JP2021188778A - Acoustic damper and refrigerator - Google Patents

Abstract

To restrain generation of noise in an acoustic damper and a refrigerator, and downsize the device.SOLUTION: An acoustic damper is provided on an outer surface part of a pipe comprising a flow passage inside which fluid flows, and comprises: a damper body provided on the outer surface part of the pipe, and of which an internal space communicates with the flow passage; and a partition plate extended from one inner wall surface of the damper body toward another inner wall surface.SELECTED DRAWING: Figure 1

Description

The present disclosure relates to an acoustic damper mounted on a pipe and a refrigerator provided with an acoustic damper.

The refrigerator includes a compressor, a condenser, an expansion valve, and an evaporator. In the refrigerating cycle of the refrigerator, the compressor compresses the refrigerant, the condenser heat-exchanges and condenses the high-temperature and high-pressure refrigerant, the expansion valve expands the overcooled liquid refrigerant, and the evaporator expands the refrigerant. Heat exchanges between the refrigerant and the medium to be cooled to evaporate the refrigerant. The evaporator is used, for example, to cool the inside of the freezer.

The causes of noise generated from refrigerators are roughly classified into two types: noise caused by mechanical incentives and noise caused by fluid incentives. Noise due to mechanical incentives is generated as pressure pulsation (NZ sound) due to periodic flow rate fluctuations due to the movement of blades and the number of diffuser blades when the compressor or pump operates. It is known that such noise has a characteristic and a single frequency characteristic, resonates with an acoustic eigenvalue of a pipe or the like used in a refrigerator, and amplifies the sound. As a technique for solving such a problem, for example, there is one described in Patent Document 1 below.

Japanese Unexamined Patent Publication No. 2018-119776

The acoustic device of Patent Document 1 described above is a device in which a main body portion having a resonance space is connected to a pipe and a perforated plate is provided at the connecting portion. However, for example, in a refrigerator, the space for arranging the acoustic device is limited, and there is a demand for miniaturization of the acoustic device.

The present disclosure is to solve the above-mentioned problems, and an object of the present invention is to provide an acoustic damper and a refrigerator for suppressing the generation of noise and reducing the size of the apparatus.

The acoustic damper of the present disclosure for achieving the above object is an acoustic damper provided on the outer surface portion of a pipe having a flow path through which a fluid flows inside, and the internal space is provided on the outer surface portion of the pipe and the internal space is the flow path. A damper main body communicating with the damper body and a partition plate extending from one inner wall surface of the damper main body toward another inner wall surface are provided.

Further, the refrigerator of the present disclosure includes a compressor that compresses the refrigerant, a condenser that condenses the refrigerant compressed by the compressor, an evaporator that evaporates the refrigerant condensed by the condenser, and the above. It comprises the acoustic damper arranged in a pipe connecting the compressor, the condenser, and any of the evaporators.

According to the acoustic damper of the present disclosure, it is possible to suppress the generation of noise and to reduce the size of the device.

FIG. 1 is a schematic configuration diagram showing the refrigerator of the present embodiment. FIG. 2 is a schematic view showing an attached state of the acoustic damper of the present embodiment. FIG. 3 is a vertical sectional view showing the acoustic damper of the present embodiment. FIG. 4 is a horizontal cross-sectional view showing the acoustic damper of the present embodiment. FIG. 5 is a horizontal sectional view showing a first modification of the acoustic damper of the present embodiment. FIG. 6 is a schematic view showing a second modification of the acoustic damper of the present embodiment.

Preferred embodiments of the present disclosure will be described in detail below with reference to the drawings. It should be noted that the present disclosure is not limited by this embodiment, and when there are a plurality of embodiments, the present embodiment also includes a combination of the respective embodiments. Further, the components in the embodiment include those that can be easily assumed by those skilled in the art, those that are substantially the same, that are, those in a so-called equal range.

[refrigerator]
FIG. 1 is a schematic configuration diagram showing the refrigerator of the present embodiment, and FIG. 2 is a schematic diagram showing the mounting state of the acoustic damper of the present embodiment.

