JP2006104943A - Cooling air guiding structure in heat radiating part - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To adjust the cooling air volume introduced into two heat exchangers, in a cooling air guiding part for biasedly arranging a cooling fan on any one side of the two heat exchangers for juxtaposing an air receiving surface on the same plane. <P>SOLUTION: A baffle plate 42 is arranged in a shroud 41 for surrounding a space between the cooling fan 30 and the heat exchangers 21 and 22. The cooling air volume introduced into the other heat exchanger 22 is increased, by allowing cooling air introduced into the shroud 41 on one heat exchanger 21 side being the biased side of the cooling fan to swirl toward the other heat exchanger 22 side, and regulating the cooling air introduced into the shroud 41 on the other heat exchanger 22 side in swirling toward the one heat exchanger 21 side. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a cooling air induction structure for introducing cooling air generated by a cooling fan into a heat exchanger such as a radiator or an oil cooler, and more specifically, an engine such as an oil-cooled engine-driven compressor. The present invention relates to a structure for guiding cooling air in a heat radiating section of a working machine having two heat exchangers such as a radiator that exchanges heat of the cooling water and an oil cooler that exchanges heat of cooling oil of a compressor body.

  Cooling oil used for cooling the cooling water used to cool the engine, etc., and cooling oil used for lubrication of each part, etc. are cooled in devices equipped with heat generating parts that generate heat when the engine or compressor operates. A heat exchanger such as an oil cooler is installed, and the cooling air generated by the cooling fan is passed through the core of the heat exchanger such as the oil cooler or radiator to exchange heat between cooling water and cooling oil with the cooling air. In general, the cooling water or the cooling oil is again introduced into the engine or the like.

  As an example, an engine-driven screw compressor includes a radiator for exchanging heat with cooling water that has cooled the engine that drives the compressor body, a screw rotor that meshes and rotates within the compressor body, and the screw is housed. It is equipped with an oil cooler that exchanges heat between the cooling oil to lubricate and cool between the cylinder inner walls and seal the compression working space formed between them, and introduce cooling air to this radiator and oil cooler The cooling water for cooling the engine and the cooling oil for the compressor body are cooled, and the cooled cooling water and the cooling oil are reintroduced into the heat generation part for the engine and the compressor body, so that these heat generating parts It is comprised so that it can cool.

  As described above, in an engine-driven screw compressor including a radiator and an oil cooler as an example, an oil cooler is disposed upstream with respect to a flow of cooling air generated by a cooling fan, and a radiator is disposed downstream. Are arranged side by side, and the cooling air after the heat exchange that has passed through the oil cooler is introduced into the radiator so that both the cooling oil and the cooling water can be cooled by heat exchange ( (See Patent Documents 1 and 2).

Prior art document information of the present invention includes the following.
JP 2000-213464 A Japanese Patent Laid-Open No. 10-266964

  As shown in the prior art, when the oil cooler and the radiator are arranged side by side with respect to the flow direction of the cooling air, the cooling air introduced to the radiator passes through the oil cooler and is heated. Since the cooling air is warmed after the replacement, the cooling efficiency of the coolant in the radiator is lowered.

  In order to prevent such a decrease in cooling efficiency by the radiator, the oil cooler and the wind receiving surface of the radiator are arranged side by side in parallel on the same plane, and a cooling fan is arranged opposite to the oil cooler and the radiator to cool the cooling air. It is conceivable to arrange the cooling air generated by the fan so that it directly hits both the radiator and the oil cooler. As an example, as shown in FIGS. It is also conceivable to arrange the radiator 22 and the oil cooler 21 in parallel at the position where the opening 15 formed in the partition plate 11 divided into the air chamber 13 is formed.

  In this case, the rotational axis of the axial-flow type cooling fan 30 is placed on the total wind receiving surface of the oil cooler 21 and the wind receiving surface of the radiator 22, that is, on the center line of the opening 15 surface of the partition plate 11. By arranging the core O, a substantially equal amount of cooling air can be introduced to the air receiving surface on the left and right sides of the center line of the opening, thereby efficiently exchanging heat between the radiator 22 and the oil cooler 21. Can do.

