JP2007076602A - Air guide sheet for heat exchanger and construction machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To ensure a space in which auxiliaries can be installed in an engine room and to reduce that a ventilation amount of each heat exchanger in such a state that they are installed in the engine room is deviated from a target value of a ventilation amount led out based on an air amount of a fan. <P>SOLUTION: The air guide sheets 48, 49 are provided over a predetermined range from the heat exchangers 41, 42, 43 to an upstream side in a flowing direction of cooling air at a border of the adjacent heat exchangers 41, 42, 43. The cooling air in the engine room 18 is branchingly flowed to the adjacent heat exchangers 41, 42, 43 by the air guide sheets 48, 49. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a wind guide plate and a construction machine applied to a heat exchanger installed in an engine room of a construction machine.

  Conventionally, as disclosed in, for example, Patent Documents 1 to 3 below, a heat exchanger such as a radiator installed in an engine room of a construction machine is provided with a duct. Patent Document 1 below discloses that the inside of a duct is divided into a plurality of air guide passages, and the opening area of the entrance is increased as the air guide passage communicates with the lower side of the radiator. This is because the lower side of the radiator is more distant from the air intake than the upper side, and the distribution of the passing wind speed of the radiator becomes non-uniform. The resistance is made uniform.

  Further, in Patent Document 2 below, focusing on the fact that the flow resistance varies depending on the length of the flow path from the air intake to the radiator, the flow path length can be reduced by providing air intakes above and below the engine cover. It is disclosed to make the thickness as uniform as possible to reduce the deviation of the flow velocity distribution of the incoming air.

Further, in Patent Document 3 below, attention is paid to the fact that the sound guide plate becomes thicker when both sides of the wind guide plate that divides the inside of the duct are covered, and between the outlet end of the wind guide plate and the heat exchanger. It is disclosed that a sufficient gap is provided to eliminate the uneven flow of the cooling air and suppress fluctuations in the flow velocity of the cooling air.
JP-A-9-195711 Japanese Unexamined Patent Publication No. 2000-16094 JP 9-123771 A

  However, those disclosed in Patent Documents 1 and 2 make the flow resistance in the air duct from the air intake port to the heat exchanger uniform, and consider the ventilation resistance of the heat exchanger itself. Not. Moreover, in patent document 3, only the inside of a duct is divided | segmented, and the ventilation resistance of heat exchanger itself is also not considered. For this reason, it is difficult to apply these disclosed techniques as they are to a plurality of heat exchangers arranged in parallel in the engine room. That is, each heat exchanger includes, for example, a radiator for radiating cooling water used for cooling the engine, an oil cooler for cooling the hydraulic oil, an intercooler for cooling the intake air of the engine, a condenser for an air conditioner in the cab, etc. Since the specifications are completely different and the ventilation resistance is often different, just equalizing the flow resistance in the air duct to the heat exchanger will not equalize the ventilation volume in each heat exchanger. Have difficulty.

  Moreover, even if the air flow rate of each heat exchanger obtained from the air flow of the fan is set as a target value based on the air flow resistance in each heat exchanger, when setting each heat exchanger, Due to the influence of the installation position, fan shroud, etc., the designed air flow rate may not be obtained in each heat exchanger. Therefore, even if the target value of airflow is set in consideration of the airflow resistance of each heat exchanger, it is difficult to match the airflow rate of each heat exchanger to the target value when it is actually installed in the engine room. It is.

  Further, in the above-mentioned patent document, a duct that guides cooling air from the air intake port to the heat exchanger is provided so as to occupy most of the interior of the engine room. Therefore, an air cleaner is provided in the space upstream of the heat exchanger. In addition, it is difficult to install auxiliary equipment such as an electrical box, and there is also a problem that the maintenance workability is hindered.

  Therefore, the present invention has been made in view of such points, and the object of the present invention is to secure a space in which an auxiliary device can be installed in the engine room and a state in which the auxiliary device is installed in the engine room. It is to reduce the amount of ventilation of each heat exchanger from the target value of the amount of ventilation derived based on the air volume of the fan.

  In order to achieve the above object, the present invention is based on the premise of a wind guide plate applied to a plurality of heat exchangers arranged in parallel in the air flow direction in an engine room of a construction machine. The cooler is configured so that cooling air introduced into the engine room from the air intake port is driven by driving a fan disposed on the downstream side of the heat exchanger, and at the boundary between the adjacent heat exchangers Is provided over a predetermined range to the upstream side in the flow direction of the cooling air, and the cooling air flowing toward one of the heat exchangers is prevented from flowing into the other heat exchanger.

