JP7208064B2 - Package type compressor - Google Patents

Description

The present invention relates to a package type compressor.

Patent Literature 1 discloses a package-type compressor in which a gas cooler is arranged in an exhaust duct so as to be inclined with respect to an exhaust port, and the exhaust port is partitioned by a single sound insulating plate.

However, in the package-type compressor disclosed in Patent Document 1, sufficient studies have been conducted to see how variations in the flow velocity of the cooling air supplied to the gas cooler affect the cooling of the compressed air flowing through the gas cooler. not

JP 2017-223177 A

SUMMARY OF THE INVENTION An object of the present invention is to provide a package-type compressor capable of effectively cooling compressed air flowing inside by suppressing variations in the flow velocity of air supplied to a gas cooler.

As a means for solving the above problems, the present invention includes a compressor body for compressing a part of the air that has flowed in from the intake port and a compressor body that compresses a part of the air that has flowed in from the intake port and a package that has an intake port and an exhaust port. an air-cooling fan that supplies the rest of the air that has flowed in from the intake port to the gas cooler as a swirling flow and then discharges it from the exhaust port; and the air-cooling fan causes the swirling flow to rise. A collision surface with the swirl flow is inclined with respect to a normal direction of a circle centered at the center of the swirl flow so that the air is guided toward the center of the swirl flow before the air reaches the gas cooler. To provide a package-type compressor comprising:

With this configuration, variations in the flow velocity of the air supplied to the outside of the gas cooler can be suppressed. This makes it possible to effectively cool the compressed air flowing inside the gas cooler. Also, with this configuration, it is possible to suppress the flow resistance of the swirling flow that collides with the fins, and obtain a smooth air flow. As a result, the compressed air can be cooled more effectively.

It is preferable that the fins are composed of a plurality of fins arranged at predetermined intervals in the flow direction of the swirling flow.

With this configuration, it becomes easier to guide the air toward the center of the swirling flow, and the compressed air flowing inside the gas cooler can be cooled more effectively.

The fins preferably have a sound absorbing material on their surfaces.

With this configuration, noise can be reduced even when the direction of the swirling flow is forcibly changed by the fins.

ADVANTAGE OF THE INVENTION According to this invention, the variation in the flow velocity of the air supplied to a gas cooler can be suppressed, and the compressed air which flows inside can be cooled effectively.

1 is a schematic cross-sectional view of a package-type compressor according to this embodiment; FIG. FIG. 2 is a sectional view taken along line II of FIG. 1; FIG. 2 is a sectional view taken along line II-II of FIG. 1; 2 is a schematic front wall view of the opening of the package shown in FIG. 1; FIG. FIG. 3 is a diagram showing the velocity distribution of normal pressure air passing through the gas cooler when no fins are provided as shown in FIG. 2; 3 is a diagram showing the velocity distribution of normal pressure air passing through the gas cooler when the fins shown in FIG. 2 are provided; FIG. FIG. 10 is a schematic cross-sectional view of a package-type compressor according to another embodiment;

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. It should be noted that the following description is essentially merely an example, and is not intended to limit the present invention, its applications, or its uses.

As shown in FIGS. 1 to 3, the package type compressor (hereinafter simply referred to as compressor 1) according to the present embodiment includes a compressor main body 20, an oil recovery device 30, a gas cooler 40 in a package 10. , and an air cooling fan 41 . The gas cooler 40 is also provided with an oil cooler (not shown) for cooling the oil supplied to the compressor body 20 .

The package 10 is formed by forming a metal plate (for example, a steel plate) into a box shape. In FIG. 1, the upper wall is the upper wall 10a, the lower wall is the lower wall 10b, the left side is the front wall 10c, and the right side is the rear wall 10d. The side surface located on the upper side is referred to as a left side wall 10e, and the side surface located on the lower side is referred to as a right side wall 10f.