In the present embodiment, as shown in FIG. 1, the refrigerator 100 is, for example, a part of an air-conditioning equipment that adjusts the temperature, humidity, etc. of a building or a factory, or an air-conditioning equipment that cools a freezer compartment. The refrigerator 100 is a device that supplies cold water or air to an installed building, factory, or freezing room to cool the installed building, factory, or freezing room. The refrigerator 100 includes a compressor 101, a condenser 102, an evaporator 103, and an intercooler 104.

The compressor 101 and the condenser 102 are communicated with each other by a refrigerant pipe 106a through which a refrigerant flows. The condenser 102 and the evaporator 103 are communicated with each other by a refrigerant pipe 106b through which a refrigerant flows. The intercooler 104 is interposed in the refrigerant pipe 106b. The evaporator 103 and the compressor 101 are communicated with each other by a refrigerant pipe 106c through which a refrigerant flows. That is, the compressor 101, the condenser 102, the evaporator 103, and the intercooler 104 are provided in the circulation path 106 for circulating the refrigerant via the refrigerant pipes 106a, 106b, 106c. The refrigerant pipe 106b is provided with a high-stage expansion valve 107 on the upstream side of the intercooler 104 and a low-stage expansion valve 108 on the downstream side in the path. The condenser 102 and the evaporator 103 are provided with a bypass pipe 109 that bypasses and supplies the high-temperature refrigerant gas from the evaporator 103 to the condenser 102 without passing through the circulation path 106. The bypass pipe 109 is provided with a regulating valve 110 for adjusting the flow rate of the refrigerant gas.

The compressor 101 is configured as a turbo compressor that compresses the refrigerant by the rotational motion of the impeller. That is, the refrigerator 100 is a so-called turbo chiller. The compressor 101 as a turbo compressor has a compression unit 112 driven by an electric motor 111. The compression unit 112 includes a two-stage compression system including two impellers coaxially driven by the electric motor 111 and a single-stage compression system including one impeller driven by the electric motor 111. When the compression unit 112 is two-stage compression, the gas phase refrigerant sent from the evaporator 103 to the compressor 101 is compressed by the first-stage compression unit, then further compressed by the second-stage compression unit, and the pressure is increased. And the temperature rises and is sent to the condenser 102 via the refrigerant pipe 106a. On the other hand, when the compression unit 112 is single-stage compressed, the gas phase refrigerant sent from the evaporator 103 to the compressor 101 is compressed by the compression unit 112, and the pressure and temperature rise while passing through the refrigerant pipe 106a. It is sent to the condenser 102.

The condenser 102 is connected to a cooling water pipe 121 to which a refrigerant cooling fluid (for example, water) is supplied. The gas phase refrigerant sent from the compressor 101 to the condenser 102 exchanges heat with the refrigerant cooling fluid supplied by the cooling water pipe 121 and condenses, that is, heat is discharged to the refrigerant cooling fluid and liquefied, and the refrigerant pipe is used. It is sent to the evaporator 103 via 106b. The cooling water pipe 121 is provided with a pump 122 and a cooling water supply unit 123. The pump 122 circulates the cooling water in the cooling water pipe 121. The cooling water supply unit 123 supplies cooling water to the cooling water pipe 121, and recovers the cooling water that has exchanged heat with the refrigerant.

The evaporator 103 is connected to a cold water pipe 131 to which a cooling medium (water in this embodiment) is supplied. The liquid phase refrigerant sent from the condenser 102 to the evaporator 103 exchanges heat with the cooling medium supplied by the cold water pipe 131 and evaporates. In this process, the temperature of water drops due to the absorption of heat by the liquid phase refrigerant. As a result, the water becomes cold water. Then, the liquid phase refrigerant that has exchanged heat with water evaporates to become a gas phase refrigerant, and is sent to the compressor 101 via the refrigerant pipe 106c. The cold water pipe 131 is provided with a pump 132 and a cold water consumption unit 134. The pump 132 circulates water (cold water) in the cold water pipe 131. The cold water consumption unit 134 supplies cold water to the cold water pipe 131, exchanges heat with the refrigerant, and recovers the cooled cold water. The cold water consumption unit 134 uses the recovered cold water to cool the air of the equipment in which the air conditioning equipment (not shown) is installed. A fluid other than water can also be used as the cooling medium.

