Cooling device for construction machinery

Abstract

A cooling device includes a housing having a peripheral wall, a plurality of heat exchangers arranged side by side in the housing, and a plurality of fans opposed to the plurality of heat exchangers. The housing has a plurality of air guide plates arranged in the direction of arrangement of the plurality of heat exchangers and extending from the side of the group of heat exchangers toward the side of the group of cooling fans in the space surrounded by the peripheral wall. One side end of the air guide plate is positioned on the boundary between two adjacent heat exchangers or on either heat exchanger. A fifth fan is arranged at a position opposed to one of the plurality of air guide plates, and the other fans are arranged at positions between the peripheral wall and the air guide plates or between the plurality of air guide plates.

Description

Technical Field

[0001] This invention relates to a cooling device for construction machinery, and more specifically, to a cooling device for construction machinery that supplies cooling air generated by one or more cooling fans to multiple heat exchangers such as radiators and oil coolers. Background Technology

[0002] In construction machinery such as hydraulic excavators and hydraulic cranes, overheating needs to be prevented by properly dissipating the heat generated by the engine and hydraulic system to the outside of the machine. Therefore, construction machinery is equipped with multiple heat exchangers, such as radiators for water cooling of the engine, oil coolers for cooling the working oil circulating in the hydraulic system, and intercoolers for cooling the air compressed by the turbocharger.

[0003] In construction machinery, there are devices that supply cooling air to multiple heat exchangers using multiple cooling fans (see, for example, Patent Document 1). The heat exchange device described in Patent Document 1, in order to supply the required airflow to each heat exchanger and reduce fuel consumption and noise, comprises multiple heat exchangers arranged side-by-side, multiple air supply mechanisms (cooling fans) arranged face-to-face with each heat exchanger, multiple electric drive sources driving each air supply mechanism (cooling fan), multiple temperature detection mechanisms detecting the temperature of the fluid passing through each heat exchanger, and a control mechanism controlling the drive speed of each electric drive source based on the temperature detected by each temperature detection mechanism.

[0004] Furthermore, in construction machinery, there is a device that supplies cooling air to all of the multiple heat exchangers by a single cooling fan (see, for example, Patent Document 2). The construction machinery described in Patent Document 2 is driven by a fan located downstream of the heat exchangers in the engine compartment to introduce cooling air into the heat exchangers. Multiple heat exchangers are arranged side by side in the engine compartment in relation to the airflow direction, and at the boundaries between adjacent heat exchangers, air guide vanes are provided over a predetermined range upstream of the heat exchangers in the airflow direction.

[0005] Existing technical documents

[0006] Patent documents

[0007] Patent Document 1: Japanese Patent Application Publication No. 2017-198135

[0008] Patent Document 2: Japanese Patent Application Publication No. 2007-76602 Summary of the Invention

[0009] The problem that the invention aims to solve

[0010] However, in construction machinery, given that the heat dissipation load of each heat exchanger is significantly different, the performance of each heat exchanger is significantly different, and the various devices inside the machine are positioned as obstructions to the cooling air supplied to the heat exchangers due to space constraints, it is also assumed that the required air volume and suction force of each heat exchanger are significantly different.

[0011] In the heat exchange device described in Patent Document 1, cooling air is supplied to each heat exchanger by separate air supply mechanisms (cooling fans). Therefore, when the required airflow and suction force differ significantly between the multiple heat exchangers, a large load variation occurs between the multiple air supply mechanisms (cooling fans). If the loads on each air supply mechanism (cooling fan) differ significantly, the overall operating efficiency of the heat exchange device decreases, and the overall power required by the device sometimes increases.

[0012] In the technology described in Patent Document 2, the cooling air is diverted to adjacent heat exchangers by a guide vane, which aims to prevent excessive cooling air from being drawn into heat exchangers with stronger suction. However, when the required airflow and suction force differ significantly between multiple heat exchangers, simply placing the guide vane upstream of the heat exchanger in the direction of cooling air flow relative to the boundary between the heat exchangers is considered insufficient to achieve the aforementioned suppression effect.

[0013] The present invention was made to solve the above-mentioned problems, and its purpose is to provide a cooling device for construction machinery that, when multiple cooling fans supply cooling air to multiple heat exchangers, can reduce the load deviation between multiple cooling fans, and when a single cooling fan supplies cooling air to all multiple heat exchangers, can appropriately distribute the air volume to each heat exchanger.

[0014] Solution for solving the problem

[0015] This application includes several solutions to the aforementioned problems. One example is a cooling device for construction machinery, comprising: a housing having a peripheral wall; a plurality of heat exchangers arranged side-by-side transversely within the housing; and a plurality of fans arranged opposite the heat exchangers, generating cooling air at the heat exchanger side as the suction side relative to the heat exchangers. The cooling device for construction machinery is characterized in that the housing has a plurality of air guide plates extending from the heat exchanger side toward the fan side within a space surrounded by the peripheral wall and arranged in the arrangement direction of the heat exchangers. The ends of the air guide plates on the heat exchanger side are located on the boundary of two adjacent heat exchangers or on any one of the heat exchangers. A first fan of the plurality of fans is positioned opposite one of the air guide plates, and a second fan is positioned between the air guide plate adjacent to the peripheral wall and the peripheral wall, or between the plurality of air guide plates.

[0016] Furthermore, as another example, a cooling device for construction machinery includes: a housing having a peripheral wall; a plurality of heat exchangers arranged side by side in a transverse manner within the housing; and a separate fan arranged opposite to the plurality of heat exchangers, generating cooling air on the heat exchanger side as the suction side relative to the plurality of heat exchangers. The cooling device for construction machinery is characterized in that the housing has a plurality of air guide plates that extend from the heat exchanger side toward the fan side within the space surrounded by the peripheral wall and are arranged in the arrangement direction of the plurality of heat exchangers.

[0017] The effects of the invention are as follows.

[0018] According to the present invention, by positioning the first fan opposite the air guide plate, the airflow of the cooling air generated by the first fan can be distributed to adjacent flow paths separated by the air guide plate. Therefore, compared to the case where only a portion of the airflow from each fan is supplied to the heat exchanger without distribution, the degree of freedom in distributing the airflow generated by multiple fans relative to each heat exchanger is increased. As a result, the load deviation generated among the multiple fans can be reduced.

[0019] Furthermore, according to the present invention, multiple flow paths are formed between multiple heat exchangers and individual fans by the peripheral wall and multiple air guide plates, which enables accurate adjustment of the distribution of the cooling air volume generated by the individual fan relative to each flow path. Therefore, compared with a structure in which multiple flow paths are not formed between multiple heat exchangers and fans, the cooling air volume passing through each heat exchanger located upstream of the multiple flow paths can be appropriately distributed.

[0020] The issues, structures, and effects other than those described above will become clear through the following description of the implementation methods. Attached Figure Description

[0021] Figure 1 This is a side view of a hydraulic excavator showing a first embodiment of the cooling device for construction machinery according to the present invention.

[0022] Figure 2 Observing from arrow II-II Figure 1 The diagram shows a cross-sectional view of a hydraulic excavator, and is a simplified diagram illustrating the internal structure of the excavator's machine compartment.

[0023] Figure 3 This is a perspective view of the first embodiment of the cooling device for the construction machinery of the present invention, viewed from the fan side.

[0024] Figure 4 This is a front view of the first embodiment of the cooling device for construction machinery of the present invention, viewed from the heat exchanger side.

[0025] Figure 5 Observe from the VV arrow Figure 4 A simplified cross-sectional view of a first embodiment of the cooling device for construction machinery of the present invention is shown.

[0026] Figure 6 Observe from the VI-VI arrow Figure 4 A simplified cross-sectional view of a first embodiment of the cooling device for construction machinery of the present invention is shown.

[0027] Figure 7 Observe from arrow VII-VII Figure 4 A simplified cross-sectional view of a first embodiment of the cooling device for construction machinery of the present invention is shown.

[0028] Figure 8 This is a simplified perspective view showing the internal structure of the housing, which constitutes part of the cooling device of the construction machinery of the present invention, with a portion omitted.

[0029] Figure 9 This is an explanatory diagram showing the flow of cooling air in a cooling device of a comparative example of a cooling device for construction machinery according to the present invention, representing a first embodiment.

[0030] Figure 10 From and Figure 4 The arrows corresponding to arrows VI-VI show a simplified cross-sectional view of the second embodiment of the cooling device for construction machinery of the present invention.

[0031] Figure 11 It is to constitute Figure 10 A simplified perspective view of the internal structure of the outer casing of a portion of a second embodiment of the cooling device for construction machinery of the present invention is shown, with a portion omitted.

[0032] Figure 12 From and Figure 4 The arrow corresponding to the VV arrow is a simplified cross-sectional view of the first variation of the second embodiment of the cooling device for construction machinery of the present invention.

[0033] Figure 13 From and Figure 4 The arrows corresponding to arrows VI-VI are used to observe a simplified cross-sectional view of a first variation of the second embodiment of the cooling device for construction machinery of the present invention.

[0034] Figure 14 From and Figure 4 The arrows corresponding to VII-VII are shown in a simplified cross-sectional view of the first variation of the second embodiment of the cooling device for the construction machinery of the present invention.

[0035] Figure 15 It is to constitute Figures 12-14 A simplified perspective view of the internal structure of the outer casing of a portion of a first variation of the second embodiment of the cooling device for construction machinery of the present invention is shown, with a portion omitted.

[0036] Figure 16 From and Figure 4 The arrow corresponding to the VV arrow is a simplified cross-sectional view of a second variation of the second embodiment of the cooling device for construction machinery of the present invention.

[0037] Figure 17 From and Figure 4 The arrows corresponding to arrows VI-VI are shown in a simplified cross-sectional view of a second variation of the second embodiment of the cooling device for construction machinery of the present invention.

[0038] Figure 18 It is to constitute Figures 16-17 A simplified perspective view of the internal structure of the outer casing of a portion of a second variation of the second embodiment of the cooling device for construction machinery of the present invention, with a portion omitted.

[0039] Figure 19 This is a perspective view of the third embodiment of the cooling device for the construction machinery of the present invention, viewed from the fan side.

[0040] Figure 20 This is a front view of the third embodiment of the cooling device for the construction machinery of the present invention, viewed from the heat exchanger side.

[0041] Figure 21 Observe from the XXI-XXI arrow Figure 20 A simplified cross-sectional view of a third embodiment of the cooling device for construction machinery of the present invention is shown.