An intake port 11 is formed in the upper right half of the front wall 10c of the package 10. As shown in FIG. In this embodiment, the intake port 11 is covered with a panel 11b having a plurality of oblong holes 11a (see FIG. 4). Each hole 11a can be formed in various shapes such as circular and square. Also, without providing the panel 11b, it is possible to leave the opening as it is or to make the panel 11b itself mesh-like. A filter (not shown) is attached to the intake port 11 so that foreign matter such as dust cannot pass through.

An intake duct 12 is attached to the intake port 11 . The intake duct 12 is formed by forming a plate material into a tubular shape. The air intake duct 12 has a channel cross-sectional area that gradually decreases from one end 12 a that communicates with the air intake port 11 toward the other end 12 b that terminates inside the package 10 . In this embodiment, the air intake duct 12 has a rectangular cross section, and the upper surface of the air intake duct 12 slopes downward from one end 12a toward the other end 12b, thereby gradually decreasing the flow passage cross-sectional area. Thereby, a space is formed above the intake duct 12 . A transfer pipe 13, which will be described later, is arranged in a space formed above the intake duct 12. As shown in FIG. Thus, the compressor 1 is miniaturized by effectively utilizing the limited space within the package 10 . Note that the intake port 11 and the intake duct 12 may have any cross-sectional shape such as circular or polygonal.

An exhaust port 14 is formed in the right half of the upper surface wall 10a of the package 10 in the middle area in the front-rear direction. A fan duct 45 , which will be described later, is attached to the exhaust port 14 .

The compressor main body 20 is of a screw type, and is arranged in the lower part of the package 10 on the right side wall 10f side. The compressor body 20 includes a suction port 21 , a filter portion 22 , an intake control valve 23 , a discharge port 24 , a motor 25 and a compression portion 26 . A screw rotor (not shown) that rotates when driven by the motor 25 is accommodated in the compression section 26 . When the screw rotor rotates, air is sucked from the suction port 21 located on the lower side of the intake duct 12 . Foreign matter is removed from the sucked air by the filter portion 22 , the amount of intake air is adjusted by the intake control valve 23 , and the air is compressed by the compression portion 26 and then discharged from the discharge port 24 . The compressor main body 20 is oil-cooled, and lubricating oil is supplied to the screw rotor. The supplied oil cools, lubricates and seals the screw rotor, and is discharged from the discharge port 24 together with the compressed air.

The oil recovery device 30 has a substantially columnar shape extending in the vertical direction, and is arranged in the front part of the package 10 on the left side wall 10e side. The oil recovery device 30 is fluidly connected to the discharge port 24 of the compressor body 20 via the discharge pipe 27 and separates and recovers oil from the compressed air discharged from the compressor body 20 . The recovered oil is stored in an oil recovery device 30 and supplied again to the compressor main body 20 after passing through the oil cooler. Compressed air from which oil is separated flows through the transfer pipe 13 .

The gas cooler 40 is connected in the middle of the transfer pipe 13 and attached to the exhaust port 14 formed in the upper wall 10 a of the package 10 . Although details are not shown, the gas cooler 40 is a heat exchanger having meandering pipes and radiation fins integrated therewith. In the gas cooler 40, heat is exchanged between the compressed air flowing inside the pipe and the air (normal pressure air) flowing outside the pipe to cool the compressed air. The normal-pressure air whose temperature has been increased by absorbing heat from the compressed air is discharged from the exhaust port 14 to the outside of the package 10 .

