JP5684031B2 - Silencer for turbo compressor and arrangement method of silencer - Google Patents

Description

  The present invention relates to a silencer for a turbo compressor and a method for arranging such a silencer, which are configured according to the writing of claim 1.

  The silencer of the above-described aspect is known from Patent Document 1.

European Patent Application Publication No. 0 574 605

  The object of the present invention is to reduce the intake pressure loss while maintaining the acoustic attenuation characteristics, or to insert the intake pressure loss without change, as long as the overall dimensions are the same. It is to provide a silencer according to claim 1, wherein the loss is increased. It is a further object of the present invention to provide a method for arranging such silencers.

  The above problem is solved by the silencer according to claim 1 or the method according to claim 11. Developments of the invention are defined in the respective dependent claims.

  According to a first aspect of the present invention, a silencer for an intake side of a turbo compressor is provided. The silencer includes a desirably cylindrical housing having a rear wall and a front wall as a cover member, and having an internal space formed between the rear wall and the front wall, A connection opening to the interior space and means for attaching the silencer to the turbo compressor. The silencer further includes a plurality of ring-shaped attenuation members each having an inner periphery and an outer periphery, and the attenuation members are arranged in layers in the axial direction of the housing and arranged in layers in the inner space. Arranged, each having a plurality of attenuation sectors. The silencer further includes a plurality of partition plates that are spaced apart from each other in the circumferential direction of the housing and extend radially in the inner space, preferably in a star shape, and these partition plates. Thus, the attenuation sector of each attenuation member is held at a position aligned in the tangential direction, and the internal space is divided into a plurality of spatial sectors. The silencer of the present invention is characterized in that the damping members are arranged at least partially apart from each other in the axial direction.

  In the present invention, the silencer is generated in the axial direction by the damping members being arranged at least partially different from each other in the axial direction, that is, not arranged at equal intervals in the axial direction. With regard to the partial pressure loss of the vessel, it can be adapted to the specific muffler requirements.

  That is, the distance between the attenuation members of the silencer is the internal space axis region where the achievable ratio of the total silencer by the silencer is high in the internal space axis region where the achievable ratio is low. Compared to, it can be made wider.

  By making the spacing between the damping members wider, some partial pressure loss and thereby the total intake pressure loss of the silencer can be reduced even if the total silence is optimal. On the other hand, more attenuating surfaces are placed or more reflective by narrowing the spacing of the attenuating members in the axial region within the interior space where the majority of the acoustic propagation in the relevant mode occurs. A ratio is achieved, thereby improving the silencer insertion loss overall.

  Therefore, preferably, in the interior space axial region where the achievable percentage of the total silencer of the silencer is the lowest, the spacing between the attenuation elements in the axial direction is wider than in the other axial regions of the interior space. ing. Desirably, in the interior space axial region where the achievable percentage of the total silencer of the silencer is the highest, the distance between the attenuation elements in the axial direction is narrower than in the other axial regions of the interior space. ing.

  According to a further embodiment of the silencer of the invention, the damping member arranged near the front wall with respect to the axial center of the housing is compared to the damping member arranged near the rear wall with respect to the axial center of the housing. The distance between each other in the axial direction is wider.

  It has been recognized by the present invention that the muffler has a relatively low rate of total silencing that can be achieved by a damping member located near the front wall relative to the axial center of the housing. Therefore, here, by increasing the spacing between the damping members without deteriorating the insertion loss of the silencer, for example, reducing the flow rate of the gaseous compressed fluid (e.g. air), the partial pressure loss and thereby the overall Intake pressure loss can be reduced.

  Desirably, the damping members are spaced apart from each other in the axial direction in the range of 5 mm to 150 mm.