  However, depending on the arrangement of various devices in the bonnet 10, the rotation axis O of the cooling fan 30 may not be arranged on the above-described opening center line. For example, as shown in FIG. When the engine 2 is attached to the engine 2, the arrangement of the engine 2 in the bonnet 10 is biased with respect to the center in the width direction in the bonnet 10 in relation to other devices such as the receiver tank 4 and the fuel tank 5. May be detained.

  As described above, when the rotation axis O of the cooling fan 30 is displaced with respect to the center line of the opening 15 and is disposed so as to be biased toward the oil cooler 21 in the illustrated example, it passes through the oil cooler 21. Although the cooling air volume is large and the cooling efficiency of the oil cooler can be improved and the cooling capacity can be afforded, the air volume of the cooling air passing through the end of the radiator 22 (the dotted portion on the right side in FIG. 13) is reduced. As a whole, the cooling air passing therethrough is reduced, the cooling efficiency of the radiator 22 is lowered, and the cooling water cannot be sufficiently cooled.

  On the contrary, when the rotation axis O of the cooling fan 30 is biased toward the radiator 22, the cooling efficiency of the oil cooler 21 is lowered and the cooling oil cannot be sufficiently cooled, and in any case, the cooling oil is efficient. The problem arises that the heat exchange cannot be performed.

  Therefore, the object of the present invention is to arrange the wind receiving surfaces of the two heat exchangers on the same plane, with respect to the center of the total wind receiving surface including the wind receiving surfaces of the two heat exchangers. In the heat dissipating part in which the rotating shaft core of the cooling fan is biased toward one of the heat exchangers, an equal amount of cooling air is introduced to the two heat exchangers, or is distributed by the desired amount. It is an object of the present invention to provide a cooling air guiding structure capable of introducing a cooling air.

In order to achieve the above object, the cooling air induction structure of the present invention surrounds a space between a heat exchanger and an axial-flow type cooling fan 30 to exchange the cooling air generated in the cooling fan 30 with the heat exchange. In the cooling air induction structure with the shroud 41 to be introduced into the vessel,
The wind receiving surfaces of two heat exchangers (the oil cooler 21 and the radiator 22 in the embodiment) are arranged side by side on the same surface, and the total wind receiving surface of the two heat exchangers 21 and 22 is combined. The rotating shaft core O of the cooling fan 30 is arranged so as to be biased toward the heat exchanger (oil cooler 21 in the embodiment) side with respect to the center,
The cooling air introduced into the space on the one heat exchanger 21 side in the shroud 41 allows swirl to flow into the space on the other heat exchanger 22 side, and the other heat exchange in the shroud 41 An air guide plate 42 is provided to restrict swirling of cooling air introduced into the space on the side of the heat exchanger 22 and flowing into the space on the side of the one heat exchanger 21 (Claim 1).

  In the cooling air guiding structure having the above-described configuration, the above-described air guide plate 42 may be provided on a boundary b between the two heat exchangers 21 and 22 (Claim 2).

Further, the air guide plate 42 is formed continuously with the first part 42a provided on the boundary b between the two heat exchangers 21 and 22, and the first part 42a, While forming a substantially L-shape consisting of the second portion 42b provided in the crossing direction,
The air guide plate 30 may be disposed so that the extension of the rotation axis O of the cooling fan 30 is located between the first portion 42a and the second portion 42b.

  With the structure of the present invention described above, in the cooling air guiding structure of the present invention, the cooling air introduced into the shroud 41 on the one heat exchanger 21 side, which is the biased side of the cooling fan 30, is transferred to the other side. The cooling air introduced into the shroud 41 on the other heat exchanger 22 side is restricted from flowing into the space on the one heat exchanger 21 side. Therefore, it is possible to increase the amount of cooling air passing through the other heat exchanger 22 provided on the side opposite to the biasing side of the cooling fan 30 and adjust the arrangement, shape, size, etc. of the air guide plate. Thus, it was possible to provide an induction structure capable of introducing cooling air with a desired distribution to the two heat exchangers 21 and 22.

