RU2579104C2 - Soundproofing cladding of technical room - Google Patents

Abstract

FIELD: construction.

SUBSTANCE: soundproofing cladding of a technical room is represented by a soundproofing front flat-sheet and/or soundproofing non-flat formed panel, spaced mounted with reference to an oppositely located bearing wall (ceiling) structure of the technical room, with the formation of respective closed air cavities. To the named soundproofing front panels and/or the bearing wall (ceiling) structures of the technical room in a respective manner quarter wave acoustic R' resonators and/or half-wave acoustic resonators R" are fixed, which are frequency adjusted and temperature adapted for the suppression of acoustic resonances which are formed in the air cavities formed in their own cross and longitudinal acoustic modes. The similar function of suppression of amplitude values of the acoustic resonances formed in the air cavities between the oppositely located walls of the soundproofing front panel and the bearing wall (ceiling) structure of the technical room is performed by isolated briquetted sound-absorbing modules which are appropriately placed in pre-set spatial zones of the air cavities. Basic constructive elements of the soundproofing cladding - soundproofing front panels (flat-sheet and/or non-flat formed), acoustic resonators (quarter wave - R', half-wave - R"), the isolated briquetted sound-absorbing modules containing in compositions of formed nodal structures can be added by elements of their assembly fixture - mechanical fasteners, adhesive substances (sticky glue, thermoactive substances), and also they are in addition fitted with respective sealing soundproofing elements, anti-vibration bearing elements, thermoinsulating elements, dissipative soundproofing elements, coating sound transparent layers of film foil, fabric (nonwoven) materials. To provide efficient functioning of the acoustic resonators R' and R" in the expanded (changing) frequency range caused, inter alia, by the change of temperature of the environment of propagation of sound waves (air), the composition of their structures is integrated by dissipative sound damping elements of various types - perforation holes in walls of tubular parts, and/or porous airblown plugs placed in the cavities of the tubular parts, and/or the coating sound-transparent layers of materials mounted on throat parts of the acoustic resonators and/or on punched sections of the tubular parts of the acoustic resonators. To provide efficient functioning of the isolated briquetted sound-absorbing modules by the accompanying reduction of volume of the used porous sound-absorbing substance (isolated shredded fragmented sound-absorbing elements) their pre-set spatial placement in an air cavity under the soundproofing cladding envisions the installation in the peripheral angular and/or end sections formed by mounting interfaces of the walls of the front soundproofing panels with the respective counter surfaces of bearing elements of the technical room (walls, ceiling, internal partition). Various combinations and types of constructional materials are given, effective ranges of the change of their structural compositions and physical parameters favouring to solving the target task of the development of the technical device "Soundproofing Cladding of Technical Room" are established.

EFFECT: invention allows improving the noise-reducing efficiency of the technical device which is performed in the expanded frequency range of the sound spectrum.

25 cl, 31 dwg

Description

The invention relates to the field of noise reducing structures, designed to reduce noise levels of various types of noise-vibrational technical objects that produce acoustic (noise) pollution. First of all, this applies to production and technological equipment (pumping, compressor stations), power plants (internal combustion engines, diesel generator sets), ventilation and air conditioning systems, electric machines (electric motors, electric transformers), sanitary appliances and other noise-vibration technical devices located inside noise-generating (noise-active) technical premises. It can also be used to improve acoustic comfort in residential, industrial and public premises of buildings and structures adjacent to these noise generating technical rooms.

It is known that in order to protect the environment from intense acoustic pollution produced by various types of noise-generating technical objects, various types of soundproofing (soundproofing) fencing of technical rooms (screens, casings, panel soundproofing linings of bearing and / or hull structures, equipped with additional layers of vibration and sound damping are widely used) , and / or sound-absorbing and / or sound-insulating materials.Single or various types of acoustic resonators interlocked in the form of aggregated modular batteries - quarter-wave, half-wave, Helmholtz, or volume expansion chambers connected to noise-transmitting channels of the corresponding type are used.In the vast majority of cases, various combined combinations of the above types of noise-suppressing (noise-reducing) technical devices are used. a wide variety of types of noise-suppressing techniques and devices for It will to some extent to ensure the safe and shumokomfortnuyu habitat for humans and animals. In particular, various types of hybrid noise-reducing structures are widely used, using the combined implementation of physical processes of sound absorption and sound insulation, where the total noise-reducing effect of the technical device used can be based both on the effects of sound energy reflection and on the combined combination of sound absorption and sound reflection effects. This type of technical sound-attenuating devices may, in particular, not contain porous sound-absorbing structures, and the arising sound-attenuation effect can be realized solely by the functioning of individual frequency-tuned resonant acoustic elements, including the use of perforated plate-like structures located near hard sound-reflecting surfaces, with the formation cavity resonator devices (Helmholtz acoustic resonators).

As well-known examples of the use of technical devices operating according to the physical principle noted above, in particular, various types of panel-cavity noise-reducing structures can be indicated:

- international application for the invention of WO 2009/131855 A2 (published on October 29, 2009);

- international application for the invention of WO 2008/138840 A1 (published on November 20, 2008);

- international application for the invention of WO 2009/037765 A1 (published on September 20, 2007);

- German patent for invention DE 4315759 (published on 05/11/1993);

- international application for the invention WO 2006056351 (published on January 6, 2006);

- RF patent for the invention RU 2206458 (published on 06/20/2003);

- French patent for the invention of FR 2910685 (published on June 27, 2008);

- Japan's application for the invention of JP 2008-96826 A (published on October 13, 2006);

- Japan's application for the invention of JP 2007-186186 (published on July 26, 2007);

- RF patent for utility model RU 61353 (published on 02.27.2007);

- RF patent for utility model RU 67650 (published October 27, 2007).

The expressed useful advantages of using the above technical devices include the possibility of their use in aggressive environments, high temperatures and intense dynamic loads, due to the exclusion of the use of porous fibrous and / or foamed open-cell structures of organic or synthetic origin characterized by insufficiently high thermal moisture and bioresistant characteristics. They use exclusively dense structures of perforated metal or heat-resistant polymeric materials with the possible inclusion of heat-resistant porous fibrous (basalt, glass) and / or foamed open-cell metallic and / or ceramic materials. At the same time, the negative technical characteristics of this type of noise suppressing devices include their narrow operating frequency range of operation with an insufficiently high level of achievement of the sound attenuation effect, high cost, poor overall performance and increased material consumption. At the current level of technological development, these factors may limit their widespread distribution in the effective solution of urgent practical problems of suppressing noise emissions produced by noise-generating technical objects.

Accordingly, panel-cavity noise-reducing structures are known and widely distributed, the formed cavities of which are completely or partially filled with a porous sound-absorbing substance of a fibrous and / or open-cell foam type (organic, mineral, synthetic origin), characterized by higher sound-absorbing (noise-reducing) characteristics in the middle and high frequencies of a sound range (over 500 Hz). In this type of noise-reducing designs, the front (front) wall of the panel is usually perforated with a high value of the perforation coefficient, which gives it the properties of acceptable sound transparency and ensures the passage of sound waves into the cavity filled with porous sound-absorbing material. Through, mainly round holes or narrow slotted grooves with bends are the most common type of perforation of this type of front panel wall. As examples of this type of known noise reduction technical devices, it should be noted:

- French patent for the invention of FR 2899919 (published on 10/19/2007);

- French patent for the invention of FR 2899992 (published on 10/19/2007);

- US patent for the invention of US 3991848 (published 16.09.1974);

- US patent for the invention of US 5422466 (published 03/11/1994);

- Japan patent for invention JP 11104898 (published on 04/20/1999);

- international application for the invention of WO 2007/017317 (published 02.15.2007);

- Japan patent for invention JP 62165043 (published July 21, 1987);

- German application for invention DE 4332856 (published on 09/27/1993);

- European patent for the invention of EP 1477302 A1 (published on November 17, 2004);

- Japan's application for invention JP 2000034937 (published 02.02.2000);

- German application for invention DE 202004018241 (published on November 24, 2004);

- UK patent for the invention of GB 1579897 (published on 06/03/1976);

- German patent for the invention DE 4332845 A1 (published on 09/27/1993);

- European patent for the invention EP 0697051 B1 (published on 04/20/1994);

- international application for the invention WO 2004/013427 A1 (published 12.02.2004);

- RF patent for the invention RU 2042547 (published on 08.27.1995).

The above-mentioned well-known noise-reducing technical devices, along with satisfactory acoustic characteristics that are realized in the medium and high frequencies of the sound range, are characterized by a certain loss of sound-damping properties due to the formation of an abrupt change in the wave acoustic resistance at the flat boundary of the separation of the elastic medium of propagation of sound waves in the considered zone of air adjacent to a solid flat wall perforated l front panel. This entails a partial loss of sound-absorbing effect, while the perforation holes distributed over the entire surface of the wall also cause a certain loss of soundproofing properties. Also, there is a relatively high cost of porous sound-absorbing substances used in this type of construction, produced mainly from non-renewable carbon raw materials (oil, gas), and they are also characterized by rather complex and labor-intensive problems of the final disposal of heterogeneous structural materials used in the components and assemblies of the specified type of noise-reducing technical devices after they complete their life cycle.

To increase the noise-reducing properties of this type of structure, by providing smoother (non-spasmodic) coordination of wave (acoustic) impedances along the propagation paths of sound waves in the boundary zones of the elastic air medium, the propagation of sound waves, including the boundaries of contact of the external hard-shell surface of the panel of the technical device with the external and non-planar corrugations are attached to the internal cavity zones of the adjoining air environment The ideal geometric shape (wedge-shaped, wave-like), as it is, in particular, presented in the following well-known technical devices:

- RF patent for the invention RU 2249258 (published September 27, 2004);

- US patent for the invention of US 4097633 (published on 06/27/1978);

- German application for invention DE 4237513 (published on November 7, 1992);

- US application for invention US 2003207086 (published June 11, 2003);

- European patent for the invention EP 0253376 A2 (published on 01.20.1988);

- RF patent for the invention RU 2161825 (published on January 10, 2001);

- Australian application for invention AU 2007100636 (published August 16, 2007).

The above noise-reducing constructions of technical devices are characterized, first of all, by the complexity of the technological design and relatively high cost, with insufficiently high sound-insulating ability (the presence of “sound-proof dips” in separate frequency ranges of the noise damping characteristic due to the formation of cavity airborne acoustic resonances).

Another well-known technical direction for improving the design of technical devices for attenuating sound energy generated by vibro-noise-related technical objects associated with an increase in the proportion of absorbed sound energy is the implementation in the front face panel of a technical device that directly receives incident sound waves, perforation holes of predetermined geometric shapes and certain overall dimensions . This type of noise reducing technical devices are known from the following patent documents:

- German patent for the invention DE 4315759 C1 (published on 05/11/1993);

- US patent for the invention of US 6194052 B1 (published on 06/20/1998);

- European patent for the invention EP 1146178 A2 (published March 15, 2001);

- European patent for the invention EP 1950357 A1 (published on July 30, 2000);

- US applications for the invention US 2007/0272472 A1 (published November 29, 2007);

- international application for the invention WO 2006/101403 A1 (published on September 28, 2006);

- US applications for the invention US 2007/0151800 A1 (published 05.06.2007).

These noise-reducing technical devices can be characterized, to a certain extent, by improved operational and decorative (improved external design) properties. However, their noise-reducing properties are not high enough due to the limited potential used for the effectiveness of the structural modification of a technical device based on the rationalization of the geometric shapes of perforation holes. Also, their manufacture is associated with the need to use sufficiently sophisticated technological equipment to ensure compliance with narrow technological tolerances for manufacturing.

Known noise-reducing technical devices made in the form of composite soundproof fencing, the structural elements of which combined combine several technical methods (realizable effects), borrowed from the groups of the known technical devices considered above, which make it possible to purposefully improve their acoustic properties. This type of hybrid hybrid noise reduction technical devices are described in the following patent documents:

- RF patent for the invention RU 2295089 (published March 10, 2007);

- French patent for the invention FR 2929749 (published 09.10.2009);

- UK patent for invention GB 822954 (published 04.11.1959);

- RF patent for the invention RU 2340478 (published on December 10, 2008);

- Japanese application for invention JP 2002175083 (published June 21, 2002).

The disadvantages of the noise-reducing technical devices presented above are the higher complexity and laboriousness of their manufacture, with unsatisfactory environmental and cost indicators, as well as insufficiently high achievable potentials for improving noise-attenuation characteristics in a normalized wide range of sound frequencies.

As a prototype, a technical solution was made according to the RF patent for invention No. 2465390, published on January 20, 2011, which describes the design of a soundproof fence made in the form of a noise-reducing screen containing load-bearing elements such as transverse struts and longitudinal profiles, the corresponding type of sound-absorbing element, located with a predetermined air gap in the cavity between the rear sound-reflecting panel and the front sound-transparent panel perforated through the holes, while the specified noise the absorbing element contains a supporting base of sheet perforated or mesh type, fixed by mechanical fasteners to horizontal profiles and / or the base of the noise-reducing screen, lined with at least one of its sides, separated by sound-absorbing panels representing a set of crushed fragments of porous fibrous or foamed open-mesh sound-absorbing materials that are distributed in a certain way and fixedly mounted on the surface of the carrier base, with the formation of the corresponding air gaps between them. At least from the standpoint of the placement of separate sound-absorbing panels, the surface of the noise-reducing element is lined with a layer of a soundproof gas-impermeable film or fabric. A significant drawback of the presented technical solution for the prototype is the limited possibility of its effective use, which is carried out mainly in open spaces to protect residential areas of settlements from negative noise impacts generated by vehicles and industrial equipment installed near roads and railways, airfields, open sections of lines subway, test sites, noise building and industrial sites, or any other spatially directed sources of increased noise radiation, producing intense acoustic pollution of the environment. This necessitates, in particular, the need to use additional load-bearing supporting elements (transverse struts and longitudinal profiles) as part of this type of soundproofing fence, which significantly complicates this design and leads to an increase in its weight and size parameters and cost. At the same time, the use of a supporting base in the form of a flat-sheet geometric shape, fixed in a vertical position on horizontal profiles or the base, complicates the process of subsequent placement of separate sound-absorbing panels, and also complicates the implementation of sound-insulating fencing of complex spatial geometric shape. A limited choice of overall dimensions and geometric shapes, physical and mechanical parameters, if necessary, compliance with the specified values of the air gaps between individual samples of separate sound-absorbing panels, determines the insufficient absorption of sound energy in a diffuse sound field in enclosed spaces and is observed in a narrowed working frequency range characteristic only for spatially expressed local emitters of sound energy in a free sound field ty pa moving vehicles (cars and trucks, buses) or railway vehicles in open spaces.

The technical result achieved by the implementation of the claimed invention consists in a predetermined improvement in noise-reducing efficiency, carried out in the extended frequency range of the sound spectrum, including the conditions of non-directional generation of diffuse sound field formed in the confined spaces of technical rooms, increasing the possible areas of application of the technical device, increasing its "universalization", "unification", and "typification", including by simplifying the process placement of separate sound-absorbing panels as part of the design of a sound-insulating fence, which, ultimately, ensures a reduction in material and labor costs in its manufacture. The above technical terms imply the implementation of the following effects. Universalization provides an increase in the efficiency of use of the claimed technical object by expanding its functions, with an increase in the range of possible realizable technical areas of use (telling it the properties of multifunctionality). In this case, the main economic importance of universalization is realized, which consists in replacing several specialized technical objects (elements) that perform separate functions or are used in separate areas with one universal multifunctional technical object. The term unification means a relative reduction in the variety of elements used in the claimed technical device, compared with the known variety of systems in which they are used. The term typification means a unification method that implements well-known standard solutions when creating the claimed technical device.

For these reasons, the inventive technical device presented takes into account, in particular, the use of original sound-absorbing elements formed from the corresponding semi-finished raw materials produced by recycled recycled processing of solid polymer structures, which are represented, in particular, by industrial and technological marriage and production waste, mainly polymer sound-absorbing and soundproofing materials and structures of noise-reducing devices (screens, covers, upholstery, hl ), as well as a similar type of construction of parts and assemblies dismantled from technical facilities that have completed their life cycle and are subject, in this regard, to appropriate disposal processes (cars, trucks, buses, river and sea vessels, air and rail vehicles , building constructions, household appliances, etc.)

In this type of recycling technologies and devices, appropriate terminological definitions of the type “recycling, waste, disposal, recycling” are used, which are given below.

The term "recycling" means the collection, transportation, disassembly, disposal of technical objects and the disposal of unused waste. The term "disposal" means the use of waste for good. The term "waste" means any substance or object that has completed its life cycle that the owner of a technical object throws away, or intends to throw it away, or they are to be thrown away. The term "recycling" means the return to production of materials for their subsequent processing. The use of recycled materials, for example, for the manufacture of vehicles is an important environmental and social task and is encouraged at the international level, in particular by the action of the European Community Directive (Directive 2000/53 / EC). At the same time, it must be borne in mind that in such cases, the characteristics of the manufactured components (technical devices) made of this type of recycled materials should in no way be impaired. Using the appropriate labeling system, decisions are made on the separated sorting of materials, their subsequent separated processing or disposal as part of non-recyclable materials. For these purposes, vehicle manufacturers, together with manufacturers of components (parts, assemblies) and manufacturers of materials for them, are required to use the relevant international standards for the code designation of assemblies and materials and, in particular, to identify those parts and materials that are suitable for recovery, recycled recycling, or energy recovery.

As the advantages of the claimed technical solution in relation to well-known analogues and prototype, it should include the implementation of physical principles in it of effective suppression of resonating intrinsic acoustic modes (transverse, longitudinal) arising in air cavities formed by the clearance of the walls of the front (flat-sheet or non-planar molded) panels relative to Opposite surfaces of sound-reflecting enclosing panels as part of a noise-reducing structure of a technical device represented by soundproofing sewn technical premises. This eliminates the numerous "gaps" of the noise reduction effects in the frequency response of the sound insulation of the technical device and, as a result, increase its resulting noise-damping efficiency. Implementation of the principle of minimizing the degree of perforation of the walls of the front panels, optimizing the location of the holes of the perforations on the walls of the front panels, installing in the zones of the perforated areas with their effective overlap by separate constructions of isolated briquette sound-absorbing modules made using separate fragmented fragmented elements, using quarter-wave and half-wave acoustic resonators, throat parts of which are placed in predetermined spaces the zones of the air cavities formed by the walls of the front panels and the opposed surfaces of the sound-reflecting enclosing panels, minimizing the mass of the used porous sound-absorbing substance used in the composition of the isolated briquetted sound-absorbing modules - can ultimately significantly improve both technical (sound-damping) and environmental and cost characteristics of the claimed technical device - soundproofing sewn technical premises. In more detail, the implementation of these technical (structural-technological) techniques and the used composite structural elements will be described below.