  According to a further embodiment of the silencer according to the invention, the respective inner circumference of the damping member is at least partly configured with a different diameter. In other words, taking into account the specific flow conditions or requirements of the application, the compressed fluid is put into the turbo compressor in an optimal way, i.e. with minimal losses and turbulence, via a connection opening in the rear wall. In order to guide, the radial spacing between the damping members can be non-uniform. Thereby, the optimization of the inflow to the compressor is achieved by arranging the damping member in accordance with the purpose.

  According to a further embodiment of the silencer of the invention, the thickness of the absorber of the damping member is 5 mm or more. In accordance with the present invention, it has been recognized that the material thickness should not be less than 5 mm for optimal absorption behavior in the acoustic airborne sound excitation spectrum associated with the present invention.

  For example, the damping sector of each damping member may be composed of two perforated plate parts adjacent to each other with an absorbent material or a sound absorbing material in between, with the two perforated plate parts being separated from each other. The material thickness is 5 mm or more.

  According to a further embodiment of the silencer of the present invention, each damping member extends in a wave shape from its outer periphery toward its inner periphery.

  The dampening member having a corrugated or wavy shape prevents the sound waves spreading in the direction of the flow in the compressed fluid from passing straight, and the contact between the dampening member and the compressed fluid. The surface also increases, thereby improving absorption within the damping member.

  Preferably, each attenuating member corrugation has at least two opposite wave phases, i.e. one wave crest and one wave trough.

  According to a further embodiment of the silencer of the present invention, the wave form of the damping member has a respective fluid inflow path of the silencer formed by respective spacings between adjacent damping members in the region of the inner circumference. It is formed to bend in the direction toward the connection opening of the rear wall.

  By optimizing the shape of the damping member, the optimization of the inflow to the compressor can be easily achieved, and no additional guide member is required.

  According to a second aspect of the present invention, there is provided a method for arranging a silencer based on any possible combination of one, a plurality, or all of the above-described embodiments of the present invention, wherein: The respective radii of curvature of the damping members, and the respective axial spacings between the damping members, the mode configuration of the airborne sound that is prominent in the operating region of the turbo compressor, and in the silencer, It is defined according to the propagation.

  According to one embodiment of the method of the present invention, the respective corrugations of the damping member and the respective position of the damping member in the interior space of the silencer housing should be supplied to the turbo compressor via the silencer. It is defined that the maximum flow rate of the compressed fluid is achieved.

It is a perspective view of the silencer of one example of the present invention, and a part is cut open and illustrated.

  Hereinafter, the present invention will be described in detail using preferred embodiments and with reference to the accompanying drawings.

  FIG. 1 is a perspective view of a silencer 1 of one embodiment of the present invention for a turbo compressor (not shown), partially cut away.

  As shown in FIG. 1, the silencer 1 of the present invention for mounting on the intake side of a turbo compressor has a cylindrical housing 10, a plurality of ring-shaped damping members 20, and a plurality of partition plates 30. ing.

  The housing 10 has a rear wall 11 and a front wall 12 as a cylindrical cover member formed by the housing 10. An internal space 13 of the housing 10 is formed between the rear wall 11 and the front wall 12, and the rear wall 11 has a connection opening 11 a to the internal space 13.

  A ring flange 11b is provided outside the rear wall 11, and the silencer 1 can be attached to the intake side of the turbo compressor via the ring flange 11b.

  The damping members 20 each have an inner periphery 21 and an outer periphery 22, and are arranged in the inner space 13 so as to be layered with each other at intervals A in the axial direction AR of the housing 10.

  Each of the damping members 20 has a plurality of, in this figure, eight, partial annular damping sectors 23, which are one tangential direction or one in the circumferential direction UR of the housing 10. They are arranged in a circle.

  In this figure, the eight partition plates 30 are mutually arranged at the same angular distance in the circumferential direction UR of the housing 10, and are arranged on the central axis MA of the housing 10 in the center of the internal space 13 to be arranged on the front wall 12. The inner space 13 extends radially outward from the central tube 40 attached to the outer surface, particularly in a star shape, so that the damping sectors 23 of the respective damping members 20 are aligned with each other by the partition plate 30. The internal space 13 is subdivided into a plurality of spatial sectors 13a. Since the partition plates 30 are respectively attached to the rear wall 11 and the front wall 12, the housing 10 has a stable structure.

