JP2005061276A - Engine driven work machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce cost by facilitating an cleaning operation, cooling a radiator and a heat exchanger in a balanced manner, enhance a heat exchanging efficiency of the heat exchanger, and reducing the burden of a component management of the heat exchanger. <P>SOLUTION: This engine driven work machine comprises: an engine E; a work machine body C driven by the engine E; a cooling fan 2; the radiator 3 having a heat radiating surface 3a arranged so as to face the cooling fan 2; and the heat exchangers 10 and 20 arranged side by side to the radiator 3. The heat radiators 10 and 20 are divided and arranged to be at least positions which are symmetrical, of an edge side of the heat radiating surface 3a of the radiator 3, with the radiator 3 of being as a center. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an engine-driven work machine capable of realizing a well-balanced cooling between a radiator and a heat exchanger.

  Conventional engine-driven work machines (for example, a compressor, a generator, and a welder) are known in which a work machine body driven by an engine is housed in a soundproof case or the like in order to reduce noise. One of the compressors is required to be equipped with an oil cooler for cooling the lubricating oil. On the other hand, in general, engine-driven work machines are required to comply with environmental standards. When a large engine is installed, it is necessary to equip a heat exchanger such as an aftercooler or an intercooler to comply with exhaust gas regulations. In addition, oil coolers for cooling engine oil are often used with higher engine output.

  Various structures have been proposed for cooling heat exchangers such as these oil coolers, aftercoolers, and intercoolers. FIG. 9 is a schematic side view showing an example of the structure. An oil cooler A as a heat exchanger is provided inside the soundproof case K so as to face the radiator R. From the direction of the engine E, FIG. A so-called serial arrangement structure in which an air cooler AR, an engine fan F, a radiator R, and an oil cooler A are sequentially provided (see, for example, Patent Document 1). FIG. 10 is a schematic plan view showing another structure, in which an oil cooler A as a heat exchanger and a radiator R are arranged in parallel in the width direction so as to face the engine fan F, respectively. It has an arrangement structure (see, for example, Patent Document 2).

  Each of these engine-driven work machines sucks air from the outside of the engine-driven work machine by the engine fan F and blows it as cooling air to the oil cooler A and the radiator R, and the oil cooler A and the radiator R cool down. It is configured to be.

By the way, since such an engine-driven work machine is often used outdoors such as a construction site, dust is often mixed in the cooling air. For this reason, dust easily adheres to the core portion of the oil cooler A and the radiator R. If the state is left as it is, it may cause overheating of the engine E and early deterioration of the lubricating oil. Cleaning work is performed for the purpose of removal.
JP 2001-263964 (paragraphs 0011 to 0013, FIG. 1) JP 2001-355445 A (paragraphs 0037 to 0038, FIG. 4)

  In the engine-driven work machine having the conventional serial arrangement structure shown in FIG. 9, the cooling air that has passed through the oil cooler A is configured to pass through the radiator R, so that the cooling air is uniform in the oil cooler A and the radiator R. In the situation where the distance between the engine fan F and the radiator R, or the distance between the radiator R and the oil cooler A is narrow, There is a problem that it is difficult to clean the dust adhering to the fin portion of the heat radiating surface A1 of the oil cooler A.

  On the other hand, the engine-driven work machine having the conventional parallel arrangement structure shown in FIG. 10 has the advantage that a relatively large space around the radiator R and the oil cooler A can be secured and the cleaning work is easy to perform. However, as described below, the radiator R and the oil cooler A have a problem that it is difficult to realize a well-balanced cooling.

  That is, the one shown in FIG. 10 is arranged so that the center of the rotating shaft of the engine fan F is located at the boundary between the radiator R and the oil cooler A, and the cooling air is substantially uniformly distributed to both. Although it is configured to blow air, the radiator R and the oil cooler A usually have different heat exchange amounts. For this reason, as described above, there is a problem that it is difficult to achieve a cooling balance even if the cooling air is blown almost uniformly to both. Further, depending on the model, there is a case where the engine fan F is biased and arranged on the radiator R side or the oil cooler A side depending on the layout of each device in the soundproof case. Cooling balance with oil cooler A was difficult.

  Further, in the engine-driven work machine shown in FIG. 10, in order to reduce the cost by omitting the upper tank, a so-called two-pass structure in which the oil flow path A2 as shown in FIG. 11 is formed in an inverted U shape. The oil cooler A was mainly used. However, such an oil cooler A has a structure in which the oil inlet A3 and the outlet A4 are arranged close to each other, and therefore, between the vicinity of the inlet A3 through which the high temperature oil passes and the vicinity of the outlet A4 through which the low temperature oil passes. In this case, heat exchange was performed between the two, and the problem of reduced efficiency was likely to occur.