  Since the air guide plate for a heat exchanger of the present invention is provided in a predetermined range from the heat exchanger to the upstream side so that a space remains between the air intake and the heat exchanger, according to the present invention, Not only can the space on the upstream side of the heat exchanger be used for installing auxiliary equipment and the like, but also the maintenance workability can be prevented from being hindered. And, by providing the air guide plate of the present invention immediately upstream of the heat exchanger, the flow direction is changed immediately before the cooling air flows into the heat exchanger, and the heat exchanger to be introduced from the space It can suppress flowing into the adjacent heat exchanger. That is, even if a plurality of heat exchangers having the same ventilation resistance are installed, due to the arrangement relationship of fans, heat exchangers, air intakes, etc., a difference occurs in the suction force of each heat exchanger, There will be a difference in the amount of cooling air sucked into each heat exchanger. For this reason, when a heat exchanger with a strong suction force by a fan is arranged next to a certain heat exchanger, if the air guide plate is not provided, the cooling flow that flows toward the heat exchanger with a weak suction force Before the air is introduced into the heat exchanger, the flow direction is changed and flows into the adjacent heat exchanger with a strong suction force. It may not be obtained. Therefore, by providing a baffle plate at the boundary between the heat exchangers, it is possible to prevent the cooling air from being introduced excessively into the heat exchanger having a strong suction force, and the influence of the fan suction force, the arrangement relationship, etc. Can be reduced. As a result, not only the influence of the ventilation resistance of the heat exchanger itself and the flow path resistance on the upstream side of the heat exchanger, but also the influence of the positional relationship between the fan and each heat exchanger can be reduced. The amount can be close to the design value obtained from the fan airflow. Moreover, since the heat exchanger air guide plate according to the present invention is arranged at the boundary between the heat exchangers in a predetermined range on the upstream side of the heat exchanger, a duct is provided between the air intake port and the heat exchanger. It can suppress that the frictional resistance in a flow path increases like the structure connected, and it can prevent that the air volume introduce | transduced into a heat exchanger falls by it.

  In addition, it is possible to improve the heat exchange efficiency simply by measuring the actual ventilation rate of each heat exchanger installed in the construction machine and adding a baffle plate of a size according to the measurement result. By applying the air guide plate according to the present invention to the heat exchanger that has been made, the current organic heat exchange efficiency can be improved at low cost.

  Here, if the air guide plate of the present invention is provided in a range of half or less of the interval between the heat exchanger and the air intake port disposed to face the heat exchanger, each heat exchange It is possible to secure a space that can be effectively used on the upstream side of the heat exchanger while the amount of air flowing into the heat exchanger approaches the target value.

  Moreover, it is preferable that the air guide plate of the present invention is provided with a guide plate that changes the flow direction of the cooling air toward the heat exchanger in the vertical direction. If it does so, the bias | inclination of the vertical direction distribution of the cooling air introduced into a heat exchanger can be suppressed.

  Moreover, it is preferable that the air guide plate of the present invention is subjected to a treatment for reducing the shearing force of the cooling air on the surface. If it does so, the ventilation resistance of a baffle plate can be reduced.

  Moreover, it is preferable that the surface of the air guide plate of the present invention is subjected to a sound absorption treatment. If it does so, it can suppress that a baffle plate produces | generates a sound, and it can utilize also for the sound absorption of the noise by a fan, an engine, etc.

  Further, the present invention is based on the premise of a construction machine that introduces cooling air from an air intake to the heat exchanger by driving a fan disposed downstream of the heat exchanger in the engine room. Are provided in parallel in the air flow direction in the engine room, and the air guide plate is provided at the boundary between the adjacent heat exchangers.

  In this construction machine, when three or more heat exchangers are arranged in parallel, the air guide plate for the heat exchanger is provided at at least one place on each boundary between the heat exchangers. Is preferred. If it does so, also in the construction machine in which three or more heat exchangers are installed, the amount of air flowing into each heat exchanger can be brought close to the target value.

  As described above, according to the present invention, it is possible to secure a space in which auxiliary equipment can be installed in the engine room, and the air flow rate of each heat exchanger in the state installed in the engine room Deviation from the target value of the ventilation amount derived based on the ventilation resistance of the heat exchanger can be reduced.