To ensure an unambiguous perception of the differences of the essential features of the claimed technical solution, the following are the corresponding digital designations of its constituent structural elements, as well as the alphabetic designations of the constituent structural elements and the associated physical parameters of the vibro-acoustic fields, the name of graphic (outline) images of the circuits of the applied structural elements depicted on the figures of the description of the application for invention. Also included are some specific terminological definitions used in the text of the description of the application for an invention (in italics).

Name of graphic (outline) images:

- in FIG. 1 shows a general view of a technical room 1 with a sound-generating technical object 25 located in it, in which, opposite to the surfaces of the sound-reflecting enclosing panels of the supporting elements 2 (walls) with a predetermined air gap, sound-insulating front flat-panel panels 4 are placed, and separate air cavities formed by them are mounted briquetted sound-absorbing modules 10;

- in FIG. 2 shows a general view of a technical room 1 with a noise-generating technical object 25 (not shown in FIG. 1), in which soundproof front flat panels 4 are placed opposite to the surfaces of the sound-reflecting enclosing panels of the supporting elements 2 (walls) with a given air gap of width d and in each of the air cavities formed by them, nine separate briquetted sound-absorbing modules 10 are mounted;

- in FIG. 3 shows a fragment of a technical room 1 with a noise generating technical object 25 (not shown in FIG. 1), in which the soundproofing face plate panels 4 are placed on the opposite to the surface of the sound-reflecting enclosing panel of the supporting element 2 (wall) with a given air gap of width d the inner surfaces of which quarter-wave acoustic resonators R ^{I are} mounted in the formed air cavity (pos. 26);

- in FIG. 4 shows a fragment of a technical room 1 with a noise-generating technical object 25 (not shown in FIG. 1), in which soundproof front flat panels 4 are placed opposite to the surface of the sound-reflecting enclosing panel of the bearing element 2 (wall) with a given air gap of width d formed air cavity on the inner surfaces of the sound-reflecting enclosing panel of the bearing element 2 (wall) and the sound-insulating front flat panel 4 mounted quarter-wave acoustic female resonators R ^I (pos. 26);

- in FIG. 5 shows a fragment of a technical room 1 with a sound-generating technical object 25 (not shown in FIG. 1) placed in it, in which the soundproof face plate panels 4 are placed opposite to the surface of the sound-reflecting enclosing panel of the bearing element 2 (wall) with a given air gap of width d formed air cavity on the inner surfaces of the sound-reflecting enclosing panel of the bearing element 2 (wall) mounted quarter-wave acoustic resonators R ^I (key 26), and on the inner surface the soundproof front panel 4 - mounted half-wave acoustic resonators R ^II (item 27);

- in FIG. 6 is a fragment of a technical room 1 with a sound-generating technical object 25 (not shown in FIG. 1) placed in it, in which the soundproof front flat panels 4 are placed opposite to the surface of the sound-reflecting enclosing panel of the bearing element 2 (wall) with a given air gap of width d formed air cavity on the inner surfaces of the sound-reflecting enclosing panel of the bearing element 2 (wall) and the sound-insulating front plane-sheet panel 4 mounted acoustically e resonators R ^II (pos. 27);

- in FIG. 7 shows the mounting circuit quarter-wave acoustic resonators R ^I (pos. 26) mounted in the air cavity formed by a reflecting cladding panel of the carrier element 2 and oppositely installed sound insulating face ploskolistovoy 4 or soundproofing face shaped nonplanar 5 panel on the surface of a reflecting cladding panel of the carrier element 2 with using a mechanical fastener 23 (Fig. 7a, b) and / or an intermediate layer of an adhesive viscoelastic vibration-damping about the material 18 (Fig. 7B);

- in FIG. 8 is a diagram of the sound-reflecting enclosing panel of the bearing element 2 (wall) of the technical room 1, the opposite of which with a given air gap (width from d _min to d _max ) is placed a sound-insulating front molded non-planar panel 5, mounted in the formed air cavity on the inner surfaces of the said panel 5 quarter-wave acoustic resonators R ^I (pos. 26);

- in FIG. 9 is a diagram of a sound-reflecting enclosing panel of a bearing element 2 (wall) of a technical room 1, opposite which with a given air gap (width d _min to d _max ) is placed a sound-insulating front molded non-planar panel 5, mounted in the formed air cavity on the inner surfaces of said panel 5 half-wave acoustic resonators R ^II (pos. 27);

- in FIG. 10 is a diagram interlocked prefabricated modular assembly composed of four quarter-wave acoustic resonators R ^I (26 pos.) From the hollow tubular parts 31;

- in FIG. 11 is a diagram of a blocked modular assembly made up of four quarter-wave acoustic resonators R ^I (key 26) with installed damping elements (key 9, 16, 34);

- in FIG. 12 is a diagram of a blocked modular assembly made up of four half-wave acoustic resonators R ^II (key 27) with hollow tubular parts 31;

- in FIG. 13 is a diagram of a blocked modular modular assembly 13 composed of four half-wave acoustic resonators R ^II (pos. 27) with installed damping elements (pos. 9, 16, 34);

, $${\text{l}}_{\text{r}}{}^{\text{II}}$$

и динамические длины $${\text{l}}_{\text{R}}{}^{\text{I}}$$

, $${\text{l}}_{\text{R}}{}^{\text{II}}$$

четвертьволнового акустического резонатора R^I (поз. 26) и полуволнового акустического резонатора R^II (поз. 27), а также параметр γ - в виде кратчайшего расстояния между контурами горловых частей 30, трубчатой 31 части полуволнового акустического резонатора R^II (поз. 27), отсчитываемого в плоскости его открытых геометрических срезов трубчатой части 31;- in FIG. 14 are diagrams illustrating geometric lengths $${\text{l}}_{\text{r}}{}^{\text{I}}$$

, $${\text{l}}_{\text{r}}{}^{\text{II}}$$

and dynamic lengths $${\text{l}}_{\text{R}}{}^{\text{I}}$$

, $${\text{l}}_{\text{R}}{}^{\text{II}}$$

a quarter-wave acoustic resonator R ^I (pos. 26) and a half-wave acoustic resonator R ^II (pos. 27), as well as parameter γ - in the form of the shortest distance between the contours of the neck parts 30, a tubular 31 part of a half-wave acoustic resonator R ^II (pos. 27) counted in the plane of its open geometric sections of the tubular part 31;

- in FIG. 15 shows diagrams of quarter-wave acoustic resonators R ^I (key 26, FIG. 15a, c) and half-wave acoustic resonators R ^II (key 27, FIG. 6, d) integrated into the structural structures of the supporting elements 2 of the technical room 1, in embodiments without damping elements (Fig. 15a, b) and with a damping element in the form of a lining soundproof layer 16 (Fig. 15c, d);

- in FIG. 16 is a diagram of the sound-reflecting enclosing panel of the bearing element 2 (wall) of the technical room 1, the opposite of which with a given air gap (width d) is placed on the soundproofing face plate 4, in the formed air cavity on the inner surfaces of said panel 4, at the end sections of the interfaces of which on the opposite surfaces of the supporting element 2 and in the spatial zones of the halves and / or quarters of the overall lengths of the air cavity of the soundproofing suturing 28, separate bricks are mounted ted absorbing units 10;

- in FIG. 17 shows a fragment of a technical room 1 with a noise generating technical object 25 (not shown in FIG. 1), in which a soundproof front flat panel 4 is placed opposite to the surface of the sound-reflecting enclosing panel of the bearing element 2 (wall) with a predetermined air gap (width d), at the end sections of the interfaces of which with the counter surfaces of the supporting element 2 and in the central spatial zone of the air cavity of the soundproofing suturing 28, there are mounted to a friend, separate briquetted sound-absorbing modules 10;

- in FIG. 18 is a diagram of the sound-reflecting enclosing panel of the bearing element 2 (wall) of the technical room 1, the opposite of which with a given air gap (width d) is placed on the soundproofing face plate 4, in the formed air cavity on the inner surfaces of the panel 4, at the end sections of the interfaces of which with the oncoming the surfaces of the supporting element 2 and in the Central spatial zone of the air cavity of the soundproofing suturing 28, mounted five separate briquetted sound-absorbing fashion lei 10;

- in FIG. 19 is a diagram of the sound-reflecting enclosing panel of the bearing element 2 (wall) of the technical room 1, the opposite of which with a given air gap (width d) is placed on the soundproofing face plate 4, in the formed air cavity on the inner surfaces of the panel 4, at the end sections of the interfaces with the surfaces of the supporting element 2 and in the central spatial zone of the air cavity of the soundproofing suturing 28, five groups of nine gaping located to each other mounted osoblennyh briquetted sound absorbing units 10;

- in FIG. 20 shows a diagram of a sound-reflecting enclosing panel of a bearing element 2 (wall) of a technical room 1, the opposite of which with a given air gap (width d), has a sound-insulating front flat-panel panel 4, in the formed air cavity on the inner surfaces of the panel 4, at the end sections of the interfaces of which with the oncoming the surfaces of the supporting element 2 and in the central spatial zone of the air cavity of the soundproofing suturing 28, five groups of nine nine spaced apart osoblennyh briquetted sound-absorbing module 10, with a central surface zone soundproofing ploskolistovoy front panel 4 are perforations 9;

- in FIG. 21 is a diagram of a sound-reflecting enclosing panel of a bearing element 2 (wall) of a technical room 1, opposite which with a predetermined air gap (width d) is placed a sound-insulating front flat-panel panel 4, thirteen separate briquetted sound-absorbing modules 10 are mounted on the inner surfaces of the panel 4;

- in FIG. 22 is a diagram of a sound-reflecting enclosing panel of a bearing element 2 (wall) of a technical room 1, opposite which with a given air gap (width d _min ... d _max ) is placed a sound-insulating front molded non-flat panel 5 using sealing sound-insulating elements 29 of the peripheral zones in the undercavity cavities, formed by separate five convex containers made in the wall of the soundproofing front molded non-flat panel 5, fifteen separate briquetted sound opogloschayuschih modules 10, upper and lower end surfaces of the sound insulating molded nonplanar front panel 5 overlapped footer sound transmission layer 16 (not shown);

- in FIG. 23 is a diagram of a sound-reflecting enclosing panel of a bearing element 2 (wall) of a technical room 1, opposite which with a given air gap (width d _min ... d _max ) is placed a sound-insulating front molded non-planar panel 5, in the undercut cavities formed by five separate convex containers made in the wall of the soundproofing front molded non-planar panel 5, mounted fifteen separate briquetted sound-absorbing modules 10, the upper and lower end surfaces of the soundproofing the front molded non-planar panel 5 is blocked by a lining sound-transparent layer 16 until contacting with the enclosing panel of the supporting element 2 (wall) of the technical room 1;

- in FIG. 24 is a diagram of a sound-reflecting enclosing panel of a bearing element 2 (wall) of a technical room 1, opposite which with a predetermined air gap (width d) a sound-insulating front molded non-planar panel 5 is placed in the undercut cavities formed by fifteen separate convex containers 6 having a cross section of a truncated pyramid made in the wall of the soundproofing front molded non-planar panel 5, mounted fifteen separate briquetted sound-absorbing modules 10;

- in FIG. 25 is a diagram of a sound-reflecting enclosing panel of a bearing element 2 (wall) of a technical room 1, opposite which with a predetermined air gap (width d) is placed a sound-insulating front molded non-flat panel 5, in the undercavity cavities formed by fifteen separate convex containers 6 having a cross section of a circle, made in the wall of the soundproofing front molded non-planar panel 5, mounted fifteen separate briquetted sound-absorbing modules 10, while soundproofing the front molded non-planar faceplate 5 in the walls of the peaks 8 bounded by contact mating zones with the surfaces of the isolated briquette sound-absorbing modules 10 is perforated with perforation holes 9;

- in FIG. 26 is a diagram of a sound-reflecting enclosing panel of a bearing element 2 (wall) of a technical room 1, opposite which with a given air gap (width d), a sound-insulating front molded non-planar panel 5 is placed in the undercut cavities formed by fifteen separate convex containers 6 having a cross section of a truncated pyramid made in the wall of the soundproofing front molded non-planar panel 5, mounted fifteen separate briquetted sound-absorbing modules 10, while m soundproof front molded non-planar panel 5 in the walls of the peaks 8, limited by zones of contact mating with the surfaces of separate briquetted sound-absorbing modules 10 is perforated with perforation holes 9;

- in FIG. 27 is a diagram of the sound-reflecting enclosing panel of the supporting element 2 (wall) of the technical room 1, the opposite of which with a predetermined air gap (width d) is placed on the sound-insulating front molded non-flat panel 5, in the undercut cavities formed by fifteen separate convex containers 6 having a cross section of a truncated pyramid made in the wall of the soundproofing front molded non-planar panel 5, mounted fifteen separate briquetted sound-absorbing modules 10, while m soundproof front molded non-planar panel 5 in the walls of the peaks 8 and the side walls 7 limited by zones of contact mating with the surfaces of the isolated briquetted sound-absorbing modules 10 is perforated with perforation holes 9;

- in FIG. 28 is a diagram of a sound-reflecting enclosing panel of a bearing element 2 (wall) of a technical room 1, opposite which with a predetermined air gap (width d) is placed a sound-insulating front molded non-flat panel 5, in the undercavity cavities formed by four separate convex containers 6 having a cross section of a truncated pyramid made in the wall of the soundproofing front molded non-planar panel 5, four separate briquetted sound-absorbing modules 10 are mounted;

- in FIG. 29 is a diagram of a sound-reflecting enclosing panel of a bearing element 2 (wall) of a technical room 1, opposite which with a predetermined air gap (width d) is placed a sound-insulating front molded non-planar panel 5, in the undercavity cavities formed by five separate convex containers 6 having a cross section of a truncated pyramid made of the central part of the wall of the soundproofing front molded non-planar panel 5, five separate briquetted sound-absorbing modules 10 are mounted, with this soundproof front molded non-planar panel 5 in the walls of the peaks 8 limited by zones of contact mating with the surfaces of the isolated briquetted sound-absorbing modules 10 is perforated with perforation holes 9;

- in FIG. 30 shows diagrams of isolated briquette sound-absorbing modules 10 formed by separate crushed fragmented sound-absorbing elements 13 having a porous 14 and non-porous 15 material structure, placed in the cavities of closed separate containers 6 of sound-transparent shells 11, having a cross section of a rectangle (a), triangle (b) , trapezoid (c), circle (d), circular segment (e);

- in FIG. 31 shows diagrams of separate briquetted sound-absorbing modules 10 formed by separate crushed fragmented sound-absorbing elements 13 having a porous 14 and non-porous 15 structure of the material, placed in the cavities of closed separate containers 6 of sound-transparent shells 11, with integrated sound-transparent embedded reinforcing elements 33 of the core 35 () mesh 36 (b) and sheet perforated 37 (c) types.

Accepted digital designations of the constituent structural elements of the claimed device "Soundproofing sewing of technical premises":

1 - technical room with the noise-generating technical object 25 located therein (the position is not shown in the figures);

2 - load-bearing elements - walls, ceiling, internal partitions of the technical room 1;

3 - the surface of the sound-reflecting enclosing panels of the supporting elements 2 - walls, ceiling, internal partitions of the technical room 1;

4 - soundproofing front flat panel soundproofing suturing 28;

5 - soundproofing front molded non-flat panel of soundproofing suturing 28;

6 - separate containers of the soundproofing front molded non-planar panel 5 of the soundproofing suturing 28;

7 - side walls of separate containers 6 of the soundproofing front molded non-planar panel 5 of the soundproofing suturing 28;

8 - walls of the vertices of the separate containers 6 of the soundproofing front molded non-planar panel 5 of the soundproofing suturing 28;

9 - perforation holes;

10 - separate briquetted sound-absorbing modules;

11 - load-bearing transparent translucent shells of separate briquetted sound-absorbing modules 10;

12 - closed separate capacitance of the supporting sound-transparent shells 11 of the separate briquetted sound-absorbing modules 10;

13 - separate fragmented fragmented sound-absorbing elements;

14 - porous structure of a separate crushed fragmented sound-absorbing element 13;

15 - non-porous (dense) structure of a separate crushed fragmented sound-absorbing element 13;

16 - futuristic soundproof layer of an air-blown elastic polymer film, metal foil, and / or an air-blown layer of fabric, non-woven fabric, microperforated polymer film, microperforated metal foil;

17 - vibration-isolating supporting elements of sound-insulating front flat-panel panels 4 and / or sound-insulating front molded panels 5 of sound-insulating covers 28 (not shown in the figures);

18 - an intermediate layer of adhesive viscoelastic vibration-damping material;

19 - a layer of sticky adhesive adhesive substance (not shown in the figures);

20 - layer of film thermoactive adhesive substance (not shown in the figures);

21 - hot-melt adhesive fibers (not shown in the figures);

22 - hot-melt powdery adhesive substance (not shown in the figures);

23 - mechanical fasteners;

24 - heat-insulating layer of metal foil (not shown in the figures);

25 - noise generating technical object;

26 - quarter-wave acoustic resonator R ^I ;

27 - half-wave acoustic resonator R ^II ;

28 - soundproofing sewing of load-bearing elements 2 - wall, ceiling, internal partitions of the technical room 1;

29 - sealing soundproofing elements of the peripheral zones of the soundproofing front flat sheets 4 and / or soundproofing front molded non-flat panels 5 soundproofing lining 28;

30 - throat portion of the acoustic resonator R ^I or R ^II ;

31 - tubular part of the acoustic resonator R ^I or R ^II ;

32 - bottom part (hard sound-reflecting bottom) of the acoustic resonator R ^I ;

33 - sound-transparent embedded reinforcing elements of separate briquetted sound-absorbing modules 10;

34 - porous air-blown tube tubes 31 of the acoustic resonators R ^I or R ^II ;

35 is a flat section of the soundproofing front molded non-planar panel 5 of the soundproofing suturing 28;

36 is a non-planar portion of the soundproofing front molded non-planar panel 5 of the soundproofing sewing 28.

Accepted letter designations of the constituent structural elements and physical parameters of the vibro-acoustic fields of the soundproofing sewing of the technical room.