The intercooler 104 separates the refrigerant that has passed through the high-stage expansion valve 107 into a liquid phase and a gas phase after being liquefied in the condenser 102. The intermediate cooler 104 maintains a constant pressure difference between the condenser 102 and the evaporator 103, and evaporates a part of the refrigerant in the liquid phase to increase the latent heat in the evaporator 103. Further, in the intermediate cooler 104, the gas-phase refrigerant that has not been completely condensed by the condenser 102 and the liquid-phase refrigerant are introduced as a gas-liquid two-phase flow fluid, and the phase refrigerant and the liquid-phase refrigerant are used. It functions as a gas-liquid separator for separation, and the separated gas-phase refrigerant is sent to the compressor 101, and the liquid-phase refrigerant is sent to the low-stage expansion valve 108. The refrigerant that has passed through the low-stage expansion valve 108 is sent to the evaporator 103.

The high-stage expansion valve 107 is a mechanism for expanding the refrigerant liquefied by the condenser 102. Specifically, the refrigerant is depressurized from the condensation pressure to the intermediate pressure. The refrigerant decompressed by the high-stage expansion valve 107 is supplied to the intercooler 104.

The low-stage expansion valve 108 is a mechanism for expanding a liquid refrigerant (saturated liquid refrigerant) that has passed through the intercooler 104. Specifically, the refrigerant is depressurized from the intermediate pressure to the vapor pressure. The refrigerant decompressed by the low-stage expansion valve 108 is supplied to the evaporator 103.

The refrigerator 100 has the above configuration. However, the refrigerator 100 is not limited to the above configuration. The refrigerator 100 may include a compressor 101, a condenser 102, and an evaporator 103, and the piping configuration, pump arrangement, valve arrangement, and the like thereof may be various.

In the refrigerator 100, when the compressor 101 operates, periodic flow rate fluctuations occur according to the movement of the blades, the number of blades of the diffuser, and the like, and noise due to pressure pulsation, so-called NZ sound, is generated. The generation of NZ sound has the property of having a specific frequency characteristic. Then, the NZ sound may resonate with the acoustic field in each pipe included in the circulation path 106 of the refrigerator 100, and the noise may be amplified. Therefore, it is required to suppress the resonance between the NZ sound and the acoustic field in each pipe.

Therefore, as shown in FIGS. 1 and 2, in addition to the above configuration, the refrigerator 100 of the present embodiment is provided in the pipe through which the refrigerant gas (gas fluid) flows among the pipes included in the circulation path 106. It is equipped with an acoustic damper 10. In the embodiment, the acoustic damper 10 is a side branch type acoustic damper provided in the bypass pipe 109.

That is, the condenser 102 and the evaporator 103 are connected by a bypass pipe 109. The high-temperature refrigerant gas generated by the evaporator 103 is supplied to the condenser 102 through the bypass pipe 109 without going through the circulation path 106. The acoustic damper 10 is mounted on the outer surface of the bypass pipe 109. The bypass pipe 109 is a vibration generation source and is arranged along the axial direction (flow direction of the cooling medium) A1 so as to connect the condenser 102 and the evaporator 103. The acoustic damper 10 is arranged on the outer surface of the bypass pipe 109 along the axial direction A2 orthogonal to the axial direction A1.

[Acoustic damper]
FIG. 3 is a vertical cross-sectional view showing the acoustic damper of the present embodiment, and FIG. 4 is a horizontal cross-sectional view showing the acoustic damper of the present embodiment.

As shown in FIGS. 3 and 4, the acoustic damper 10 is provided on the outer surface of the bypass pipe (pipe) 109 having the flow path 109a through which the refrigerant gas (fluid) flows. The acoustic damper 10 includes a damper main body 11 and a plurality of (six in this embodiment) partition plates 12.

The damper main body 11 is arranged along the axial direction A2 orthogonal to the axial direction A1 which is the extending direction of the bypass pipe 109. The damper main body 11 is fixed to the outer surface of the bypass pipe 109. The damper body 11 has a hollow square pillar shape. The damper main body 11 has four side wall portions 21, 22, 23, 24 and an end portion 25. The four side wall portions 21, 22, 23, 24 are connected in a square tubular shape, the end portion 25 is connected to one end portion in the longitudinal direction (axial direction A2), and the opening portion 26 is formed at the other end portion. ..