  Hereinafter, the best mode for carrying out the present invention will be described in detail with reference to the drawings.

(Embodiment 1)
FIG. 1 schematically shows a main part of a construction machine 10 to which a heat exchanger wind guide plate according to the present invention is applied. As shown in FIG. 1, this construction machine 10 is configured as a hydraulic excavator, for example, and a lower traveling body 11 is provided with a pair of left and right crawlers 12 and 12. An upper swing body 14 is turnably provided on the lower traveling body 11, and the upper swing body 14 is provided with a cab 16, an engine room 18, and the like. FIG. 1 mainly shows the rear part of the upper swing body 14 as viewed from above.

  The cab 16 is disposed on the left side of the upper swing body 14, and the attachment 20 is attached to the right side of the cab 16 so as to be raised and lowered. The engine room 18 is provided on the rear side of the mounting portion of the cab 16 and the attachment 20.

  A rear side portion of the engine room 18 is constituted by a counterweight 22, and a front side portion, a left side portion and a right side portion of the engine room 18 are constituted by engine guards 24, 25 and 26. An air intake 28 is provided in the engine guard 25 on the left side. A counterweight 22 formed in a convex curved shape is connected from the rear end of the air intake port 28 to the rear.

  An engine 30 is disposed slightly to the right in the engine room 18. The engine 30 is installed on the turning frame 34 such that the drive shaft 32 extends in the width direction of the upper turning body 14. The drive shaft 32 of the engine 30 protrudes from the engine body 30a on both sides in the width direction. A pump 36 is coupled to the tip of the drive shaft 32 that protrudes to the right from the engine body 30a, and a fan 38 is coupled to the tip of the drive shaft 32 that protrudes to the left from the engine body 30a.

  A plurality of heat exchangers 41, 42, and 43 are disposed on the left side of the fan 38. The heat exchangers 41, 42, and 43 are installed in the right side from the left engine guard 25, and various auxiliary devices are arranged in a space between them, though not shown. In the present embodiment, three heat exchangers 41, 42, and 43 are provided. These heat exchangers 41, 42, and 43 are, for example, a radiator, an oil cooler, and an intercooler, and each is constituted by a plate fin type heat exchanger.

  As shown also in FIG. 2, the heat exchangers 41, 42, 43 are installed sideways so that the width direction is the front-rear direction of the upper swing body 14, and these are arranged in the front-rear direction of the upper swing body 14. They are arranged in a line. That is, the heat exchangers 41, 42, 43 are installed in parallel with the direction in which the cooling air introduced from the air intake 28 flows. The first heat exchanger 41 disposed on the front side of the revolving structure is disposed just on the side of the air intake 28, and the second heat exchanger 42 disposed in the center extends from the air intake 28 to the rear thereof. The third heat exchanger 43 disposed on the side of the revolving structure and disposed on the rear side of the revolving structure is disposed behind the air intake port 28.

  The fan 38 is arranged at a position slightly away from the heat exchangers 41, 42, 43 in the right direction in the figure. A fan shroud 45 having a shape extending from the heat exchangers 41, 42, 43 to the right in the drawing is attached to the heat exchangers 41, 42, 43. A circular opening 45a is formed in the fan shroud 45, and the fan 38 is disposed in the opening 45a. A space between the heat exchangers 41, 42, 43 and the fan 38 is covered with a fan shroud 45.

  The fan 38 is disposed so that the drive shaft 32 is positioned at the approximate center in the width direction of the second heat exchanger 42, and has a size extending from the first heat exchanger 41 to the third heat exchanger 43. Is used. The third heat exchanger 43 is selected to be narrower than the other heat exchangers 41 and 42, and the fan 38 is more than half of the air flow surface for the third heat exchanger 43. Has advanced to. On the other hand, the first heat exchanger 41 is arranged such that the fan 38 reaches only a part of the air flow surface. Due to this arrangement relationship, the suction force of each heat exchanger 41, 42, 43 by driving the fan 38 is different.

  In each heat exchanger 41, 42, 43, cooling air flows from the left side of the figure by driving the fan 38 and flows in the thickness direction of the heat exchangers 41, 42, 43, for example, cooling the coolant of the engine 30, etc. To do. The cooling air that has passed through the heat exchangers 41, 42, and 43 passes through the space covered with the fan shroud 45 and is discharged to the right from the opening 45a.