R is the acoustic resonator;

R ^I - quarter-wave acoustic resonator;

R ^II - half-wave acoustic resonator;

- акустические резонаторы (R), предназначенные для устранения резонансного усиления звукового давления в воздушной полости, образованной стенкой звукоизолирующей лицевой плосколистовой панели 4 или формованной неплоской панели 5 звукоизолирующей зашивки 28 и оппозитно расположенной на расстоянии d поверхностью звукоотражающей ограждающей панели несущих элементов 2 - стены, потолка, внутренней перегородки технического помещения 1, формируемого на собственных поперечных акустических модах указанной воздушной полости по толщине d воздушного промежутка; $${\text{R}}_{\text{d}}\left({\text{R}}_{\text{d}}{}^{\text{I}}{\text{, R}}_{\text{d}}{}^{\text{II}}\right)$$

- acoustic resonators (R), designed to eliminate the resonant amplification of sound pressure in the air cavity formed by the wall of the soundproofing face flat panel 4 or the molded non-flat panel 5 of the soundproofing suturing 28 and the surface of the sound-reflecting enclosing panel of the supporting elements 2 - wall, ceiling, located at a distance d , the internal partition of the technical room 1, formed on its own transverse acoustic modes of the specified air cavity thickness d air wow gap;

- акустические резонаторы (R), предназначенные для устранения резонансного усиления звукового давления в воздушной полости, образованной стенкой звукоизолирующей лицевой плосколистовой панели 4 или формованной неплоской панели 5 звукоизолирующей зашивки 28 и оппозитно расположенной на расстоянии d поверхностью звукоотражающей ограждающей панели несущих элементов 2 - стены, потолка, внутренней перегородки технического помещения 1, формируемого на собственных продольных акустических модах указанной воздушной полости по длине L воздушного промежутка; $${\text{R}}_{\text{mL}}\left({\text{R}}_{\text{mL}}{}^{\text{I}}{\text{, R}}_{\text{mL}}{}^{\text{II}}\right)$$

- acoustic resonators (R), designed to eliminate the resonant amplification of sound pressure in the air cavity formed by the wall of the soundproofing face flat panel 4 or the molded non-flat panel 5 of the soundproofing suturing 28 and the surface of the sound-reflecting enclosing panel of the supporting elements 2 - wall, ceiling, located at a distance d , the internal partition of the technical room 1, formed on its own longitudinal acoustic modes of the specified air cavity along the length L of the air about the gap;

- акустические резонаторы (R), предназначенные для устранения резонансного усиления звукового давления в воздушной полости, образованной стенкой звукоизолирующей лицевой плосколистовой панели 4 или формованной неплоской панели 5 звукоизолирующей зашивки 28 и оппозитно расположенной на расстоянии d поверхностью звукоотражающей ограждающей панели несущих элементов 2 - стены, потолка, внутренней перегородки технического помещения 1, формируемого на собственных продольных акустических модах указанной воздушной полости по ширине В воздушного промежутка; $${\text{R}}_{\text{mB}}\left({\text{R}}_{\text{mB}}{}^{\text{I}}{\text{, R}}_{\text{mB}}{}^{\text{II}}\right)$$

- acoustic resonators (R), designed to eliminate the resonant amplification of sound pressure in the air cavity formed by the wall of the soundproofing face flat panel 4 or the molded non-flat panel 5 of the soundproofing suturing 28 and the surface of the sound-reflecting enclosing panel of the supporting elements 2 - wall, ceiling, located at a distance d , the internal partition of the technical room 1, formed on its own longitudinal acoustic modes of the specified air cavity across the width In air th period;

- акустические резонаторы (R), предназначенные для устранения резонансного усиления звукового давления в воздушной полости, образованной стенкой звукоизолирующей лицевой плосколистовой панели 4 или формованной неплоской панели 5 звукоизолирующей зашивки 28 и оппозитно расположенной на расстоянии d поверхностью звукоотражающей ограждающей панели несущих элементов 2 - стены, потолка, внутренней перегородки технического помещения 1, формируемого на собственных продольных акустических модах указанной воздушной полости по высоте Н воздушного промежутка; $${\text{R}}_{\text{mH}}\left({\text{R}}_{\text{mH}}{}^{\text{I}}{\text{, R}}_{\text{mH}}{}^{\text{II}}\right)$$

- acoustic resonators (R), designed to eliminate the resonant amplification of sound pressure in the air cavity formed by the wall of the soundproofing face flat panel 4 or the molded non-flat panel 5 of the soundproofing suturing 28 and the surface of the sound-reflecting enclosing panel of the supporting elements 2 - wall, ceiling, located at a distance d , the internal partition of the technical room 1, formed on its own longitudinal acoustic modes of the specified air cavity height H air th period;

f is the frequency of sound vibrations, Hz (s ^-1 );

s is the speed of sound, m / s;

λ is the sound wavelength, m;

c (t) is the speed of propagation of sound waves (speed of sound) in an elastic medium (air) at an air temperature of t ° C, m / s;

Δλ is the change in the sound wavelength, m;

Δt is the temperature change in ° C;

Δc is the change in the speed of sound, m / s;

,

,

,

- время распространения фронта звуковой волны от открытых срезов горловых частей 30 четвертьволновых акустических резонаторов

,

,

,

(поз. 26) до их закрытых жесткими звукоотражающими донышками 32 концевых участков, отражения от них Р_отр и возвращения к открытым срезам (горловых частей 30), с;

,

,

,

- propagation time of the sound wave front from open sections of the throat parts of 30 quarter-wave acoustic resonators

,

,

,

(pos. 26) to their 32 end sections closed by rigid, sound-reflecting bottoms, reflection from them Р _otr and return to open sections (neck parts 30), s;

,

,

,

- время через которое импульсы звуковых давлений проходят трубчатые части 31 полуволновых акустических резонаторов R^II, с;

,

,

,

- the time through which the sound pressure pulses pass through the tubular parts 31 of the half-wave acoustic resonators R ^II , s;

T _d , T _L , T _B , T _H - periods of sound vibrations propagating through the thickness d of the air gap, length L, width B and height H of the ribs of the technical room 1, s;

T _rL , T _rB , T _rd , T _rH - periods of sound vibrations propagating along the lengths of the tubular parts of the acoustic resonators R, s;

m _d , m _L , m _B , m _H are integers of intrinsic acoustic modes that fit along the thickness d of the air gap, length L, width B and height H of the edges of the technical room 1;

- геометрическая длина в м трубчатой части 31 четвертьволнового акустического резонатора R^I (26), предназначенного для подавления резонансных амплитуд звукового давления на первой (m=1) поперечной собственной акустической моде f_d, формирующейся по толщине (ширине) d воздушного промежутка, образованного поверхностью звукоотражающей ограждающей панели несущего элемента 2 - стены, потолка, внутренней перегородки технического помещения 1 и соответствующей оппозитно расположенной поверхностью звукоизолирующей лицевой плосколистовой панели 4 или плоского участка 35 звукоизолирующей лицевой формованной неплоской панели 5 звукоизолирующей зашивки 28; $${\text{l}}_{\text{rd}}{}^{\text{I}}$$

- the geometric length in m of the tubular part 31 of the quarter-wave acoustic resonator R ^I (26), designed to suppress the resonant amplitudes of sound pressure at the first (m = 1) transverse intrinsic acoustic mode f _d formed along the thickness (width) d of the air gap formed by the surface sound-reflecting enclosing panel of the bearing element 2 - wall, ceiling, internal partition of the technical room 1 and the corresponding opposed surface of the soundproofing face plate 4 and whether the flat portion 35 of the soundproofing front molded non-planar panel 5 of the soundproofing suturing 28;

- геометрическая длина в м трубчатой части 31 полуволнового акустического резонатора R^II (27), предназначенного для подавления резонансных амплитуд звукового давления на первой (m=1) поперечной собственной акустической моде f_d, формирующейся по толщине (ширине) d воздушного промежутка, образованного поверхностью звукоотражающей ограждающей панели несущего элемента 2 - стены, потолка, внутренней перегородки технического помещения 1 и соответствующей оппозитно расположенной поверхностью звукоизолирующей лицевой плосколистовой панелью 4 или плоского участка 35 звукоизолирующей лицевой формованной неплоской панели 5 звукоизолирующей зашивки 28; $${\text{l}}_{\text{rd}}{}^{\text{II}}$$

- the geometric length in m of the tubular part 31 of the half-wave acoustic resonator R ^II (27), designed to suppress the resonant amplitudes of sound pressure at the first (m = 1) transverse intrinsic acoustic mode f _d forming along the thickness (width) d of the air gap formed by the surface sound-reflecting enclosing panel of the bearing element 2 - wall, ceiling, internal partition of the technical room 1 and the corresponding opposed surface of the sound-insulating face plate 4 or a flat portion 35 of the soundproofing front molded non-planar panel 5 of the soundproofing suturing 28;

, $${\text{l}}_{\text{rB}}{}^{\text{I}}$$

, $${\text{l}}_{\text{rH}}{}^{\text{I}}$$

- геометрические длины в м трубчатых частей 31 четвертьволновых акустических резонаторов R^I (26), предназначенных для подавления резонансных амплитуд звуковых давлений на первых (m=1) продольных собственных акустических модах f_L, f_B, f_H, формирующихся вдоль габаритных длин ребер L, В и Н, определяемых габаритными размерами L, В, Н трехмерных воздушных полостей технического помещения 1, образующихся зазорным, на расстоянии d, расположением звукоизолирующих лицевых плосколистовых панелей 4, и/или звукоизолирующих лицевых формованных неплоских панелей 5 звукоизолирующей зашивки 28, относительно соответствующих оппозитно расположенных поверхностей звукоотражающих ограждающих панелей 2 - стен, потолка, внутренней перегородки технического помещения 1; $${\text{l}}_{\text{rL}}{}^{\text{I}}$$

, $${\text{l}}_{\text{rB}}{}^{\text{I}}$$

, $${\text{l}}_{\text{rH}}{}^{\text{I}}$$

- geometric lengths in m of tubular parts of 31 quarter-wave acoustic resonators R ^I (26), designed to suppress the resonant amplitudes of sound pressures at the first (m = 1) longitudinal eigen acoustic modes f _L , f _B , f _H , formed along the overall lengths of the edges L , B and H, determined by the overall dimensions L, B, H of the three-dimensional air cavities of the technical room 1, formed by the gap, at a distance d, by the location of the soundproofing face plate panels 4, and / or the soundproofing face shaped non-planar nels 5 of soundproofing suturing 28, relative to the corresponding opposed surfaces of the sound-reflecting enclosing panels 2 - walls, ceiling, internal partition of the technical room 1;

, $${\text{l}}_{\text{rB}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rH}}{}^{\text{II}}$$

- геометрические длины в м трубчатых частей полуволновых акустических резонаторов R^II, предназначенных для подавления резонансных амплитуд звуковых давлений на первых (m=1) продольных собственных акустических модах f_L, f_B, f_H, формирующихся вдоль габаритных длин ребер L, В и Н, определяемых габаритными размерами L, В, Н трехмерных воздушных полостей технического помещения 1, образующихся зазорным на расстоянии d расположением звукоизолирующих лицевых плосколистовых панелей 4 и/или звукоизолирующих лицевых формованных неплоских панелей 5 звукоизолирующей зашивки 28 относительно соответствующих оппозитно расположенных поверхностей звукоотражающих $${\text{l}}_{\text{rL}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rB}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rH}}{}^{\text{II}}$$

- geometric lengths in m of tubular parts of half-wave acoustic resonators R ^II , designed to suppress the resonant amplitudes of sound pressures at the first (m = 1) longitudinal eigen acoustic modes f _L , f _B , f _H , formed along the overall lengths of the ribs L, B and H defined by the overall dimensions L, B, H of the three-dimensional air cavities of the technical room 1, formed by the gap at a distance d from the location of the soundproofing face flat panels 4 and / or soundproofing front molded non-flat panels 5 stars quenching suturing 28 relative to the corresponding opposed sound-reflecting surfaces

- динамическая длина в м четвертьволнового акустического резонатора R^I (поз. 26), отсчитываемая от поверхности его жесткого звукоотражающего донышка (донной части) 32 до плоскости открытого среза его горловой части 30, равная ее геометрической длине $${\text{l}}_{\text{rd1}}{}^{\text{I}}$$

, дополненная динамическим удлинением, создаваемым колеблющимся воздушным столбом, сосредоточенным в полости трубчатой части 31, с учетом вязкоприсоединенной колеблющейся массы воздуха, находящейся за плоскостью открытого среза его горловой части 30, равным (0,1…0,3) d_пр; $${\text{l}}_{\text{R}}{}^{\text{I}}$$

- the dynamic length in m of the quarter-wave acoustic resonator R ^I (pos. 26), measured from the surface of its hard, sound-reflecting bottom (bottom) 32 to the plane of the open cut of its neck portion 30, equal to its geometric length $${\text{l}}_{\text{rd1}}{}^{\text{I}}$$

supplemented by the dynamic elongation created by the oscillating air column concentrated in the cavity of the tubular part 31, taking into account the viscous-attached oscillating mass of air located beyond the plane of the open cut of its throat part 30, equal to (0.1 ... 0.3) d _pr ;

- динамическая длина в м полуволнового акустического резонатора R^II (поз.27), включающая геометрическую длину $${\text{l}}_{\text{rd}}{}^{\text{II}}$$

его трубчатой части 31, дополненную двумя концевыми участками динамических удлинений, создаваемых колеблющимся в полости трубчатой части 31 воздушным столбом, с учетом вязкоприсоединенных к нему колеблющихся масс воздуха, находящихся за плоскостями открытых (геометрических) срезов горловых частей 30, суммарное удлинение которых составляет (0,2…0,6) d_пр; $${\text{l}}_{\text{R}}{}^{\text{II}}$$

- dynamic length in m of a half-wave acoustic resonator R ^II (pos. 27), including the geometric length $${\text{l}}_{\text{rd}}{}^{\text{II}}$$

its tubular part 31, supplemented by two end sections of dynamic extensions created by the air column oscillating in the cavity of the tubular part 31, taking into account the vibrating air masses viscously attached to it, located beyond the planes of open (geometric) sections of the neck parts 30, the total elongation of which is (0, 2 ... 0.6) d _ol ;

d is the thickness (width) in m of the air gap formed by the surface of the sound-reflecting enclosing panel of the bearing element 2 — the wall, ceiling, internal partition of the technical room 1 and the corresponding opposed surface of the sound-insulating face flat panel 4 or flat section 35 of the sound-insulating front molded non-flat soundproofing panel 5 suturing 28;

d _min , d _max - the minimum and maximum thickness (width) in m of the air gap formed by the surface of the sound-reflecting enclosing panel of the bearing element 2 - wall, ceiling, internal partition of the technical room 1 and the corresponding opposed surface of the flat section 35 of the sound-insulating front molded non-flat panel 5 soundproofing suturing 28;

, где S_T - площадь в м² проходного сечения трубчатой части 31 акустического резонатора R, π=3,14;d _CR - reduced hydraulic diameter in m of the bore of the tubular part 31 of the quarter-wave acoustic resonator R ^I or half-wave acoustic resonator R ^II ; defined from expression

where S _T is the area in m ^{2 of the} bore of the tubular part 31 of the acoustic resonator R, π = 3.14;

S _T is the flow area in m ^{2 of the} tubular part of the acoustic resonator R;

k _lane - perforation coefficient;

F _lane - the total area in m ² passage section _{of holes} n holes perforations 9 formed in the wall of the tubular portion 31 of the acoustic resonator ^{R (R I, R II)} ;

n _holes - the number of perforations, NY;

L, B, N - overall lengths of the ribs in m, determined by the overall dimensions of the three-dimensional air cavity of the technical room along the length L, width B and height H;

b is the size of one of the sides (base, chords) of the segment section of the tubular part 31 of the acoustic resonator R, m;

W is the height of the segment section of the tubular part 31 of the acoustic resonator R, m;

B _b - the thickness of the isolated briquetted sound-absorbing module 10, m;

ΔB _b is the distance between the tangent zone of the location of the extreme contours of the holes of the perforation 9, made in the wall of the soundproof flat sheet 4 or molded non-planar 5 panels and the extreme surface of the contour of a separate briquetted sound-absorbing module 10, overlapping the zone of the location of the extreme contours of the holes of the perforation 9;

- собственная (резонансная) частота в Гц акустического резонатора R (R^I, R^II); $${\text{f}}_{\text{R}}\left({\text{f}}_{\text{R}}{}^{\text{I}}{\text{f}}_{\text{R}}{}^{\text{II}}\right)$$

- intrinsic (resonant) frequency in Hz of the acoustic resonator R (R ^I , R ^II );

γ is the shortest distance in m between the contours of the passage sections of the throat parts 30, measured in the plane of open geometric sections of the tubular part 31 of a given single sample of a half-wave acoustic resonator R ^II (item 27);

P _pad - incident sound wave;

P _ol - the transmitted sound wave;

R _neg - reflected sound wave;

R _{pad 1} , R _{pad 2} , R _{pad 3} , P _{pad 4} - incident sound waves in the throat 30 of four samples of single autonomous acoustic resonators R (R ^I , R ^II ) or a blocked modular unit consisting of four acoustic resonators R (R ^I , R ^II );

P _Otr.1 , P _Otr.2 , P _Otr.3 , P _Otr.4 - reflected sound waves from the bottom of 32 quarter-wave acoustic resonators R ^I , as part of a blocked modular unit of four acoustic resonators R ^I ;

f _m are the frequencies in Hz of the intrinsic acoustic modes of the air cavity formed by the wall of the soundproofing face plate 4 or the molded non-flat panel 5 of the soundproofing suturing 28 and the surface of the sound-reflecting enclosing panel of the supporting elements 2 opposite the distance d - wall, ceiling, internal partition of the technical room 1 ;

f _md is the frequency in Hz of the intrinsic transverse acoustic modes of the air cavity along the width d of the air gap formed by the wall of the soundproofing face plate 4 or the molded non-planar panel 5 of the soundproofing cover 28 and the surface of the sound-reflecting enclosing panel of the supporting elements 2 - wall, ceiling , the internal partition of the technical room 1;

f _mL are the frequencies in Hz of the longitudinal longitudinal acoustic modes of the air cavity along the length L of the air gap formed by the wall of the soundproofing face plate 4 or the molded non-planar panel 5 of the soundproofing cover 28 and the surface of the sound-reflecting enclosing panel of the supporting elements 2 — wall, ceiling, located at a distance d , the internal partition of the technical room 1;

f _mB is the frequency in Hz of the natural longitudinal acoustic modes of the air cavity across the width B of the air gap formed by the wall of the soundproofing face plate 4 or the molded non-planar panel 5 of the soundproofing cover 28 and the surface of the sound-reflecting enclosing panel of the supporting elements 2 — wall, ceiling, located at a distance d , the internal partition of the technical room 1;

f _mH — frequencies in Hz of the natural longitudinal acoustic modes of the air cavity along the height H of the air gap formed by the wall of the soundproofing face flat panel 4 or the molded non-planar panel 5 of the soundproofing cover 28 and the surface of the sound-reflecting enclosing panel of the supporting elements 2 of the wall, ceiling, located at a distance d , the internal partition of the technical room 1;

f _d , f _L , f _B , f _H are the frequencies in Hz of the first (m = 1) eigenmodes of the air cavity formed by the wall of the soundproofing face plate 4 or the molded non-flat panel 5 of the soundproofing board 28 and the sound-reflecting surface opposite to the distance d the enclosing panel of the supporting elements 2 - wall, ceiling, internal partition of the technical room 1;

T _Rd , T _RL , T _RB , T _RH - values of natural (resonant) frequencies in Hz of sound vibrations of various types of acoustic resonators R;

ρ _f - density in kg / m ³ filling of separate containers 12 bearing sound-transparent shells 11 separate briquetted sound-absorbing modules 10 separate crushed fragmented sound-absorbing elements 13;

V _f - volume in m ^{3 of a} single isolated crushed fragmented sound-absorbing element 13.