[0042] Figure 22 Observing from the XXII-XXII arrow Figure 20 A simplified cross-sectional view of a third embodiment of the cooling device for construction machinery of the present invention is shown.

[0043] Figure 23 It is to constitute Figures 21-22 A simplified perspective view of the internal structure of the outer casing of a portion of a third embodiment of the cooling device for construction machinery of the present invention is shown, with a portion omitted.

[0044] Figure 24 This is a perspective view of the fourth embodiment of the cooling device for the construction machinery of the present invention, viewed from the fan side.

[0045] Figure 25 This is a front view of the fourth embodiment of the cooling device for construction machinery of the present invention, viewed from the heat exchanger side.

[0046] Figure 26 Observe from the XXVI-XXVI arrow Figure 25 A simplified cross-sectional view of a fourth embodiment of the cooling device for construction machinery of the present invention is shown.

[0047] Figure 27 It is to constitute Figure 26 A simplified perspective view of the internal structure of the outer casing of a portion of a fourth embodiment of the cooling device for construction machinery of the present invention is shown, with a portion omitted.

[0048] Figure 28 This is a simplified cross-sectional view showing the construction of a fifth embodiment of the cooling device for construction machinery according to the present invention.

[0049] Figure 29 This is a simplified cross-sectional view showing the structure of a sixth embodiment of the cooling device for construction machinery according to the present invention. Detailed Implementation

[0050] Hereinafter, embodiments of the cooling device for the construction machinery of the invention will be described using the accompanying drawings. In this embodiment, a hydraulic excavator will be used as an example of construction machinery.

[0051] [First Implementation Method]

[0052] First, use Figure 1 and Figure 2 The structure of a hydraulic excavator according to a first embodiment of the cooling device for construction machinery of the present invention will be described. Figure 1 This is a side view of a hydraulic excavator showing a first embodiment of the cooling device for construction machinery according to the present invention. Figure 2 Observing from arrow II-II Figure 1The diagram shown is a cross-sectional view of a hydraulic excavator, and is a simplified diagram illustrating the internal structure of the excavator's machine compartment. The description uses views from the operator seated in the driver's seat, showing the front, back, left, and right sides.

[0053] Figure 1 In this hydraulic excavator 1, it generally consists of a self-propelled lower traveling body 2, an upper slewing body 3 rotatably mounted on the lower traveling body 2, and a working front section 4 located at the front of the upper slewing body 3, capable of pitching. The lower traveling body 2 has tracked traveling devices 6 on both sides (only one side is shown). The left and right traveling devices 6 are each driven by a travel motor (not shown) that acts as a hydraulic actuator. The upper slewing body 3 rotates relative to the lower traveling body 2 by a slewing motor (not shown) that acts as a hydraulic actuator. The working front section 4 is a multi-joint type working device for excavation operations, etc., and includes a boom 7, a stick 8, and a bucket 9 as a working tool. The base end of the boom 7 is rotatably connected to the front of the upper slewing body 3. The base end of the stick 8 is rotatably connected to the front end of the boom 7. The base end of the bucket 9 is rotatably connected to the front end of the stick 8. The boom 7, stick 8, and bucket 9 are driven by the boom cylinder 7a, stick cylinder 8a, and bucket cylinder 9a, respectively, which are hydraulic actuators.

[0054] The upper slewing body 3 comprises: a slewing frame 11, which is rotatably mounted on the lower traveling body 2 as a support structure; a driver's cab 12 located on the left front side of the slewing frame 11; a counterweight 13 located at the rear end of the slewing frame 11; and a machine room 20 located between the driver's cab 12 and the counterweight 13. The driver's cab 12 is equipped with a driver's seat for the operator, and various operating devices (not shown) for operating the lower traveling body 2, the working front part 4, etc. The counterweight 13 is used to achieve weight balance with the working front part 4.

[0055] like Figure 2 As shown, an engine 31 serving as a prime mover is housed in the machine room 20. The engine 31 is supported by a left tail frame 11a and a right tail frame 11b at the ends of the counterweight 13 forming the rotating frame 11, and is arranged in a transverse configuration with the output shaft extending along the width of the machine body. An exhaust pipe 32 for discharging exhaust gases is connected to the engine 31. An exhaust gas aftertreatment device 33 for purifying the exhaust gases of the engine 31 is connected downstream of the exhaust pipe 32. The exhaust gas aftertreatment device 33 consists, for example, a PM capture device 34 for capturing particulate matter (PM) generated by the combustion of the engine 31 and a NOx purification device 35 for purifying NOx contained in the exhaust gases of the engine 31. The exhaust gas aftertreatment device 33 is, for example, located on one side of the engine 31. Figure 2 Above the right side of the middle.

[0056] A hydraulic pump 37 is connected to the engine 31 via a power transmission device 38. The hydraulic pump 37 is, for example, located below the exhaust aftertreatment device 33. Driven by the engine 31, the hydraulic pump 37 pumps the cylinders 7a, 8a, and 9a (see reference 4) of the front working section 4. Figure 1 The hydraulic actuators of the lower traveling body 2, such as the traveling motor and the rotary motor (not shown), are supplied with pressurized oil.

[0057] In the machine room 20 and on the opposite side from the exhaust aftertreatment device 33 and hydraulic pump 37, separated by the engine 31 ( Figure 2 A cooling device 39 is located on the left side of the center. The cooling device 39 releases heat generated by the hydraulic system, including the hydraulic pump 37, hydraulic actuators 7a, 8a, 9a, etc., and heat generated by the engine 31 to the outside of the hydraulic excavator 1. The detailed structure of the cooling device 39 will be described below.

[0058] The machine compartment 20 is formed by a cover 21 that surrounds various devices such as the engine 31, exhaust aftertreatment device 33, hydraulic pump 37, and cooling device 39. The cover 21 is, for example, formed as a roughly box-shaped structure opening to the rear, and consists of a lower cover 22, a left side cover 23 erected at the left end of the lower cover 22, a right side cover 24 erected at the right end of the lower cover 22, a front cover 25 erected at the front end of the lower cover 22 and extending across the front ends of the left and right side covers 23 and 24, and an upper cover 27. The upper cover 27 covers the upper opening formed by the left and right side covers 23 and 24 and the front cover 25. The rear opening of the cover 21 is sealed by the front wall of the counterweight 13.

[0059] The left side cover 23 has an intake port 23a for introducing external gas into the machine room 20. The lower side cover 22 and the right side cover 24 have exhaust ports 22a and 24a for discharging cooling air out of the machine room 20, respectively. In the upper side cover 27, the tailpipe 32a for discharging exhaust gas from the engine 31 protrudes upward.

[0060] Next, use Figures 2-8 The structure of the first embodiment of the cooling device for construction machinery of the present invention will be described. Figure 3 This is a perspective view of the first embodiment of the cooling device for the construction machinery of the present invention, viewed from the fan side. Figure 4 This is a front view of the first embodiment of the cooling device for construction machinery of the present invention, viewed from the heat exchanger side. Figure 5 Observe from the VV arrow Figure 4 A simplified cross-sectional view of a first embodiment of the cooling device for construction machinery of the present invention is shown. Figure 6 Observe from the VI-VI arrow Figure 4A simplified cross-sectional view of a first embodiment of the cooling device for construction machinery of the present invention is shown. Figure 7 Observe from arrow VII-VII Figure 4 A simplified cross-sectional view of a first embodiment of the cooling device for construction machinery of the present invention is shown. Figure 8 This is a simplified perspective view showing the internal structure of the housing, which constitutes part of the cooling device of the construction machinery of the present invention, with a portion omitted.

[0061] Figure 3 and Figure 4 In the cooling device 39, there are: a heat exchanger assembly 40 consisting of multiple heat exchangers; a cooling fan assembly 50 consisting of multiple fans supplying cooling air to the heat exchanger assembly 40; and a housing 60 holding the heat exchanger assembly 40 on one side and the cooling fan assembly 50 on the other side. Figure 2 As shown, the cooling device 39 is fixed in the machine room 20 via the mounting bracket 29.

[0062] For example, Figure 4 As shown, the heat exchanger assembly 40 consists of the following components: an oil cooler (hereinafter, sometimes referred to as the first heat exchanger) 41, which houses hydraulic cylinders 7a, 8a, and 9a (refer to...) that operate the front section 4. Figure 1 ), hydraulic pump 37 (reference) Figure 2 The engine 31 is cooled by circulating working oil in its hydraulic circuit; a radiator (hereinafter, sometimes referred to as a second heat exchanger) 42 cools the engine 31's cooling water; and an intercooler (hereinafter, sometimes referred to as a third heat exchanger) 43 cools the air compressed by the turbocharger. The required heat exchange capacity of the intercooler 43 is smaller than that of the oil cooler 41 and the radiator 42, and its size (outer dimensions) is also smaller than those of the oil cooler 41 and the radiator 42. The airflow required by each heat exchanger 41, 42, and 43 is determined by its respective heat exchange capacity. That is, the airflow required by the intercooler 43 is smaller than that required by the oil cooler 41 and the radiator 42. For example, Figures 4-7 As shown, the oil cooler 41, radiator 42, and intercooler 43 are rectangular in shape with approximately the same height but different widths, and are located approximately on the same plane. That is, the oil cooler 41, radiator 42, and intercooler 43 are arranged side by side in a transverse manner within the housing 60.

[0063] The cooling fan assembly 50 is configured to generate cooling air from one side of the outer casing 60 in the extending direction (the extending direction of the peripheral wall 61 hereinafter referred to as the extending direction) towards the other side, i.e., cooling air on the heat exchanger assembly 40 side becomes the suction side. In the cooling fan assembly 50, the number of fans corresponding to each heat exchanger 41, 42, 43 (not a single unit) is set according to the relative magnitude of the heat exchange. That is, the number of fans corresponding to the oil cooler 41 and radiator 42, which have relatively large heat exchange, is set to be greater than the number of fans corresponding to the intercooler 43, which has relatively small heat exchange. For example, as... Figures 3-7 As shown, the cooling fan assembly 50 consists of a first fan 51 and a second fan 52 primarily used to supply cooling air to the oil cooler 41, a third fan 53 and a fourth fan 54 primarily used to supply cooling air to the radiator 42, and a fifth fan 55 used to supply cooling air to both the radiator 42 and the intercooler 43. The first to fifth fans 55 are arranged side-by-side relative to the extending direction of the outer casing 60 (hereinafter referred to as the extending direction of the peripheral wall 61). The first fan 51 and the second fan 52 are positioned opposite the first heat exchanger 41 and spaced apart vertically. The third fan 53 and the fourth fan 54 are positioned opposite the second heat exchanger 42 and spaced apart vertically. The fifth fan 55 is positioned opposite the second and third heat exchangers 43, passing over both the second and third heat exchangers. The fifth fan 55 is positioned vertically between the third fan 53 and the fourth fan 54.