  In the region of the connection opening 11 a of the rear wall 11, the partition plates 30 each have a corrugated recess 31. As shown in FIG. 1, the recess has a boundary end of the recess 31 at the center axis MA. Is formed in a bell shape, the open side opens to the connection opening 11a, the closed side is connected to the center tube 40, and particularly opens into the center tube 40. It is formed as follows. This bell-shaped shape offers particularly structural mechanical advantages.

  Although not shown in FIG. 1, the damping members 20 are arranged at a distance A that is at least partially different in the axial direction AR.

  More specifically, the damping member 20 has an interval A in the axial direction AR in the axial region (region along the axial direction AR) of the internal space 13 that can achieve the lowest ratio of the total silencing of the silencer 1. Compared to the remaining axial region of the internal space 13, it is wider.

  On the other hand, in the axial region of the internal space 13 in which the damping member 20 can achieve the highest proportion of the total silencing of the silencer 1, the interval A in the axial direction AR is different from the remaining axial region of the internal space 13. In comparison, it is narrower.

  According to the embodiment of the present invention illustrated in FIG. 1, the damping member 20 disposed near or closest to the front wall 12 with respect to the axial center of the housing 10 (intermediate position of the length of the axial direction AR of the housing 10). Compared with the damping member 20 disposed near the rear wall 11 with respect to the axial center, the interval A in the axial direction AR is wider.

  Then, with respect to the embodiment of the present invention shown in FIG. 1, the two or three damping members 20 arranged on the right in FIG. 1 are more than the remaining damping members 20 arranged on the left side. It is also possible to widen the interval A.

  According to the present invention, the axial distance A between the damping members 20 is 5 mm to 150 mm.

  Although not so shown in FIG. 1, it is also possible for each inner circumference 21 of the damping member 20 to be at least partly configured with a different diameter, i.e. spaced apart from one another in the radial direction.

  The damping sector 23 of each damping member 20 is composed of two perforated plate parts 24 and 25 adjacent to each other, and has a material thickness (absorbing material thickness) of 5 mm or more between the two perforated plate parts. An absorbent material 26 is accommodated.

  Each of the damping members 20 starts from its outer periphery 22 and extends in a wave shape towards its inner periphery 21, which has at least two opposite wave phases, namely a wave peak and It has one wave valley.

  As can be seen from FIG. 1, in the region of the inner periphery 21, the wave shape of the damping member 20 is formed by the respective spaces A between the adjacent damping members 20, and the fluid inflow passages 27 of the silencer 1 are formed on the rear wall. 11 is formed to bend in a direction toward the connection opening 11a.

  By doing so, the compressed fluid (for example, air) that flows into the internal space 13 of the housing 10 from the outside in the radial direction via the respective fluid inlets 27a of the fluid inflow passage 27 can be connected to the rear wall 11 with less turbulence. It can guide to the opening part 11a and can guide to the intake side of a turbo compressor from there.

  Although not visible in FIG. 1, the fluid inlet 27a of the fluid inflow passage 27 is circumferentially covered as a cylindrical jacket member formed by the housing 10 for filtering the compressed fluid before entering the turbo compressor. A filter material can be provided.

  According to the method of the present invention for arranging the silencer 1, the radius of curvature of each of the damping members 20 and the respective spacing A in the axial direction AR between the damping members 20 is determined by the operating range of the turbo compressor. Is defined according to the mode structure of the air-transmitted sound and its propagation in the silencer.

  According to the method of the present invention for arranging the silencer 1, the respective corrugation of the attenuation member 20 and the position of the attenuation member 20 in the internal space 13 of the housing 10 of the silencer 1 are further silenced. It is defined that the maximum flow rate of the compressed fluid to be supplied to the turbo compressor via the vessel 1 is realized.