  At the boundary between adjacent heat exchangers 41, 42, 43, there are provided heat exchanger air guide plates (hereinafter simply referred to as air guide plates) 48, 49 according to the present invention. The air guide plates 48 and 49 are formed in a rectangular flat plate shape having substantially the same length as the heat exchangers 41, 42, and 43, and upstream of the heat exchangers 41, 42, and 43 into which cooling air flows. It is each arrange | positioned with the attitude | position extended in the up-down direction at each boundary of the side. The attachment structure of the air guide plates 48 and 49 may be any, but for example, the heat exchangers 41, 42, and 43 can be fixed to a frame (not shown) that fixes the revolving frame 34.

  The direction of each of the air guide plates 48 and 49 is appropriately set according to the direction of the flow of the cooling air introduced from the air intake port 28. That is, the direction of each air guide plate 48, 49 according to the positional relationship of the air intake 28, the heat exchangers 41, 42, 43 and the fan 38, the shape of the space in the engine room 18, the arrangement relationship of the auxiliary devices, etc. Is decided.

  Each of the air guide plates 48 and 49 is formed to have a width so as to be within half of the distance D between the air intake port 28 and the heat exchangers 41, 42, and 43. Thereby, the space which can be effectively used can be secured on the upstream side of the heat exchangers 41, 42 and 43 while the amount of air flowing into each of the heat exchangers 41, 42 and 43 is brought close to the target value. Each of the air guide plates 48 and 49 is formed to have a width of 10% or more of the thickness C of the heat exchangers 41, 42, and 43 in the direction in which the cooling air flows. As a result, the airflow guiding effect of the airflow guide plates 48 and 49 is ensured. The air guide plates 48 and 49 may have different widths or the same width. For example, in the present embodiment, the air guide plate 48 provided at the boundary between the first heat exchanger 41 and the second heat exchanger 42 is provided at the boundary between the second heat exchanger 42 and the third heat exchanger 43. The width is wider than the air guide plate 49. That is, the air guide plates 48 and 49 may be appropriately set in width according to the flow rate and direction of the cooling air from the air intake port 28 toward the heat exchangers 41, 42, and 43. The width of each of the air guide plates 48 and 49 may be constant in the vertical direction or may be different in the vertical direction. For example, the air guide plates 48 and 49 may be configured in a shape in which the upper side is wide and the lower side is narrow.

  Each of the air guide plates 48 and 49 may be subjected to a process for reducing the shearing force of the cooling air on the surface. For example, a large number of grooves on the order of several microns to several hundred microns are provided on the surfaces of the air guide plates 48 and 49. Thereby, the ventilation resistance of the baffle plates 48 and 49 can be reduced.

  Further, the surface of each of the air guide plates 48 and 49 may be subjected to a sound absorption process. For example, a sound absorbing material such as a porous material is attached, urethane coating, or the like. Thereby, it is possible to suppress the generation of sound due to vibrations of the air guide plates 48 and 49, and it is also possible to utilize the noise absorption by the fan 38, the engine 30, and the like.

  In the engine room 18, when the fan 38 is driven, cooling air is introduced from the air intake 28. The cooling air flows in the engine room 18 toward the heat exchangers 41, 42, 43 by the suction action by driving the fan 38, and flows into the heat exchangers 41, 42, 43. At this time, the cooling air flowing into the heat exchangers 41, 42, 43 is diverted by the air guide plates 48, 49. That is, even if there is a difference in the suction force of each of the heat exchangers 41, 42, 43 due to the arrangement relationship of the fan 38, the heat exchangers 41, 42, 43, the air intake 28, etc., for example, the first heat exchange The cooling air to be sucked into the vessel 41 is suppressed from being introduced into the second heat exchanger 42 having a large suction force. The cooling air that has flowed into the heat exchangers 41, 42, 43 flows in the thickness direction in the heat exchangers 41, 42, 43 and cools, for example, the coolant of the engine 30. The cooling air that has passed through the heat exchangers 41, 42, and 43 passes through the space covered with the fan shroud 45 and is discharged to the right from the opening 45 a of the fan shroud 45.