The damper main body 11 is formed with a space portion (internal space) 27 inside by connecting the four side wall portions 21, 22, 23, 24 and the end portion 25. On the other hand, the bypass pipe 109 has a flow path 109a inside, and has an opening 109b in which the flow path 109a is opened at a predetermined position. The damper main body 11 is fixed so as to close the opening 109b of the bypass pipe 109. In the damper main body 11, the space portion 27 communicates with the flow path 109a via the opening portion 26 and the opening portion 109b of the bypass pipe 109.

Therefore, in the damper main body 11, air vibration generated in the flow path 109a from the bypass pipe 109 is taken into the space portion 27 through the openings 109b and 26 and propagates. The damper body 11 has an end portion 25 formed of a material having a predetermined rigidity, and is configured as a terminal (node) of a sound wave that blocks the downstream side of the propagation of air vibration and becomes a resistance to air vibration.

The damper main body 11 is not limited to a hollow quadrangular prism shape, but may be a hollow polygonal shape, a hollow cylindrical shape including an ellipse, or the like. Further, although the damper main body 11 is arranged along the axial direction A2 orthogonal to the axial direction A1, it may be arranged along the intersecting direction so as to be inclined by a predetermined angle with respect to the axial direction A1 direction. Further, although the damper main body 11 is linear along the axial direction A2, it may be curved.

The partition plate 12 is provided so as to project from the inner wall surface of the damper main body 11 to form a passage 28 that bends inward. The partition plate 12 extends from the inner wall surface of the damper main body 11 toward the facing inner wall surface. Each side wall portion 21, 22, 23, 24 and the end portion 25 of the damper main body 11 have inner wall surfaces 21a, 22a, 23a, 24a, 25a. The partition plate 12 has a first partition plate 12a and a second partition plate 12b. The first partition plate 12a and the second partition plate 12b have the same shape. The first partition plate 12a extends from the inner wall surface (first inner wall surface) 21a toward the inner wall surface (second inner wall surface) 22a. The second partition plate 12b extends from the inner wall surface (second inner wall surface) 22a toward the inner wall surface (first inner wall surface) 21a. That is, the base end portion of the first partition plate 12a is fixed to the inner wall surface 21a, the left and right side portions are fixed to the inner wall surface 23a, 24a, and a gap is secured between the tip end portion and the inner wall surface 22a. The base end portion of the second partition plate 12b is fixed to the inner wall surface 22a, the left and right side portions are fixed to the inner wall surface 23a and 24a, and a gap is secured between the tip end portion and the inner wall surface 21a.

The first partition plate 12a and the second partition plate 12b are parallel to each other and intersect the axial direction (flow direction of the cooling medium) A1 of the bypass pipe 109 in the axial direction A2, that is, the first partition plate 12a and the second partition. The plates 12b are arranged at predetermined intervals (equal intervals) in the arrangement direction. The first partition plate 12a and the second partition plate 12b are alternately arranged in the axial direction A2. At this time, a part of the first partition plate 12a and the second partition plate 12b is arranged so as to overlap with each other in the axial direction A2. That is, the distance between the inner wall surface 21a and the inner wall surface 22a of the damper main body 11 is L, and the length of the first partition plate 12a (second partition plate 12b) in the direction orthogonal to the inner wall surface 21a and the inner wall surface 22a is L1. do. At this time, the length L1 of the first partition plate 12a (second partition plate 12b) is set as L / 2 <L1. That is, when the first partition plate 12a and the second partition plate 12b are viewed from the bypass pipe 109 side, the first partition plate 12a and the second partition plate 12b appear to overlap by the length L2.

The number, shape, and arrangement of the first partition plate 12a and the second partition plate 12b are not limited to the above-described configuration. For example, the first partition plate 12a and the second partition plate 12b may be a set, or may be only one of the first partition plate 12a and the second partition plate 12b. Further, the first partition plate 12a and the second partition plate 12b may have different shapes (size, thickness, etc.). Further, the first partition plate 12a and the second partition plate 12b may be arranged at unequal intervals. Further, the first partition plate 12a and the second partition plate 12b may be arranged so as to be inclined at a predetermined angle instead of being parallel to each other. That is, the first partition plate 12a and the second partition plate 12b may be fixed at an angle that is not perpendicular to the inner wall surfaces 21a and 22a.