DESCRIPTION OF SYMBOLS 1 Silencer 10 Housing 11 Rear wall 11a Connection opening 11b Ring flange 12 Front wall 13 Internal space 13a Spatial sector 20 Damping member 21 Inner circumference 22 Outer 23 Damping sector 24 Perforated plate component 25 Perforated plate component 26 Absorber 27 Fluid inflow path 27a Fluid inlet 30 Partition plate 31 Recess 40 Central tube A Distance AR axial direction UR circumferential direction MA central axis

Claims (11)

A silencer (1) for a turbo compressor,
The housing (10) includes a rear wall (11) and a front wall (12) as cover surface members, and is formed between the rear wall (11) and the front wall (12). Means for attaching the opening (11a) to the inner space (13) and the silencer (1) to the turbo compressor on the rear wall (11). (11b) is provided,
Furthermore, it has a plurality of ring-shaped damping members (20) each having an inner circumference (21) and an outer circumference (22), and the damping members (20) are spaced from each other in the axial direction (AR) of the housing (10). (A) arranged in the inner space (13) side by side in layers, each having a plurality of attenuation sectors (23),
And a plurality of partition plates (30) extending radially in the internal space (13) and spaced apart from each other in the circumferential direction (UR) of the housing (10). In the silencer (1) in which the damping sector (23) of each damping member (20) is held by the partition plate (30) and the internal space (13) is divided into a plurality of spatial sectors (13a),
The attenuating members (20) are arranged at least partially in the axial direction (AR) at different intervals (A) ;
A silencer, wherein each damping member (20) extends in a wave shape from its outer periphery (22) toward its inner periphery (21) .   In the axial region where the damping member (20) can achieve the lowest proportion of the total silence of the silencer (1) of the internal space (13), the remaining axial region of the internal space (13) 2. The silencer according to claim 1, wherein the distance (A) in the axial direction (AR) is wider than the other.   In the axial region where the damping member (20) can achieve the highest proportion of the total silence of the silencer (1) in the internal space (13), the remaining axial region of the internal space (13) 3. The silencer according to claim 1, wherein the distance (A) in the axial direction (AR) is narrower than the other.   A damping member (20) disposed near the front wall (12) with respect to the axial center of the housing (10) is disposed in the vicinity of the rear wall (11) with respect to the axial center. The silencer according to any one of claims 1 to 3, wherein a distance (A) between each other in the axial direction (AR) is wider than that in the axial direction (AR).   The silencer according to any one of claims 1 to 4, wherein the damping member (20) has an interval (A) in the range of 5 mm to 150 mm in the axial direction (AR).   6. The muffler according to claim 1, wherein an inner circumference (21) of each of the damping members (20) is at least partially configured with a different diameter.   The silencer according to any one of claims 1 to 6, wherein the thickness of the absorbing member (20) is 5 mm or more. The muffler according to any one of claims 1 to 7, wherein the corrugation of each attenuation member (20) has at least two opposite wave phases. In the silencer (1), the corrugation of the damping member (20) is formed in the region of the inner circumference (21) by the respective intervals (A) between the adjacent damping members (20). Each of the fluid inflow paths (27) is formed so as to bend in a direction toward the connection opening (11a) of the rear wall (11) . The silencer according to one item . A method of arranging the silencer (1) as claimed in any one of claims 9, each of the corrugated radius of curvature of the damping member (20), and said damping member (20 ) In the axial direction (AR) is defined according to the air transmission sound mode configuration prominent in the operating region of the turbo compressor and its propagation in the silencer (1). A method characterized by that. The respective wave types and the respective positions of the attenuation members (20) in the internal space (13) of the housing (10) of the silencer (1) are arranged via the silencer (1). The method according to claim 10 , characterized in that a maximum flow rate of the compressed fluid to be supplied to the turbocompressor is defined.

Images