The air-cooling fan 41 is a centrifugal fan such as a multi-blade fan, a turbo fan, or a radial fan, and is attached to a fan support portion 43 supported by a support base 42 . In this embodiment, the air-cooling fan 41 includes a motor 41a and a multi-blade fan attached to the rotating shaft of the motor 41a and rotated by driving the motor 41a. The support base 42 includes a support base main body 42a having a rectangular shape in plan view, and leg portions 42b extending from four corners of the support base main body 42a. The support base main body 42a has an open center portion and a bell mouth 48 attached thereto so that cooling air can pass through. The legs 42b are fixed to the bottom wall 10b of the package 10 (specifically, a support plate fixed on the bottom wall 10b) so as not to interfere with the compressor body 20 arranged below the support base 42. The fan support portion 43 includes a top plate 43a and leg portions 43b extending from the top plate 43a and fixed to the support base main body 42a. The air cooling fan 41 is attached to the top plate 43 a of the fan support portion 43 . Specifically, the motor 41 a of the air cooling fan 41 is attached to the top plate 43 a of the fan support portion 43 . In this mounting state, the air cooling fan 41 is positioned on the lower side of the top plate 43a, and the motor 41a is positioned on the upper side of the top plate 43a. The air-cooling fan 41 is driven by a motor 41a to cause the air sucked from the bell mouth 48 on the lower side to flow upward as a swirling flow. The top plate 43a may be configured to have a plurality of vents so that upward normal-pressure air can pass through, or may be configured to be formed only in a region where fins 44, which will be described later, can be fixed. The point is that the structure should be strong enough to support the air cooling fan 41 and capable of reducing the flow resistance of normal pressure air. In this embodiment, the top plate 43a is formed in a rectangular shape in plan view. That is, the top plate 43a has a short side having a width larger than the outer diameter of the motor 41a and smaller than the outer diameter of the cooling fan 41, and a width larger than both the outer diameter of the motor 41a and the outer diameter of the cooling fan 41. have sides. Further, the top plate 43a has openings 43c and 43d as vents at portions other than the mounting position of the motor 41a.

A plurality of fins 44 are fixed to the top wall of the top plate 43 a of the fan support portion 43 . In this embodiment, the fins 44 are composed of three pieces (first fin 44a, second fin 44b and third fin 44c). Each fin 44 has a flat plate shape and is arranged so as to intersect the flow direction of the air that is swirled by the cooling fan 41 . Specifically, the plane of each fin 44 (surface on the side with which the swirling flow collides: collision surface) is aligned in the diameter (normal) direction of a circle centered on the rotation center of the air-cooling fan 41 (or a curve drawn by the swirling flow). On the other hand, it is inclined in the flow direction of the swirl flow toward the center of the swirl flow. Each fin 44 has its lower end fixed to the top wall of the top plate 43 a and its upper end extended to the vicinity of the gas cooler 40 . Further, each fin 44 has an outer end positioned near a fan duct 45 described later, and an inner end positioned near a motor 41 a of the air cooling fan 41 in plan view. The angle of inclination of the collision surface with respect to the radial (normal) direction can be freely set according to the flow velocity of the air so that the air can be guided to the center side. In this embodiment, the inclination angle of the collision surface with respect to the radial (normal) direction is 45 degrees. As a result, the swirling air flow does not collide with the fins 44 at right angles, so that the air can be smoothly directed toward the swirling center without increasing the flow resistance. Further, the space between the first fin 44a and the second fin 44b and the space between the second fin 44b and the third fin 44c are equal (positional relationship in which the air cooling fan 41 is rotated by about 90 degrees around the rotation center of the air cooling fan 41). are placed in However, it is preferable to arrange all the arranged fins 44 at regular intervals in the circumferential direction.

A fan duct 45 is arranged around the air cooling fan 41 . The fan duct 45 is rectangular in plan view and fixed to the top wall 10 a of the package 10 so that the upper end opening surrounds the gas cooler 40 . A lower end opening of the fan duct 45 is fixed to the upper wall of the support base body 42a. As a result, an air flow path (part of a second flow path, which will be described later) is formed from the support base 42 to the exhaust port 14 . One side surface of the fan duct 45 is a partition panel 45A that faces the air flow path of the intake duct 12 . That is, the partition panel 45A plays a role of guiding the normal-pressure air sucked from the intake duct 12 downward.

The compressor 1 configured as described above has a first flow path for generating and flowing compressed air and a second flow path for flowing cooling air in the package 10 .