To increase the sound insulation of structures of the enclosing walls of the technical room 1, in particular the engine room of the vessel, sound insulating closures 28, which are lightweight solid-state lamellar elements made of aluminum alloys, plywood, placed at some distance d from the surface of the enclosing wall, are widely used. The terminological definition of “soundproofing sewing” is given, in particular, on pages 98 ... 99 of the monograph [1].

[1] Nikiforov A.S. Acoustic design of ship structures: a Handbook. - L .: Shipbuilding, 1990. - 200 p.

As a result of using this type of soundproofing structures installed on the propagation paths of sound waves, two dense solid-state barriers appear that provide the corresponding jumps in acoustic impedance created both by the enclosing wall of the room itself and by an additionally mounted plate-like solid-state element - soundproofing suturing 28. At the same time , the presence of an air gap d formed between these solid-state barriers has a certain effect on the physical The process of transferring (transforming) acoustic energy through them. These features are characterized not only by the excited mechanical vibrational resonance of the masses of the solid plate obstacles, but also by the emerging airborne acoustic resonance of the elastic mass of air concentrated in the cavity formed between the solid plate plates. In particular, these resonant acoustic phenomena are pronounced primarily when an integer (multiple) number of half the lengths of sound waves (λ _in / 2) is stacked along the thickness of the air gap d, with the corresponding formation of resonant transverse eigen acoustic modes f _md . This type of arising airborne acoustic resonances entail a significant loss of the soundproofing effect in the applied design of the soundproofing suturing 28, which are manifested at the frequencies of the lower transverse natural acoustic modes of the formed air cavity (f _md ). As follows from the results of [2], amplification of sound radiation in the high-frequency region of the sound spectrum (over 500 Hz) by 1.7 ... 7.7 dB is even possible.

[2] Nurova E.N., Fesina M.I. On the issue of determining the potential for increasing the sound insulation of the partition walls of the engine room of a floating dredger projectile. Vector Science of Togliatti State University, No. 2 (24), 20013. - p. 183 ... 186.

At the same time, in these cases there are not only high-frequency resonant transverse eigen acoustic modes f _md , but also longitudinal eigen acoustic modes f _mB , f _mH , f _mL arising in the formed dead-end air cavities that are formed along the overall dimensions (length L, width B and heights H) of wall, ceiling (intermediate partitions) panels formed by the enclosing walls of the technical room 1, and soundproofing suturing 28 with the mating end surfaces of the supporting elements 2 of the wall and ceiling floors the clinical premises 1 (see figure 1, 2). Due to the large size of the formed dead-end air acoustic waveguides, which coincide with the overall dimensions of the technical room 1, the resonant longitudinal eigen acoustic modes are located mainly in the low- and mid-frequency sound ranges. As you know, the effective suppression of low-frequency acoustic resonances produced using monolithic layers of porous sound-absorbing materials, in most cases is not productive enough and / or requires the use of sufficiently technologically complex, time-consuming and expensive technical techniques (use of thick layers of expensive porous sound-absorbing material, increase in overall dimensions air gaps). The transverse and longitudinal acoustic resonances of the air cavity arising under thin-walled soundproofing siding 28 on their lower eigenmodes produce intense structural (dynamic) force impact on the thin-walled lamellar soundproofing suturing 28. This causes secondary re-emission by it of its own sound radiation, with the corresponding corresponding negative »In the frequency response of the sound insulation of the construction used. For these reasons, in order to eliminate the noted negative effect aimed at weakening the structural dynamic excitation of thin-walled soundproofing suturing 28, the known technical devices use the corresponding typical technical methods of tightening its structure, for example, by increasing the thickness of its wall, using ribbed geometric shapes of its walls, using additional layers of laminate viscoelastic vibration-damping wall coatings, the use of structural materials rial walls with high internal friction, including multilayer composite structures with intermediate viscoelastic interlayers of the MPM type (metal-plastic-metal), filling the cavity under the soundproofing lining 28 with a continuous layer of porous sound-absorbing substance (fibrous, open-cell foam) and / or installation of an additional a layer of dense viscoelastic polymer soundproofing material. That is why, formed by the thin-walled sound-insulating face plate 4 of the sound-insulating suturing 28 and the supporting element 2 (wall, ceiling, internal partition) that is oppositely positioned against it, a large-sized dead-end acoustic waveguide, characterized by the overall dimensions of the bearing elements 2 (wall, ceiling, internal partition) room 1, containing a thin-walled dynamically compliant vibration-noise-excitable wall, in the form of a specified sound-insulating face flat panel and 4, needs an appropriate structural and technological improvement. One of the integral technical methods of such improvement presented in the claimed technical device can be considered as the structural fragmentation of a large dead-end acoustic waveguide into several small-sized parts (into several separate separate acoustic waveguides of smaller dimensions). In particular, it can be carried out by introducing internal dividing walls fixed to the walls of the supporting elements 2 (walls, ceiling, internal partitions) of the technical room 1, and / or fixing them directly to the wall of the soundproofing face plate 4 of the soundproofing suturing 28. However, more rational, from the point of view of reducing material consumption and cost, the technical technique presented in the claimed technical device is the use of "crushed" waveguide design Vuco-insulating suturing 28, presented in the form of using appropriate sound-insulating front molded non-flat panels 5 of sound-insulating suturing 28, represented in particular by corrugated (cross-section-triangle, rectangle, trapezoid, flat segment) geometric designs (see Fig. 8, 9, 22 ... 29). In this case, a monolithic single-volume large-sized dead-end acoustic waveguide element is converted to several separate small-sized dead-end narrow-band corrugated acoustic waveguides. Thus, the formation of low-frequency resonant intrinsic acoustic modes in the direction perpendicular to the arrangement of the corrugations is eliminated. Also, of this type, the modified design of the thin-walled soundproofing front molded non-planar panel 5 has increased stiffness properties (higher bending stiffness in the direction of the length of the corrugations and less vibroacoustic excitability of the thin-walled structure in the low-frequency region of the sound spectrum). However, the “crushing” of the waveguide structure carried out in one spatial direction as compared to the flat-plate design is characterized by greater material consumption and complexity of the production technology in comparison with the simplest flat-sheet version, which entails a corresponding deterioration in cost indicators.

A further degree of “crushing” of large air cavities formed under the soundproofing front panels (4, 5) of the soundproofing lining 28 into the corresponding dead-end waveguide elements of smaller dimensions is also possible, by a modified design of the soundproofing front molded non-flat panel 5, with the formation of distinguished separate containers 6 containing the corresponding geometric shapes, the side walls 7 and the walls of the peaks 8. (see Figs. 8, 9, 22 ... 29). However, of this type of design, it is characterized by deteriorated technological, material-intensive, and cost-related indicators with respect to the simplest planar embodiment of soundproofing protection 28. Thus, a single-volume dead-end acoustic waveguide element formed by a gap-wise positioned relative to the surface of the sound-reflecting enclosing panel 3 (walls , ceiling, internal partition) of the technical room 1 soundproofing face plate 4 soundproofing conductive linings 28 by sealingly abutting (mating) perpendicularly disposed with a reflecting therein the partition plate 3 (walls, ceilings, interior partitions), can be suitably modified by its bounding crushing. This, in a certain way, will allow to influence the soundproofing properties of soundproofing suturing 28 and reduce the resonant transmission of sound energy from the cavity of the technical room 1 to the surrounding space (adjoining adjacent room, open space), however achieved with technological complication and deterioration of material consumption and cost.

In general terms, a three-dimensional air volume, as an elastic air mass oscillating at its own frequencies, located in a closed (partially-closed) three-dimensional cavity defined by the overall dimensions of length L, width B and height H limited by rigid sound-reflecting walls, is characterized by a spectrum of natural frequencies oscillations (natural acoustic modes), the discrete values of which are determined according to [3] by the expression (1):

where c is the speed of sound in air, m / s (s = 344,057 m / s at + 20 ° C);

L, B, H — rib lengths (overall dimensions of a three-dimensional cavity), m;

m _L , m _B , m _H = 1,2,3 ... (integers).

[3] Helmut V. Fuchs, Schallabsorber und Schalldampfer. Springer-Verlag Berlin Heidelberrg 2004, 2007, p. 546.

As a rule, the first three lowest intrinsic acoustic modes (m _{L, B, H} = 1,2,3) are the most energy-intensive.

Placing the wall of the soundproofing face plate 4 of the soundproofing siding 28, made of dense sound-reflecting material, at a distance d from the surface of the sound-reflecting enclosing panel 3 of the corresponding load-bearing elements (wall, ceiling, internal partition) 2 of the technical room 1, forms a closed (dead-end) three-dimensional single-volume air a cavity bounded by said rigid sound-reflecting walls.

The air volume of such a closed three-dimensional cavity, presented as an elastic dead-end acoustic waveguide oscillating at its own frequencies of air mass, determined by its overall dimensions, is characterized by the corresponding

the spectrum of their natural vibration frequencies f _md , f _mB , f _mH , f _mL (natural acoustic modes), the discrete values of which can be determined taking into account the known relation [3] from the corresponding expressions (2), (3), (4):

- when installing soundproofing suturing 28 on the side (left and right) walls of the technical room 1 - (see Fig. 1 ... 6, 17)

- when installing soundproofing suturing 28 on the front and rear wall of the technical room 1 - (see Fig. 1, 2)

- when installing soundproofing suturing 28 on the ceiling of the technical room 1 - (not shown in FIG.)

Here L, B, H are the overall lengths of the ribs (overall dimensions of the three-dimensional air cavity of the technical room 1), m;

m _L , m _B , m _H , m _d = 1,2,3 ... (integers);

d is the thickness of the air gap in m formed between the back surface of the wall of the soundproofing face plate 4 or the flat section 35 of the molded non-flat panel 5 of the soundproofing suturing 28 and the opposite surface of the sound-reflecting wall panel 3 of the supporting elements 2 (ceiling wall, internal partition) of the technical room 1 .

According to the claimed technical solution, a porous sound-absorbing substance located in a closed separate container 12 formed by a supporting sound-transparent shell 11, separate briquetted sound-absorbing modules 10, which is represented by separate crushed fragmented sound-absorbing elements 13, made mainly of identical or different types of structures and grades of porous sound-absorbing materials, can be used. materials 14 characterized by identical or physically different and characteristics, chemical composition, porosity, pore tortuosity, the number and combination of structures used types of porous layers consisting of mono- and / or their multilayer combinations, identical or different geometrical shape and dimensions. The composition of the isolated crushed fragmented sound-absorbing elements 13 can also include non-porous 15, mainly solid polymer structures of materials. However, their total volume should not exceed 30% of the total volume used in the mixture of porous separate crushed fermented sound-absorbing elements 13.

As the composition of the feedstock used for the manufacture of porous separate crushed fragmented sound-absorbing elements 13, materials obtained from products of secondary recycled recycling utilization of technological waste and / or technological marriage of the production of fibrous, foamed open-cell sound-absorbing materials, and / or defective parts made from the specified types of sound-absorbing materials, as well as those obtained from parts (panels, upholstery, laying - made of porous sound-absorbing materials), selected for secondary recycled recycling of dismantled soundproofing packages from a variety of noise-generating technical objects, for example, vehicles (driver's cab, passenger compartment, engine compartment, luggage compartment) that have completed their life cycle and are subject to in connection with this, the relevant disposal processes, as well as dismantled from a similar type of standard noise reduction packages used and other utilized noise-related technical objects, for example, means of transport (railway, aircraft, tractors, combines, mobile communal and road-building equipment, etc.), units and systems of power plants (stationary internal combustion engines, stationary and mobile compressor and pumping installations, etc.) used in construction projects (soundproofing fibrous and / or foamed open-cell panels for wall linings, floors, elevators s mines, ventilation systems, etc.). Their renewable “environmentally friendly” recycled (repeated) repeated use ultimately entails a decrease in the initially demanded consumption of feedstock intended both for the production of sound-absorbing materials and for the manufacture of “new” noise-reducing products from it (due to appropriate compensation replacement semi-finished products already available for appropriate secondary recycled recycling). This, ultimately, reduces the cost of the produced technical device, and also ensures the reduction of environmental pollution by generated industrial wastes and unused products for the utilization of materials used as part of noise-absorbing packages of various types of noise-generating technical objects and, above all, vehicles (as the most mass production object and disposal). Thus, ultimately, this helps to improve the environmental characteristics of the claimed technical device, including by reducing the number of used sound-absorbing substances to be compelled to be buried (for example, disposable noise-reducing packages in vehicle components that have expired), which do not allow their direct energy utilization by burning (due to the intensive release of harmful and toxic substances into the environment). To simplify the technological operations of crushing / cutting / cutting and to ensure a predetermined more accurate dosing of separate crushed fragmented sound-absorbing elements 13, placed in closed separate containers 12 of the load-bearing transparent shells 11 of the separate briquetted sound-absorbing modules 10, in terms of structural composition, weight and size parameters and physical characteristics, as the initial semi-finished raw material for the manufacture of a porous sound-absorbing substance isolated briquette of the sound-absorbing modules 10, the “new” isolated crushed fragmented sound-absorbing elements 13 may also be used. The term “new” means newly produced elements from a “new” raw material, for example, from a semi-finished product, mainly of a flat-sheet type (flat sheets or rolls of sound-absorbing material) , and not from recyclable materials and parts. Combined mixtures of specified dosage proportions of isolated crushed fragmented sound-absorbing elements 13 obtained from recycled recycling materials and parts that can contain a certain amount of “new” separate crushed fragmented sound-absorbing elements 13 of the same or different type, geometric shape and overall dimensions can also be used. sizes made from the "new" source of semi-finished raw materials, presented in the form of corresponding porous structures of 14 separate fragmented fragmented sound-absorbing elements 13. In a number of cases, this makes it possible to simplify and more flexibly purposefully control the final technical parameters of the formed mixed mass (acoustic, weight, density, stiffness, operational, etc.) due to the introduction in the required proportions of a given known quantitative and qualitative dosed additives of "new" isolated porous crushed fragmented sound-absorbing elem ENTOV 13 with predetermined known, for example, located in a narrower tolerance field acoustic (sound deadening) parameters improvers varying extent required specifications resulting preformed separate sound-absorbing modules 10 as a whole. It is also possible to use a certain number of separate non-porous (dense) structures 15 materials as separate crushed fragmented elements 13, obtained mainly from dense air-blown polymer recycled waste and technological marriage of production and / or a similar type of dense air-blown polymer materials of recycled technical objects that have completed their life cycle.

The analysis of scientific, technical and patent documentation on the priority date in the main and related sections of the MKI shows that the set of essential features of the claimed technical solution was not previously known, therefore, it meets the patentability condition of “novelty”.

The analysis of known technical solutions in the art showed that the claimed device has features that are not available in the known technical solutions, and their use in the claimed combination of features makes it possible to obtain a new technical result, therefore, the proposed technical solution has an inventive step compared to the existing level technicians.

The proposed technical solution is industrially applicable, because can be manufactured industrially, efficiently, feasibly and reproducibly, therefore, meets the patentability condition “industrial applicability”.

Other features and advantages of the claimed invention will become apparent from the graphical representation and the following detailed description of the claimed device.

The inventive device "Soundproofing sewn-up technical premises" is intended to reduce the level of acoustic (noise) energy emitted from various types of noise-active noise-generating technical objects 25, presented in the form of functioning production and technological equipment, sanitary equipment, power plants (ICE, diesel-generator installations, electric motors, compressors, pumps, mechanical reducers, refrigeration units), ventilation and air conditioning systems air inside the technical room 1, the noise levels in which are regulated by the relevant regulatory standards and technical conditions (technical requirements) of their operation, as well as which can characterize the acoustic comfort in the adjacent premises of residential, industrial and public buildings, including the requirements for reducing acoustic pollution of open spaces of residential territories.

As devices for attenuating the process of resonant amplification of acoustic energy arising at discrete frequencies of natural acoustic modes of the air volume of cavities formed by the surfaces of sound-reflecting enclosing panels of load-bearing elements 2, represented by walls, a ceiling, an internal partition and oppositely placed sound-insulating front flat sheets 4 and / or soundproofing to them front molded non-flat 5 panels of soundproofing suturing 28 (hereinafter - air cavities soundproofing sheathing 28) uses the corresponding types of acoustic resonators R — quarter-wave acoustic resonators R ^I (key 26) and half-wave acoustic resonators R ^II (key 27), shown in the diagrams of FIG. 3 ... 15. The indicated types of acoustic resonators R (pos. 26, 27) can be mounted on the inner surfaces of soundproofing face flat sheets 4 and / or soundproofing front molded non-flat 5 panels of soundproofing suturing 28 (see Fig. 3 ... 9), surfaces of sound-reflecting enclosing panels of load-bearing elements 2 (see Fig. 4 ... 7). Mounting of the tubular parts 31 of the acoustic resonators R (pos. 26, 27) to the mating surfaces of the soundproofing face flat sheets 4 and / or soundproofing face molded non-flat 5 panels of soundproofing suturing 28 (see Fig. 3 ... 9) and / or the surfaces of sound-reflecting enclosing panels load-bearing elements 2 (see Fig. 4 ... 7) can be produced using appropriate adhesive joints 18, 19, 20, 21, 22 and / or mechanical fasteners 23.

четвертьволнового акустического резонатора R^I (поз. 26), см. фиг. 15 (а, в).The quarter-wave acoustic resonators R ^I (pos. 26) can be integrated into the structures of the supporting elements 2 - walls, ceiling, internal partition of the technical room 1 by formed blind blind holes with a bottom part 32 and a given depth, which form the corresponding geometric length of the tubular part $${\text{l}}_{\text{rd}}{}^{\text{I}}$$

a quarter wave acoustic resonator R ^I (key 26), see FIG. 15 (a, c).