  By the way, there are various types of engine-driven work machines, ranging from small to large, and as a heat exchanger (oil cooler A, etc.) attached to each model, appropriate heat exchange that matches the capacity of the work machine. It was necessary to use one with a quantity. For this reason, it is necessary to prepare a large number of heat exchangers, and there is also a problem that parts management for that purpose is complicated and expensive.

Then, the subject of this invention is providing the engine drive working machine which can cool a radiator and a heat exchanger with sufficient balance, which is easy to perform a cleaning operation.
Another object is to provide an engine-driven work machine capable of improving the heat exchange rate of the heat exchanger.
Furthermore, another problem is to provide an engine-driven work machine that can reduce the burden of component management of a heat exchanger and can reduce costs.

  In order to solve the above problem, an engine-driven work machine according to claim 1 is provided with an engine, a work machine body driven by the engine, a cooling fan, and a heat dissipation surface facing the cooling fan. In the engine-driven work machine including the radiator arranged as described above and the heat exchanger arranged in parallel with the radiator, the heat exchanger is centered on the radiator and is on the edge side of the radiator heat dissipation surface. It is characterized by being divided and arranged at least in a symmetrical position.

  Here, the heat exchanger includes all air-cooled heat exchangers such as an oil cooler, an air supply cooler such as an intercooler or an aftercooler.

According to this engine-driven work machine, the heat exchanger is divided and arranged at least symmetrically on the side of the edge of the heat radiating surface of the radiator with the radiator as the center, so the heat exchanger divided and arranged with the radiator Is a so-called parallel arrangement structure. Therefore, there is an advantage that the radiator and the heat exchanger can be easily cleaned.
Further, since the heat exchangers are divided and arranged, the region occupied by the heat exchanger can be dispersed in the flow of the cooling air, and accordingly, the flow of the cooling air can be improved. In addition, since the heat exchanger is divided and arranged around the radiator, the cooling air flows in a balanced manner with respect to the radiator and the heat exchanger. Therefore, it is possible to achieve cooling with a good balance between the radiator and the heat exchanger as compared with a simple parallel arrangement. And since the heat exchanger is divided and arranged at least in a symmetrical position on the side of the edge of the heat radiating surface of the radiator with the radiator as the center, for example, a cooling fan is arranged at the center position in the width direction of the radiator As a result, the cooling air is supplied almost uniformly to the heat exchangers arranged in a divided manner. Therefore, the structure is simplified and the cost of the engine-driven work machine is prevented from increasing.

  The engine-driven work machine according to claim 2 is the engine-driven work machine according to claim 1, wherein the heat exchanger has a flow path of the heat medium flowing in the heat exchanger from one to the other. It is configured to flow in the direction.

  According to this engine-driven work machine, since the flow path of the heat medium flowing in the heat exchanger is unidirectional from one side to the other, it flows in the heat exchanger like a conventional heat exchanger. It is possible to avoid a structure in which the inlet side and the outlet side of the heat medium are arranged close to each other. Therefore, a situation in which the heat medium having a high temperature and the heat medium having a low temperature mutually exchange heat in the heat exchanger does not occur, thereby preventing a decrease in heat exchange rate. And since the heat exchanger is divided and arrange | positioned, the malfunction that heat exchange is performed between heat exchangers does not arise.

  The engine-driven work machine according to claim 3 is the engine-driven work machine according to claim 1 or 2, wherein the heat exchanger can be appropriately combined and removed from a plurality of types having different heat exchange amounts. It is characterized by being.

According to this engine-driven work machine, heat exchangers can be attached in appropriate combinations from a plurality of types with different heat exchange amounts, and heat exchangers with different heat exchange amounts can be obtained by changing the combination of heat exchangers. It can be provided. Thereby, it is not necessary to prepare a dedicated heat exchanger for each model, and various engine-driven work machines from small to large can be supported by changing the combination. Therefore, it is possible to reduce the burden of managing the parts of the heat exchanger, reduce the cost, and realize excellent economic efficiency.
In addition, since the heat exchanger is provided so as to be attachable / detachable, it can be replaced with a heat exchanger having a different product specification after the heat exchanger is attached, and the specification change can be flexibly dealt with.

  The engine-driven work machine according to claim 4 is the engine-driven work machine according to any one of claims 1 to 3, wherein the radiator has a heat dissipation surface opposite to a side facing the cooling fan. On the side, a radiator air volume adjusting device that adjusts an air volume passing through the radiator is provided.