  In particular, when the air guide plate having the first portion 42a and the second portion 42b is used, the cooling air introduced into the shroud 41 in the space between the first portion 42a and the second portion 42b. Is restricted from flowing out of the space between the first and second portions 42a, 42b, so that the amount of cooling air introduced into one heat exchanger 21 is secured and the other heat exchanger 22 is secured. The amount of cooling air introduced into the system could be increased. As a result, the cooling efficiency of the other heat exchanger 22 could be improved without reducing the cooling efficiency of the one heat exchanger 21.

  Next, embodiments of the present invention will be described below with reference to the accompanying drawings.

Embodiment 1
In FIG. 1, reference numeral 1 denotes an engine-driven oil-cooled compressor having the cooling air guiding structure of the present invention.

  The oil-cooled compressor 1 includes an engine 2, a compressor body 3, a receiver tank 4, a fuel tank 5, and a bonnet 10 that accommodates other devices constituting the compressor.

  The inside of the bonnet 10 is divided into two chambers, an exhaust chamber 13 and an engine chamber 12, by a partition plate 11, and an engine 2 in the engine chamber 12, a compressor main body 3 driven by the engine 2, and a compression A receiver tank 4 for introducing and separating and storing a mixed fluid of cooling oil and compressed air discharged from the machine main body 3 and a fuel tank 5 for storing fuel supplied to the engine 2 are housed.

  The aforementioned partition plate 11 is provided with a rectangular opening 15 that allows the engine chamber 12 and the exhaust chamber 13 to communicate with each other, and heat is exchanged between the cooling water for cooling the engine 2 in the partition plate 11 at the position where the opening 15 is formed. A radiator 22 and an oil cooler 21 that exchanges heat between the cooling oil supplied to the compressor body 3 are attached and arranged in the width direction in the bonnet 10.

  Then, the axial-flow type cooling fan 30 provided in the engine 2 is arranged so that the rotational axis O of the cooling fan 30 is orthogonal to the air receiving surface of the radiator 22 or the oil cooler 21. ing.

  The partition plate 11 is provided with a shroud 41 that surrounds the opening 15 portion on the engine compartment 12 side. The cooling fan 30 is disposed in the shroud 41 and is generated by turning the cooling fan 30. The cooling air is introduced into the two heat exchangers 21 and 22.

  The cooling fan 30 has a center of the total wind receiving surface in which the extension of the rotation axis O is the sum of the wind receiving surface of the radiator 22 and the air receiving surface of the oil cooler 21, that is, the center of the opening 15 of the partition plate 11. On the other hand, it is biased to one side of the radiator 22 or the oil cooler 21 (in the present embodiment, the oil cooler 21 side) and disposed in the above-described shroud 41.

  Further, a suction duct 16 for introducing outside air into the engine chamber 12 is formed on the side wall of the bonnet 10 in the engine chamber 12 described above, and cooling air is provided above the exhaust air chamber 13. Is formed in the hood 10, and the cooling air introduced into the engine compartment 12 through the suction duct 16 by rotating the cooling fan 30 described above is formed in the partition plate 11. Through the opening 15 formed in the heat exchanger, passes through the core of the heat exchanger such as the radiator 22 and the oil cooler 21, reaches the exhaust chamber 13, and the hood 10 through the exhaust port 17 formed above the exhaust chamber 13. Cooling can be performed by heat exchange of cooling water and cooling oil by the radiator 22 and the oil cooler 21 with each device discharged to the outside and housed in the bonnet 10. It is configured.

  With respect to the radiator 22 and the oil cooler 21 arranged as described above, the guide structure for guiding the cooling air to the radiator 22 and the oil cooler 21 has a rotational axis O biased toward the oil cooler 21 as described above. In order to guide the cooling air generated by the cooling fan 30 having the same amount to the oil cooler 21 and the radiator 22 with an equal amount or a predetermined distribution, the air guide for guiding the cooling air introduced into the shroud 41 A plate 42 is provided.