четвертьволновых акустических резонаторов R^I (поз. 26) определяется выражением (5):The geometric length of the tubular part (key 31) $${\text{l}}_{\text{rd}}^{\text{I}}$$

quarter-wave acoustic resonators R ^I (pos. 26) is determined by the expression (5):

- геометрическая длина в м трубчатой части четвертьволнового акустического резонатора R^I (поз. 26), предназначенного для подавления резонансных амплитуд звукового давления на первой (m=1) поперечной собственной акустической моде f_d, формирующейся по толщине (ширине) d воздушного промежутка, образованного поверхностью звукоотражающей ограждающей панели несущего элемента 2 - стены, потолка, внутренней перегородки технического помещения 1 и соответствующей оппозитно расположенной поверхностью звукоизолирующей лицевой плосколистовой панели 4 или плоского участка 35 звукоизолирующей лицевой неплоской панели 5 звукоизолирующей зашивки 28;Where $${\text{l}}_{\text{rd}}^{\text{I}}$$

- the geometric length in m of the tubular part of the quarter-wave acoustic resonator R ^I (key 26), designed to suppress the resonant amplitudes of sound pressure at the first (m = 1) transverse intrinsic acoustic mode f _d , which is formed along the thickness (width) d of the air gap formed the surface of the sound-reflecting enclosing panel of the bearing element 2 — the wall, the ceiling, the internal partition of the technical room 1 and the corresponding opposed surface of the sound-insulating front flat-panel panel 4 or a flat portion 35 of the soundproofing front non-planar panel 5 of the soundproofing suturing 28;

d is the thickness (width) in m of the air gap formed by the surface of the sound-reflecting enclosing panel of the bearing element 2 - the wall, ceiling, internal partition of the technical room 1 and the corresponding opposed surface of the sound-insulating face plate 4 or a flat section of the sound-insulating face molded non-flat panel 5 of the soundproofing sewing 28;

S _T is the flow area in m ^{2 of the} tubular part 31 of the quarter-wave acoustic resonator R ^I (pos. 26);

π = 3.14.

The quarter-wave acoustic resonators R ^I (pos. 26) can be integrated into the structures of the supporting elements 2 — walls, ceiling, and internal partition of the technical room 1 and are presented as embedded dead-end tubular elements of a dead end type 32 of which are located inside the structure of the structures of these supporting elements 2 - walls, ceiling, internal partition of the technical room 1, and the open throat part 30 is located on the side of the air cavity formed by the sound-reflecting gap the enclosing panels of the supporting elements 2 - walls, ceiling, internal partitions of the technical room 1 and the corresponding opposite placed soundproofing front flat sheets 4 and / or soundproof molded non-flat 5 soundproofing panels 28 (see Fig. 15).

полуволновых акустических резонаторов R^II (поз. 27, см. фиг. 15).The used half-wave acoustic resonators R ^II (pos. 27) can also be integrated into the structural structures of the supporting elements 2 — walls, ceiling, and internal partition of the technical room 1 and are presented as embedded U-shaped hollow tubular elements corresponding to the geometric length of the tubular parts 31 $${\text{l}}_{\text{rd}}^{\text{II}}$$

half-wave acoustic resonators R ^II (pos. 27, see Fig. 15).

полуволновых акустических резонаторов R^II (поз. 27) определяется выражением (6):The geometric length of the tubular part (key 31)

half-wave acoustic resonators R ^II (pos. 27) is determined by the expression (6):

- геометрическая длина в м трубчатой части полуволнового акустического резонатора R^II (поз. 27), предназначенного для подавления резонансных амплитуд звукового давления на первой (m=1) поперечной собственной акустической моде f_d, формирующейся по толщине (ширине) d воздушного промежутка, образованного поверхностью звукоотражающей ограждающей панели несущего элемента 2 - стены, потолка, внутренней перегородки технического помещения 1 и соответствующей оппозитно расположенной поверхностью звукоизолирующей лицевой плосколистовой панели 4 или плоского участка 35 звукоизолирующей лицевой неплоской панели 5 звукоизолирующей зашивки 28;Where $${\text{l}}_{\text{rd}}^{\text{''}}$$

- the geometric length in m of the tubular part of the half-wave acoustic resonator R ^II (pos. 27), designed to suppress the resonant amplitudes of sound pressure at the first (m = 1) transverse intrinsic acoustic mode f _d , which is formed along the thickness (width) d of the air gap formed the surface of the sound-reflecting enclosing panel of the bearing element 2 - wall, ceiling, internal partition of the technical room 1 and the corresponding opposed surface of the sound-insulating face plate panel 4 il and a flat portion 35 of the soundproofing front non-planar panel 5 of the soundproofing suturing 28;

d is the thickness (width) in m of the air gap formed by the surface of the sound-reflecting enclosing panel of the bearing element - the wall, ceiling, internal partition of the technical room and the corresponding opposed surface of the sound-insulating front flat-panel panel or flat section of the sound-insulating front molded non-flat sound-insulating panel;

S _T is the bore in m ^{2 of the} tubular part of the quarter-wave acoustic resonator R ^I (pos. 26);

π = 3.14.

, геометрической длины трубчатой части 31 - $${\text{l}}_{\text{r}}^{\text{I}}$$

, динамической длины - $${\text{l}}_{\text{R}}^{\text{I}}$$

, приведенного гидравлического диаметра проходного сечения трубчатой части 31 - d_пр, коэффициента перфорации стенки трубчатой части 31 - K_пер.о., суммарной площади проходных сечений n_отв отверстий перфорации 9 - F_пер.о., выполненных в стенке трубчатой части 31, включая использование демпфирующих пористых воздухопродуваемых пробок 34 трубчатой части 31, использования защитных футерующих демпфирующих слоев материалов 16, монтируемых на горловой 30 и/или на участке перфорированной зоны стенки трубчатой части 31, которое производится дополняющим или альтернативным выбором указанных выше физических и конструктивных параметров четвертьволновых акустических резонаторов R^I (см. фиг. 7, 10, 11, 14). Оно осуществляется с учетом заданных спектральных характеристик доминирующих источников шумовых излучений, сосредоточенных в техническом помещении 1 с размещенным в нем шумогенерирующим техническим объектом 25, габаритных геометрических параметров воздушных полостей звукоизолирующей зашивки 28, температуры воздушной среды в техническом помещении 1, компоновочного пространственного размещения между собой отдельных горловых частей 30 акустических резонаторов R^I (поз. 26), обладающих (наделенных) близкими (совпадающими) или существенно (более чем в 1, 2 раза) отличающимися значениями собственных (резонансных) частот f_R.The design of the quarter-wave acoustic resonators R ^I (pos. 26) is represented by a hollow tubular element bounded by rigid sound-reflecting walls - the tubular part 31, one of the end sections of which is overlapped by a hard sound-reflecting bottom forming its bottom part 32 (see Fig. 10, 11, fourteen). The open end zone of the tubular part 31 with the part of the air column oscillating in the tubular part 31 (located beyond the plane of the open cut of the tubular part 31) viscously attached to it forms the throat part 30 of the quarter-wave acoustic resonator R ^I (key 26). The formation of the specified values of the physical and structural parameters of the quarter-wave acoustic resonators R ^{I is} carried out by choosing their own (resonant) frequency

, the geometric length of the tubular part 31 - $${\text{l}}_{\text{r}}^{\text{I}}$$

dynamic length - $${\text{l}}_{\text{R}}^{\text{I}}$$

Given hydraulic diameter of the flow cross section of the tubular portion 31 - d _etc., perforation coefficient wall of the tubular portion 31 - K _per.o. , Total area of the passage section _{of holes} of bores n 9 - F _per.o. made in the wall of the tubular part 31, including the use of damping porous air-blown plugs 34 of the tubular part 31, the use of protective lining damping layers of materials 16 mounted on the throat 30 and / or on the perforated area of the wall of the tubular part 31, which is made by a complementary or alternative choice of these above the physical and structural parameters of quarter-wave acoustic resonators R ^I (see Fig. 7, 10, 11, 14). It is carried out taking into account the specified spectral characteristics of the dominant sources of noise, concentrated in the technical room 1 with the noise-generating technical object 25 located therein, the overall geometric parameters of the air cavities of the soundproofing suture 28, the temperature of the air in the technical room 1, and the spatial distribution of the individual throats 30 parts of acoustic resonators R ^I (pos. 26) having (endowed) close (coincident) or substantially (b Lee than 1, 2 times) their own different values (resonant) frequency f _R.

Similar conditions and requirements for the execution of designs of acoustic resonators R are presented to the half-wave acoustic resonator R ^II (pos. 27), see FIG. 12, 13, 14. A complementary structural parameter of the design of effective devices of half-wave acoustic resonators R ^II (pos. 27) is the need to comply with the maximum possible structural and technological considerations for approaching their neck parts 30, which is carried out by the appropriate choice of their curved U- shaped geometric shape, providing the choice of the shortest distance γ between the contours of the bore sections in the throat plane 30 tubular 31 parts of half-wave acoustic R ^II (pos. 27), in order to ensure in-phase penetration and subsequent conditions of the in-phase propagation of sound waves into both open throat parts 30 of the tubular part 31 towards each other in each individual sample of the half-wave acoustic resonator R ^II (pos. 27) and their further effective antiphase compensation occurring in the middle zone of the tubular part 31 during the counterpropagation of sound pressure pulses towards each other in both sections of their U-shaped tubular part 31 ("antiphase collapse ). The same applies to complementary and / or alternative modification improvements aimed at increasing the efficiency of the functioning of the designs of half-wave acoustic resonators R ^II (key 27), which were already described above, with reference to quarter-wave acoustic resonators R ^I (key 26).

To attenuate the process of resonant amplification of acoustic energy that occurs at discrete frequencies of natural acoustic modes of the volume of air cavities of sound-insulating suturing 28 in spatial zones of localization of antinodes of sound pressures of their own acoustic modes, separate, briquette sound-absorbing modules 10 can be installed as an alternative or complementary technical solution. crushed fragmented sound-absorbing elements 13 placed in strips closed closed capacitance 12 carrying sound-transparent shells 11 (Fig. 16 ... 31). Separate briquetted sound-absorbing modules 10 are mated to the surfaces of the sound-insulating face plate 4 or the molded non-planar 5 panel of the sound-insulating suturing 28 and fixed to it using appropriate mechanical fasteners 23 or adhesive substances (not shown in the figures), for example, a layer of adhesive adhesive adhesive substance 19, a layer of film thermosetting adhesive substance 20, hot-melt fibers adhesive substance 21, hot-melt powder adhesive 22. Separate briquetted sound-absorbing modules 10 can be mounted in undercutting cavities formed by separate convex containers 6, made in the walls of soundproofing front molded non-flat panels 5, and / or made in the structures of the supporting elements 2 - walls, ceiling, internal partition of the technical room 1 .

The specified limited localized spatial zones in the air cavities in which the separate briquetted sound-absorbing modules 10 are mounted can be concentrated in peripheral angular and / or end sections formed by mates of the soundproofing front flat-sheeted 4 and / or soundproofing front shaped molded non-planar 5 panels with corresponding facing load-bearing elements 2 (floor, ceiling, walls and internal partitions) of the technical room 1 (see Fig. 16 ... 21).

Distributedly concentrated groups of separate briquetted sound-absorbing modules 10 can be additionally mounted in the central spatial zones of intersection of the main axes of inertia of the projections of air volumes enclosed in the air cavities of the soundproofing lining 28 and / or in the spatial zones of the intersection of the main axes of inertia of four identical parts of the air volumes formed by the intersecting longitudinal and transverse planes in the respective centers of gravity of the volumes of air strips s soundproofing linings 28 (see. FIGS. 16, 17, 18, 19, 20, 21, 29).

The limited localized spatial zones of the air cavities in which the separate briquetted sound-absorbing modules 10 are mounted can be located at the end sections of the mates of the corresponding sound-insulating front molded non-flat panels 5 with the opposing surfaces of the supporting elements 2, represented by the floor, ceiling, mating walls, internal partition of the technical room 1, which are also complemented by installed standalone briquetted sound-absorbing modules 10, co edotochennymi spatial zones in halves and / or the fourth marker lengths air cavities soundproofing linings 28 (see. FIGS. 22, 23, 24, 25, 26, 27, 28).

The limited area of contact interface briquetted separate sound-absorbing module 10 to the soundproof walls facial ploskolistovyh 4 and / or sound insulating face nonplanar shaped panels 5 may comprise corresponding bores 9, wherein the perforation ratio _per k of said zones of limited contact interface must not exceed the value 0.1 (see Fig. 20, 25, 26, 27, 29).

The boundary perimeter of a closed geometric shape, covering limited areas for the location of perforation holes 9, made in the wall of the soundproofing face flat sheet 4 or the soundproofing face of the molded non-planar 5 panel, is overlapped by the equidistant placed boundary perimeter of the closed geometric shape of the interface with it the contact surface of the isolated briquetted sound absorption module 10, each which is removed from the boundary perimeter of the limited area of the location of the holes perforation 9 by a value of ΔB _b , which is not less than the overall thickness B _{b of a} separate briquette sound-absorbing module 10, covering this limited area of the location of the perforation holes 9.

The soundproofing cladding plate 28 included in the structure of the soundproofing closure 28 and / or the soundproofing molded non-flat panel 5 can be made in the form of continuous non-perforated and / or local perforated plate panels in separate peripheral peripheral zones. The perforated sections in the local limited zones of the walls of the soundproofing face plate 4 or the soundproofing face molded non-planar panel 5 can be additionally lined with inner and / or outer sides with a corresponding futuristic sound-transparent layer 16, in particular, a layer of air-blown elastic polymer film and / or futuristic soundproof metal foil, and / or a futuristic sound-transparent layer of air-blown fabric, non-woven fabric, microperforated by imernoy film microperforated metal foil. The difference between the terms “perforation” and “microperforation” is solely in the overall dimensions of the perforation holes 9. In those cases where the diameter of the round perforation hole 9 does not exceed 1 mm (≤0.001 m), the term “microperforation” is used. When the diameter of the round hole 17 exceeds the specified value (> 0.001 m), the term "perforation" is used.

To ensure fire safety requirements during operation of the claimed technical device, appropriate substances, fire retardants, which protect the used structural materials from ignition and self-combustion, can be added to the structures of separate crushed fragmented sound-absorbing elements 13 or to other composite structural elements of separate briquetted sound-absorbing modules 10. This type of flame retardant disintegrates with the formation of non-combustible substances and / or prevents the decomposition of the material with the release of combustible gases. The flame retardants used can be applied in the form of solutions either directly on the surface of separate crushed sound-absorbing elements 13, or they can also impregnate their porous structure 14 (as well as the structures of other constituent elements of separate briquetted sound-absorbing modules 10). As flame retardants, aluminum hydroxide, boron compounds, antimony, chlorides, organic and inorganic phosphorus compounds can be used.

The provided sound transparency properties of the supporting sound-transparent shell 11 of the isolated briquetted sound-absorbing modules 10 as part of the design of the sound-insulating suture 28 are substantially characterized by the selected values of the parameters of resistance to blowing by the air flow (fabric or microperforated film or microperforated foil layers), and / or set values of thickness, bending and specific surface mass, determined by the mass per 1 m ² surface (continuous film or foil layers not blown by the air flow). The values of the resistance to blowing through the air stream of sound-transparent air-blown fabrics or air-blown non-woven webs (perforated polymer film or perforated foil metal layers) should be within 20 ... 500 n · s / m ³ , with the thicknesses of the fibrous layer of fabric material, fibrous non-woven fabric, microperforated film polymeric or microperforated foil metal layer constituting 0.025 ... 0.25 mm and their surface density of 20 ... 300 g / m ² .

The values of the surface density (specific surface mass) of continuous sound-transparent films not blown by the air flow should be in the range of 20 ... 70 g / m ² , with a film thickness of 0.01 ... 0.1 mm. The sound-transparent carrier shell 11 of the isolated briquetted sound-absorbing modules 10 can be made of various structural materials - polyester aluminized, urethane, polyvinyl chloride films, or from a similar type of other polymeric materials suitable for these purposes. Bearing sound-transparent shell 11 of separate briquetted sound-absorbing modules 10, made using microperforated foil metal material, provides for the use of aluminum, copper, brass as a structural material. Carrying sound-transparent shell 11 of separate briquetted sound-absorbing modules 10, made of a continuous layer of air-blown fabric (non-woven fabric) can be made of materials such as “malifliz”, “filts”, fiberglass, a fabric based on superthin basalt fibers. The use of such a type of structural materials for the manufacture of load-bearing transparent shells 11 of detached briquette sound-absorbing modules 10, provides for a given packing density of closed separate tanks 12 of sound-transparent shells 11 with separate crushed fragmented sound-absorbing elements 13, eliminating unwanted ingress and accumulation (absorption) into porous fibrous structures of isolated crushed fragmented sound absorbing elements 13 of different type of technology and / or operating fluids (water, fuel, coolants) and / or ingress of small amorphous particles or insects in the operation of a technical object shumogeneriruyuschego 25.

The carrier sound-transparent shell 11 of the separate briquetted sound-absorbing modules 10 can be made in the form of both single-layer and multi-layer sound-transparent structures, and is also presented, for example, in the form of at least one perforated layer made of dense air-blown material and lining its external ( front) and / or internal (back) surface (relative to the oncoming direct incidence of sound waves) or at least one thin continuous layer of an airless polymer a film, an air-blown microperforated polymer film, an air-blown micro-perforated metal foil, or an air-blown fibrous fabric material or an air-blown non-woven fabric.

The use of soundproof transparent shells 11 of separate isolated briquette sound-absorbing modules 10 of thin foil metal layers, if necessary, can provide acceptable thermal insulation of the composite structures of separate crushed fragmented sound-absorbing elements 13, when installing soundproof lining 28 in noisy high-temperature zones of technical rooms 1.

As part of the designs of soundproofing lining 28, various types of soundproof adhesive joints used for “technological mounting stitches” of their constituent elements can be used. They are provided with appropriate layers of sticky adhesive adhesives 19 or appropriate temperature heating and melting of the used layers of film thermoactive adhesive substances 20, hot-melt adhesive fibers 21 or hot-melt powder adhesives 22 during the implementation of the technological cycle of their mounting compounds. For individual structural and technological options for the implementation of soundproofing suturing 28 in technical room 1, when a polymer material is used as part of a load-bearing transparent shell 11, which does not provide the required adhesive bond by direct thermal fusion (with appropriate heating of its structure), the necessary strong adhesive connection can be provided with the help of the additional introduction of translucent (not having a negative, not more than 10%, reduction of the sound absorption coefficient) of a non-continuous adhesive adhesive layer (in the form of sticky adhesive 19 or thermosetting hot-melt 20, 21, 22 substances) made mainly of surface-separated spaced thin solid lines, or surface-spaced separated thin thin lines, or in the form of a thin film perforated through holes a layer of adhesive substance 20, or in the form of a thin sound-transparent layer of sticky adhesive adhesive substance 19, endowed with a low specific hnostnom weight (not more than 100 g / m ² ), or in the form of a thin sound-transparent layer of a film thermoactive adhesive substance 20, endowed with a low specific surface weight (not more than 50 g / m ² ).

To ensure a given noise-reducing effect, regulated, for example, by the technical specifications for designing sound-insulating suturing 28 implemented on a specific sound-generating technical object 25, closed separate containers 12 of load-bearing soundproof shells 11 of separate briquetted sound-absorbing modules 10 can be selectively filled with corresponding differentiated types of fragmented separate sound-absorbing fragments of separate 13, made from different types of structures, in made of various overall dimensions and geometric shapes, with differing physical, mechanical and operational characteristics.