According to this engine-driven work machine, it is possible to adjust the passing air amount of the radiator by the radiator air amount adjusting device, and thereby to adjust the heat exchange amount of the radiator. Further, by adjusting the passing air amount of the radiator by the radiator air amount adjusting device, the passing air amount in the heat exchanger divided and arranged around the radiator is also relatively adjusted, and accordingly, the radiator and the heat exchanger The amount of passing air can be adjusted in a well-balanced manner.
In addition, since the radiator air volume adjusting device is provided on the heat radiation surface opposite to the side facing the cooling fan in the radiator, a space for providing the radiator air volume adjusting device is relatively easily secured. It becomes easy to perform adjustment work and cleaning work.

  The engine-driven work machine according to claim 5 is the engine-driven work machine according to any one of claims 1 to 4, wherein the side facing the cooling fan in at least one of the heat exchangers. A heat exchanger air volume adjusting device that adjusts the air volume passing through the heat exchanger is provided on the heat radiating surface opposite to the heat exchanger surface.

According to this engine-driven work machine, it is possible to adjust the passing air volume of the heat exchanger by the heat exchanger air volume adjusting device, thereby adjusting the heat exchange volume of the heat exchanger. In addition, by adjusting the air flow rate of the heat exchanger using the heat exchanger air flow rate adjusting device, the air flow rate of the radiator is also relatively adjusted. Therefore, the air flow rate between the radiator and the heat exchanger is balanced. Can be adjusted.
Moreover, since the air volume adjusting device for heat exchanger is provided on the heat radiating surface opposite to the side facing the cooling fan in the heat exchanger, a space for providing the air volume adjusting device for heat exchanger is relatively secured. It becomes easy to perform adjustment work and cleaning work.

According to the engine-driven work machine of the present invention, it is easy to clean the radiator and the heat exchanger, and it is possible to cool the radiator and the heat exchanger in a well-balanced manner.
Further, the heat exchange rate of the heat exchanger can be improved, and further, the burden of managing the parts of the heat exchanger can be reduced, and the cost can be reduced.

  Hereinafter, an engine-driven work machine according to an embodiment of the present invention will be described in detail with reference to the drawings. In the description of each embodiment, the same reference numerals are used for the same components, and duplicate descriptions are omitted. In each embodiment, an engine-driven compressor (hereinafter referred to as a compressor) will be described as an engine-driven work machine.

(First embodiment)
In the drawings to be referred to, FIG. 1 is a partial cross-sectional view showing the internal structure of the compressor according to the first embodiment of the present invention, (a) is a schematic plan view, and (b) is a schematic side view. FIG. 2C is a schematic front view. 2A and 2B are views showing the main part, wherein FIG. 2A is a plan view, FIG. 2B is a front view, and FIG. 2C is a cc cross-sectional view of FIG. In the following description, “front” refers to the front frame X1 side of the soundproof case K centering on the engine E shown in FIG. 1A, and “rear” refers to the rear of the soundproof case K. The frame X2 side is referred to, and the “left and right” refers to the side frames X3 and X3 side in the soundproof case K. Further, the upstream and downstream of the cooling air is based on the flow of the cooling air from the inlet K1 of the rear frame X2 to the air outlet K2 near the front frame X1.

  1, the compressor 1 of the present embodiment is surrounded by a soundproof case K, and includes an engine E and a compressor main body C as a working machine main body driven by the engine E. , A cooling fan 2 and a radiator 3 through which cooling air flows from the cooling fan 2. As a heat exchanger for cooling the oil for the compressor body C, on the left and right sides of the radiator 3, The first and second oil coolers 10 and 20 are divided and arranged so as to be detachable. As shown in FIG. 2B, the upper portion of the radiator 3, the upper portions of the first and second oil coolers 10 and 20, and one side thereof are partitioned by a partition plate 6 so as not to allow ventilation.

Details will be described below.
As shown in FIG. 1A, the compressor body C is provided at the rear end Eb of the engine E, and is driven by an output shaft (not shown) at the rear of the engine E. The compressor body C is supplied with oil cooled through the first and second oil coolers 10 and 20 from the receiver tank 4 disposed on the side of the compressor body C for lubrication and cooling. Is done. Compressed air containing oil is discharged from the compressor body C toward the receiver tank 4, and the oil is separated from the compressed air in the receiver tank 4 and collected in the receiver tank 4. The compressed air from which the oil has been removed is supplied to the consumer via a service valve (not shown).