  The arrangement of the air guide plate 42 is relative to the direction of deviation of the cooling fan 30, the direction of swirling of the cooling air generated by the cooling fan 30, and the distribution of the amount of cooling air introduced to the radiator 22 and the oil cooler 21. Although it depends on the relationship, at least the displacement side of the cooling fan 30 is rotated by the rotation of the cooling fan 30 disposed to be deviated toward the heat exchangers 21 and 22 on either side with respect to the center line of the opening 15 of the partition plate 11. While allowing the cooling air introduced into the shroud 41 on the heat exchanger (oil cooler 21 in this embodiment) side to swirl to the other heat exchanger (radiator 22 in this embodiment) side. The cooling air introduced into the shroud 41 on the other heat exchanger (radiator 22) side is directed toward the one heat exchanger (oil cooler 21) side. Restricted to pivot, it is provided in the space in the Sheraudo 41 so as to be perpendicular to the total swept surface.

  In the embodiment shown in FIG. 3, the rotational axis O of the cooling fan 30 is also biased toward the oil cooler 21 side (left side in the figure) with respect to the center line of the opening 15, and the cooling fan In the cooling air introduction part structure 30 in which a swirling flow in the counterclockwise direction is generated in the drawing, the length direction of the air guide plate 42 on the boundary b between the oil cooler 21 and the radiator 22 is defined as the partition plate 11. At the oil cooler 21 side, the lower end 42 'of the air guide plate 42 is terminated at a position above the lower edge 15c of the opening 15 and attached to the lower edge 15c from the upper edge 15a of the opening 15. The cooling air introduced into the shroud 41 swirls and flows into the space on the radiator 22 side through an interval (introduction path 51) provided between the lower edge 15c of the opening 15 and the lower end 42 'of the air guide plate 42. To do The cooling air introduced into the shroud 41 on the radiator 22 side, or the cooling air introduced into the space on the radiator 22 side through the introduction path 51 is swirled so that the space on the oil cooler 21 side is swung. The amount of cooling air passing through the core of the oil cooler 21 is reduced, and the amount of cooling air passing through the core of the radiator 22 is increased.

  In the illustrated example, the above-described air guide plate 42 protrudes from the upper edge 15a of the opening 15 toward the lower edge 15c, and the introduction path 51 is formed on the lower side in the drawing. The formation position differs depending on which direction the cooling fan 30 is deviated with respect to the boundary b between the oil cooler 21 and the radiator 22, and a swirling flow in the counterclockwise direction in the figure is generated as in the case shown in FIG. 3. In this case, when the oil cooler 21 and the radiator 22 are arranged one above the other as shown in FIG. 4A and the cooling fan is biased toward the oil cooler 21 (the lower side in the figure), this guide is used. The wind plate projects from the opening side edge on the left side in the drawing toward the opening side edge on the right side in the drawing, and as shown in FIG. 4 (B), the oil cooler 21 is on the right side in the drawing and the radiator 22 is on the left side in the drawing. Arrangement and cooling fan 3 Is biased toward the oil cooler 21 side (left side in the figure), the air guide plate 42 is projected upward from the lower edge of the opening 15, and further, as shown in FIG. Is arranged on the upper side in the figure, the radiator 22 is arranged on the lower side in the figure, and the cooling fan 30 is arranged on the oil cooler side (upper side in the figure), the direction from the opening side edge on the right side in the figure to the opening side edge on the left side. Thus, the projecting direction of the air guide plate 42 and the positional relationship between the introduction paths 51 are the positional relationship between the cooling fan and the air guide plate when FIG. 3 is rotated.

  Contrary to the illustrated embodiment, when the cooling fan 30 rotates to produce a clockwise swirling flow in the figure, the projecting direction of the air guide plate 42 and the formation position of the introduction path 51 are as shown in FIG. The embodiment described with reference to FIGS. 4 (A) to 4 (C) is vertically and horizontally reversed.

  As described above, the arrangement of the air guide plate 42 in the shroud 41 is determined by the relative relationship between the deflection direction of the cooling fan 30 and the turning direction of the cooling air generated by the rotation of the cooling fan 30. The cooling air introduced into the biased side space is allowed to flow into the space opposite to the biased side space by swirling, while the cooling air introduced into the space opposite to the biasing side is swung away by the swirling side. The present invention is not limited to the illustrated embodiment as long as it can regulate the flow into the space.