In each of the closed separate capacitances 12 carrying the soundproof shells 11, the separate briquetted sound-absorbing modules 10, a separate different type of corresponding separate crushed fragmented sound-absorbing elements 13 can be placed, or all of them can be placed of the same type, separate crushed fragmented sound-absorbing elements 13, or can be placed several different types of isolated crushed fragmented sound-absorbing elements 13, in the form specified dosage mixtures randomly or ordered evenly (layer by layer) distributed over separate volumes of the specified closed separate containers 12.

The inventive device soundproofing suturing 28 provides not only an additional increase in the effects of sound absorption and sound insulation produced by the enclosing load-bearing elements 2 (walls, ceiling, internal partition) of the technical room 1, but its constituent elements can provide a certain vibration-damping suppression of structural mechanical vibrations of thin-walled enclosing load-bearing elements 2 (walls, ceiling, internal partition) of the technical room 1, perceived by them as solid bonds (vibration tional bridges). In particular, this relates to structural and technological versions presented in the form of thin-walled sheet metal structures of load-bearing elements 2 (walls, ceiling, internal partition) of the technical room 1, subjected to intense vibration loads, as is the case, for example, in vibration-noise structures of engine rooms water transport facilities. Additional placement of the intermediate layer of adhesive viscoelastic vibration-damping material 18 in the assembly zones located between the surfaces of the sound-reflecting enclosing panels of the supporting elements 2 (walls, ceiling, internal partition) and the mating sections of the sound-insulating face plate 4 or the sound-insulating soundproof faceplate 5 of the molded 28 , contributes to the additional effective suppression of structural (body) mechanical vibrations and derestimation levels of secondary structure (housing) noise. Moreover, the specified intermediate layer of the adhesive viscoelastic vibration damping material 18 can be intermittent, consisting of several separate parts, viscoelastic vibration damping material 18, and continuous along the entire length of the abutment with the mating surface zones of these structural elements.

The structure of the soundproofing lining 28 may include vibration isolating supporting elements 17 (not shown in FIG.) Mounted in separate contact zones of the soundproofing front plate 4 or the soundproofing front molded non-flat panel 5 of the soundproofing suturing 28 with sound-reflecting enclosing panels of the supporting elements 2 (walls , ceiling, internal partition).

In order to ensure acceptable convenience and reduce the complexity of installing soundproofing sewing 28 on the supporting elements 2 (walls, ceiling, internal partition) of the technical room 1, various mechanical fasteners can be additionally integrated into the structures of soundproofing face plate panels 4 or soundproofing front molded non-flat panels 5 23, or directly on the inner surfaces of their walls may contain mounting adhesive coating in the form of a layer of sticky adhesive adhesive substance 19 or a layer of film thermosetting adhesive substance 20, protected until installation by an additional layer of release paper or film (dismantled during installation operations).

Based on the requirements of the technical conditions (given acoustic, technological, operational characteristics) and established cost restrictions, certain types of structural and technological versions of soundproofing shields 28 in some cases can be additionally blocked (aggregated) as part of the corresponding standard protective screen elements and / or lining sound-absorbing coatings of structures of noise-active, (noise-generating) technical objects 25 located in technical room 1 (as part of the construction of casings, cabins, screens).

During the operation of various noise generating objects 25 located inside the technical room 1, they produce the corresponding generation of sound energy (noise), due to the implementation of dynamic working (mechanical, gas-dynamic) processes in composite functioning units, assemblies and systems, which are radiated directly into the air the cavity of the technical room 1 and / or is transmitted by various intermediate interconnected airways through the m technical room 1 sound-transmitting channels with unsatisfactory (insufficient) sound-insulating ability (window and door openings, technological hatches and openings, leaky sound-transparent communication, technological and structural elements) to adjacent spaces (closed rooms and / or open spaces). In this case, the generated sound radiation (generated sound fields) negatively affects the well-being and health of the operators (workers) directly involved in the implementation of the technological process, as well as the surrounding subjects located in these rooms and / or in open spaces (people, animals).

When using the claimed technical solution in the composition of various types of noise-free technical rooms 1, during the propagation of sound waves in the air cavity formed by the opposed surfaces of the walls of the soundproofing face plate 4 (soundproofing face molded non-flat panel 5) soundproofing suturing 28 and sound-reflecting enclosing panels of the bearing elements 2 (walls, ceiling, internal partitions), and their falling on the oncoming surfaces of the soundproofing face plate of the sheet panel 4 or the soundproofing front molded non-planar panel 5 of the soundproofing suturing 28, they are partially reflected from the solid-state structure of these panels in the opposite direction to the sound source concentrated in the technical room 1, and partially, dynamically exciting these solid-state structures, are reradiated into a limited air cavity forming a closed dead-end waveguide, exciting resonating eigenmodes in it, pass through a futuristic translucent the layer 16 of an air-blown polymer film, a metal foil and / or an air-blown fabric of a non-woven fabric, a micro-perforated polymer film, a micro-perforated metal foil, propagate through its sound-transparent structure, fall on the opposing surfaces of the bearing sound-transparent shells 11 of the separate briquetted sound-absorbing modules 10, pass through them fall onto the opposing surfaces of the separate crushed fragmented sound-absorbing elements 13 and propagate I am in their structures. Formed by the use of soundproofing sewing 28, a multilayer soundproofing fence, including standard structures of the protective panels of the supporting elements 2 (walls, ceiling, internal partition), a soundproofing front flat sheet 4 and / or a soundproofing front molded non-flat panel 5, as well as an intermediate air layer of thickness d ( air cavity), formed between the indicated opposite placed solid-state sound-reflecting barriers (pos. 2 and pos. 4 or 5), provides tvetstvuyuschie "jumps" (abrupt changes) of acoustic impedances in the path of propagation of sound waves from the radiation source (shumogeneriruyuschego technical object - poz.25) towards the external environment (open spaces, adjoining rooms of the building). The indicated “jumps” in acoustic impedances and the associated increase in the sound insulating effect are noted in the zones of contact separation of sound wave propagation media: “technical room air is the solid structure of the soundproof front molded non-planar panel 5 is the intermediate layer air of thickness d is the solid structure of the standard structure of the supporting panel of the bearing element 2 (walls, ceilings, internal partitions) - air of open space (air of the adjacent building premises). ” The soundproofing qualities of the considered type of multilayer soundproofing fencing, with alternating wave (acoustic) impedances, in addition to the factors determining the sound insulation of composite single-layer fencing, depend on the air gap thickness d and the ratio of the surface masses (densities) of each of the composite solid fencing (pos. 2 and item 4 or item 5). The factors that determine the sound insulation of this type of multilayer fencing include the arising acoustic resonances of the vibrational system "mass - elasticity - mass". The role of the oscillating elastic masses here is played by the enclosing walls of the solid-state structure of the standard structure of the enclosing panel of the bearing element 2 (wall, ceiling, internal partition) and the walls of the solid-state structure of the sound-insulating face flat panel 4 and / or the sound-insulating front molded non-flat panel 5. The role of the elastic element connecting these oscillating elastic masses are performed by an air mass concentrated in a closed dead-end cavity formed by opposed wall surfaces to the enclosing panels of the supporting elements 2 (wall, ceiling, internal partition) and the walls of the soundproofing face plate 4 and / or the soundproofing molded non-flat panel 5. The specified closed dead-end air cavity, characterized by overall dimensions d, L, B, H, should be considered as a waveguide acoustic system (acoustic waveguide), endowed with its own physical characteristics in the form of its own acoustic modes, on which acoustic resonances also appear, which contribute to the appearance of NIJ "failures" in the frequency response of the acoustic multi-layer soundproof enclosure. These resonance phenomena, which manifest themselves on the individual frequency components of the sound spectrum, determine the amplification of the transmission of noise radiation into the open space and / or adjacent rooms of the building building located next to the technical room 1, in which the noise-generating technical object 25 is concentrated. Suppression of resonant amplification of amplitudes (levels ) of sound pressures formed in closed dead-end cavities on their own acoustic modes, is carried out by the used quarter-wave designs acoustic resonators R ^I (pos. 26), and / or half-wave acoustic resonators R ^II (pos. 27), and / or localized spatial placement in the closed dead-end cavities of single (or several grouped) structures of isolated briquette sound-absorbing modules 10. Zones of predominant the spatial localization of briquetted sound-absorbing modules 10, presented in the form of porous dissipative scatterers of sound energy, are fragmented spatial areas of closed dead ends stuffy cavities are formed in which sound pressure antinodes of natural acoustic modes (the end portions, the central zone of the space). The used designs of the briquetted sound-absorbing modules 10 provide effective suppression of not only resonant amplitudes (levels) of sound pressures arising on the eigenmodes of a closed dead-end air cavity, but also absorb sound wave energy in other frequency regions of the sound spectrum excited by mechanical structural vibrations of the walls of the sound insulating front flat plate 4 (soundproofing front molded non-flat panel 5), standard design th enclosing panels of supporting elements 2 (walls, ceiling, internal partition). This type of structural "parasitic" mechanical vibrations of the walls are excited both by the sound waves incident on them, and by the mechanical vibrations transmitted by solid contact couplings (mounting vibration-conducting couplings of the components of the claimed technical device). Thus, the use of briquetted sound-absorbing modules 10, in contrast to the applied frequency-tuned acoustic resonators R ^I and R ^II (pos. 26 and pos. 27), allows for wideband absorption of acoustic energy in an extended sound frequency range. They can also carry out a noticeable concomitant vibration-damping effect on the easily excitable thin-walled structures of soundproofing shields 28 made, for example, of thin aluminum sheets or plywood, which further improves the acoustic (soundproofing) properties of the claimed device.

During the passage (propagation) of sound waves through porous fibrous and / or porous open-cell foam structures 14 of materials of separate crushed fragmented sound-absorbing elements 13, the basic process of absorption of sound energy with its irreversible conversion (dissipation) into thermal energy is carried out. At the same time, a concomitant process of attenuation (damping) of the amplitudes of sound pressures is also implemented, which occurs both due to the corresponding conversion of sound energy into work to overcome the dynamic deformations of the porous skeleton and the friction of the propagated sound waves through communicating labyrinth channels (cells) of the porous structures of sound-absorbing substances, as well as in the surface interfragment zones of channels and air cavities formed between individual By means of contacting) faces (ribs) of separate crushed fragmented sound-absorbing elements 13 made by crushing both porous 14 and non-porous dense structures 15 of materials (mainly polymeric), with a final effective irreversible conversion (dissipation) of sound energy into thermal energy. When using a porous sound-absorbing substance represented by separate crushed fragmented sound-absorbing elements 13, relative to, for example, a comparable identical in mass (volume) use case of a continuous monolithic layer of identical sound-absorbing substance, in this case numerous surface of porous end zones are additionally included in the process of sound energy absorption families of open surfaces of contacting zones (faces, edges) of isolated dr Blenheim fragmented sound absorbing members 13. Accordingly, increasing, therefore, the total surface absorption area. Also, additional communicating inter-faceted air channels and cavities between them along which sound waves propagate, are included in the indicated process of absorption of sound energy. In addition, the diffraction edge mechanism for scattering the energy of sound waves is additionally effectively implemented, which occurs during the propagation of sound waves to the edge face (rib) zones of each of the separate crushed fragmented sound-absorbing elements 13, with the corresponding frictional losses of sound energy due to the multiple growth of the total perimeter of the edge (edge) ) zones. Ultimately, the resulting implementation of the above-mentioned simultaneously existing several additional effective mechanisms of dissipation of sound energy is carried out. Most of it is converted (irreversibly dissipated) into thermal energy. This allows you to achieve high efficiency using the proposed technical solution (compared with the well-known typical monolithic designs of sound-absorbing elements described in the analogues) with respect to reducing the level of sound radiation produced by various noise-active technical objects 25 located in closed spaces of technical rooms 1, with more low cost indicators spent on their implementation, with a reduced (excluded) harmful ecologist impact on the environment through the use of utilized porous polymeric substances as feedstock in the manufacture of the individual components of the claimed technical device. It should be noted that this type of porous sound-absorbing substance can be used repeatedly, when implementing typical utilized technologies, by the corresponding opening of the load-bearing sound-transparent shells 11 and extraction of separate crushed fragmenting sound-absorbing elements 13 from the composition of the isolated briquetted sound-absorbing modules 10 for their possible reuse.

The use of the inventive device for soundproofing sewing 28 of the technical room 1, as part of thin-walled metal wall partitions of the technical room 1, for example, in the construction of a river or sea vessel, in particular, the engine room, and / or walls of air ducts and hull elements of ventilation systems, and / or as part of the enclosing walls and partitions of the engine compartments of various types of vehicles, and / or as part of stationary power plants, etc.) - allows not only providing there is a certain noise-reducing effect associated with the attenuation of the energy of incident sound waves on soundproofing stitching by air, but also create an additional soundproofing effect, including the implementation of both absorption effects and reflection of airborne sound waves incident on the surface of soundproofing stitching 28. A certain vibration-damping is also provided effect associated with the suppression of structural vibrations of this type of thin-walled vibro-noise-active wall, ceiling, intermediate burnups doc It is carried out due to the implementation of dynamic processes of viscoelastic damping of attached 28 flexible contact zones of intermediate layers of adhesive viscoelastic vibration damping material 18 distributed between the mating contacting surfaces of the sound-reflecting enclosing panels of the supporting elements of the interior room 2 and the ceiling 1) soundproofing suturing 28. There is also high-frequency damping bending mechanical vibration of the walls, contributing to the reduction of noise in distributed contact surface areas between the rear sound-reflecting panel of the supporting elements 2 (walls, ceiling, internal partition) of the technical room 1, separate briquetted sound-absorbing modules 10 and a sound-insulating front flat-panel panel 4 or sound-insulating non-insulating 5 soundproofing suturing 28. In this regard, the final achieved noise reduction effect of the claimed design ii soundproofing linings technical premises 28 1 will reach higher values, providing technical object on which it is mounted weighty improving its acoustic, cost, performance and environmental properties.

When mounting the claimed design of the soundproofing suturing 28 on wall and ceiling structures (internal partitions), which are represented by large-sized multilayer structures weakly excited from vibro-noise structures through various “vibration bridges” attached to them, the total soundproofing effect will be based mainly on sound-absorbing and sound-insulating components introduced directly (exclusively) by the constituent elements of the claimed sound-insulating suturing 28. There will also be weaker intrinsic dynamic structural excitation of the sound-insulating face plate 4 or the sound-insulating face molded non-flat panel 5 due to their effective damping by intermediate layers of adhesive viscoelastic vibration-damping material 18 and directly elastically elastic structurally elastic 10 mounted in distributed spaces venous zones of their mutual contact mating.

Soundproofing front flat sheet 4 or soundproofing front molded non-planar 5 panels are mated to the surfaces of the sound-reflecting enclosing panels of the supporting elements 2 (walls, ceiling, internal partition) and fixed with them using appropriate mechanical fasteners 23 and / or layers of adhesive adhesive 19, thermoactive film 20 adhesive substances, and / or an intermediate layer of adhesive viscoelastic vibration-damping material 18. Moreover, in separate areas of their immediate nnogo contact interface may be further mounted corresponding constructions of sealing elements 29 soundproof.

Soundproofing front molded non-planar panels 5 can be represented by corrugated geometric designs with cross sections of a triangle, trapezoid, flat segment (see Fig. 8, 9, 22, 23). Soundproofing front flat sheets 4 and / or soundproofing front molded non-planar panels 5 can be made of structural metal or polymer materials and / or their composite puff combinations with a total wall thickness of 0.5 ... 15 mm.

Inside the enclosed separate containers 12 of the supporting sound-transparent shells and the separate briquetted sound-absorbing modules 10, sound-transparent embedded reinforcing elements 33 of rod, plate or mesh types can be placed. The embedded sound-transparent reinforcing elements of the rod type 33 (see Fig. 31) can be made of the corresponding types of metal (steel, aluminum) or polymeric materials (polyamide, polypropylene, polyethylene, polyvinyl chloride) and are presented in the form of cast, glued, welded or brazed and appropriately spatially placed rod (wire) structural elements. From the same types of structural materials can be made of translucent mesh reinforcing elements, translucent reinforcing form-forming perforated layers of a polymer or metal sheet material (see Fig. 31).

The functioning of acoustic resonators R (quarter-wave R ^I - pos. 26, half-wave R ^II - pos. 27), as technical frequency-selective devices for attenuation (damping) of acoustic energy in given narrow frequency ranges, is determined by the corresponding discrete values of their natural (resonant) vibration frequencies f _R and Q-factors (determined by the width of the resonant characteristics - the frequency domain with respect to the value of the natural resonant frequency of oscillations f _R ) of the indicated types of acoustics of resonators R. The Q factor is equal to the ratio of the value of the natural (resonant) vibration frequency ΔR of the acoustic resonator R (keys 26, 27) to the frequency band Δf _R , at the boundaries of which the acoustic energy during stimulated resonant vibrations is half (3 dB) less than the acoustic energy at the resonant frequency f _R. The quality factor of the acoustic resonator R (pos. 26, 27) is determined (formed) by the magnitude of internal dissipative losses realized in it, arising both directly in the composite structures (elements) of the acoustic resonator R (pos. 26, 27), and external energy losses, directly associated with the process of radiation of sound into the environment, which also consumes the vibrational energy of the acoustic resonator R (pos. 26, 27). The frequency tuning of the acoustic resonators R (pos. 26, 27) is based on the corresponding wave (wavelength λ, wave phase φ) interaction with the resulting effect of interference compensation suppression of the energy of sound waves propagating in an elastic (air) medium of a given frequency range that coincides (close in values) with natural (resonant) frequencies f _{R of the} acoustic resonators R (pos. 26, 27). The frequency f and the wavelength λ of sound vibrations are related to the speed with their propagation in an elastic (air) medium by the following known [4] relation (7)

where λ is the sound wavelength, m;

f is the frequency of sound vibrations, Hz (s ^-1 );

C is the speed of propagation of sound waves (speed of sound), m / s;

[4] Tupov VB Noise reduction from power equipment: a textbook for universities in the direction of "Power Engineering", M: MEI Publishing House, 2005. - 232 p.

In turn, the propagation velocity of sound waves with in an elastic (air) medium is associated with a known functional dependence with the temperature state of this medium t ° C [4], according to expression (8)

where c (t) is the speed of propagation of sound waves (speed of sound) in an elastic medium (air) at an air temperature of t ° C, m / s,

t ° C - air temperature in ° C.