The cooling fan 2 is attached to the front end Ea of the engine E. In this embodiment, the cooling fan 2 is driven to rotate from an output shaft (not shown) at the front of the engine E via a drive pulley, a transmission belt, and a driven pulley. It has become. The cooling fan 2 is not limited to be driven to rotate by an output shaft (not shown) of the engine E, but may be driven to rotate using an electric motor or the like that is separate from the engine E. Thus, when an electric motor is used as a drive source for the cooling fan 2, the engine E and the cooling fan 2 can be separated from each other, so that the degree of freedom in the internal layout of the compressor 1 can be increased.
When the cooling fan 2 is driven to rotate, the outside air serving as cooling air is supplied to the suction port K1 provided in the rear frame X2 of the soundproof case K or the side frame X3, as shown in FIGS. It is sucked into the soundproof case K from a suction port (not shown in FIG. 1B) provided in X3. The cooling air passes through the downstream radiator 3 and the first and second oil coolers 10 and 20, and then, as shown in FIG. 1B, the soundproof case from the air outlet K2 near the front frame X1. It is designed to be discharged outside K.

The radiator 3 is formed in a thin rectangular plate shape, and is for cooling the cooling water of the engine E. As shown in FIG. As shown in FIG. 2B, the rotation shaft of the cooling fan 2 is arranged so that the center of the rotation axis is positioned on the substantially center line O1 in the left-right direction. That is, the cooling air from the cooling fan 2 is almost uniformly ventilated over the entire heat radiating surface 3 a of the radiator 3.
As shown in FIGS. 1A, 1B and 2A, 2C, a shroud 2b is provided between the cooling fan 2, the radiator 3, and the first and second oil coolers 10, 20. The cooling fan 2 faces the opening at the rear part (upstream side). The shroud 2b serves as an air guide path for guiding the cooling air to the radiator 3 and the first and second oil coolers 10 and 20 through the cooling fan 2. The shape of the shroud 2b is a cooling function in a plan view. The fan 2 is tapered toward the downstream side. Therefore, the entire amount of the cooling air sucked into the soundproof case K by the cooling fan 2 is guided to the radiator 3 and the first and second oil coolers 10 and 20 through the shroud 2b.
A fan cover 2a is provided at the rear (upstream side) of the shroud 2b so as to surround the cooling fan 2. As shown in FIG. 2 (c), the fan cover 2a includes a slit 2c formed to a size that does not allow a finger of an operator's hand to enter. Coolant air can be passed through the slit 2c. It is possible. As shown in FIG. 2A, a reserve tank 3c for the coolant of the radiator 3 is provided on the side of the fan cover 2a. The CFC and frame X1n shown in FIG.

The first and second oil coolers 10, 20 are formed in a thin rectangular shape and have a plurality of flat hollow oil passages with fins, as shown in FIGS. 2 (a) and 2 (b). Furthermore, it attaches to each side of edge part 3b, 3b (right-and-left edge part) of the thermal radiation surface 3a of the radiator 3 which becomes a symmetrical position centering on the radiator 3 via a cushioning material 4, 4 having sealing properties. It has been. In the present embodiment, the first and second oil coolers 10 and 20 having the same specifications are used.
As shown in FIG. 2 (a), the first and second oil coolers 10 and 20 have communication ports 10b and 20b provided in the upper tanks 10a and 20a, each having a U-shaped connection pipe 30 in plan view. As shown in FIG. 3, oil as a heat medium flowing inside flows from the first oil cooler 10 to the second oil cooler 20 through the connection pipe 30 as shown in FIG. 3. Is configured to do. The connection pipe 30 is provided so as to be attachable to and detachable from the connection ports 10b and 20b by connection means such as screwing.

  As shown in FIG. 2A, the heat radiating surfaces 10 c and 20 c (upstream side) of the first and second oil coolers 10 and 20 are substantially flush with the heat radiating surface 3 a (upstream side) of the radiator 3. Is arranged. Further, as shown in FIG. 2B, the end portions 2e of the blades 2d of the cooling fan 2 are opposed to the heat radiation surfaces 10c and 20c of the first and second oil coolers 10 and 20, respectively. . Thereby, the cooling air from the cooling fan 2 is directly supplied to the heat radiation surfaces 10c, 20c of the first and second oil coolers 10, 20.

  The first and second oil coolers 10 and 20 are divided and arranged at least symmetrically on the side of the upper and lower and right and left edges (left and right edges 3b and 3b) of the heat radiating surface 3a with the radiator 3 as the center. For example, it is provided on the side of the upper edge and the lower edge of the heat radiating surface 3a, or the side of the upper edge and the left and right edges, the lower edge and the right and left edges. You may provide with respect to the side.