  As described above, according to the present embodiment, not only can the space on the upstream side of the heat exchangers 41, 42, and 43 be used for installing auxiliary equipment and the like, but also the maintenance workability is prevented from being hindered. You can also. And by providing the baffle plates 48, 49 immediately upstream of the heat exchangers 41, 42, 43, the flow direction is changed immediately before the cooling air flows into the heat exchangers 41, 42, 43, and It can suppress flowing in into the heat exchanger 41, 42, 43 adjacent to the heat exchanger 41, 42, 43 which should be introduce | transduced from space. That is, even if a plurality of heat exchangers 41, 42, and 43 having the same ventilation resistance are installed, due to the arrangement relationship of the fan 38, the heat exchangers 41, 42, and 43, the air intake port 28, and the like, A difference arises in the suction force of each heat exchanger 41,42,43, and a difference will arise in the amount of cooling air suck | inhaled by each heat exchanger 41,42,43. For this reason, when the heat exchangers 41, 42, and 43 having a strong suction force by the fan 38 are arranged next to a certain heat exchanger 41, 42, and 43, if the air guide plates 48 and 49 are not provided. The cooling air flowing toward the heat exchangers 41, 42, 43 having a weak suction force changes the direction of the flow just before being introduced into the heat exchangers 41, 42, 43, and the adjacent suction force is strong. The heat exchangers 41, 42, 43 may flow into the heat exchangers 41, 42, 43, and the heat exchangers 41, 42, 43 with a weak suction force may not be able to obtain an air flow rate as designed. Therefore, by providing the air guide plates 48 and 49 at the boundary between the heat exchangers 41, 42, and 43, the cooling air is introduced into the heat exchangers 41, 42, and 43 having a strong suction force. Thus, the influence of the suction force, the arrangement relationship, etc. of the fan 38 can be reduced. As a result, not only the airflow resistance of the heat exchangers 41, 42, 43 themselves and the flow resistance on the upstream side of the heat exchangers 41, 42, 43, but also the fan 38 and the heat exchangers 41, 42, 43, Thus, the air flow rate of each of the heat exchangers 41, 42, 43 can be made close to the design value obtained from the air flow rate of the fan 38. Moreover, since the air guide plates 48 and 49 according to the present embodiment are arranged at the boundary between the heat exchangers 41, 42, and 43 in a predetermined range on the upstream side of the heat exchangers 41, 42, and 43, It is possible to suppress an increase in frictional resistance in the flow path as in the configuration in which the inlet 28 and the heat exchangers 41, 42, 43 are connected by a duct, and thereby the air volume introduced into the heat exchangers 41, 42, 43. Can be prevented from decreasing.

  Further, the actual air flow rate of each of the heat exchangers 41, 42, 43 installed in the construction machine 10 is measured, and the heat exchange efficiency is obtained simply by adding the air guide plates 48, 49 having a size corresponding to the measurement result. Therefore, the heat exchange efficiency of the heat exchangers 41, 42, and 43 installed in the current organic can be improved at low cost.

  In the present embodiment, the air guide plates 48 and 49 are provided at the boundaries between the heat exchangers 41, 42, and 43. It is also possible to adopt a configuration to do so. In short, it is only necessary to appropriately determine at which boundary the air guide plates 48 and 49 should be installed according to the way the cooling air flows.

  Here, an example of the result of measuring the air flow rate of each heat exchanger 41, 42, 43 will be described. This measurement is performed when a propeller-type anemometer with an outer diameter of 60 mm is installed for each heat exchanger, and the ventilation amount when the air guide plates 48 and 49 are not provided and the air guide plates 48 and 49 are provided. This was done by measuring the air flow. In the measurement, time is taken until a steady state is reached, and thereafter, the instantaneous rotational speed is measured 60 times per second, the average value is derived, and the average value is multiplied by the cross-sectional area of the air flow through the heat exchanger. Was calculated.

  FIG. 3 shows the result of comparing the design value (target value) and the measurement result for each of the first heat exchanger 41, the second heat exchanger 42, and the third heat exchanger 43. In this figure, the design value (target value) is 1, and the measured passing air volume is shown as a dimensionless value. As can be seen from this figure, when the air guide plates 48 and 49 are not provided, the passing air amounts of the heat exchangers 41, 42, and 43 are all deviated from the design values. As can be seen from the fact that the passing air volume of the second heat exchanger 42 is larger than the design value, and conversely, the passing air volumes of the first heat exchanger 41 and the third heat exchanger 43 are smaller than the design value. The deviation of the passing air amount from the design value is due to the cooling air that should be sucked into the first heat exchanger 41 or the third heat exchanger 43 due to the positional relationship between the fan 38 and the heat exchangers 41, 42, 43. This is considered to be due to the fact that the air was sucked into the second heat exchanger 42. And by providing the baffle plates 48 and 49, it is possible to prevent the cooling air from being concentratedly introduced into the second heat exchanger 42, and in each of the heat exchangers 41, 42 and 43, respectively. It can be seen that a passing air volume close to the design value can be obtained.