[0064] For example, Figure 3 As shown, the first fan 51 to the fifth fan 55 are all identical in shape and size. By making all the first fan 51 to the fifth fan 55 the same, cost reduction can be achieved. Each fan 51, 52, 53, 54, and 55 has an impeller consisting of a rotatable rotating shaft 57 and multiple blades 58 arranged on the outer periphery of the rotating shaft 57, and an annular member (sleeve) 59 disposed with an open gap on the outer periphery of the impeller. For example, an electric motor as a drive device is built into the rotating shaft 57. Using a motor mounted on the engine 31 (see reference...) Figure 2 The electric motor is driven by the electricity generated by the alternator (not shown) of the AC generator.

[0065] For example, Figures 5-8 As shown, the outer casing 60 has a length along one direction that serves as the main body of the outer casing ( Figures 5-7 A rectangular cylindrical peripheral wall 61 extending in the vertical direction, extending from the heat exchanger assembly 40 side within the space surrounded by the peripheral wall 61. Figures 5-7 (Lower middle side) facing the cooling fan assembly 50 side ( Figures 5-7A first air guide plate 62 and a second air guide plate 63 extend from the upper middle side and are arranged in the direction (transverse direction of the peripheral wall 61) of the parallel arrangement of multiple heat exchangers 41, 42, and 43. The peripheral wall 61 is composed of a first side portion 65 on the left and a second side portion 66 on the right when viewed from its extending direction side (heat exchanger group 40 side), a lower surface portion 67 connecting the lower end of the first side portion 65 to the lower end of the second side portion 66, and an upper surface portion 68 connecting the upper end of the first side portion 65 to the upper end of the second side portion 66. The first air guide plate 62 and the second air guide plate 63 are formed parallel to the first side portion 65 and the second side portion 66 of the peripheral wall 61. In this embodiment, the peripheral wall 61 is formed in a square tube shape, but the peripheral wall 61 can be cylindrical, and the cross-sectional shape in the extending direction can be any shape such as a polygon.

[0066] The first air guide plate 62 and the second air guide plate 63 of the outer casing 60, together with the peripheral wall 61, form a number that corresponds to the number of heat exchangers 41, 42, and 43 in the heat exchanger assembly 40. Figures 5-8 (three) consistent multiple ( Figures 5-8 The housing 60 functions as the intake flow path for multiple cooling fans 51, 52, 53, 54, and 55. The first flow path 81, the second flow path 82, and the third flow path 83, which are multiple flow paths, are arranged side by side and extend along the extension direction of the peripheral wall 61.

[0067] A first flow path 81 is formed by a first side surface 65 of the peripheral wall 61, a portion of the lower surface 67, a portion of the upper surface 68, and a first air guide plate 62. A third flow path 83 is formed by a second side surface 66 of the peripheral wall 61, a portion of the lower surface 67, a portion of the upper surface 68, and a second air guide plate 63. A second flow path 82 adjacent to the first flow path 81 and the third flow path 83 is formed by the remaining portion of the lower surface 67 of the peripheral wall 61, the remaining portion of the upper surface 68, the first air guide plate 62, and the second air guide plate 63. That is, the first air guide plate 62 separates the adjacent first flow path 81 and the second flow path 82, and the second air guide plate 63 separates the adjacent second flow path 82 and the third flow path 83.

[0068] An opening 81a of a first flow path 81, an opening 82a of a second flow path 82, and an opening 83a of a third flow path 83 are formed on one side of the extending direction of the peripheral wall 61. An oil cooler 41 is disposed in the opening 81a on one side of the first flow path 81. A radiator 42 is disposed in the opening 82a on one side of the second flow path 82. An intercooler 43 is disposed in the opening 83a on one side of the third flow path 83. That is, the end 62a of the extending direction of the peripheral wall 61 of the first air guide plate 62 (the end on the heat exchanger assembly 40 side) is located on the boundary between the adjacent oil cooler 41 and the radiator 42. The end 63a of the extending direction of the peripheral wall 61 of the second air guide plate 63 (the end on the heat exchanger assembly 40 side) is located on the boundary between the adjacent radiator 42 and the intercooler 43.

[0069] like Figure 3 and Figures 5-7 As shown, on the other side of the extending direction of the peripheral wall 61 ( Figures 5-7 The upper middle side is provided with a mounting wall 69 for mounting the cooling fan assembly 50. The mounting wall 69 blocks the other side of the first flow path 81, the second flow path 82, and the third flow path 83. Five mounting holes 71, 72, 73, 74, and 75 are formed in the mounting wall 69 corresponding to the number of fans in the cooling fan assembly 50. The impellers of the first fan 51, the second fan 52, the third fan 53, and the fourth fan 54 are respectively arranged inside the first mounting hole 71, the second mounting hole 72, the third mounting hole 73, and the fourth mounting hole 74. The opening edges of the first mounting holes 71 to the fourth mounting holes 74 are respectively provided with annular members 59 of the first fan 51 to the fourth fan 54 protruding outwards. The impeller of the fifth fan 55 is arranged with a gap from the opening of the fifth mounting hole 75. The opening edge of the fifth mounting hole 75 is provided with annular members 59 of the fifth fan 55 protruding outwards.

[0070] The first mounting hole 71 and the second mounting hole 72 are located between the first side surface 65 of the peripheral wall 61 and the other end 62b (the end on the cooling fan assembly 50 side) of the peripheral wall 61 in the first air guide plate 62 extending in the direction of extension. That is, the first fan 51 and the second fan 52 are positioned at a position corresponding to the range of the first flow path 81 (the position between the peripheral wall 61 and the first air guide plate 62) without crossing the other end 62b of the first air guide plate 62, and the first mounting hole 71 and the second mounting hole 72 constitute the outlet of the first flow path 81. The third mounting hole 73 and the fourth mounting hole 74 are located between the other end 62b of the first air guide plate 62 and the other end 63b (the end on the cooling fan assembly 50 side) of the peripheral wall 61 in the second air guide plate 63 extending in the direction of extension. That is, the third fan 53 and the fourth fan 54 are positioned within the range of the second flow path 82 (between the first air guide plate 62 and the second air guide plate 63) without crossing the other end 62b of the first air guide plate 62 and the other end 63b of the second air guide plate 63. The third mounting hole 73 and the fourth mounting hole 74 constitute the outlet of the second flow path 82. The fifth mounting hole 75 is formed across the other end 63b of the second air guide plate 63. That is, the fifth fan 55 is positioned across the other end 63b of the second air guide plate 63, opposite to the other end 63b of the second air guide plate 63, and only crosses both the adjacent second flow path 82 and the third flow path 83. The fifth mounting hole 75 constitutes the outlet of both the second flow path 82 and the third flow path 83. That is, the first fan 51 to the fifth fan 55 are configured such that the cooling air generated by any one of the first fan 51 to the fifth fan 55 flows to each of the first flow path 81 to the third flow path 83.

[0071] Thus, in the cooling device 39, the relative positions of one side ends 62a and 63a (ends on the heat exchanger assembly 40 side) of the first air guide plate 62 and the second air guide plate 63 relative to the plurality of heat exchangers 41, 42, and 43, and the relative positions of the other side ends 62b and 63b (ends near the cooling fan assembly 50 side) of the first air guide plate 62 and the second air guide plate 63 relative to the plurality of fans 51, 52, 53, 54, and 55, are determined according to the relative heat exchange amounts among the plurality of heat exchangers 41, 42, and 43. That is, the mutual configuration of the plurality of fans 51, 52, 53, 54, and 55 relative to the plurality of flow paths 81, 82, and 83 is determined as follows: The second heat exchanger 42, which has the largest relative heat exchange amount, is supplied with an airflow equivalent to approximately 2.5 fans; the first heat exchanger 41, which has the second largest relative heat exchange amount, is supplied with an airflow equivalent to approximately 2 fans; and the third heat exchanger 43, which has the smallest relative heat exchange amount, is supplied with an airflow equivalent to approximately 0.5 fans. Instead of allocating the number of fans to each heat exchanger 41, 42, 43 on a per-unit basis, this cooling device 39 allocates the airflow of one fan by adjusting the position of the ends 62b and 63b of the fan side of the air guide plates 62 and 63 that separate the multiple flow paths 81, 82, 83, thereby adjusting the airflow supplied to each heat exchanger 41, 42, 43.

[0072] Next, use Figure 2 , Figure 8 , Figure 9 The operation, function, and effect of the cooling device for construction machinery of the present invention will be described in the first embodiment. Figure 9 This is an explanatory diagram showing the flow of cooling air in a cooling device of a comparative example of a cooling device for construction machinery according to the present invention, relative to a first embodiment of the cooling device. Figure 2 , Figure 8 , Figure 9 In the image, the thick arrows indicate the flow and direction of the cooling air.

[0073] In the hydraulic excavator 1, where the cooling device 39 is housed in the machine compartment 20, such as Figure 2 As shown, when the cooling fan assembly 50 is driven, external gas is drawn in from the intake 23a of the shroud 21 of the machine compartment 20, generating cooling air within the machine compartment 20. This cooling air, after cooling the heat exchanger assembly 40 within the machine compartment 20, is discharged from the cooling fan assembly 50 via flow paths 81, 82, and 83 within the outer casing 60. The cooling air discharged from the cooling fan assembly 50, after cooling the periphery of the engine 31, exhaust aftertreatment device 33, and hydraulic pump 37, is discharged to the outside of the machine compartment 20 from the exhaust ports 22a and 24a of the shroud 21. In this way, various devices housed within the machine compartment 20, such as the heat exchanger assembly 40, are cooled by the cooling air generated by the cooling fan assembly 50, thus enabling the various devices within the machine compartment 20 to operate normally.

[0074] However, Figure 9The comparative example cooling device 139 shown does not have the second air guide plate 63 of the outer casing 60 of the cooling device 39 of this embodiment (see reference). Figure 8 Furthermore, the structures of the heat exchanger assembly 40 and the cooling fan assembly 50 in the comparative example cooling device 139 are the same as those in the cooling device 39 of this embodiment.