Next, referring to FIGS. 2 (a) and 2 (b), the mounting structure of the first and second oil coolers 10, 20 will be described. The upper portions of the first and second oil coolers 10 and 20 are held by upper covers 5 and 5, and the upper covers 5 and 5 are formed in screw holes (not shown) of the partition plate 6 by a plurality of bolts 5 a. Screwed and fixed. The lower portions of the first and second oil coolers 10 and 20 are engaged with a groove portion (not shown) provided on the floor surface of the soundproof case K (see FIG. 1B), so that the soundproof case is obtained. It is designed to be detachably fixed to the K floor. Accordingly, the screwing of the plurality of bolts 5a is released, the upper covers 5 and 5 are removed from the partition plate 6, and the first and second oil coolers 10 for the groove portions (not shown) provided on the floor surface of the soundproof case K. The first and second oil coolers 10 and 20 can be detached from the left and right sides of the radiator 3 by releasing the engagement at the lower part of the radiator 3. The first and second oil coolers 10 and 20 may be fixed to the floor surface of the soundproof case K by bolts.
Further, by removing the connecting pipe 30 connecting the first and second oil coolers 10 and 20 and the inlet pipe 11b and outlet pipe 21b of the lower tanks 11a and 21a, the first and second oil coolers 10, It is also possible to remove or attach any one of 20 individually. Thus, since the 1st, 2nd oil coolers 10 and 20 are comprised so that attachment or detachment is possible with respect to the soundproof case K, it replaces | exchanges with the other oil cooler from which a heat exchange amount differs so that it may mention later. Is also possible.

Here, the flow path of the oil flowing through the first and second oil coolers 10 and 20 will be described with reference to FIG. 3. As described above, the oil flows from the first oil cooler 10 through the connection pipe 30. A one-way path of flowing to the second oil cooler 20 is followed.
Specifically, oil sent by pressure feeding by an oil pump (not shown) or the compressor main body C first flows into the core 12 from the inlet pipe 11b of the lower tank 11a of the first oil cooler 10, and then the upper tank. The fluid flows from the communication port 10b of 10a through the connecting pipe 30 to the upper tank 20a from the communication port 20b of the second oil cooler 20. Then, it flows in the core 22 of the second oil cooler 20 and reaches the outlet pipe 21b of the lower tank 21a. Thereafter, the oil is returned to the compressor body C through the return pipe H as shown in FIG.

By the way, in general, the heat exchange amount of the oil cooler can be made different by changing the specifications such as the fin pitch and the thickness and length of the pipe. FIGS. 4A to 4D are schematic views showing examples of oil coolers having different specifications from the first and second oil coolers 10 and 20, and the first and second oil coolers 10 and 20. Instead, it can be attached to the sides of the edges 3b, 3b of the radiator 3 shown in FIGS. 2 (a) and 2 (b).
The oil cooler 13 shown in FIG. 4A has a heat radiating surface 13a narrower than the first and second oil coolers 10 and 20 (see FIG. 2B), and the heat exchange amount accordingly. The specifications are few. Note that a partition plate 13b is attached to the oil cooler 13 in order to compensate for a portion where the heat radiation surface 13a is narrowly formed.
Further, the oil cooler 14 shown in FIG. 4B has a heat radiating surface 14a wider than the oil cooler 13 shown in FIG. 4A, and the amount of heat exchange is larger than that of the oil cooler 13. There are many specifications. In addition, a partition plate 14b is attached to this as necessary.
Furthermore, the oil cooler 15 shown in FIG. 4C has a heat radiating surface 15a that is longer (wider) than the first and second oil coolers 10 and 20 (see FIG. 2B). Therefore, the heat exchange amount is larger than that of the first and second oil coolers 10 and 20.
Further, the oil cooler 16 shown in FIG. 4 (d) has a heat radiation surface 16a narrower than the oil cooler 15 shown in FIG. 4 (c). There are few specifications. Note that a partition plate 16b is attached to this as necessary.

  By installing these oil coolers 13 to 16 in place of one or both of the first and second oil coolers 10 and 20 shown in FIGS. 2 (a) and 2 (b), heat of the oil cooler of the compressor 1 can be obtained. The exchange amount can be different.

The first and second oil coolers 10 and 20 and the oil coolers 13 to 16 that can be exchanged with the first and second oil coolers 13 and 16 are formed with thicker dimensions in the front-rear direction as shown in FIGS. It can also be set as the specification which increased the quantity from the standard thing (the oil coolers 13-16 are not shown in figure). FIG. 5 (a) shows a state when the first oil cooler 10 side is formed thick, and FIG. 5 (b) shows a state when the second oil cooler 20 side is formed thick. Show. The first and second oil coolers 10 and 20 having such a thick dimension in the front-rear direction can be attached within a space allowed on the downstream side of the first and second oil coolers 10 and 20. . Contrary to this, the first and second oil coolers 10 and 20 and the oil coolers 13 to 16 exchangeable with the first and second oil coolers 13 to 16 are formed so as to be thin in the front-rear direction so that the heat exchange amount is smaller than the standard one. The specification can also be reduced.
As shown in FIGS. 1A and 1B, the side frames X3 and X3 on the left and right sides of the first and second oil coolers 10 and 20 are provided with inspection ports T and T with lids. It has been. The inspection ports T and T have such a size that the radiator 3 and the first and second oil coolers 10 and 20 can be inspected or cleaned. , T can be used to discharge dust and the like.