Thus, the adaptive frequency tuning of the acoustic resonators R (pos. 26, 27) determined, inter alia, by the parameter of sound speed c (t), must take into account the change in the operational temperature range Δt of their functioning. It can be carried out, for example, by alternative relatively complex and expensive ways of stabilizing thermostating of the physical parameters of the propagation medium of sound waves (air), or by implementing a tracking (reconfigurable) adaptive change in the structural (geometric) parameters of the constituent elements of acoustic resonators R (pos. 26, 27) providing (forming) their corresponding tracking frequency adjustment due to a change in the sound wavelength Δλ, due to the temperature Δt changes in fluid density and velocity of propagation of sound waves c (t) in it (air) to effect the resulting reduction (attenuation mute) acoustic energy determined frequency band (for specific values of the sound of discrete frequencies f). To weaken the sensitivity (reduce the temperature dependence) of non-adjustable (non-tunable) designs of acoustic resonators R (pos. 26, 27), which are efficient in a certain variable operating temperature Δt of the ambient air environment, which are easy to manufacture, is possible by a corresponding change in the “quality factor” of acoustic resonator R (pos. 26, 27), with some possible loss of suppression (damping) efficiency in terms of the amplitude response of the acoustic energy at discrete values of natural (resonant) frequencies f _R. This, in particular, can be achieved by introducing into the resonant oscillating (acoustic) system containing acoustic resonators R (keys 26, 27), additional dissipative losses, which provide a corresponding extension of the frequency range of the effectiveness of the acoustic resonators R. In these cases, expanding the frequency range of the efficiency It means a possible increase in the number of damped sound frequencies are located near its own discrete value (resonant) frequency f _R and the corresponding, wavelength λ (quat mercury of lengths λ / 4, half-lengths λ / 2) of sound waves that are laid during their propagation in the cavity of the tubular part 31 of the acoustic resonator R (keys 26, 27), with the implementation of the corresponding interference compensation effects of suppression (attenuation) of acoustic energy in the specified extended frequency range.

The generated (excited) intrinsic acoustic resonances of the air cavity of the soundproofing suturing 28, at its own acoustic modes with sound frequencies f _md , f _mL , f _mB , f _mH (m = 1, 2, 3 ...), can significantly enhance the resonance transfer of acoustic energy from the specified air cavity to adjacent rooms or into open space, with a corresponding increase in acoustic pollution of the environment, which poses the problem of using appropriate technical means of elimination (suppression, attenuation i) this type of resonant amplification of acoustic radiation.

и $${\text{l}}_{\text{R}}^{\text{''}}$$

) акустических резонаторов R′ и R″. Возникающие в объеме воздушной полости звукоизолирующей зашивки резонансные усиления акустических колебаний являются результатом формирования и распространения в ней продольных, поперечных и повысотных звуковых волн от источников их динамического (механического, газодинамического) возбуждения и последующих процессов многократных отражений звуковых волн от противолежащих (оппозитно расположенных) звукоотражающих стенок звукоизолирующей лицевой плосколистовой панели 4 (или формованной неплоской панели 5) звукоизолирующей зашивки 28 и оппозитно расположенной к ней на расстоянии d поверхностью звукоотражающей ограждающей панели несущих элементов 2 - стены, потолка, внутренней перегородки технического помещения 1 и соответствующего образования в ней резонансных стоячих звуковых волн (собственных акустических мод). Соответственно, периоды этих звуковых колебаний Т по толщине d воздушного промежутка, длине L, ширине В и высоте Н ребер технического помещения 1 определяются согласно выражения (9):The condition for suppressing (eliminating) the resonant amplification of the emission of sound energy concentrated on intrinsic acoustic modes of air volume formed by the thickness of the air gap d, length L, width B and height H of the edges of the technical room 1 - f _md , f _mL , f _mB , f _mH , (where m = 1, 2, 3, ...), is based on the frequency-adjusted combination of the values of natural (resonant) frequencies of sound vibrations of various types of acoustic resonators R (pos. 26, 27) - f _Rd , f _RL , f _RB , f _RH forming, in particular, a battery of acoustic resonances R endowed with a reason the natural frequencies of vibrations f _R , which coincide with the indicated frequencies of the natural acoustic modes of the air cavity of the soundproofing lining - f _md , f _mL , f _mB , f _mH . This is achieved by ensuring that the overall dimensions of the air cavity match the thickness of the air gap d, length L, width B and height H, with the corresponding values of quarters of the lengths of sound waves (λ / 4) and half of the lengths of sound waves (λ / 2) that fit (multiple ) the specified overall dimensions of the air cavities of the tubular parts 31 (dynamic lengths $${\text{l}}_{\text{R}}^{\text{''}}$$

and $${\text{l}}_{\text{R}}^{\text{''}}$$

) acoustic resonators R ′ and R ″. The resonant amplifications of acoustic vibrations arising in the volume of the air cavity of soundproofing stitching are the result of the formation and propagation of longitudinal, transverse and elevational sound waves in it from sources of their dynamic (mechanical, gasdynamic) excitation and subsequent processes of multiple reflections of sound waves from opposing (opposite) sound-reflecting walls sound insulating front flat panel 4 (or molded non-flat panel 5) sound insulating stitching 28 and opposite to it at a distance d from the surface of the sound-reflecting enclosing panel of the supporting elements 2 — the wall, ceiling, internal partition of the technical room 1 and the corresponding formation of resonant standing sound waves (intrinsic acoustic modes) in it. Accordingly, the periods of these sound vibrations T by thickness d of the air gap, length L, width B and height H of the ribs of the technical room 1 are determined according to the expression (9):

where c is the speed of propagation of sound waves (speed of sound), m / s.

In turn, the process of reflection of sound waves P _Otr from the hard sound-reflecting walls of the sound-insulating face plate 4 or of the molded non-flat panel 5 of the sound-insulating suturing 28 and the surfaces of the sound-reflecting enclosing panel of the supporting elements 2, wall, ceiling, internal partition of the technical room 1, which are opposite at a distance d occurs in phase with the incident waves P _pad :

The dependence of the pressure fluctuations in this type of reflected sound waves at the opposite walls of the front flat panel 4 or the molded non-flat panel 5 of the soundproofing suturing 28 and the surfaces of the sound-reflecting enclosing panel of the supporting elements 2 opposite at a distance d varies according to the harmonic law (cosine). Pressure pulses excited by incident sound waves P _pad1 , P _pad2 , P _pad3 , P _pad4 , located, for example, at the 28 open ends (sections) of the throats (neck parts) of 30 half-wave acoustic resonators R ^II (pos. . 27), U-shaped geometric shape (see Fig. 12, 13), propagate in opposite directions in the cavities of the tubular parts 31, towards each other with the speed of sound c. In the cavities of the tubular parts of 31 acoustic resonators R _md , R _mL R _mB , R _{mH, the} sound pressure pulses are in phase (due to the close, not exceeding the γ value, location of the neck parts 30) of the incident sound waves P _pad1 , P _pad2 , P _pad3 , P _pad4 in the throat parts 30 and extending towards each other through the tubular parts 31, are out of phase with each other. If the time t ^II through which the sound pressure pulses pass through the tubular parts 31 of the acoustic resonators R ^II (pos. 27) is:

then the positive impulses of sound pressure add up with the negative impulses of sound pressure and compensate for them.

, $${\text{t}}_{\text{B}}^{\text{II}}$$

, $${\text{t}}_{\text{d}}^{\text{II}}$$

, $${\text{t}}_{\text{H}}^{\text{II}}$$

определяются из соотношения (12):Quantities $${\text{t}}_{\text{L}}^{\text{II}}$$

, $${\text{t}}_{\text{B}}^{\text{II}}$$

, $${\text{t}}_{\text{d}}^{\text{II}}$$

, $${\text{t}}_{\text{H}}^{\text{II}}$$

are determined from relation (12):

, $${\text{l}}_{\text{Rmd}}^{}{}^{\text{II}}$$

, $${\text{l}}_{\text{RmB}}^{}{}^{\text{II}}$$

, $${\text{l}}_{\text{RmH}}^{}{}^{\text{II}}$$

- динамические длины полуволновых акустических резонаторов $${\text{R}}_{\text{md}}^{}{}^{\text{II}}$$

, $${\text{R}}_{\text{mL}}^{}{}^{\text{II}}$$

, $${\text{R}}_{\text{mB}}^{}{}^{\text{II}}$$

, $${\text{R}}_{\text{mH}}^{}{}^{\text{II}}$$

;Where $${\text{l}}_{\text{Rmd}}^{}{}^{\text{II}}$$

, $${\text{l}}_{\text{Rmd}}^{}{}^{\text{II}}$$

, $${\text{l}}_{\text{Rmb}}^{}{}^{\text{II}}$$

, $${\text{l}}_{\text{Rmh}}^{}{}^{\text{II}}$$

- dynamic lengths of half-wave acoustic resonators $${\text{R}}_{\text{md}}^{}{}^{\text{II}}$$

, $${\text{R}}_{\text{mL}}^{}{}^{\text{II}}$$

, $${\text{R}}_{\text{mB}}^{}{}^{\text{II}}$$

, $${\text{R}}_{\text{mH}}^{}{}^{\text{II}}$$

;

In this way:

, $${\text{l}}_{\text{Rmd}}^{}{}^{\text{II}}$$

, $${\text{l}}_{\text{RmB}}^{}{}^{\text{II}}$$

, $${\text{l}}_{\text{RmH}}^{}{}^{\text{II}}$$

(см. фиг. 12, 13), учитывающие присоединенные к горлам (горловым частям) 30 колеблющиеся массы воздуха (фиг. 14) будут соответственно равны:In this regard, when using this type of noise suppressing structures, presented, in particular, in the form of U-shaped half-wave acoustic resonators R ^II (item 27), with the tubular part 31 open at both ends, with two receiving throats (throat parts) 30, their dynamic lengths $${\text{l}}_{\text{Rmd}}^{}{}^{\text{II}}$$

, $${\text{l}}_{\text{Rmd}}^{}{}^{\text{II}}$$

, $${\text{l}}_{\text{Rmb}}^{}{}^{\text{II}}$$

, $${\text{l}}_{\text{Rmh}}^{}{}^{\text{II}}$$

(see Fig. 12, 13), taking into account the oscillating masses of air attached to the throats (throat parts) 30 (Fig. 14) will be respectively equal to:

полуволновых акустических резонаторов R^II (поз. 27) составляют:Accordingly, natural (resonant) oscillation frequencies $${\text{f}}_{\text{R}}^{\text{II}}$$

the half-wave acoustic resonators R ^II (pos. 27) comprise:

со скоростью звука с определяется из выражения (16):Similarly, the dynamic lengths of three samples of quarter-wave acoustic resonators R ^I (key 26) are determined, in which one of the end sections of the tubular part 31 is closed by a rigid sound-reflecting bottom 32 (see Figs. 8, 10, 11, 14). In this case, through the open receiving section of the throat (throat part) 30, the quarter-wave acoustic resonator R ^I (key 26), the sound wave P _pad enters its tubular part 31, “reaches” (propagates) to its closed by a hard sound-reflecting bottom 32 end portion, reflected from it P _Otr and returns to the open section (neck portion 30). Round trip time of the wave $${\text{(t}}_{\text{L}}^{\text{I}}{\text{, t}}_{\text{B}}^{\text{I}}{\text{, t}}_{\text{d}}^{\text{I}}{\text{, t}}_{\text{H}}^{\text{I}}\text{)}$$

with the speed of sound c is determined from the expression (16):

, $${\text{t}}_{\text{B}}^{\text{I}}={\text{T}}_{\text{B}}\text{/}2$$

, $${\text{t}}_{\text{d}}^{\text{I}}={\text{T}}_{\text{d}}\text{/}2$$

, $${\text{t}}_{\text{H}}^{\text{I}}={\text{T}}_{\text{H}}\text{/}2$$

необходимо чтобы динамические длины $${\text{l}}_{\text{R}}^{\text{I}}$$

(фиг.14) четвертьволновых акустических резонаторов R^I (поз.26) были равны половинам габаритных параметров d, L, В, Н:In order to $${\text{t}}_{\text{L}}^{\text{I}}={\text{T}}_{\text{L}}\text{/}2$$

, $${\text{t}}_{\text{B}}^{\text{I}}={\text{T}}_{\text{B}}\text{/}2$$

, $${\text{t}}_{\text{d}}^{\text{I}}={\text{T}}_{\text{d}}\text{/}2$$

, $${\text{t}}_{\text{H}}^{\text{I}}={\text{T}}_{\text{H}}\text{/}2$$

dynamic lengths required $${\text{l}}_{\text{R}}^{\text{I}}$$

(Fig) quarter-wave acoustic resonators R ^I (pos. 26) were equal to half the overall parameters d, L, B, H:

такого типа четвертьволновых акустических резонаторов R^I (поз.26) при соблюдении условия уравнения (17) составляют:Accordingly, the natural (resonant) frequencies of sound vibrations $${\text{f}}_{\text{R}}{}^{\text{I}}$$

of this type of quarter-wave acoustic resonators R ^I (pos. 26), subject to the conditions of equation (17), are:

, $${\text{f}}_{\text{RB}}{}^{\text{I}}$$

, $${\text{f}}_{\text{Rd}}{}^{\text{I}}$$

, $${\text{f}}_{\text{RH}}{}^{\text{I}}$$

будут идентичны значениям определяемым согласно выражения (15), установленного, как и для полуволновых акустических резонаторов R^II (поз. 27) и, аналогичным образом, соответствовать частотам низших (m=1) собственных акустических мод воздушного объема полости звукоизолирующей зашивки (f_d, f_L, f_B, f_H), исходя из приведенного выражения (19):Thus, subject to the conditions of the indicated type of design of the quarter-wave acoustic resonators R ^I (pos. 26), according to expression (18), the frequencies of their own (resonant) oscillations $${\text{f}}_{\text{RL}}{}^{\text{I}}$$

, $${\text{f}}_{\text{RB}}{}^{\text{I}}$$

, $${\text{f}}_{\text{Rd}}{}^{\text{I}}$$

, $${\text{f}}_{\text{Rh}}{}^{\text{I}}$$

will be identical to the values determined according to expression (15), which is established, as for the half-wave acoustic resonators R ^II (key 27) and, in a similar way, correspond to the frequencies of the lowest (m = 1) eigen acoustic modes of the air volume of the soundproofing cavity (f _d , f _L , f _B , f _H ), based on the above expression (19):

, и полуволновых акустических резонаторов R^II (поз. 27), характеризуемых их динамическими длинами - $${\text{l}}_{\text{R}}^{\text{II}}$$

, и устанавливаемым между стенками лицевой плосколистовой панели 4 или формованной неплоской панели 5 звукоизолирующей зашивки 28 и оппозитно расположенных на расстоянии d поверхностей звукоотражающей ограждающей панели несущих элементов 2, полуволновыми (λ/2) пространственными акустическими резонансами воздушных объемов полостей звукоизолирующей зашивки 28. Во всех случаях изменения параметров t°C и c(t°C), это повлечет соответствующее синхронное изменение значений частот f_md, f_mL, f_mB, f_mH, без какого-либо изменения сформированной между оппозитными противолежащими стенками длины звуковой волны λ (половины длины звуковой волны λ/2). Таким образом, будет обеспечена (сохранена) точная частотная настройка акустических резонаторов R^I и R^II, базирующаяся на интерференционном взаимодействии звуковых волн распространяемых в их трубчатых 30 и горловых 31 частях с резонансными частотами f_Rd, f_RL, f_RB, f_RH.From the above expressions it follows that the frequency tuning of the half-wave acoustic resonators R ^II (pos. 27) and the quarter-wave acoustic resonators R ^I (pos. 26) to suppress the intrinsic acoustic resonances of the air cavities of soundproofing lining, which manifest themselves on their own acoustic modes with frequencies f _md , f _mL , f _mB , f _mH , does not depend on the change in air temperature t ° C (Δt), associated with this change in the speed of sound waves c (t ° C) and the length of the sound wave λ (t ° C). This is due to the fact that there is a direct direct relationship between the basic unchanged (constant) dimensions of the air cavity of soundproofing sewing - characterized by the parameters d, L, B and H, selected overall dimensions of the quarter-wave acoustic resonators R ^I (pos. 26), characterized by dynamic lengths - $${\text{l}}_{\text{R}}^{\text{I}}$$

, and half-wave acoustic resonators R ^II (pos. 27), characterized by their dynamic lengths - $${\text{l}}_{\text{R}}^{\text{II}}$$

, and installed between the walls of the front plane-sheet panel 4 or the molded non-planar panel 5 of the sound-insulating suturing 28 and the surfaces of the sound-reflecting enclosing panel of the supporting elements 2 opposite at a distance d, the half-wave (λ / 2) spatial acoustic resonances of the air volumes of the cavities of the sound-insulating suturing 28. In all cases changing parameters t ° C and c (t ° C), it will cause a corresponding change in frequency values synchronous _{f md, f mL, f mB} , f mH, without any change generated between the opp operating actions opposite walls of the sound wavelength λ (half λ / 2 acoustic wavelength). Thus, the exact frequency tuning of the acoustic resonators R ^I and R ^II will be provided (saved), based on the interference interaction of the sound waves propagating in their tubular 30 and throat 31 parts with resonant frequencies f _Rd , f _RL , f _RB , f _RH .