[0075] That is, a first flow path 181 and a second flow path 182, separated by a first air guide plate 162, are formed within the outer casing 160 of the comparative example. The first flow path 181 of the comparative example is the same as the first flow path 81 of this embodiment, while the second flow path 182 of the comparative example is a flow path where the second flow path 82 of this embodiment is fully connected to the third flow path 83. That is, the first flow path 181 of the comparative example is a flow path where only the oil cooler 41 is arranged in the opening on one side. On the other hand, the second flow path 182 of the comparative example is a flow path where both the radiator 42 and the intercooler 43 are arranged in the opening on one side.

[0076] In the comparative example cooling device 139, a fifth fan 55, positioned opposite both the radiator 42 and the intercooler 43, draws air from both regions on the radiator 42 side and the intercooler 43 side. Furthermore, a third fan 53 and a fourth fan 54, also opposite the radiator 42, draw air from the region on the radiator 42 side. Additionally, since there is no air guide separating the radiator 42 side and the intercooler 43 side, air is also drawn from the region on the intercooler 43 side. That is, the intake regions of the third fan 53 and the fourth fan 54, opposite the radiator 42, are expanded to both regions on the radiator 42 side and the intercooler 43 side. On one side of the extension direction of the second flow path 182, within the cooling air generated by the third fan 53 and the fourth fan 54, there exists a flow Fd in a direction significantly inclined relative to the extension direction of the second flow path 182 (the extension direction of the peripheral wall 61) (the width direction of the outer casing 160). Therefore, the airflow from the fifth fan 55, combined with the airflow from the third fan 53 and the fourth fan 54, provides sufficient airflow to the intercooler 43. However, a portion of the airflow generated by the third fan 53 and the fourth fan 54 is allocated to the intercooler 43 side. To obtain the corresponding amount of airflow required by the radiator 42, it is necessary to increase the airflow of the third fan 53 and the fourth fan 54. Therefore, it is necessary for the third fan 53 and the fourth fan 54 to operate at a higher speed than the fifth fan 55.

[0077] Since the shaft power of a fan is generally proportional to the cube of its rotational speed, increasing the rotational speed of a few fans will increase the overall power consumption of the cooling fan assembly 50. Furthermore, since fan noise is generally proportional to the 5th to 6th power of its rotational speed, increasing the rotational speed of a few fans will correspondingly increase the noise of the cooling fan assembly 50.

[0078] In the comparative example cooling device 139 that does not have the second air guide plate 63 of the first embodiment, since the third fan 53 and the fourth fan 54 need to operate at a higher speed than the fifth fan 55, a load deviation occurs between the third fan 53 and the fourth fan 54 and the fifth fan 55. As a result, the overall power consumption and noise of the cooling fan assembly 50 increase.

[0079] In contrast, in this embodiment, such as Figure 8 As shown, the second air guide plate 63 of the housing 60 forms a second flow path 82 corresponding only to the heat sink 42 and a third flow path 83 corresponding only to the intercooler 43. Furthermore, the third fan 53 and the fourth fan 54 are positioned between the other end 62b of the first air guide plate 62 and the other end 63b of the second air guide plate 63, and the fifth fan 55 is positioned across the other end 63b of the second air guide plate 63 (opposite position).

[0080] Therefore, for the third fan 53 and the fourth fan 54, which are directly opposite the radiator 42, the intake of air from the area on the intercooler 43 side is obstructed by the second air guide plate 63, so air is mainly drawn in from the area on the radiator 42 side. Furthermore, the fifth fan 55, which crosses both the second flow path 82 and the third flow path 83, draws in air from both the area on the intercooler 43 side and the area on the radiator 42 side. Therefore, for the radiator 42, which has a relatively large heat exchange capacity, a portion of the airflow is supplied to the fifth fan 55 in addition to the airflow supplied to the third fan 53 and the fourth fan 54. On the other hand, for the intercooler 43, which has a relatively small heat exchange capacity, only a portion of the airflow is supplied to the fifth fan 55. Therefore, by supplementing the airflow of the fifth fan 55 to the radiator 42 side, the required airflow for both the radiator 42 and the intercooler 43 can be obtained without increasing the airflow of the third fan 53 and the fourth fan 54.

[0081] For example, when the rotational speeds of the third fan 53, the fourth fan 54, and the fifth fan 55 are set to the same level, the airflow from one portion of the fifth fan 55 may sometimes exceed the required airflow for the intercooler 43. However, by adjusting the position of the other end 63b of the second air guide plate 63, the excess airflow from the fifth fan 55 that is not needed for the intercooler 43 can be supplied to the radiator 42. This reduces the amount of airflow from the third fan 53 and the fourth fan 54 that is supplied from the fifth fan 55 to the radiator 42. In other words, the load among the multiple fans 51, 52, 53, 54, and 55 can be distributed, and the overall power consumption and noise of the cooling device 39 can be suppressed.

[0082] Furthermore, in this embodiment, by adjusting the relative position of the fifth fan 55 and the other end 63b of the second air guide plate 63, the airflow distribution ratio of the fifth fan 55 for the second flow path 82 and the third flow path 83 can be adjusted. This further suppresses load deviations among the multiple fans.

[0083] Furthermore, in this embodiment, the radiator 42 and the intercooler 43 are configured to be adjacent to each other, and the airflow of the fifth fan 55 is distributed to the radiator 42 and the intercooler 43. Since the heat exchange required by the radiator 42 and the intercooler 43 when the hydraulic excavator 1 is driven varies according to the load of the engine 31, it is reasonable to share a fan between the two, whose required airflow varies in tandem. On the other hand, since the heat exchange required by the oil cooler 41 when the hydraulic excavator 1 is driven varies according to the load of the hydraulic equipment, rather than according to the load of the engine 31, the change in required airflow is not linked to the intercooler 43 and the radiator 42. Therefore, the cooling air supplied by the fans 51 and 52 corresponding to the oil cooler 41 and the cooling air supplied by the fans 53, 54, and 55 corresponding to the radiator 42 and the intercooler 43 are completely separated by the first air guide plate 62.

[0084] As described above, the cooling device 39 for construction machinery according to the first embodiment of the present invention includes: a housing 60 having a peripheral wall 61; a plurality of heat exchangers 41, 42, 43 arranged side by side in a transverse manner within the housing 60; and a plurality of fans 51, 52, 53, 54, 55 arranged opposite to the plurality of heat exchangers 41, 42, 43 and generating cooling air on the heat exchanger assembly 40 side as the suction side for the plurality of heat exchangers 41, 42, 43. The housing 60 has a plurality of air guide plates 62, 63 extending from the heat exchanger assembly 40 side toward the cooling fan assembly 50 side within the space surrounded by the peripheral wall 61 and arranged in the arrangement direction of the plurality of heat exchangers 41, 42, 43. The first ends 62a, 63a of the plurality of air guide plates 62, 63 on the heat exchanger assembly 40 side are located on the boundary of two adjacent heat exchangers among the plurality of heat exchangers 41, 42, 43. The fifth fan 55 of the plurality of fans 51, 52, 53, 54, 55 is positioned opposite one of the plurality of air guide plates 62, 63 (the second air guide plate 63), and the first to fourth fans 51, 52, 53, 54 are positioned between the air guide plates 62, 63 adjacent to the peripheral wall 60 and the peripheral wall 60 or between the plurality of air guide plates 62, 63.

[0085] According to this structure, the fifth fan 55 is positioned opposite the other end 63b of the second air guide plate 63, thereby enabling the distribution of the cooling airflow generated by the fifth fan 55 to adjacent flow paths 82, 83 separated by the second air guide plate 63. That is, compared to the case where a portion of the airflow from each fan is supplied to the heat exchanger without distribution, the degree of freedom in distributing the airflow generated by the multiple fans 51, 52, 53, 54, 55 relative to each heat exchanger 41, 42, 43 is increased. As a result, the load deviation generated among the multiple fans 51, 52, 53, 54, 55 can be reduced.

[0086] Furthermore, in this embodiment, the fifth fan 55 is configured to face only adjacent heat exchangers 42 and 43 among the plurality of heat exchangers 41, 42, and 43. With this configuration, the fifth fan 55 can be configured to span two adjacent flow paths 82 and 83 without complicating the construction of the second air guide plate 63 of the housing 60. That is, the second air guide plate 63 can be formed parallel to the peripheral wall 61 without tilting.

[0087] [Second Implementation]

[0088] Next, use Figure 10 and Figure 11 A second embodiment of the cooling device for construction machinery of the present invention will be described. Figure 10 From and Figure 4 The arrows corresponding to arrows VI-VI show a simplified cross-sectional view of the second embodiment of the cooling device for construction machinery of the present invention. Figure 11 It is to constitute Figure 10 The simplified perspective view shows a portion of the internal structure of the outer casing of a second embodiment of the cooling device for construction machinery of the present invention, with a portion omitted. Furthermore, Figure 10 and Figure 11 In the middle, symbols and Figures 1 to 9 The symbols shown are identical, so their detailed descriptions are omitted.

[0089] Figure 10 and Figure 11 The main difference between the cooling device 39A for construction machinery according to the second embodiment of the present invention and the first embodiment is that: a cutout 63c is provided at the other end 63b (the end on the cooling fan assembly 50 side) of the second air guide plate 63A of the housing 60A, corresponding to the configuration position of the fifth fan 55; and the impeller of the fifth fan 55 is disposed inside the fifth mounting hole 75 of the housing 60A. The cutout 63c of the second air guide plate 63A is formed from the position of the mounting wall portion 69 of the housing 60A to the position of the surface of the radiator 42 and the intercooler 43 facing the fifth fan 55 (the other end face of the peripheral wall 61 extending in the direction of extension). That is, it becomes a state where the second flow path 82 and the third flow path 83 around the fifth fan 55 are connected.

[0090] The housing 60A can retain the impeller of the fifth fan 55 inside by means of the cut 63c of the second air guide plate 63A. Therefore, the impeller of the fifth fan 55 can be configured without protruding outside the housing 60A, thus increasing the freedom of placement of the cooling device 39 in the machine room 20.

[0091] However, generally speaking, a fan tends to generate flow in a direction inclined relative to the extension direction of the flow path on the side farther from the suction position, while on the side closer to the suction position, the suction force of the fan makes it difficult to generate flow in a direction inclined relative to the extension direction of the flow path. For example, Figure 9 As shown, on one side of the extension direction of the housing 160 (on the side farther from the suction position), there is no air guide plate in the second flow path 182, so the flow Fd generated by the fans 53 and 54 is in a direction that is significantly inclined relative to the extension direction of the second flow path 182 (the extension direction of the peripheral wall 61) (the width direction of the housing 160).