The compressor 1 of this embodiment is configured as described above, and the flow of cooling air is as follows.
1 (a) and 1 (b), when an operation switch (not shown) of the compressor 1 is turned on and the engine E is driven, the cooling fan 2 is driven to rotate and cool into the soundproof case K from the suction port K1 and the like. Air is inhaled. The cooling air sucked into the soundproof case K passes through the cooling fan 2, is guided by the shroud 2 b, and is almost uniformly blown around the radiator 3 to the first and second oil coolers 10 and 20. The Thereafter, the cooling air passes through the radiator 3 and the first and second oil coolers 10 and 20 and is discharged from the exhaust port K2 to the outside of the soundproof case K.

In such a flow of cooling air, the compressor 1 includes an oil cooler serving as a heat exchanger divided into first and second oil coolers 10 and 20, thereby allowing a cooling air passage region. As a result, the flow of cooling air can be improved accordingly.
The first and second oil coolers 10 and 20 are divided and arranged on the left and right sides of the heat radiating surface 3a of the radiator 3 (sides of the edges 3b and 3b), which are symmetrical with respect to the radiator 3. Therefore, as shown in FIG. 2 (b), the cooling fan 2 is arranged at the center position of the radiator 3, so that the first and second oil coolers 10 and 20 arranged separately are arranged. The cooling air is ventilated almost evenly. Therefore, it is possible to achieve a well-balanced cooling between the radiator 3 and the first and second oil coolers 10 and 20. Further, since the first and second oil coolers 10 and 20 have a simple configuration in which the first and second oil coolers 10 and 20 are divided and arranged at symmetrical positions with respect to the radiator 3, the cost of the soundproof case K of the compressor 1 is prevented from being increased. You can also

  In addition, the radiator 3 and the first and second oil coolers 10 and 20 are arranged in parallel, and cooling air is simultaneously vented to the radiator 3 and the first and second oil coolers 10 and 20. Therefore, unlike the case of the so-called serial arrangement structure, the cooling air that has passed through one side does not pass through the other, and efficient cooling of the first and second oil coolers 10 and 20 is realized. be able to.

Further, as shown in FIG. 3, the oil flowing through the first and second oil coolers 10 and 20 is configured to flow in one direction through the first and second oil coolers 10 and 20, respectively. In the conventional oil cooler, there is no case where the oil having a high temperature and the oil having a low temperature exchange heat with each other. Therefore, the compressor 1 in which the reduction of the heat exchange rate is prevented is obtained. Moreover, since the first and second oil coolers 10 and 20 are separated from each other, there is no problem that heat exchange is performed between the first and second oil coolers 10 and 20. . Further, since the radiator 3 and the first and second oil coolers 10 and 20 are arranged side by side, there is an advantage that the dust adhering to the heat radiating surfaces 3a, 10a and 20a can be easily cleaned. can get.
In addition, the radiator 3 and the first and second oil coolers 10 and 20 can be inspected or cleaned through the inspection ports T and T provided in the side frames X3 and X3. Combined with the configuration in which the oil coolers 10 and 20 are arranged in parallel, there is an advantage that the cleaning operation is easier to perform. The shroud 2b may be configured to be splittable in the vertical direction or the horizontal direction in order to simplify the cleaning work.

Furthermore, since the first and second oil coolers 10 and 20 are detachably provided, for example, they are replaced with oil coolers 13 to 16 having different heat exchange amounts as shown in each figure of FIG. Can do.
In this case, the oil coolers can be freely combined as appropriate, and the combination can correspond to the compressor 1 having various capacities. For example, if three types (a, b, c) of oil coolers having different heat exchange amounts are prepared, the combination modes are (a + a), (b + b), (c + c), (a + b), (a + c). , (B + c), for a total of six types.
Thereby, it is not necessary to prepare a dedicated oil cooler for each model, and various compressors 1 from small to large can be supported by changing the combination.
Therefore, it is possible to reduce the burden of managing the parts of the oil cooler, to reduce the cost, and to realize excellent economic efficiency.

  Further, since the first and second oil coolers 10 and 20 are detachably provided, even after the first and second oil coolers 10 and 20 are attached, for example, 4 can be replaced with oil coolers 13 to 16 having different heat exchange amounts as shown in each drawing, and therefore, it is possible to flexibly cope with a change in the specifications of the compressor 1.