(Embodiment 2)
FIG. 4 shows Embodiment 2 of the present invention. In the second embodiment, guide plates 56 are provided on the air guide plates 48 and 49. Here, the same components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the second embodiment, an air intake (upper intake) 54 is also provided in the upper engine guard 52 that forms the ceiling of the engine room 18. Therefore, the cooling air is introduced into the engine room 18 from the air intake port 28 toward the right in FIG. 4 by driving the fan 38, and the cooling air is directed obliquely downward to the right from the upper intake port 54. It is introduced into the room 18.

  The guide plate 56 is constituted by a flat plate member that extends laterally from the air guide plates 48 and 49. The guide plate 56 is fixed to the air guide plates 48 and 49 by welding or the like. Two guide plates 56 are provided on the upper and lower sides, and each guide plate 56 is disposed downward with the downstream side positioned below. However, the position and orientation of the guide plate 56 are appropriately set depending on the arrangement relationship of the air intake port 28, the upper intake port 54, and the fan 38.

  The guide plate 56 is slightly narrower than the air guide plates 48 and 49. A slight gap is formed between the guide plate 56 and the heat exchanger 42. Even if such a gap is formed, the direction of the flow of the cooling air is not affected, and when the air guide plates 48 and 49 are installed, the guide plate 56 is provided with the heat exchangers 41, 42, It is possible to prevent 43 fins (not shown) from being damaged.

  In the second embodiment, since the guide plates 56 are provided on the air guide plates 48 and 49, the flow direction of the cooling air can be changed in the vertical direction. As a result, it is possible to suppress the uneven distribution in the vertical direction of the cooling air introduced into the heat exchangers 41, 42, and 43.

  Other configurations, operations, and effects are the same as those in the first embodiment although the description thereof is omitted.

It is a top view which shows roughly the principal part of the construction machine which concerns on Embodiment 1 of this invention. It is a top view which expands and shows schematically the engine room of the construction machine of FIG. It is a characteristic view which shows the difference in the presence or absence of a baffle plate about the passing air volume of each heat exchanger. It is a side view which shows roughly the engine room of the construction machine which concerns on Embodiment 2 of this invention.

Explanation of symbols

18 Engine room 28 Air intake 38 Fan 41 First heat exchanger 42 Second heat exchanger 43 Third heat exchanger 48 Air guide plate 49 Air guide plate 54 Upper intake (air intake)
56 Information board

Claims (7)

A wind guide plate applied to a plurality of heat exchangers arranged in parallel in the air flow direction in an engine room of a construction machine,
Each of the heat exchangers is configured such that cooling air introduced into the engine room from the air intake port is driven by driving a fan disposed on the downstream side thereof,
The cooling air that is provided over a predetermined range from the heat exchanger to the upstream side in the flow direction of the cooling air at the boundary between the adjacent heat exchangers, and the cooling air that flows toward one of the heat exchangers is the heat of the other An air guide plate for a heat exchanger, wherein the air guide plate suppresses inflow into the exchanger.   2. The air guide plate for a heat exchanger according to claim 1, wherein the air guide plate is provided in a range equal to or less than half of an interval between the heat exchanger and an air intake port disposed to face the heat exchanger.   The air guide plate for a heat exchanger according to claim 1 or 2, further comprising a guide plate that changes a flow direction of the cooling air toward the heat exchanger in a vertical direction.   The air guide plate for a heat exchanger according to any one of claims 1 to 3, wherein the surface is subjected to a treatment for reducing a shearing force of the cooling air.   The heat exchanger wind guide plate according to any one of claims 1 to 4, wherein the surface is subjected to a sound absorption treatment. A construction machine that introduces cooling air from an air intake into the heat exchanger by driving a fan disposed downstream of the heat exchanger in the engine room,
A plurality of the heat exchangers are provided in the engine room so as to be parallel to the air flow direction,
A construction machine, wherein the heat exchanger air guide plate according to any one of claims 1 to 5 is provided at a boundary between the adjacent heat exchangers. Three or more heat exchangers are juxtaposed,
The construction machine according to claim 6, wherein the air guide plate for the heat exchanger is provided at at least one place on each boundary between the heat exchangers.

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