[0092] Since the second air guide plate 63A in this embodiment does not have a cutout at one end 63a (the end on the heat exchanger assembly 40 side), it can prevent the cooling air generated by the third fan 53 and the fourth fan 54 from flowing into the second flow path 82 via the intercooler 43 located on one side of the extension direction of the housing 60A. Furthermore, the second air guide plate 63A has a cutout 63c at the other end 63b on the fifth fan 55 side. However, since the flow near the suction side of the third fan 53 and the fourth fan 54 flows along the extension direction of the second flow path 82, and the flow near the suction side of the fifth fan 55 flows along the extension direction of the second flow path 82 and the third flow path 83, the flow after passing through the intercooler 43 will not be drawn into the third fan 53 and the fourth fan 54 via the cutout 63c formed near the fifth fan 55.

[0093] Furthermore, the flow drawn in by the fifth fan 55 generates turbulence and resistance due to its flow around the second guide plate 63A. However, by utilizing the cutout 63c provided at the other end 63b of the second guide plate 63A, the turbulence and resistance generated in the second guide plate 63A are reduced, and the noise is also reduced. As a result, the efficiency of the fifth fan 55 is improved.

[0094] According to the second embodiment of the cooling device for construction machinery of the present invention described above, similar to the first embodiment described above, the air volume of the cooling air generated by the fifth fan 55 can be distributed to two adjacent flow paths 82, 83 separated by the second air guide plate 63A, thereby reducing the load deviation generated among the plurality of fans 51, 52, 53, 54, 55.

[0095] [Modifications of the Second Embodiment]

[0096] Next, a first and second modification of the second embodiment of the cooling device for construction machinery of the present invention will be described using the accompanying drawings. First, using... Figures 12-15 The first variation will be explained. Figure 12 From and Figure 4 The arrow corresponding to the VV arrow is a simplified cross-sectional view of the first variation of the second embodiment of the cooling device for construction machinery of the present invention. Figure 13 From and Figure 4 The arrows corresponding to arrows VI-VI are used to observe a simplified cross-sectional view of a first variation of the second embodiment of the cooling device for construction machinery of the present invention. Figure 14 From and Figure 4 The arrows corresponding to VII-VII are shown in a simplified cross-sectional view of the first variation of the second embodiment of the cooling device for the construction machinery of the present invention. Figure 15 It is to constitute Figures 12-14The simplified perspective view shows a portion of the internal structure of the outer casing of a first variation of the second embodiment of the cooling device for construction machinery of the present invention, with a portion omitted. Furthermore, Figures 12-15 In the middle, symbols and Figures 1 to 11 The symbols shown are identical, so their detailed descriptions are omitted.

[0097] Figures 12-15 The difference between the cooling device 39B of the construction machinery in the first variation of the second embodiment of the present invention shown and the second embodiment is that the second air guide plate 63B is inclined such that its other end 63b (the end on the cooling fan assembly 50 side) is offset from one end 63a (the end on the heat exchanger assembly 40 side) towards the second side portion 66 of the peripheral wall 61 relative to one end 63a (the end on the heat exchanger assembly 40 side). The configuration of the fifth fan 55 is determined by various constraints such as the size of the fan, the size of the housing 60B, and the configuration of various devices around the cooling device 39B. Therefore, it is conceivable that when viewed from one side of the extension direction of the housing 60B towards the other, the fifth fan 55 cannot be configured to span both the radiator 42 and the intercooler 43 approximately equally, and must be configured in a position biased towards either the radiator 42 or the intercooler 43 side. Even with this configuration of the fifth fan 55, by tilting the second air guide plate 63B so that its other end 63b is offset relative to one end 63a, the fifth fan 55 can be configured to span the second flow path 82 and the third flow path 83. Furthermore, the tilted second air guide plate 63B in this variation has a cutout 63c, but it can also be a structure without a cutout 63c.

[0098] Next, use Figures 16-18 The second variation will be explained. Figure 16 From and Figure 4 The arrow corresponding to the VV arrow is a simplified cross-sectional view of a second variation of the second embodiment of the cooling device for construction machinery of the present invention. Figure 17 From and Figure 4 The arrows corresponding to arrows VI-VI are shown in a simplified cross-sectional view of a second variation of the second embodiment of the cooling device for construction machinery of the present invention. Figure 18 It is to constitute Figures 16-17 A simplified perspective view showing a portion of the internal structure of the outer casing of a second variation of the second embodiment of the cooling device for construction machinery of the present invention, with a portion omitted. Furthermore, Figures 16-18 In the middle, symbols and Figures 1 to 15 The symbols shown are identical, so their detailed descriptions are omitted.

[0099] exist Figures 16-18In the cooling device 39C of the construction machinery of the second modification of the second embodiment of the present invention shown, the depth of the outer casing 60C is greater than that of the outer casing 60A of the second embodiment (see reference). Figure 10 The distance between each heat exchanger 41, 42, 43 and each fan 51, 52, 53, 54, 55 is longer than in the second embodiment. Furthermore, the cutout 63d of the second air guide plate 63C is formed within a range from the mounting wall portion 69 of the housing 60C to a position closer to the fifth fan 55 than the surface of the radiator 42 and the intercooler 43 (the end face on the other side of the extension direction of the peripheral wall 61). That is, the other end portion 63b of the second air guide plate 63C with the cutout 63d extends further towards the fifth fan 55 than the radiator 42 and the intercooler 43. In this modified example, the range of the cutout 63d of the second air guide plate 63C is narrower than the range of the cutout 63c of the second air guide plate 63A in the second embodiment, and the second air guide plate 63C is closer to the fifth fan 55 than the second air guide plate 63A.

[0100] Therefore, compared to the structure with cutouts extending to the surfaces of the radiator 42 and the intercooler 43 (the other end face of the peripheral wall 61 in the extension direction) (the second air guide plate 63A of the second embodiment), the cutout 63d of the second air guide plate 63C in this modification has a narrower forming range. This allows for reliable prevention of cooling air generated by the third fan 53 and the fourth fan 54 from flowing into the second flow path 82 via the intercooler 43 located on one side of the housing 60C in the extension direction, by an amount greater than the extension of the radiator 42 and the intercooler 43 towards the fifth fan 55. Furthermore, it facilitates the guiding function of the cooling air and maintains the airflow distribution function of the cooling air performed by the second air guide plate 63C. That is, based on the relative position of the fifth fan 55 and the other end face 63b of the second air guide plate 63C, the airflow distribution ratio of the fifth fan 55 in the second flow path 82 and the third flow path 83 can be adjusted with high precision.

[0101] According to the first and second variations of the second embodiment of the cooling device for construction machinery of the present invention described above, similar to the second embodiment described above, the air volume of the cooling air generated by the fifth fan 55 can be distributed to two adjacent flow paths 82 and 83 separated by the second air guide plates 63B and 63C, thereby reducing the load deviation generated among the plurality of fans 51, 52, 53, 54 and 55.

[0102] Furthermore, according to the first variation, the second air guide plate 63B is tilted such that its other end 63b is located at a position offset from one end 63a in the arrangement direction of the plurality of heat exchangers 41, 42, 43. According to this structure, even if the configuration of the fifth fan 55 is restricted, the fifth fan 55 can be configured to span the second flow path 82 and the third flow path 83.

[0103] Furthermore, in the second modification, the cutout 63d of the second air guide plate 63C is formed such that the front edge of one end 63a (the heat exchanger assembly 40 side) is located closer to the fifth fan 55 than the plurality of heat exchangers 41, 42, 43. According to this structure, compared to a structure where the cutout of the second air guide plate 63C extends to the positions of the heat exchangers 41, 42, 43, the airflow distribution ratio of the fifth fan 55 relative to the adjacent flow paths 82, 83 can be adjusted with high precision based on the relative position of the fifth fan 55 and the other end 63b of the second air guide plate 63C.

[0104] [Third Implementation Method]

[0105] Next, use Figures 19-23 A third embodiment of the cooling device for construction machinery of the present invention will be described. Figure 19 This is a perspective view of the third embodiment of the cooling device for the construction machinery of the present invention, viewed from the fan side. Figure 20 This is a front view of the third embodiment of the cooling device for the construction machinery of the present invention, viewed from the heat exchanger side. Figure 21 Observe from the XXI-XXI arrow Figure 20 A simplified cross-sectional view of a third embodiment of the cooling device for construction machinery of the present invention is shown. Figure 22 Observing from the XXII-XXII arrow Figure 20 A simplified cross-sectional view of a third embodiment of the cooling device for construction machinery of the present invention is shown.

[0106] Figure 23 It is to constitute Figures 21-22 The simplified perspective view shows a portion of the internal structure of the outer casing of a third embodiment of the cooling device for construction machinery of the present invention, with a portion omitted. Furthermore, Figures 19-23 In the middle, symbols and Figures 1 to 18 The symbols shown are identical, so their detailed descriptions are omitted.

[0107] Imagine a scenario where the heat exchange capacity of the intercooler 43 in the cooling device 39D of the construction machinery according to the third embodiment of the present invention is relatively larger than that in the first embodiment. The main differences between this cooling device 39D and the cooling device 39 of the first embodiment are: the cooling fan assembly 50D consists of six fans; the fan configuration varies depending on the structure of the cooling fan assembly 50D; and the construction of the first air guide plate 62D and the second air guide plate 63D of the housing 60D varies depending on the fan configuration.

[0108] Specifically, such as Figures 19-22As shown, the cooling fan assembly 50D consists of a first fan 51 and a second fan 52 primarily used to supply cooling air to the first heat exchanger 41, a third fan 53D and a fourth fan 54D primarily used to supply cooling air to the second heat exchanger 42, and a fifth fan 55D and a sixth fan 56 used to supply cooling air to both the second heat exchanger 42 and the third heat exchanger 43. Similar to the first embodiment, the first fan 51 and the second fan 52 are positioned opposite the first heat exchanger 41 and spaced apart vertically. When cooling air is supplied from one side of the housing 60D (… Figure 21 and Figure 22 (Middle and lower side) towards the other side ( Figure 21 and Figure 22 When viewed from the upper middle side, the third fan 53D and the fourth fan 54D largely overlap with the second heat exchanger 42, and a portion of them are arranged vertically with a gap at the position where they overlap with the first heat exchanger 41. When viewed from one side of the housing 60D to the other, the fifth fan 55D and the sixth fan 56 are arranged vertically with a gap across both the second heat exchanger 42 and the third heat exchanger 43. The first fan 51, the third fan 53D, and the fifth fan 55D are located at approximately the same height. Similarly, the second fan 52, the fourth fan 54D, and the sixth fan 56 are located at approximately the same height.