In this embodiment, as shown in FIG. 2A, the heat radiating surfaces 10c, 20c of the first and second oil coolers 10, 20 are substantially flush with the heat radiating surface 3a of the radiator 3. Although the first and second oil coolers 10 and 20 are provided, the present invention is not limited to this, and an arrangement structure as shown in each drawing of FIG.
That is, the one shown in FIG. 6A is arranged by rotating the first and second oil coolers 10 and 20 to the cooling fan 2 side (upstream side) around the left and right sides of the radiator 3. FIG. 6B shows a configuration in which the first and second oil coolers 10 and 20 are moved to the cooling fan 2 side (upstream side). Furthermore, what is shown in FIG. 6 (c) is the one in which the first and second oil coolers 10, 20 are moved downstream, and what is shown in FIG. 6 (d) In the opposite direction to that shown in FIG. 6A, that is, the first and second oil coolers 10 and 20 are rotated and arranged downstream. Even in this case, oil coolers 13 to 16 as shown in FIGS. 4A and 4B can be attached in place of the first and second oil coolers 10 and 20.

  In addition, as shown in FIG. 7, first and second aftercoolers 31 and 32 may be provided in parallel on the left and right sides of the first and second oil coolers 10 and 20. In this case, the first and second aftercoolers 31 and 32 can be configured to be connected by the connecting pipe 33, and the oil flows in one direction from the first aftercooler 31 to the second aftercooler 32 side. It can be provided to flow.

(Second Embodiment)
FIGS. 8A and 8B are diagrams showing a main part of a compressor according to the second embodiment of the present invention, in which FIG. 8A is a schematic perspective view for explaining a radiator air volume adjusting device, and FIG. 8B is a heat exchange. It is a model perspective view for demonstrating a dexterous air volume adjustment apparatus.
The compressor of the present embodiment differs from the compressor of the first embodiment in that the radiator air volume adjusting device is used for the radiator 3 or the first and second oil coolers 10 and 20 as heat exchangers. In addition, at least one of the air volume adjusting devices for the heat exchanger is provided, and the other points are not changed.

1. Radiator air volume adjusting device As shown in FIG. 8A, in this embodiment, a louver 40 is used as a radiator air volume adjusting device. The louver 40 is provided so as to substantially cover the entire heat radiating surface 3a (the heat radiating surface downstream of the radiator 3) opposite to the side facing the cooling fan 2 (not shown). In the present embodiment, the louver 40 is constituted by a total of six thin plates 40a.
The louver 40 is attached to a frame (not shown) of the heat radiating surface 3a of the radiator 3 by means of a bolt (not shown), and each thin plate 40a is provided so as to be able to rise and fall with respect to the heat radiating surface 3a manually. That is, when the thin plate 40a of the louver 40 is adjusted to the state in which the thin plate 40a of the louver 40 is tilted with respect to the heat radiating surface 3a of the radiator 3, the air flow rate of the radiator 3 is limited. When the thin plate 40a of the louver 40 is adjusted to be raised with respect to the surface 3a, the air flow rate of the radiator 3 is increased.

That is, by providing such a louver 40 on the heat radiating surface 3a of the radiator 3, the amount of ventilation of the radiator 3 can be adjusted, and the heat exchange amount of the radiator 3 is adjusted by adjusting the state of each thin plate 40a. can do.
The thin plate 40a of the louver 40 may be provided in a fixed state.

2. Air exchanger for heat exchanger As shown in FIG. 8B, in this embodiment, louvers 50A and 50B are used as an air volume adjuster for heat exchanger. The louvers 50A and 50B, like the louver 40 for the radiator 3, have a heat radiating surface 3a (of the first and second oil coolers 10 and 20 opposite to the side facing the cooling fan 2 (not shown)). It is provided in a state of substantially covering the entire (downstream side). In the present embodiment, louvers 50A and 50B are configured by a total of six thin plates 50a.
Each louver 50A, 50B is attached to a frame portion (not shown) of the heat radiating surfaces 10c, 20c on the downstream side of the first and second oil coolers 10, 20 by bolts (not shown) and is manually radiated. Each thin plate 50a is provided with respect to the surfaces 10c and 20c so that it can be tilted. That is, when the thin plates 50a of the louvers 50A and 50B are adjusted to be in a tilted state with respect to the heat radiation surfaces 10c and 20c of the first and second oil coolers 10 and 20, the first and second oils The air flow rate of the coolers 10 and 20 is limited, and conversely, the louvers 50A and 50B are raised with respect to the heat radiation surfaces 10c and 20c of the first and second oil coolers 10 and 20, respectively. When the adjustment is performed, the air flow rate of the first and second oil coolers 10 and 20 is increased.