Further, in the above description, the damper main body 11 has a hollow quadrangular prism shape, the first partition plate 12a extends from the inner wall surface 21a toward the facing inner wall surface 22a, and the first partition plate 12a extends from the inner wall surface 22a toward the facing inner wall surface 21a. The second partition plate 12b was extended. In this case, the same applies even if the damper main body 11 is not a hollow quadrangular prism shape but a hollow polygonal shape or a hollow circular shape including an ellipse. For example, when the damper main body 11 has a hollow hexagonal column shape, since there are at least two facing inner wall surfaces, the first partition plate is extended from one inner wall surface toward the other inner wall surface facing each other. The second partition plate may be extended from the other inner wall surface toward the opposite inner wall surface. In this case, one inner wall surface and the other inner wall surface may not be parallel to each other, or may have a plurality of surfaces. When the damper body 11 has a hollow pentagonal prism shape, at least two facing inner wall surfaces are not parallel, but the first partition plate extends from one inner wall surface toward the other inner wall surface at the opposite position. , The second partition plate may be extended from the other inner wall surface toward one inner wall surface at a position opposite to the other inner wall surface. Further, when the damper main body 11 has a cylindrical shape, the inner wall surface is one surface continuous in the circumferential direction, but the inner wall surface is present so as to face each other in the radial direction. Therefore, the first partition plate is extended from one side (first inner wall surface) in the radial direction of the inner wall surface toward the other side (second inner wall surface) facing the inner wall surface, and the other side (second inner wall surface) in the radial direction of the inner wall surface is extended. The second partition plate may be extended from the wall surface) to one side (first inner wall surface). The same applies even if the shape is a fusion of a polygon and a circle.

Therefore, in the acoustic damper 10, a bending passage 28 is formed by arranging a plurality of partition plates 12 (first partition plate 12a, second partition plate 12b) in the space portion 27 of the damper main body 11 as described above. To. The passage 28 is formed by connecting in a series, and one end thereof communicates with an opening 26 that captures air vibration. A perforated plate may be arranged in the opening 26. Further, the passage 28 is configured as a terminal (end portion 25) at which the other end closes the downstream side of the propagation of air vibration and becomes a resistance to air vibration.

In the acoustic damper 10, when the refrigerant gas flows through the flow path 109a of the bypass pipe 109, the air vibration (pressure wave) due to the flow of the refrigerant gas passes through the openings 109b and 26 and enters the space 27 of the damper main body 11. It is captured. Then, when the air vibration captured in the space portion 27 propagates through the bent passage 28, the air vibration resonates, so that the pressure fluctuation due to the flow of the refrigerant gas is attenuated.

The acoustic damper 10 is not limited to the above-mentioned configuration. FIG. 5 is a horizontal sectional view showing a first modification of the acoustic damper of the present embodiment, and FIG. 6 is a schematic view showing a second modification of the acoustic damper of the present embodiment.

In the first modification, as shown in FIG. 5, the acoustic damper 10A includes a damper main body 11 and a plurality of partition plates 31.

The partition plate 31 has a first partition plate 31a, a second partition plate 31b, a third partition plate 31c, and a fourth partition plate 31d. In this case, the third partition plate 31c and the fourth partition plate 31d function as the first partition plate and the second partition plate of the present invention. The first partition plate 31a, the second partition plate 31b, the third partition plate 31c, and the fourth partition plate 31d have the same shape, with respect to the axial direction A2, that is, the arrangement direction of the partition plates 31a, 31b, 31c, 31d. Are arranged in a spiral shape. The first partition plate 31a extends from the inner wall surface (first inner wall surface) 21a toward the inner wall surface (second inner wall surface) 22a. The second partition plate 31b extends from the inner wall surface (first inner wall surface) 24a toward the inner wall surface (second inner wall surface) 23a. The third partition plate 31c extends from the inner wall surface (second inner wall surface) 22a toward the inner wall surface (first inner wall surface) 21a. The fourth partition plate 31d extends from the inner wall surface (second inner wall surface) 23a toward the inner wall surface (first inner wall surface) 24a.