[0109] like Figures 21-23 As shown, the first air guide plate 62D of the outer casing 60D is inclined such that the other end 62b of the first air guide plate 62D is located at a position offset from the first side surface portion 65 of the peripheral wall 61 relative to one side end 62a in the arrangement direction of the plurality of heat exchangers 41, 42, 43.

[0110] In addition to the first mounting holes 71 to 75D, a sixth mounting hole 76 is formed on the mounting wall portion 69 of the outer casing 60D. The first mounting hole 71 and the second mounting hole 72 are located between the first side surface portion 65 of the peripheral wall 61 and the other end portion 62b of the first air guide plate 62D. That is, the first fan 51 and the second fan 52 are located within the range of the first flow path 81 (between the peripheral wall 61 and the first air guide plate 62D), and the first mounting hole 71 and the second mounting hole 72 constitute the outlet of the first flow path 81. The third mounting hole 73D and the fourth mounting hole 74D are located between the other end portion 62b of the first air guide plate 62D and the other end portion 63b of the second air guide plate 63D. That is, the third fan 53D and the fourth fan 54D are configured to be located within the range of the second flow path 82 (between the first air guide plate 62D and the second air guide plate 63D), and the third mounting hole 73D and the fourth mounting hole 74D constitute the outlet of the second flow path 82. The fifth mounting hole 75D and the sixth mounting hole 76 are formed across the other end 63b of the second air guide plate 63D. That is, the fifth fan 55D and the sixth fan 56 are opposite to the other end 63b of the second air guide plate 63D and are arranged across both the second flow path 82 and the third flow path 83, and the fifth mounting hole 75D and the sixth mounting hole 76 constitute the outlets of both the second flow path 82 and the third flow path 83.

[0111] The second air guide plate 63D of the housing 60D has cutouts 63f and 63g at its other end 63b, corresponding to the positions of the fifth fan 55D and the sixth fan 56, respectively. The cutouts 63f and 63g of the second air guide plate 63D extend from the mounting wall 69 to the surfaces of the radiator 42 and the intercooler 43. The housing 60D can utilize the cutouts 63f and 63g of the second air guide plate 63 to hold the impellers of the fifth fan 55D and the sixth fan 56 inside the fifth mounting hole 75D and the sixth mounting hole 76, rather than placing them on the outer side of the housing 60D.

[0112] In the cooling device 39D with this structure, approximately 2 units of airflow are supplied to the first heat exchanger 41, approximately 2 units of airflow plus approximately 0.5 units of airflow plus approximately 0.5 units of airflow, i.e., approximately 3 units of airflow, are supplied to the second heat exchanger 42, and approximately 0.5 units of airflow plus approximately 0.5 units of airflow, i.e., approximately 1 unit of airflow, are supplied to the third heat exchanger 43. That is, in this embodiment, the airflow supplied to the intercooler 43 is greater than that in the first embodiment.

[0113] In this embodiment, the first air guide plate 62D is positioned such that its other end 62b (the end of the cooling fan assembly 50D) is offset from one end 62a (the end of the heat exchanger assembly 40) in the arrangement direction of the plurality of heat exchangers 41, 42, 43. According to this structure, even if the configuration of the fans corresponding to the radiator 42 is constrained, the required number of fans corresponding to the radiator 42 can be arranged within the range of the second flow path 82.

[0114] Furthermore, in this embodiment, the fifth fan 55D and the sixth fan 56 are positioned opposite the other end 63b of the second air guide plate 63D. Therefore, the fifth fan 55D and the sixth fan 56, spanning both the second flow path 82 and the third flow path 83, draw air from both the region on the intercooler 43 side and the region on the radiator 42 side. Thus, for the radiator 42, which has a relatively large heat exchange capacity, a portion of the airflow from the fifth fan 55D and the sixth fan 56 is supplied in addition to the airflow from the third fan 53D and the fourth fan 54D. On the other hand, a portion of the airflow from the fifth fan 55D and the sixth fan 56 is supplied to the intercooler 43, which has a relatively small heat exchange capacity. Therefore, by supplementing the airflow from the fifth fan 55D and the sixth fan 56 to the radiator 42 side, the required airflow for both the radiator 42 and the intercooler 43 can be obtained without increasing the airflow from the third fan 53D and the fourth fan 54D.

[0115] Furthermore, in this embodiment, the second air guide plate 63D has cutouts 63f and 63g at its other end 63b, corresponding to the positions of the fifth fan 55D and the sixth fan 56. According to this structure, by utilizing the cutouts 63f and 63g provided in the second air guide plate 63D, the turbulence and resistance of the cooling air generated by the fifth fan 55D due to the second air guide plate 63D can be reduced, thereby reducing noise.

[0116] According to the third embodiment of the cooling device for construction machinery of the present invention described above, similar to the first embodiment described above, the air volume of the cooling air generated by the fifth fan 55D and the sixth fan 56 can be distributed to two adjacent flow paths 82 and 83 separated by the second air guide plate 63D, thereby reducing the load deviation generated among the plurality of fans 51, 52, 53D, 54D, 55D, and 56.

[0117] [Fourth Implementation Method]

[0118] Next, use Figures 24-27 A fourth embodiment of the cooling device for construction machinery of the present invention will be described. Figure 24 This is a perspective view of the fourth embodiment of the cooling device for the construction machinery of the present invention, viewed from the fan side. Figure 25This is a front view of the fourth embodiment of the cooling device for construction machinery of the present invention, viewed from the heat exchanger side. Figure 26 Observe from the XXVI-XXVI arrow Figure 25 A simplified cross-sectional view of a fourth embodiment of the cooling device for construction machinery of the present invention is shown. Figure 27 It is to constitute Figure 26 The simplified perspective view shows a portion of the internal structure of the outer casing of a fourth embodiment of the cooling device for construction machinery of the present invention, with a portion omitted. Furthermore, Figures 24-27 In the middle, symbols and Figures 1 to 23 The symbols shown are identical, so their detailed descriptions are omitted.

[0119] Imagine a scenario where the heat exchange capacity of the radiator 42 in the cooling device 39E of the construction machinery according to the fourth embodiment of the present invention is relatively greater than that in the first embodiment. The main differences between this cooling device 39E and the cooling device 39 of the first embodiment are: the cooling fan assembly 50E consists of six fans; the fan configuration varies depending on the structure of the cooling fan assembly 50E; and the construction of the first air guide plate 62E and the second air guide plate 63E of the housing 60E varies depending on the structure of the cooling fan assembly 50E.

[0120] Specifically, such as Figures 24-26 As shown, the cooling fan assembly 50E consists of a first fan 51 and a second fan 52 primarily used to supply cooling air to the first heat exchanger 41, a third fan 53, a fourth fan 54, a sixth fan 56E primarily used to supply cooling air to the second heat exchanger 42, and a fifth fan 55 used to supply cooling air to both the second heat exchanger 42 and the third heat exchanger 43. Similar to the first embodiment, the first fan 51 and the second fan 52 are positioned opposite the first heat exchanger 41 and spaced apart vertically. Similarly to the first embodiment, the third fan 53 and the fourth fan 54 are positioned opposite the second heat exchanger 42 and spaced apart vertically. Similar to the first embodiment, the fifth fan 55 is positioned across both the second and third heat exchangers 42 and is located vertically between the third fan 53 and the fourth fan 54. When viewed from one side of the housing 60E (… Figure 26 (Middle and lower side) towards the other side ( Figure 26 When viewed from the upper middle side, the sixth fan 56E is positioned at a point that overlaps with both the first heat exchanger 41 and the second heat exchanger 42 (a position that spans across them). The sixth fan 56E is located between the third fan 53 and the fourth fan 54 in the vertical direction.

[0121] like Figure 24 and Figure 26As shown, in addition to the first mounting holes 71 to the fifth mounting holes 75, a sixth mounting hole 76E is formed on the mounting wall portion 69 of the outer casing 60E. The first mounting hole 71 and the second mounting hole 72 are located between the first side surface portion 65 of the peripheral wall 61 and the other end portion 62b of the first air guide plate 62E. That is, the first fan 51 and the second fan 52 are located within the range of the first flow path 81 (between the first side surface portion 65 of the peripheral wall 61 and the first air guide plate 62E), and the first mounting hole 71 and the second mounting hole 72 constitute the outlet of the first flow path 81. The third mounting hole 73, the fourth mounting hole 74, and the sixth mounting hole 76E are located between the other end portion 62b of the first air guide plate 62E and the other end portion 63b of the second air guide plate 63E. That is, the third fan 53, the fourth fan 54, and the sixth fan 56E are configured within the range of the second flow path 82 (between the first air guide plate 62E and the second air guide plate 63E), and the third mounting hole 73, the fourth mounting hole 74, and the sixth mounting hole 76E constitute the outlet of the second flow path 82. The fifth mounting hole 75 is formed at a position spanning the other end 63b of the second air guide plate 63E. That is, the fifth fan 55 is configured opposite to the other end 63b of the second air guide plate 63E and spans both the second flow path 82 and the third flow path 83, and the fifth mounting hole 75 constitutes the outlet of both the second flow path 82 and the third flow path 83.

[0122] like Figure 26 As shown, the first air guide plate 62E of the housing 60 is inclined such that its other end 62b (the end of the cooling fan assembly 50E) is offset from one end 62a (the end of the heat exchanger assembly 40) towards the first side portion 65 of the peripheral wall 61 in the arrangement direction of the plurality of heat exchangers 41, 42, 43. The second air guide plate 63E of the housing 60E has a cutout 63c at its other end 63b corresponding to the fifth fan 55. The cutout 63c of the second air guide plate 63E is formed from the mounting wall portion 69 to the surface of the second heat exchanger 42 and the third heat exchanger 43. The housing 60E can retain the impeller of the fifth fan 55 inside the housing 60E by means of the cutout 63c of the second air guide plate 63E.

[0123] In the cooling device 39E with this structure, approximately 2 units of airflow are supplied to the first heat exchanger 41, approximately 3.5 units of airflow are supplied to the second heat exchanger 42, and approximately 0.5 units of airflow are supplied to the third heat exchanger 43. That is, in this embodiment, the airflow supplied to the radiator 42 is greater than that in the first embodiment.

