rear of the open area. A vehicle cooling device. A cooling device for a vehicle according to any one of claims 1 to 5,
The vehicular cooling device, wherein the first heat exchanger is an intercooler for cooling the exhaust gas, and the second heat exchanger is a radiator for cooling the engine coolant.

Images