That is, the base end portion of the first partition plate 31a is fixed to the inner wall surface 21a, one side portion is fixed to the inner wall surface 24a, and a gap is secured between the tip end portion and the inner wall surface 22a. The base end portion of the second partition plate 31b is fixed to the inner wall surface 24a, one side portion is fixed to the inner wall surface 22a, and a gap is secured between the tip end portion and the inner wall surface 23a. The base end portion of the third partition plate 31c is fixed to the inner wall surface 22a, one side portion is fixed to the inner wall surface 23a, and a gap is secured between the tip end portion and the inner wall surface 21a. The base end portion of the fourth partition plate 31d is fixed to the inner wall surface 23a, one side portion is fixed to the inner wall surface 21a, and a gap is secured between the tip end portion and the inner wall surface 24a.

The partition plates 31a, 31b, 31c, 31d are parallel to each other and are arranged at predetermined intervals (equal intervals) in the axial direction A2, that is, in the arrangement direction of the partition plates 31a, 31b, 31c, 31d. The partition plates 31a, 31b, 31c, 31d are arranged in order in the axial direction A2. At this time, a part of the partition plates 31a, 31b, 31c, 31d is arranged so as to overlap with the axial direction A2. Therefore, in the acoustic damper 10A, a spiral passage is formed by arranging a plurality of partition plates 31a, 31b, 31c, 31d on the damper main body 11 as described above.

In the second modification, as shown in FIG. 6, the acoustic damper 10B includes a damper main body 41 and a plurality of partition plates (not shown).

The damper main body 41 has a first main body portion 41a and a second main body portion 41b. The first main body portion 41a is arranged along the axial direction A2 orthogonal to the axial direction (flow direction of the cooling medium of the bypass pipe 109) A1 direction which is the extending direction of the bypass pipe 109. The second main body portion 41b is arranged along the axial direction A3 orthogonal to the axial direction A2. Axial direction A1 and axial direction A3 are parallel but may not be parallel. The base end portion of the first main body portion 41a is fixed to the outer surface of the bypass pipe 109. The second main body portion 41b is connected so that the base end portion is orthogonal to the tip end portion of the first main body portion 41a. The first main body portion 41a and the second main body portion 41b communicate with each other in the internal space and also with the flow path of the bypass pipe 109.

Although not shown, the damper main body 41 has a plurality of partition plates arranged in an internal space, and extends from one inner wall surface to another inner wall surface. The arrangement of the partition plate is, for example, the same as that of the first embodiment or the first modification, and the description thereof will be omitted.

[Action and effect of this embodiment]
The acoustic damper according to the first aspect is the outer surface of the bypass pipe 109 in the acoustic dampers 10, 10A, 10B provided on the outer surface portion of the bypass pipe (pipe) 109 having the flow path 109a through which the refrigerant gas (fluid) flows. The space portion (internal space) 27 is provided in the portion so as to project from the damper main bodies 11 and 41 that communicate with the flow path 109a and the inner wall surfaces 21a, 22a, 23a and 24a of the damper main bodies 11 and 41 to be provided inside. The partition plates 12 and 31 forming the bending passage 28 are provided.

The acoustic damper according to the first aspect is a passage in which the air vibration bends when the air vibration generated when the refrigerant gas flows through the flow path 109a of the bypass pipe 109 is taken into the space 27 of the damper main bodies 11 and 41. The pressure fluctuation can be attenuated by resonating as it propagates through 28. Here, by arranging the partition plates 12 and 31 inside the damper main bodies 11 and 41, a long bent passage 28 can be formed. As a result, it is possible to suppress the generation of noise and to reduce the size of the device.

In the acoustic damper according to the second aspect, the damper main body 11 has a first inner wall surface 21a and a second inner wall surface 22a facing each other, and the partition plate 12 is from the first inner wall surface 21a to the second inner wall surface 22a. It has a first partition plate 12a extending toward the surface and a second partition plate 12b extending from the second inner wall surface 22a toward the first inner wall surface 21a. As a result, it is possible to form a long passage 28 that bends inside the damper bodies 11 and 41 with a simple configuration.

The acoustic damper according to the third aspect has a predetermined interval in the axial direction A2 which is an arrangement direction in which the first partition plate 12a and the second partition plate 12b intersect the axial direction A1 which is the flow direction of the refrigerant gas flowing through the flow path 109a. Place in a space. As a result, it is possible to form a long passage 28 that bends inside the damper bodies 11 and 41 with a simple configuration.

In the acoustic damper according to the fourth aspect, the first partition plate 12a and the second partition plate 12b are partially overlapped with each other in the axial direction A2. As a result, it is possible to form a long passage 28 that bends inside the damper bodies 11 and 41 with a simple configuration.