That is, by providing such louvers 50A and 50B on the heat radiating surfaces 10c and 20c of the first and second oil coolers 10 and 20, the flow rate of the first and second oil coolers 10 and 20 is adjusted. The heat exchange amount of the first and second oil coolers 10 and 20 can be adjusted according to the adjustment state of each thin plate 50a.
In the present embodiment, the louvers 50A and 50B are provided in both the first and second oil coolers 10 and 20, but the present invention is not limited thereto, and may be provided in either one. Moreover, you may provide in combination with the louver 40 as an air volume adjustment apparatus for radiators.
Note that the thin plates 50a of the louvers 50A and 50B may be provided in a fixed state.

  In addition, the louvers 40, 50A, and 50B of the present embodiment can be used for adjustment to appropriately perform heat exchange corresponding to the operating temperature (outside air temperature).

  As mentioned above, although embodiment which concerns on this invention was described, it cannot be overemphasized that this invention is not limited to this, The appropriate change implementation according to the summary of invention is possible. For example, the first and second oil coolers 10 and 20 are not limited to a rectangular shape, and the shape thereof is not limited. Moreover, although the said embodiment showed about the case where each part of the compressor 1 was accommodated in the soundproof case K, this invention is applicable also to the compressor which does not have the soundproof case K. Furthermore, the present invention is not limited to a compressor as long as it is an engine-driven work machine having the above-described configuration, and can be applied to all work machines generally used such as a generator and a welder. In the present invention, an interactor may be provided as a heat exchanger. In this case, the intercooler may be provided on the left and right sides of the radiator 3 and the first and second oil coolers 10 and 20, or may be provided on the front and rear sides.

It is a figure which shows the internal structure of the compressor which concerns on the 1st Embodiment of this invention, (a) is a schematic plan view, (b) is a schematic side view, (c) is a schematic front view. It is the figure which similarly showed the principal part of the compressor of this invention, (a) is a top view, (b) is a front view, (c) is cc sectional drawing of Fig.2 (a). It is a model front view for demonstrating the direction of the flow of the heat carrier which flows through the inside of a heat exchanger (oil cooler). (A)-(d) is a model front view which shows the modification of a heat exchanger (oil cooler). (A) (b) is a schematic top view which shows the modification of a heat exchanger (oil cooler). (A)-(d) is the schematic top view which showed the arrangement pattern of the heat exchanger (oil cooler). It is a model front view when a heat exchanger (aftercooler) is arranged in parallel. It is the figure which showed the principal part of the compressor which concerns on the 2nd Embodiment of this invention, (a) is a model perspective view for demonstrating the air volume adjustment apparatus for radiators, (b) is the air volume adjustment apparatus for heat exchangers. It is a model perspective view for demonstrating. It is the model side view which showed the structural example of the prior art. It is the model top view which showed the other structural example of the prior art. It is a model front view for demonstrating the direction of the flow of the heat carrier which flows through the inside of the conventional heat exchanger.

Explanation of symbols

1 Compressor (Engine-driven work machine)
2 cooling fan 2a fan cover 2b shroud 3 radiator 3a heat radiating surface 3b edge 4 receiver tank 10 first oil cooler (heat exchanger)
10c Heat radiation surface 20 Second oil cooler (heat exchanger)
20c Heat radiation surface 30 Connection piping 40 Louver 50A Louver 50B Louver C Compressor body E Engine

Claims (5)

An engine, a work machine body driven by the engine, a cooling fan, a radiator disposed so that a heat radiating surface faces the cooling fan, and a heat exchanger provided in parallel with the radiator In engine driven work machine with
The engine-driven work machine according to claim 1, wherein the heat exchanger is divided and arranged at least symmetrically on the side of the edge of the heat radiating surface of the radiator with the radiator as a center.   2. The engine-driven work machine according to claim 1, wherein the heat exchanger is configured such that a flow path of a heat medium flowing in the heat exchanger flows in one direction from one to the other. .   The engine-driven work machine according to claim 1 or 2, wherein the heat exchanger is attachable and detachable in an appropriate combination from a plurality of types having different heat exchange amounts.   The radiator air volume adjusting device that adjusts the passing air volume of the radiator is provided on a heat radiating surface side opposite to the side facing the cooling fan in the radiator. 4. The engine-driven work machine according to any one of 3 above.   An air volume adjusting device for a heat exchanger that adjusts an air volume passing through the heat exchanger is provided on a heat radiating surface side opposite to a side facing the cooling fan in at least one of the heat exchangers. The engine-driven work machine according to any one of claims 1 to 4.

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