The first flow path connects the intake port 11, the intake duct 12, the intake port 21 of the compressor body 20, the filter portion 22, the intake adjustment valve 23, the compression portion 26, the discharge port 24, the oil recovery device 30, and the gas cooler 40. It is composed of a transfer pipe 13 that

The second flow path is composed of the intake port 11 , the intake duct 12 , the fan duct 45 in which the cooling fan 41 is arranged, and the exhaust port 14 .

Next, operation of the compressor 1 will be described.

When the motor 41a is driven to rotate the air cooling fan 41, normal pressure air around the package 10 flows in through the air intake 11 (see arrow F1 in FIG. 1). The inflowing normal-pressure air flows through the intake duct 12, collides with the partition panel 45A, and travels downward.

Further, when the motor 25 is driven to rotate the screw rotor, the inflowing normal pressure air is sucked into the compressor main body 20 through the suction port 21 (see arrow F2 in FIG. 1). The sucked normal pressure air is compressed by the compressor main body 20 and discharged from the discharge port 24 (see FIG. 3) as high temperature and high pressure compressed air. The discharged compressed air flows through the discharge pipe 27 and is supplied to the oil recovery device 30, where the oil is separated. The compressed air from which the oil is separated by the oil collector 30 flows through the transfer pipe 13 and is supplied to the gas cooler 40 .

The normal pressure air that passes through without being sucked into the compressor body 20 is drawn into the air-cooling fan 41 (see arrow F4 in FIG. 1), rises as a swirling flow (see arrow F5 in FIG. 1), and passes through the fan duct. 45 to the gas cooler 40.

A plurality of fins 44 are fixed to the upper surface of the top plate 43a of the fan support portion 43 to which the air cooling fan 41 is attached. For this reason, the normal-pressure air that has become a swirling flow collides with the fins 44 and is partially forcibly changed in flow direction toward the center of the swirling flow. The angle of inclination of the fins 44 is 45 degrees toward the center of the swirling flow with respect to the radial direction of the circle centered on the rotation center of the air cooling fan 41 . Therefore, the flow of normal pressure air, which has become a swirling flow, can be smoothly directed toward the center of swirling without increasing the flow resistance.

5, and with three fins 44, as shown in FIG. It shows the air velocity distribution. In the figure, the difference in flow velocity is shown by the line spacing of hatching, and the wider the spacing, the slower the flow velocity. In FIG. 5, a first velocity region 51 having an extremely low velocity is formed over a wide range at the central portion of the swirling flow. On the other hand, in FIG. 6, there is no first speed region 51 in the central portion of the swirl flow, and a second speed region 52 having a higher speed than the first speed region 51 occupies a wide range. As is clear from these drawings, by providing the three fins 44, it is possible to suppress variations in the velocity distribution of the normal pressure air compared to the case where no fins 44 are provided.

The normal-pressure air whose velocity distribution is suppressed in this way passes through the outside of the gas cooler 40 . Inside the gas cooler 40, high-temperature compressed air flows while meandering, and heat is exchanged with normal-pressure air passing outside. At this time, if the flow velocity of the normal pressure air passing through the outside of the gas cooler 40 varies greatly depending on the location, the following problem occurs. In other words, cooling of the compressed air inside the gas cooler 40 by normal pressure air becomes insufficient at a place where the flow velocity is slow. Therefore, the cooling state of the compressed air varies. By suppressing the variation in the velocity distribution of the normal pressure air as described above, it is possible to suppress the occurrence of such variation in the cooling state of the compressed air. As a result, the compressed air flowing through the gas cooler 40 can be effectively cooled without waste.

The cooled compressed air is supplied to a supply destination (for example, an accumulator tank not shown) outside the package 10 via the transfer pipe 13 (see arrow F3 in FIG. 1). The normal-pressure air, which has been heated by absorbing heat from the compressed air, is discharged to the outside of the package 10 through the exhaust port 14 (see arrow F6 in FIG. 1).

The compressor 1 configured as described above has the following features.