In the acoustic damper according to the fifth aspect, the first partition plate 31a, the second partition plate 31b, the third partition plate 31c, and the fourth partition plate 31d are arranged spirally with respect to the axial direction A2. As a result, it is possible to form a long passage 28 that bends inside the damper bodies 11 and 41 with a simple configuration.

In the acoustic damper according to the sixth aspect, the damper main body 41 has a first main body portion 41a along the axial direction (first direction) A1 intersecting the axial direction A1 which is the flow direction of the refrigerant gas flowing through the flow path 109a. It has a second main body portion 41b along an axial direction (second direction) A3 that intersects the axial direction A2 from the first main body portion 41a. As a result, it is possible to form a long passage 28 that bends inside the damper bodies 11 and 41 without protruding in the axial direction A2.

The refrigerator according to the seventh aspect includes a compressor 101 that compresses the refrigerant, a condenser 102 that condenses the refrigerant compressed by the compressor 101, and an evaporator 103 that evaporates the refrigerant condensed by the condenser 102. , The acoustic dampers 10, 10A, 10B arranged in the bypass pipe 109 as a pipe connecting any of the compressor 101, the condenser 102, and the evaporator 103 are provided. As a result, it is possible to suppress the generation of noise in the entire refrigerator 100 and to reduce the size of the apparatus. Further, in the various pipes of the refrigerator 100, since the flow of the refrigerant is stable, the acoustic dampers 10, 10A, and 10B can be effectively functioned.

In the above-described embodiment, the acoustic dampers 10, 10A, and 10B are provided in the bypass pipe 109, but the position is not limited to this, and the pipe may be, for example, a pipe constituting the circulation path 106.

Further, in the above-described embodiment, the acoustic dampers 10, 10A, and 10B are provided in various pipes of the refrigerator 100, but may be provided in, for example, pipes through which combustion gas of a gas turbine or the like flows.

10,10A, 10B Acoustic damper 11,41 Damper body 41a 1st body 41b 2nd body 12,31 Partition plate 12a, 31a 1st partition 12b, 31b 2nd partition 31c 3rd partition 31d 4th partition Plates 21, 22, 23, 24 Side wall parts 21a, 22a, 23a, 24a Inner wall surface 25 End part 26 Opening part 27 Space part (internal space)
28 Passage 100 Refrigerant 101 Compressor 102 Condensator 103 Evaporator 106 Circulation path 106a, 106b, 106c Refrigerant piping 109 Bypass piping 109a Channel 109b Opening A1, A2, A3 Axial L, L1, L2 Length

Claims (7)

In an acoustic damper provided on the outer surface of a pipe having a flow path for fluid to flow inside.
A damper body provided on the outer surface of the pipe and having an internal space communicating with the flow path,
A partition plate that is provided so as to project from the inner wall surface of the damper body to form a passage that bends inward.
An acoustic damper equipped with. The damper main body has at least a first inner wall surface and a second inner wall surface facing each other, and the partition plate includes a first partition plate extending from the first inner wall surface toward the second inner wall surface. It has a second partition plate extending from the second inner wall surface toward the first inner wall surface.
The acoustic damper according to claim 1. The first partition plate and the second partition plate are arranged at predetermined intervals in an arrangement direction intersecting the flow direction of the fluid flowing through the flow path.
The acoustic damper according to claim 2. A part of the first partition plate and the second partition plate is arranged so as to overlap in the arrangement direction.
The acoustic damper according to claim 3. The first partition plate and the second partition plate are arranged spirally with respect to the arrangement direction.
The acoustic damper according to claim 3 or 4. The damper main body includes a first main body portion along a first direction that intersects the flow direction of the fluid flowing through the flow path, and a second main body portion along a second direction that intersects the first main body portion from the first main body portion. Have,
The acoustic damper according to any one of claims 1 to 5. A compressor that compresses the refrigerant and
A condenser that condenses the refrigerant compressed by the compressor, and
An evaporator that evaporates the refrigerant condensed by the condenser, and
The acoustic damper according to any one of claims 1 to 6, which is arranged in a pipe connecting any of the compressor, the condenser, and the evaporator.
Equipped with a refrigerator.

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