  In addition, the formation width | variety of the above-mentioned introduction path 51 can distribute suitably the cooling air volume which passes the core of the oil cooler 21, and the cooling air volume which passes the core of the radiator 22 by adjusting this, FIG. As shown in FIG. 3, the projecting length of the air guide plate 42 is shortened compared to the embodiment described with reference to FIG. 3, or compared with the embodiment described with reference to FIG. 3 as shown in FIG. Thus, the protruding length of the air guide plate 42 may be increased.

  In the embodiment described with reference to FIG. 3, the above-described air guide plate 42 is described as having a longitudinal direction in the figure. If it can guide the flow of the cooling air in 41, it will not be limited to the case where it attaches at right angles with respect to any edge 15a-15d of the opening 15 of the partition plate 11, Even if this attaches it incline Moreover, it is not necessary to be a flat plate as in the embodiment described with reference to FIG. 3, and may be a curved or bent shape, and the arrangement and shape thereof are not limited to the illustrated embodiment.

  When the cooling fan 30 is rotated by the operation of the compressor in the cooling air guiding portion structure including the air guide plate 42 configured as described above, the inside of the engine compartment 12 is introduced from the suction duct 16 formed on the side wall of the bonnet 10. The outside air is sucked into the air and the air in the engine chamber 12 sucked into the axial-flow type cooling fan 30 is introduced into the shroud 41 as cooling air.

  As shown in FIG. 3, the cooling air generated by the axial-flow type cooling fan 30 is swirled around the rotation axis O of the cooling fan 30 as shown in FIG. It flows toward the radiator 22 side, passes through the oil cooler 21, the radiator 22, and the cores of the two heat exchangers, and exchanges heat with cooling water and cooling oil.

  In this way, the cooling air introduced into the inside of the shroud 41 forms a flow that proceeds in the shroud 41 from the cooling fan 30 side toward the heat exchangers 21 and 22 side. Since it flows while turning from the fan 30 toward the heat exchangers 21 and 22, the air guide plate 42 from the upper edge 15a of the opening 15 formed in the partition plate 11 to the lower edge 15c as described above. Is provided so that the cooling air introduced into the space on the oil cooler 21 side in the shroud 41 is introduced between the lower end 42 ′ of the air guide plate 42 and the lower edge 15 c of the opening 15. A part of the air flows into the space on the radiator 22 side through the path 51.

  On the other hand, the cooling air introduced into the space on the radiator 22 side in the shroud 41 is restricted by the air guide plate 42 from flowing into the space on the oil cooler 21 side, and thus passes through the core of the radiator 22. The amount of cooling air can be increased, and as a result, the cooling efficiency of the radiator 22 is improved.

[Embodiment 2]
Next, another embodiment of the present invention will be described with reference to FIG.

  In the embodiment (embodiment 1) described with reference to FIG. 3 described above, the air guide plate 42 is a straight line that hangs downward from the upper edge 15a of the opening 15 formed in the partition plate 11. In the air guide plate 42 of the embodiment shown in FIG. 5, the first portion that hangs the air guide plate 42 downward from the upper edge 15 a of the opening 15 of the partition plate 11 is described. 42a and a second end continuous to the lower end of the first portion 42a and bent toward the side edge of the opening 15 in the biasing direction of the cooling fan 30 (the side edge 15d on the left side in the drawing in the present embodiment). It is made into the substantially L shape which has the part 42b.

  As shown in FIG. 5, the air guide plate 42 thus configured is attached so that the extension of the rotation axis O of the cooling fan 30 is located between the first portion 42a and the second portion 42b. .

  By configuring the shape of the air guide plate 42 in this way, the cooling air flowing in the space surrounded by the first portion 42a and the second portion 42b of the air guide plate 42 is restricted in its turning, It passes through the core of the heat exchanger (oil cooler 21) at the corresponding position.

  That is, the cooling air that collides with the second portion 42b of the air guide plate 42 is reflected by the collision with the air guide plate 42, and is surrounded by the first portion 42a and the second portion 42b of the air guide plate 42. As a result, a sufficient amount of cooling air is secured to the oil cooler 21.