[0124] According to the fourth embodiment of the cooling device for construction machinery of the present invention described above, similar to the first embodiment described above, the air volume of the cooling air generated by the fifth fan 55 can be distributed to two adjacent flow paths 82, 83 separated by the second air guide plate 63E, thereby reducing the load deviation generated among the plurality of fans 51, 52, 53, 54, 55, 56E.

[0125] [Fifth Implementation]

[0126] Next, use Figure 28 A fifth embodiment of the cooling device for construction machinery of the present invention will be described. Figure 28 This is a simplified cross-sectional view illustrating the construction of a fifth embodiment of the cooling device for construction machinery according to the present invention. Furthermore, Figure 28 In the middle, symbols and Figures 1 to 27 The symbols shown are identical, so their detailed descriptions are omitted.

[0127] Figure 28 The main differences between the cooling device 39F of the construction machinery of the fifth embodiment of the present invention and the fourth embodiment are: the structure of the outer casing 60F is different; and the relative positions of the fifth fan 55F and the sixth fan 56F, which are arranged in the middle position in the vertical direction among the first fan 51 to the sixth fan 56F of the cooling fan group 50F, the air guide plates 62F and 63F of the outer casing 60F, and the three heat exchangers 41, 42 and 43 are different.

[0128] Specifically, the outer casing 60F has the same cylindrical peripheral wall 61 as the outer casing 60E of the fourth embodiment, and is located on the other side of the extending direction of the peripheral wall 61. Figure 28 In addition to the mounting wall 69 on the upper side, there are also a first air guide plate 62F and a second air guide plate 63F arranged in the arrangement direction of the three parallel heat exchangers 41, 42, and 43 (the transverse direction of the peripheral wall 61). The first air guide plate 62F and the second air guide plate 63F extend from the heat exchanger group 40 side (the direction through which the peripheral wall 61 runs) within the space surrounded by the peripheral wall 61. Figure 28 The first air guide plate 62F and the second air guide plate 63F are provided extending towards the cooling fan assembly 50F from the lower middle side. More specifically, the first air guide plate 62F and the second air guide plate 63F are formed parallel to the first side surface portion 65 and the second side surface portion 66 of the peripheral wall 61. Similar to the fourth embodiment, the first air guide plate 62F separates adjacent first flow path 81 and second flow path 82. Similar to the fourth embodiment, the second air guide plate 63F separates adjacent second flow path 82 and third flow path 83.

[0129] The first air guide plate 62F is set as the end of the heat exchanger assembly 40 side. Figure 28 The lower end of the middle section (62a) is located in the width direction of the oil cooler 41. Figure 28The middle part (in the left-right direction). That is, one end 62a of the first air guide plate 62F is positioned at a position offset from the boundary between the adjacent oil cooler 41 and the radiator 42.

[0130] The second air guide plate 63F is set as the end of the heat exchanger assembly 40 side. Figure 28 The lower end of the middle section (63a) is located in the width direction of the intercooler 43. Figure 28 The middle part (in the left-right direction). That is, one end 63a of the second air guide plate 63F is positioned at a position offset from the boundary between the adjacent radiator 42 and the intercooler 43.

[0131] The first flow path 81 of the outer casing 60F is configured to primarily correspond to the oil cooler 41. The third flow path 83 is configured to primarily correspond to the intercooler 43. The second flow path 82 is configured to correspond to any one of the oil cooler 41, the radiator 42, and the intercooler 43.

[0132] The fifth mounting hole 75F of the mounting wall 69 is formed to extend across the end of the second air guide plate 63F on the side of the cooling fan assembly 50F. Figure 28 The other end 63b of the upper middle end forms the outlet of both the second flow path 82 and the third flow path 83. That is, the fifth fan 55F is positioned opposite to the other end 63b of the second air guide plate 63F and across the other end 63b of the second air guide plate 63F, configured to cross only the adjacent second flow path 82 and the third flow path 83.

[0133] The sixth mounting hole 76F is formed across the end of the first air guide plate 62F on the side of the cooling fan assembly 50F. Figure 28 The other end 62b of the upper middle end forms the outlet of both the first flow path 81 and the second flow path 82. That is, the sixth fan 56F is positioned opposite to the other end 62b of the first air guide plate 62F and across the other end 62b of the first air guide plate 62F, and is configured to cross only the adjacent first flow path 81 and second flow path 82.

[0134] Similar to the fourth embodiment, when from one side of the housing 60F ( Figure 28 (Middle and lower side) towards the other side ( Figure 28 When viewed from the upper middle side, the fifth fan 55F is positioned at a location overlapping (crossing over) both the second heat exchanger 42 and the third heat exchanger 43. Similar to the fourth embodiment, when viewed from one side of the housing 60F... Figure 28 (Middle and lower side) towards the other side ( Figure 28 When viewed from the upper middle side, the sixth fan 56F is positioned at a location that overlaps with both the first heat exchanger 41 and the second heat exchanger 42 (the position it crosses over).

[0135] In the cooling device 39F with this structure, the intake airflow of the sixth fan 56F is distributed to the first flow path 81 and the second flow path 82 by the first air guide plate 62F, and the intake airflow of the fifth fan 55F is distributed to the second flow path 82 and the third flow path 83 by the second air guide plate 63F. In this embodiment, the flow rate of the cooling air passing through the oil cooler 41 is the sum of the total amount of airflow flowing through the first flow path 81 and a portion of the airflow flowing through the second flow path 82. Furthermore, the flow rate of the cooling air passing through the radiator 42 is a portion of the airflow flowing through the second flow path 82. The flow rate of the cooling air passing through the intercooler 43 is the sum of the total amount of airflow flowing through the third flow path 83 and a portion of the airflow flowing through the second flow path 82.

[0136] According to the fifth embodiment of the cooling device for construction machinery of the present invention described above, similar to the fourth embodiment described above, the air volume of the cooling air generated by the fifth fan 55F can be distributed to two adjacent flow paths 82, 83 separated by the second air guide plate 63F, and the air volume of the cooling air generated by the sixth fan 56F can be distributed to two adjacent flow paths 81, 82 separated by the first air guide plate 62F, thereby reducing the load deviation generated among the plurality of fans 51, 52, 53, 54, 55F, 56F.

[0137] Furthermore, in this embodiment, one end 62a of the first air guide plate 62F on the heat exchanger assembly 40 side is located on the oil cooler 41 (any one of the multiple heat exchangers 41, 42, 43). One end 63a of the second air guide plate 63F on the heat exchanger assembly 40 side is located on the intercooler 43 (any one of the multiple heat exchangers 41, 42, 43).

[0138] According to this structure, compared to the fourth embodiment where one end 62a of the heat exchanger group 40 side of the first air guide plate 62E is positioned at the boundary between adjacent oil coolers 41 and radiators 42, and the fourth embodiment where one end 63a of the heat exchanger group 40 side of the second air guide plate 63E is positioned at the boundary between adjacent radiators 42 and intercoolers 43, the area where the relative positions of the multiple flow paths 81, 82, 83 of the outer casing 60F and the multiple heat exchangers 41, 42, 43 can be changed can be expanded. Therefore, by changing the relative positions of the multiple flow paths 81, 82, 83 relative to the multiple heat exchangers 41, 42, 43 according to the difference in relative heat exchange capacity between the multiple heat exchangers 41, 42, 43, the load deviation generated among the multiple fans 51, 52, 53, 54, 55F, 56F can be further reduced.

[0139] [Sixth Implementation Method]

[0140] Next, use Figure 29 A sixth embodiment of the cooling device for construction machinery of the present invention will be described. Figure 29 This is a simplified cross-sectional view illustrating the structure of a sixth embodiment of the cooling device for construction machinery according to the present invention. Furthermore, Figure 29 In the middle, symbols and Figures 1 to 28 The symbols shown are identical, so their detailed descriptions are omitted.

[0141] Figure 29 The main difference between the cooling device 39G of the construction machinery according to the sixth embodiment of the present invention and the fifth embodiment is that the structure of the cooling fan assembly 50G is different; and the construction of the outer casing 60G is different according to the structure of the cooling fan assembly 50G.

[0142] Specifically, the cooling fan assembly 50G consists of only one fan 51G. Fan 51G is capable of supplying the airflow necessary to provide all the heat exchange for the multiple heat exchangers 41, 42, and 43. When airflow is drawn from one side of the housing 60G ( Figure 29 (Middle and lower side) towards the other side ( Figure 29 When viewed from the upper middle side, fan 51G is positioned at a location that overlaps with all of the multiple heat exchangers 41, 42, and 43 (the positions it crosses).

[0143] In addition to having the same peripheral wall 61 and mounting wall 69 as the peripheral wall 60F in the fifth embodiment, the outer casing 60G also has a first air guide plate 62G and a second air guide plate 63G arranged in the arrangement direction (transverse direction of the peripheral wall 61) of the three parallel heat exchangers 41, 42, and 43. Similar to the fifth embodiment, the first air guide plate 62G extends from one side of the peripheral wall 61 in its extending direction to the other side (from the heat exchanger group 40 side to the fan 51G side) within the space surrounded by the peripheral wall 61, separating adjacent first flow paths 81 and second flow paths 82. Similarly to the fifth embodiment, the second air guide plate 63G extends from one side of the peripheral wall 61 in its extending direction to the other side within the space surrounded by the peripheral wall 61, separating adjacent second flow paths 82 and third flow paths 83.

[0144] The first air guide plate 62G is set as the end of the heat exchanger group 40 side. Figure 29 The lower end of the middle section (62a) is located in the width direction of the oil cooler 41. Figure 29 The middle part (in the left-right direction). That is, one end 62a of the first air guide plate 62G is positioned at a position offset from the boundary between the adjacent oil cooler 41 and the radiator 42.

[0145] The second air guide plate 63G is configured as the end of the heat exchanger assembly 40 side. Figure 29 The lower end of the middle section (63a) is located in the width direction of the intercooler 43. Figure 29The middle part (in the left-right direction). That is, one end 63a of the second air guide plate 63G is positioned at a position offset from the boundary between the adjacent radiator 42 and the intercooler 43.

[0146] A mounting hole 71G is formed in the mounting wall 69 relative to a fan 51G. The mounting hole 71G extends across the end of the first air guide plate 62G on the side of the cooling fan assembly 50G. Figure 29 The other end 62b of the upper middle end) and the end of the second air guide plate 63G that serves as the cooling fan assembly 50G side ( Figure 29 The fan 51G is formed at the other end 63b of the upper middle end, constituting all the outlets of the three flow paths 81, 82, and 83. That is, the fan 51G is positioned opposite to the other end 62b of the first air guide plate 62G and the other end 63b of the second air guide plate 63F, and spans the other end 62b of the first air guide plate 62G and the other end 63b of the second air guide plate 63F, thus spanning all three flow paths 81, 82, and 83.