Since the plurality of fins 44 are arranged on the downstream side in the flow direction of the normal pressure air by the air cooling fan 41, part of the swirl flow obtained by the air cooling fan 41 can be guided toward the inner diameter side. Therefore, the flow speed of the normal-pressure air passing through the gas cooler 40 is less variable, and the heat exchange efficiency in the gas cooler 40 can be enhanced. That is, it becomes possible to improve the cooling capacity of the compressed air in the gas cooler 40 .

Inside the package 10, a suction port 21, a discharge port 24, and an oil recovery device are provided in a side space (hereinafter referred to as a suitable installation space S) of the intake duct 12 (the entire area from one end 12a to the other end 12b). 30 are placed. In this embodiment, the suction port 21 , the filter portion 22 and the discharge port 24 are arranged directly below the intake duct 12 (see FIGS. 1 and 3), and the oil collector 30 is arranged on the side of the intake duct 12 . Although noise is likely to be generated from the suction port 21, the discharge port 24, and the oil recovery device 30, the sound waves must travel from the side of the suction duct 12 to the other end 12b before being transmitted to the outside of the package 10 through the suction port 11. It is necessary to turn around, pass through the air intake duct 12, and travel a long path to reach one end 12a of the air intake duct 12. - 特許庁Therefore, sound waves can be sufficiently weakened, and quietness can be improved.

Since the air intake duct 12 has a simple structure in which a plate member is formed into a cylindrical shape, the weight does not increase so much. Therefore, even when the air intake duct 12 is connected during assembly or maintenance, the package 10 can be easily attached and detached.

The present invention is not limited to the configurations described in the above embodiments, and various modifications are possible.

In the above embodiment, the case of providing three fins 44 was described, but it is also possible to provide one, two, or four or more fins. Even if two fins 44 or four or more fins 44 are provided, it is preferable to arrange the fins 44 at equal angles in the circumferential direction around the rotation center of the air cooling fan 41 . This makes it easier to increase the heat exchange efficiency in the gas cooler 40 by suppressing variations in the velocity distribution of the normal pressure air.

Although the shape of the fins 44 is flat in the above-described embodiment, the shape of the fins 44 is not limited to this, and the flow resistance may be suppressed by forming curved surfaces on the portions with which the swirling flow collides. Also, a sound absorbing material 46 may be attached to the surface of the fins 44 . For the sound absorbing material 46, for example, a nonwoven fabric formed in a mesh shape with a plurality of fibers, a porous urethane sponge, or the like can be used. Noise generated from the air cooling fan 41 or the like is reduced by the sound waves being reflected by the sound absorbing material 46 many times.

Although the discharge pipe 27 is arranged below the intake duct 12 in the above embodiment, it may be arranged in the suitable installation space S. As a result, the normal pressure air that has flowed in from the intake duct 12 does not directly flow in the vicinity of the discharge pipe 27 . That is, the normal pressure air is less likely to be heated by the compressed air, and a decrease in compression efficiency of the compressor main body 20 can be suppressed. In addition, a decrease in cooling efficiency in the gas cooler 40 can also be suppressed.

In the above embodiment, no particular reference was made to the positions of the upper and lower ends of the partition panel 45A. preferably In particular, the lower end 45b is preferably positioned lower than the straight line L connecting the upper end 11c of the intake port 11 of the package 10 and the lower end 12c of the other end 12b of the intake duct 12 . That is, when the inside of the package 10 is viewed from the air intake 11 of the package 10 through the air intake duct 12, it is preferable that the gas cooler 40 and the air cooling fan 41 cannot be seen.

According to this configuration, even if noise is generated from the gas cooler 40 and the air-cooling fan 41, the sound wave passes below the partition panel 45A and then travels through the intake duct 12 to the outside of the package 10. FIG. In particular, the lower end 45b of the partition panel 45A is arranged below the straight line L connecting the upper end 11c of the intake port 11 of the package 10 and the lower end 12c of the other end 12b of the intake duct 12. As shown in FIG. For this reason, the sound wave will wrap around the lower end 45b of the partition panel 45A, and is difficult to transmit to the outside from the air inlet 11 side.