  On the other hand, since a part of the space on the oil cooler 21 side exists outside the space between the first portion 42a and the second portion 42b of the air guide plate 42, the space on the oil cooler 21 side is present. The introduced cooling air flows into the space on the side of the radiator 22 by turning and passes through the core of the radiator 22.

  On the other hand, the cooling air introduced into the shroud 41 on the radiator 22 side tries to flow into the space on the oil cooler 21 side by the turning, and the inflow of the cooling air to the space on the oil cooler 21 side is guided air. As a result, the amount of cooling air passing through the core of the radiator 22 is increased and the cooling efficiency of the radiator 22 can be improved.

  As described above, in the cooling air guiding structure of the present embodiment, the second portion 42 b of the air guide plate 42 passes through the portion of the oil cooler 21 corresponding to the portion surrounded by the air guide plate 42. The cooling air volume is secured to improve the cooling efficiency of the oil cooler 21, and the cooling air volume passing through the radiator 22 is secured by the first portion 42a provided on the air guide plate 42, so that the cooling efficiency of the radiator 22 is improved. It has been improved, and both the oil cooler 21 and the radiator 22 can exhibit high cooling efficiency.

  Note that, in the illustrated embodiment, the second portion 42b of the air guide plate 42 bent in the biasing direction of the cooling fan 30 from the lower end of the first portion 42a of the air guide plate 42 has the tip of the partition plate 11 at its tip. Although the shape is in contact with the side edge 15d of the opening 15, the second portion 42b of the air guide plate 42 is spaced from the tip thereof without contacting the side edge 15d of the opening 15 as shown in FIG. The second portion 42b does not necessarily have to be provided horizontally as shown in FIG. 5, and may be attached with an inclination as shown in FIGS.

  As described above, the length of the second portion 42b is changed so as not to come into contact with the opening edge, or the first angle of the wind guide plate 42 is changed by changing the mounting angle of the second portion 42b of the wind guide plate 42. By changing the area of the portion surrounded by the portion 42a and the second portion 42b, the amount of cooling air flowing into the space on the radiator 22 side from the space on the oil cooler 21 side is adjusted, and passes through the two heat exchangers. It is possible to appropriately distribute the cooling air volume.

  Next, cooling in the case where the cooling air induction structure provided with the above-described air guide plate and the cooling air induction structure not provided with the air guide plate are employed in the heat radiation portion of the engine-driven screw compressor The comparative test results comparing the efficiency are shown below.

  In addition, the thermal radiation part in the engine drive type oil-cooled compressor used for the following comparative tests is as follows, respectively.

〔Measuring method〕
A radiator and an oil cooler are arranged side by side at the opening forming position of the partition plate in which the rectangular opening is formed so that the sum of the wind receiving surfaces is substantially the same size as the opening formed in the partition plate. The fan is biased to the oil cooler side, and the cooling water temperature in the radiator for each of the state where the air guide plate is attached (Examples 1 and 2) and the state where the air guide plate is not attached (Comparative Example), and The temperature of the compressed air discharged from the compressor body was measured.

  The cooling water temperature and the discharge air temperature shown in the table below are the temperatures when the outside air temperature is converted to 20 ° C., and the cooling water temperature and the discharge air temperature are measured in the operating state of the compressor. And when the discharge air temperature was stable.

  In Examples 1 and 2 and the comparative example, a flat air guide plate is arranged in the state of FIG. 3 (Example 1), and L-shaped (the horizontal part and the vertical part intersect at right angles). It is the example (Example 2) which has arrange | positioned the wind guide plate in the state of FIG. 5, and the example (comparative example) which does not provide the wind guide plate.

〔Measurement result〕
Table 1 shows the measurement results in the above comparative test.

  As is clear from the above measurement results, in Example 1, the cooling water temperature could be reduced by 5 ° C. compared to the comparative example by providing the air guide plate. On the other hand, it was confirmed that the discharge air temperature rose by 2 ° C. compared to the comparative example.