[0147] However, generally speaking, fans tend to generate airflow in a direction that is angled relative to the cooling airflow direction relative to the heat exchanger on the side farther from the suction position, while on the side closer to the suction position, the suction force of the fan makes it difficult to generate airflow in a tilted direction. For example, in situations like... Figure 9 In the case where the second flow path 182 lacks a guide vane, the fans 53 and 54 generate a flow Fd in a direction significantly inclined relative to the extension direction of the second flow path 182 (the extension direction of the peripheral wall 61) on one side of the extending direction of the outer casing 160 (the side farther from the suction position). Even if a guide vane is provided upstream of the heat exchangers 41, 42, and 43, because the guide vane is located on the side farther from the suction position of the fans 53 and 54, the airflow generated by the fans 53 and 54 may not be properly distributed to each heat exchanger 41, 42, and 43.

[0148] In contrast, in this embodiment, since a housing 60G with multiple flow paths 81, 82, 83 is provided between the multiple heat exchangers 41, 42, 43 and a fan 51G, the airflow of the cooling air generated by the fan 51G relative to each flow path 81, 82, 83 can be accurately adjusted by adjusting the relative position of the fan 51G and the multiple flow paths 81, 82, 83. Therefore, the airflow of the cooling air passing through the multiple heat exchangers 41, 42, 43 located immediately upstream of the multiple flow paths 81, 82, 83 can be appropriately distributed.

[0149] As described above, the cooling device 39G for construction machinery according to the sixth embodiment of the present invention includes: a housing 60G having a peripheral wall 61; a plurality of heat exchangers 41, 42, 43 arranged side by side in a transverse manner within the housing 60G; and a separate fan 51G arranged opposite to the plurality of heat exchangers 41, 42, 43 and generating cooling air on the heat exchanger assembly 40 side as the suction side for the plurality of heat exchangers 41, 42, 43. The housing 60G has a plurality of air guide plates 62G, 63G extending from the heat exchanger assembly 40 side toward the fan 51G side within the space surrounded by the peripheral wall 61 and arranged in the arrangement direction of the plurality of heat exchangers 41, 42, 43.

[0150] According to this structure, multiple flow paths 81, 82, and 83 are formed between multiple heat exchangers 41, 42, and 43 and a fan 51G by a peripheral wall 61 and multiple air guide plates 62G and 63G. This allows for the accurate adjustment of the distribution of the cooling airflow generated by the individual fan 51G relative to each flow path 81, 82, and 83. Therefore, compared to a structure where multiple flow paths are not formed between multiple heat exchangers 41, 42, and 43 and the fan 51G, the cooling airflow passing through each heat exchanger 41, 42, and 43 located immediately upstream of the multiple flow paths 81, 82, and 83 can be appropriately distributed.

[0151] Furthermore, in this embodiment, the first air guide plate 62G of the outer casing 60G is configured such that one end 62a of the plate is located on the oil cooler 41 (any one of the multiple heat exchangers 41, 42, 43). Furthermore, the second air guide plate 63G of the outer casing 60G is configured such that one end 63a of the plate is located on the intercooler 43 (any one of the multiple heat exchangers 41, 42, 43).

[0152] According to this structure, compared to the fourth embodiment where one end 62a of the first air guide plate 62E is positioned at the boundary between adjacent oil coolers 41 and radiators 42, and the fourth embodiment where one end 63a of the second air guide plate 63E is positioned at the boundary between adjacent radiators 42 and intercoolers 43, the area where the relative positions of the multiple flow paths 81, 82, 83 of the housing 60G and the multiple heat exchangers 41, 42, 43 can be changed can be expanded. Therefore, by changing the relative positions of the multiple flow paths 81, 82, 83 with respect to the multiple heat exchangers 41, 42, 43 according to the difference in relative heat transfer between the multiple heat exchangers 41, 42, 43, the airflow of the cooling air passing through each heat exchanger 41, 42, 43 can be easily adjusted.

[0153] [Other Implementation Methods]

[0154] Furthermore, the present invention is not limited to this embodiment and includes various modifications. The embodiments described above are embodiments that have been explained in detail for ease of understanding of the present invention, and are not limited to having all the structures described. It is possible to replace a part of the structure of a certain embodiment with the structure of another embodiment, and it is also possible to add the structure of another embodiment to the structure of a certain embodiment. Furthermore, it is also possible to add, delete, or replace other structures in a part of the structure of each embodiment.

[0155] For example, in the first to sixth embodiments and variations described above, examples are shown of applying the present invention to the cooling devices 39, 39A, 39B, 39C, 39D, 39E, 39F, and 39G of a hydraulic excavator 1. However, the present invention can be widely applied to the cooling devices of various construction machinery such as hydraulic cranes and wheel loaders.

[0156] Furthermore, in the above embodiments, an example is shown where an electric motor is used as the drive device for each fan of the cooling fan assembly 50, 50D, 50E, 50F, and 50G, but a hydraulic motor or the like can also be used as the drive device.

[0157] Furthermore, in the first to fifth embodiments described above, an example is shown where all the fans in the cooling fan assemblies 50, 50D, 50E, and 50F are of the same specification. However, the multiple fans constituting the cooling fan assembly may also have different shapes, sizes, and other specifications depending on various conditions such as installation space and price.

[0158] Furthermore, in the first to fourth embodiments described above, examples are shown where cooling devices 39, 39A, 39B, 39C, 39D, and 39E include three heat exchangers: an oil cooler 41, a radiator 42, and an intercooler 43. The outer casings 60, 60A, 60B, 60C, 60D, and 60E each have three flow paths 81, 82, and 83 corresponding to the three heat exchangers. However, the present invention can be configured such that the cooling device includes at least two heat exchangers, and the outer casing has the same number of flow paths as the number of heat exchangers. In this case, the number of air guides is determined based on the number of flow paths in the outer casing. For example, when there are two heat exchangers, since there are two flow paths in the outer casing, one air guide is required for the outer casing.

[0159] Furthermore, in the fifth embodiment described above, an example is shown where one end portion 62a of the first air guide plate 62F of the outer casing 60F is positioned offset from the boundary between adjacent oil coolers 41 and radiators 42, and an example is shown where one end portion 63a of the second air guide plate 63F is positioned offset from the boundary between adjacent radiators 42 and intercoolers 43. However, it is also possible to configure it in the same way as in the first to fourth embodiments, with either one end portion 62a of the first air guide plate or one end portion 63a of the second air guide plate positioned on the boundary between adjacent heat exchangers 41, 42 or adjacent heat exchangers 42, 43.

[0160] Furthermore, in the sixth embodiment described above, an example is shown where one end 62a of the first air guide plate 62G of the outer casing 60G is positioned offset from the boundary between the adjacent oil cooler 41 and the radiator 42, and an example is shown where one end 63a of the second air guide plate 63G is positioned offset from the boundary between the adjacent radiator 42 and the intercooler 43. However, it is also possible to configure it in the same way as in the first to fourth embodiments, with one end 62a of the first air guide plate and one end 63a of the second air guide plate located on the boundary between adjacent heat exchangers 41, 42, and 43. That is, multiple heat exchangers 41, 42, and 43 are arranged in a one-to-one correspondence with multiple flow paths 81, 82, and 83 of the outer casing within the openings 81a, 82a, and 83a on one side of each flow path. According to this structure, the air volume of the cooling air flowing in each flow path 81, 82, 83 can be made to correspond approximately one-to-one with the flow rate of the cooling air passing through each heat exchanger 41, 42, 43.

[0161] Symbol Explanation

[0162] 1—Hydraulic excavator (construction machinery); 39, 39A, 39B, 39C, 39D, 39E, 39F, 39G—Cooling device; 41—Oil cooler (heat exchanger); 42—Radiator (heat exchanger); 43—Intercooler (heat exchanger); 51—First fan (fan, second fan); 51G—Single fan; 52—Second fan (fan, second fan); 53, 53D—Third fan (fan, second fan); 54, 54D—Fourth fan (fan, second fan); 55, 55D, 55F—Fifth fan (fan, first fan); 56—Sixth fan (fan, first fan); 56E, 56F—Sixth fan (fan, second fan); 60, 60A, 60B, 60C, 60D, 60E, 60F, 60G—Outer casing; 61—Peripheral wall; 62, 62D, 62E, 62F, 62G—First air guide plate (air guide plate); 62a—One side end (end on the heat exchanger side); 62b—The other side end (end on the fan side); 63, 63A, 63B, 63C, 63D, 63E, 63F, 63G—Second air guide plate (air guide plate); 63a—One side end (end on the heat exchanger side); 63b—The other side end (end on the fan side); 63c, 63d, 63f, 63g—Slits.

Claims

1. A cooling device for construction machinery, comprising: The outer shell has a peripheral wall; Multiple heat exchangers are arranged side-by-side in a manner that traverses the aforementioned housing; and Multiple fans are arranged opposite to the aforementioned multiple heat exchangers and generate cooling air on the heat exchanger side, which becomes the suction side. The cooling device of the aforementioned construction machinery is characterized in that, The aforementioned housing has multiple air guide vanes that extend from the heat exchanger side toward the fan side within the space surrounded by the aforementioned peripheral wall and are arranged in the arrangement direction of the multiple heat exchangers. The ends of the aforementioned multiple air guide plates on the heat exchanger side are located on the boundary of two adjacent heat exchangers or on any one of the aforementioned heat exchangers. On one of the aforementioned air guide plates, a cut is formed from the fan-side end of the air guide plate toward the heat exchanger side, and the end of the air guide plate with the cut on the heat exchanger side is located on the boundary between two adjacent heat exchangers. The aforementioned multiple fans include a first fan and a second fan. The second fan is positioned between the air guide plate adjacent to the peripheral wall or between the multiple air guide plates. The first fan is positioned opposite two adjacent heat exchangers across the plurality of heat exchangers and is configured to enter the aforementioned cutout.

2. The cooling device for construction machinery according to claim 1, characterized in that, The aforementioned cut is formed such that the front edge of the heat exchanger side is located closer to the first fan than the plurality of heat exchangers.

3. The cooling device for construction machinery according to claim 1, characterized in that, The aforementioned air guide plate is inclined such that the end on the fan side is located at a position offset from the end on the heat exchanger side in the arrangement direction of the plurality of heat exchangers.

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