The partition panel 45A is arranged between the air intake duct 12 and the gas cooler 40 and air cooling fan 41 . Therefore, it is possible to prevent sound waves from the gas cooler 40 and the air cooling fan 41, which are noise sources, from being directly transmitted to the outside from the intake port 11. FIG.

Although not specifically mentioned in the above embodiment, sound absorbing materials 15 and 47 similar to those provided on the fins 44 are provided on the inner surface of the air intake duct 12 and the surface of the partition panel 45A facing the air intake duct 12. You may make it stick each. In this case, as shown in FIG. 3, it is preferable to attach a thin sound absorbing material 15 to all four inner surfaces of the intake duct 12 . Moreover, it is preferable to attach a sound absorbing material 47 to substantially the entire surface of the partition panel 45A facing the intake duct 12 .

According to this configuration, the inner surface of the air intake duct 12 and the surface of the partition panel 45A on the side facing the air intake duct 12 form a path through which sound waves of noise propagate. Therefore, by attaching the sound absorbing materials 15 and 47 to the paths of the sound waves, it is possible to effectively reduce the noise.

Although not specifically mentioned in the above embodiment, it is preferable that the channel area of the other end 12b of the intake duct 12 is larger than the total opening area of the plurality of holes 11a of the intake port 11 of the package 10. FIG.

According to this configuration, the flow path area of air (sound) leaking from the air intake port 11 of the package 10 through the air intake duct 12 changes in the order of small, large, and small. Specifically, the other end 12b of the air intake duct 12 has the smallest flow area in the air intake duct 12, and the flow area increases as the air intake duct 12 progresses from the other end 12b to the one end 12a. Then, at the air inlet 11 of the package 10, the passage area is reduced again by the plurality of holes 11a. Due to this change in flow path area, an expansion space is formed in the intake duct 12, and the expansion space serves as a muffling chamber. Therefore, a silencing effect is obtained, and noise can be further reduced. In addition, since the channel area of the other end 12b of the intake duct 12 is larger than the total opening area of the plurality of holes 11a of the intake port 11 of the package 10, a large pressure loss occurs in the intake air channel. You can inhale efficiently.

In the above-described embodiment, the top plate 43a of the fin support portion 43 has the configuration shown in FIG. 2, but as shown in FIG. It may be formed into a shape.

1 package type compressor 10 package 10a top wall 10b bottom wall 10c front wall 10d rear wall 10e left side wall 10f right side wall 11 intake port 11a hole 11b panel 11c top end 12 intake duct 12a one end 12b other end 12c bottom end 13 transfer pipe 14 exhaust port 15 sound absorbing material 20 compressor body 21 suction port 22 filter portion 23 intake control valve 24 discharge port 25 motor 26 compression portion 27 discharge pipe 30 oil collector 40 gas cooler 41 air cooling fan 42 support base 42a support base body 42b leg portion 43 fan support Part 43a Top plate 43b Leg 44 Fin 45 Fan duct 45A Partition panel 45a Upper end 45b Lower end 46, 47 Sound absorbing material 48 Bell mouth S Suitable installation space

Claims (3)

In a package having an inlet and an outlet,
a compressor main body that compresses a part of the air that has flowed in from the intake port;
a gas cooler through which the air compressed by the compressor body flows;
an air-cooling fan for supplying the rest of the air that has flowed in from the intake port as a swirling flow to the gas cooler and then discharging it from the exhaust port;
In the normal direction of a circle centered on the center of the swirl flow, the air that rises as a swirl flow by the air cooling fan is guided toward the center of the swirl flow before the air reaches the gas cooler. On the other hand, a fin having an inclined collision surface with the swirling flow ,
A packaged compressor. 2. The package-type compressor according to claim 1, wherein said fins are composed of a plurality of fins arranged at predetermined intervals in the flow direction of said swirling flow. 3. The package-type compressor according to claim 1 , wherein said fin has a sound absorbing material on its surface.

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