  From this, when the air guide plate of Example 1 is provided, the cooling air amount passing through the radiator is increased and the cooling efficiency of the radiator is improved, while the cooling air amount passing through the oil cooler is decreased, It is considered that the discharge air temperature discharged from the compressor main body increased as a result of the cooling efficiency in the oil cooler decreasing.

  On the other hand, when the air guide plate of Example 2 was provided, the temperature of the cooling water could be reduced by 5 ° C. compared to the comparative example by providing the vertical portion of the air guide plate as in Example 1. In addition, the discharge air temperature could be maintained equal to the discharge air temperature in the comparative example without increasing the discharge air temperature.

  As described above, in the air guide plate of the second embodiment, the amount of cooling air passing through the radiator is increased while securing the amount of cooling air passing through the oil cooler in the space surrounded by the first portion and the second portion. Therefore, it is considered that the cooling water temperature could be lowered without increasing the discharge air temperature, and the amount of cooling air introduced into the oil cooler and the radiator can be appropriately adjusted depending on the shape and arrangement of the air guide plate. Was confirmed.

FIG. 3 is a schematic perspective plan view of a compressor having a cooling air guiding structure. The schematic perspective left view of a compressor provided with the induction structure of cooling air. FIG. 3 is a cross-sectional view taken along line AA in FIG. 2. It is a figure explaining the correspondence of the deflection direction of a cooling fan, and the attachment position of a baffle plate, (A) is downward, (B) is the right, (C) is the upper example, respectively. It is. The AA sectional view taken on the line of FIG. 2 which shows the modification of an air guide plate. The AA sectional view taken on the line of FIG. 2 which shows the modification of an air guide plate. The AA sectional view taken on the line of FIG. 2 which shows the modification of an air guide plate. The AA sectional view taken on the line of FIG. 2 which shows the modification of an air guide plate. The AA sectional view taken on the line of FIG. 2 which shows the modification of an air guide plate. The AA sectional view taken on the line of FIG. 2 which shows the modification of an air guide plate. The schematic perspective plan view of the compressor provided with the induction structure of the cooling air which does not have an air guide plate. The schematic see-through left view of the compressor provided with the induction structure of the cooling air which does not have an air guide plate. AA line sectional view of Drawing 12.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Compressor 2 Engine 3 Compressor body 4 Receiver tank 5 Fuel tank 10 Bonnet 11 Partition plate 12 Engine chamber 13 Exhaust chamber 15 Opening (partition plate)
15a Upper edge (opening)
15b Right edge (opening)
15c Lower edge (opening)
15d Left edge (opening)
16 Suction duct 17 Ventilation port 21 Heat exchanger (oil cooler)
22 Heat exchanger (radiator)
30 Cooling fan 41 Shroud 42 Wind guide plate 42 'Lower end (of the wind guide plate)
42a First part (of the air guide plate)
42b Second part (of the air guide plate)
51 Introducing path b Boundary (oil cooler and radiator)
O Rotating shaft core (for cooling fan)

Claims (3)

In the cooling air induction structure including a shroud that surrounds the space between the heat exchanger and the axial flow type cooling fan and introduces the cooling air generated by the cooling fan to the heat exchanger,
The air receiving surfaces of the two heat exchangers are arranged side by side on the same surface, and are biased toward one of the heat exchangers with respect to the center of the total air receiving surface including the air receiving surfaces of the two heat exchangers. And arrange the rotation axis of the cooling fan,
The cooling air introduced into the space on the one heat exchanger side in the shroud allows swirling to flow into the space on the other heat exchanger side, and the space on the other heat exchanger side in the shroud An induction structure for cooling air in a heat dissipating part, characterized in that an air guide plate is provided for restricting swirling of the cooling air introduced into the space on the one heat exchanger side.   The induction structure of cooling air in the heat radiating section according to claim 1, wherein the air guide plate is provided on a boundary between the two heat exchangers. A first portion provided on the boundary between the two heat exchangers, and a second portion formed continuously with the first portion and in a direction intersecting the boundary. A substantially L-shape consisting of
The structure for guiding cooling air in a heat radiating portion according to claim 1, wherein the air guide plate is disposed so that an extension of a rotation axis of the cooling fan is located between the first portion and the second portion.

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