Translation of the dynamic length parameters of the half-wavelength R ^II (pos. 27) and the quarter-wavelength R ^I (pos. 26) of the acoustic resonators R (R _md , R _mL , R _mB , R _mH ) intended for the suppression of intrinsic acoustic resonances of the air cavity of soundproof sewing 28 , manifesting themselves in their own acoustic modes with frequencies f _md , f _mL , f _mB , f _mH into design parameters expressed by their geometric lengths l _r (provided m = 1), can be implemented according to the following expressions (20) ... (27 ):

, $${\text{l}}_{\text{rL}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rB}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rH}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rd}}{}^{\text{I}}$$

, $${\text{l}}_{\text{rL}}{}^{\text{I}}$$

, $${\text{l}}_{\text{rB}}{}^{\text{I}}$$

, $${\text{l}}_{\text{rH}}{}^{\text{I}}$$

- геометрические длины трубчатых частей 31 акустических резонаторов R^II и R^I ( $${\text{R}}_{\text{rd}}{}^{\text{II}}$$

, $${\text{R}}_{\text{rL}}{}^{\text{II}}$$

, $${\text{R}}_{\text{rB}}{}^{\text{II}}$$

, $${\text{R}}_{\text{rH}}{}^{\text{II}}$$

, $${\text{R}}_{\text{rd}}{}^{\text{I}}$$

, $${\text{R}}_{\text{rL}}{}^{\text{I}}$$

, $${\text{R}}_{\text{rB}}{}^{\text{I}}$$

, $${\text{R}}_{\text{rH}}{}^{\text{I}}$$

)Where $${\text{l}}_{\text{rd}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rL}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rB}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rH}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rd}}{}^{\text{I}}$$

, $${\text{l}}_{\text{rL}}{}^{\text{I}}$$

, $${\text{l}}_{\text{rB}}{}^{\text{I}}$$

, $${\text{l}}_{\text{rH}}{}^{\text{I}}$$

- the geometric lengths of the tubular parts 31 of the acoustic resonators R ^II and R ^I ( $${\text{R}}_{\text{rd}}{}^{\text{II}}$$

, $${\text{R}}_{\text{rL}}{}^{\text{II}}$$

, $${\text{R}}_{\text{rB}}{}^{\text{II}}$$

, $${\text{R}}_{\text{rH}}{}^{\text{II}}$$

, $${\text{R}}_{\text{rd}}{}^{\text{I}}$$

, $${\text{R}}_{\text{rL}}{}^{\text{I}}$$

, $${\text{R}}_{\text{rB}}{}^{\text{I}}$$

, $${\text{R}}_{\text{rH}}{}^{\text{I}}$$

)

d, L, B and H - overall dimensions, in m (d - thickness of the air cavity of the soundproofing suturing 28, L - length, B - width, N - height of the ribs of the technical room 1);

S _T is the bore of the tubular part 15 in m ² half-wave 27 or quarter-wave 26 acoustic resonators R ^II and R ^I ;

π = 3.14

и $${\text{l}}_{\text{r}}{}^{\text{I}}$$

такого типа полуволновых R^II (поз. 27) и четвертьволновых R^I (поз. 26) акустических резонаторов R (R_md, R_mL, R_mB, R_mH), на 2, 3, 4…, которые будут в кратное число короче по отношению к их базовым геометрическим длинам $${\text{l}}_{\text{r}}{}^{\text{II}}$$

и $${\text{l}}_{\text{r}}{}^{\text{I}}$$

определенных для случая m=1.The suppression of the intrinsic acoustic resonances of the air cavity at the higher multiple harmonic components (overtones) of the intrinsic acoustic modes when m> 1 (m = 2, 3, 4, 5, 6 ...) can be carried out by choosing the appropriate values of the geometric lengths $${\text{l}}_{\text{r}}{}^{\text{II}}$$

and $${\text{l}}_{\text{r}}{}^{\text{I}}$$

of this type of half-wave R ^II (pos. 27) and quarter-wave R ^I (pos. 26) acoustic resonators R (R _md , R _mL , R _mB , R _mH ), 2, 3, 4 ... which will be a multiple shorter in relation to their basic geometric lengths $${\text{l}}_{\text{r}}{}^{\text{II}}$$

and $${\text{l}}_{\text{r}}{}^{\text{I}}$$

defined for the case m = 1.

и $$\left(\mathrm{0,1}\cdots \mathrm{0,3}\right)\sqrt{{\text{4S}}_{\text{T}}\text{/π}}$$

учитывают величины вязкоприсоединенных к плоскостям открытых срезов горловых частей 30 акустических резонаторов R^II и R^I, колеблющихся в полостях их трубчатых частей 31 дополнительных масс воздуха, что приводит к соответствующим динамическим удлинениям реально колеблющихся воздушных столбов на конкретных значениях собственных (резонансных) частот акустических колебаний f_R акустических резонаторов R^II и R^I (см. фиг. 14). Величины динамических удлинений $$\left(\mathrm{0,2}\cdots \mathrm{0,6}\right)\sqrt{{\text{4S}}_{\text{T}}\text{/π}}$$

и $$\left(\mathrm{0,1}\cdots \mathrm{0,3}\right)\sqrt{{\text{4S}}_{\text{T}}\text{/π}}$$

, как следует из приведенных выражений (20)…(27), являются функцией площади поперечного сечения S_T трубчатой части 31 акустических резонаторов R^II и R^I. Ввиду того, что полуволновой акустический резонатор R^II (поз. 27) представлен двумя открытыми срезами (двумя горловыми частями 30), то его суммарная величина динамического удлинения геометрической длины, при прочих равных условиях в два раза превышает соответствующую величину динамического удлинения четвертьволнового акустического резонатора R^I (поз. 26), наделенного одной горловой частью 30. Введенные диапазоны значений (0,2…0,6) и (0,1…0,3) учитывают (охватывают) влияющие на изменение (установление заданных значений) величин динамических удлинений горловых частей 30, образуемых дополняющих или альтернативных многообразий конкретных конструктивных исполнений геометрических форм горловых частей 30, и/или наличия в полостях трубчатых частей 31 демпфирующих пористых воздухопродуваемых пробок 34, и/или наличия в стенках трубчатых частей 31 перфорированных отверстий 9 и/или наличие близкорасположенных к горловым частям 30 жестких звукоотражающих или пористых звукопоглощающих элементов, относящихся к другим деталям (узлам) технического объекта, а также наличие в плоскости горловой части 30 расположенных рядом других образцов акустических резонаторов R (R^II, R^I) и/или применения воздухопродуваемых слоев пористых тканевых, нетканого полотка, микроперфорированной пленки или микроперфорированной фольги диссипативных рассеивателей резонансных колебаний звукового давления (поз. 16), перекрывающих сечение трубчатой 31 и/или горловой 30 частей акустических резонаторов R (R^II, R^I), как это представлено на фиг. 9, 11 и 13.In the above expressions (20) ... (27), their components $$\left(0.2\cdots 0.6\right)\sqrt{{\text{4S}}_{\text{T}}\text{/ π}}$$

and $$\left(0.1\cdots 0.3\right)\sqrt{{\text{4S}}_{\text{T}}\text{/ π}}$$

take into account the values of viscous acoustic cavities R ^II and R ^I attached to the planes of open sections of the throat parts 30, oscillating in the cavities of their tubular parts 31 of additional air masses, which leads to corresponding dynamic elongations of really oscillating air columns at specific values of the natural (resonant) frequencies of acoustic vibrations f _R acoustic resonators R ^II and R ^I (see Fig. 14). Dynamic elongation values $$\left(0.2\cdots 0.6\right)\sqrt{{\text{4S}}_{\text{T}}\text{/ π}}$$

and $$\left(0.1\cdots 0.3\right)\sqrt{{\text{4S}}_{\text{T}}\text{/ π}}$$

, as follows from the above expressions (20) ... (27), are a function of the cross-sectional area S _{T of the} tubular part 31 of the acoustic resonators R ^II and R ^I. Due to the fact that the half-wave acoustic resonator R ^II (pos. 27) is represented by two open sections (two neck parts 30), its total value of the dynamic elongation of the geometric length, ceteris paribus, is twice the corresponding value of the dynamic elongation of the quarter-wave acoustic resonator R ^I (pos. 26), endowed with one throat part 30. The entered ranges of values (0.2 ... 0.6) and (0.1 ... 0.3) take into account (cover) the dynamic elongated values influencing the change (establishment of set values) throat parts 30 formed by complementary or alternative varieties of specific designs of geometric shapes of the throat parts 30, and / or the presence in the cavities of the tubular parts 31 of damping porous air-blown plugs 34, and / or the presence of perforated holes 9 in the walls of the tubular parts 31 and / or 30 rigid sound-reflecting or porous sound-absorbing elements adjacent to the throat parts related to other parts (nodes) of the technical object, as well as the presence of the throat part in the plane and 30 adjacent other samples of acoustic resonators R (R ^II , R ^I ) and / or the use of air-blown layers of porous fabric, non-woven fabric, microperforated film or microperforated foil of dissipative diffusers of resonant sound pressure oscillations (pos. 16), overlapping the section of the tubular 31 and / or throat 30 parts of the acoustic resonators R (R ^II , R ^I ), as shown in FIG. 9, 11 and 13.

, $${\text{l}}_{\text{r}}{}^{\text{II}}$$

, акустических резонаторов R^I, R^II, учитываемых величиной соответствующего приращения присоединенной к открытому срезу четвертьволнового акустического резонатора R^I - (поз. 26), равного (0,1…0,3) d_пр или двум открытым срезам трубчатых частей 31 - для полуволнового акустического резонатора R^II (поз. 27) трубчатого типа с сечением круга равного 0,2…0,6 d_пр.Non-circular geometric shapes of the sections of the tubular parts 31 of the acoustic resonators R (pos. 26, 27), made mainly in the form of regular geometric shapes - a triangle, a rectangle, a trapezoid, a segment in which the specified proportions of the overall dimensions of one of the sides (base, chord) are maintained height (arrow), forming the indicated types of geometric shapes, which are in the range of ratios b: W = 0.3 ... 3, also satisfy the condition of the corresponding corresponding conservation specified in the formula of the range of values, dynamic th extension geometric lengths $${\text{l}}_{\text{r}}{}^{\text{I}}$$

, $${\text{l}}_{\text{r}}{}^{\text{II}}$$

, acoustic resonators R ^I , R ^II , taken into account by the value of the corresponding increment attached to the open section of the quarter-wave acoustic resonator R ^I - (key 26), equal to (0.1 ... 0.3) d _pr or two open sections of tubular parts 31 - for a half-wave acoustic resonator R ^II (pos. 27) of a tubular type with a circle cross-section equal to 0.2 ... 0.6 d, _etc.

Here d _CR - the hydraulic diameter of the bore of the tubular part 31 of the acoustic resonators R ^I (pos. 26) or R ^II (pos. 27), determined from the expression (28)

where S _T is the flow area of the tubular part 15 of the acoustic resonator R (pos. 26, 27), m ² ;

π = 3.14.

The introduction of various types of additional sound-damping elements into the structures of acoustic resonators R - (keys 26, 27), for example, by making perforation holes 9, installing damping porous air-blown plugs 34 in the cavities of the tubular elements 31, and using a protective lining damping layer of material 16 mounted on the throat 30 and / or tubular 31 parts (see FIGS. 11 and 13) pursues, inter alia, deliberate implementations of partial compensation for the loss of noise reduction effects that may occur if possible frequency detunings of acoustic resonators R - (pos. 26, 27) from given fixed frequencies of acoustic radiation, not taking into account (insufficiently taken into account) occurring temperature changes in the environment (air) Δt, causing corresponding changes in the speed of propagation of sound waves with and related changes in the lengths of sound λ (λ / 4, λ / 2). This determines the feasibility of using the lower-quality frequency characteristics of the acoustic resonators R (pos. 26, 27), endowed with less sensitivity to the accuracy of the frequency tuning. Accordingly, the use of designs of acoustic resonators R (keys 26 and 27) with a wider bandwidth efficiency in frequency composition, but with a smaller effect of suppressing the amplitudes of resonant acoustic vibrations, due to the introduction of additional dissipative losses of sound energy into the vibrational resonating acoustic system, allows to reduce the sensitivity of the used acoustic resonators R (pos. 26, 27) to their frequency detuning.

The use of perforation holes 9 as an added complementary or alternative dissipative sound-damping element in the structures of tubular parts 31 of the acoustic resonators R ^I , R ^II (keys 26, 27), implies the implementation (compliance) of a given boundary ratio of the total passage area of n-holes ( n _holes) perforation 9 - F _per.o. to the area of the passage section of the corresponding zone of the tubular part 31 - S _T in the wall of which perforation holes 9 are made. It is characterized by a perforation coefficient K _lane. and is determined according to the expression (29)

where K _lane - the coefficient of perforation of the wall of the tubular part 31 of the acoustic resonator R (R ^I , R ^II );

F _lane - the total area in m ² passage section _{of holes} n holes perforations 9 formed in the wall of the tubular portion 31 of the acoustic resonator ^{R (R I, R II)} ;

S _T is the area in m ^{2 of the} bore of the tubular part 31 of the acoustic resonator R (R ^I , R ^II );

Observance of the condition in expression (29) implies the exclusion of the effect of constructive shortening of the dynamic lengths l _{R of the} tubular parts 31 of the acoustic resonators R (R ^I , R ^II ), and the elimination of the subsequent violation of the corresponding frequency tuning of the acoustic resonators R (R ^I , R ^II ) with exceeding the value of the limit value K _lane ≤0.05. Otherwise, the dynamic cut of the tubular part 31 and the throat part 30 of the acoustic resonators R (R ^I , R ^II ) is no longer a free end cut of the tubular part 31, but a made belt of perforation holes 9, the total area of the passage section, which exceeds the limit value 0 , 05 S _T. The minimum value of the parameter F _lane is determined by the practical effects of damping the resonant amplitudes of sound vibrations in the air cavity of the tubular part 31 of the acoustic resonator R (R ^I , R ^II ). Also complicated technological problems perform small calibrated perforations 9 in dynamic compliance (nonrigid) thin wall structures of tubular elements 31. At the same time, other conditions being equal (with the same value of the total area F _per.o. passage section _{of holes} n perforation holes 9) preference should be given to a larger number of small-sized perforation holes 9. In this case, at a constant F _per.o. It increases the total perimeter of the passage section _{of holes} n perforations 9. This is directly related with the increase of the friction effect dissipative dispersion (sold perimeter increases friction friction pulsating pressure in the cavity of the tubular portion 31 of the wall a large number of small perforations 9, characterized by a large total perimeter).

Of course, the claimed invention is not limited to exclusively specific structural examples of its implementation presented in the application materials, described in the text and shown in the accompanying figures in the graphic part of the application. Some minor changes to the various structural elements or materials from which these elements are made, or to replace them with technically equivalent ones that do not go beyond the scope of the claims indicated by the claims, remain possible.

Claims (25)

1. Soundproofing sewn-up technical room containing load-bearing elements represented by sound-reflecting enclosing panels in the form of walls, a ceiling, an internal partition of the technical room, on which separate sound-absorbing panels are made by mechanical fasteners, made in the form of crushed fragments of porous fibrous and / or foamed open-cell materials and opposed faceplates that form air cavities with predetermined gaps relative to the sound path surfaces of the enclosing enclosing panels of said load-bearing elements and forming corresponding sound-absorbing elements, characterized in that the crushed fragments of porous fibrous and / or foamed open-cell materials are made in the form of corresponding separate crushed fragmented sound-absorbing elements placed in the cavities of closed separate containers of load-bearing sound-transparent shells with the formation of isolated sound-absorbing modules placed in air cavities formed by radios of sound-reflecting enclosing panels of load-bearing elements represented by walls, a ceiling, an internal partition and an oppositely placed sound-insulating front flat-sheet and / or sound-insulating front molded non-flat panel, and / or by the fact that in air cavities formed by the surfaces of sound-reflecting enclosing panels of load-bearing panels, represented by the ceiling, the inner partition and the opposed soundproofed face flat sheet and / or soundproofed face molded non-planar panels, are mounted quarter-wave acoustic resonators R ^I and / or half-wave acoustic resonators R ^II. 2. Soundproofing the sewing of the technical room according to claim 1, characterized in that the isolated briquetted sound-absorbing modules are placed in the respective defined limited localized spatial zones of the air cavities formed by the surfaces of the sound-reflecting enclosing panels of the supporting elements, represented by the walls, the ceiling, the internal partition and the opposite placed sound-insulating faces flat-sheet and / or soundproofing front molded non-flat panels. 3. Soundproofing sewing of a technical room according to claim 2, characterized in that the corresponding predetermined limited localized spatial zones of the air cavities, in which separate isolated briquette sound-absorbing modules are mounted, are concentrated in peripheral angular and / or end sections formed by mates of sound-insulating front flat-sheeted and / or soundproofing front molded non-planar panels with corresponding counter surfaces of the supporting elements (floor, sweat ka, walls and internal partitions), technical room. 4. Soundproofing sewing of a technical room according to claim 3, characterized in that the distributed concentrated separate briquetted sound-absorbing modules are additionally mounted in spatial zones of intersection of the main axes of inertia of the projections of air volumes enclosed in air cavities formed by the respective surfaces of the sound-reflecting enclosing panels of the supporting elements represented by the walls , ceiling, internal partition, and soundproofing face plates by sheet panels, and / or in spatial zones of intersection of the main axes of inertia of four identical parts of air volumes formed by intersecting longitudinal and transverse planes at the centers of gravity of the air volumes of cavities formed by the surfaces of the corresponding sound-reflecting enclosing panels of the supporting elements, represented by walls, ceiling, internal partition and opposite soundproofed face plate panels. 5. Soundproofing sewing of the technical room according to claim 3, characterized in that the limited localized spatial zones of the air cavities in which the separate briquetted sound-absorbing modules are mounted are located at the end sections of the mates of the corresponding soundproofing front molded non-planar panels with the opposing surfaces of the supporting elements represented by the floor, ceiling, walls, internal partition of the technical room, complemented by installed separate briquettes sound absorbing modules concentrated in the spatial zones of the halves and / or quarters of the overall cavity lengths formed by the corresponding mates of the soundproofing front molded non-planar panels with the opposing surfaces of the specified load-bearing elements, represented by the floor, ceiling, walls, internal partition of the technical room. 6. Soundproofing sewing of the technical room according to claim 1, characterized in that in the limited contact zones of the isolated briquetted sound-absorbing modules with the walls of the soundproofing face flat-sheet or soundproofing front molded non-planar panels, the corresponding perforation holes are made in the latter, while the perforation coefficient of said limited contact zones pairing does not exceed the value of 0.1. 7. Soundproofing sewing of a technical room according to claim 6, characterized in that the boundary perimeter of a closed geometric shape, covering limited areas of perforation holes made in the wall of a soundproofing front flat sheet or soundproofing front molded non-planar panel, is overlapped by an equidistant placed boundary perimeter of closed geometric shape with it the contact surface of a separate briquetted sound-absorbing module, each point of which alena from the boundary perimeter of the limited area of the location of the perforation holes by an amount not less than the overall thickness of the isolated briquette sound-absorbing module that overlaps this limited area of the location of the perforation holes. 8. Soundproofing sewing up of a technical room according to claim 1, characterized in that the soundproofing sheaths of the isolated briquette sound-absorbing modules are made of a layer of structural material with a thickness of 0.025 ... 0.25 mm and a specific surface weight of 20 ... 200 g / m ² , represented by an air-blown polymer film , with metal foil or made of an air-blown fabric layer, non-woven fabric, microperforated polymer film, microperforated metal foil, blowing resistance which is the air flow in the range of 20 ... 500 N · s / m ^3. 9. Soundproofing sewing of the technical room according to claim 7, characterized in that the surface area of the closed geometric shape of the boundary perimeter, covering the limited areas of the perforation holes made in the wall of the soundproofing face plane or soundproofing face formed non-planar panels, is covered by a lining sound-transparent air-impermeable film , metal foil and / or an air-blown layer of fabric, non-woven fabric, microperforated polymer molecular film microperforated metal foil 10. Soundproofing sewing of a technical room according to claim 1, characterized in that the isolated briquette sound-absorbing modules contain appropriate sound-transparent embedded reinforcing elements of the rod and / or mesh, and / or perforated sheet types 11. Soundproofing sewing-up of a technical room according to claim 2, characterized in that the isolated briquetted sound-absorbing modules are mounted in undercutting cavities formed by separate convex containers made in the walls of the soundproofing front molded non-planar panels and / or made in the structures of the supporting elements - walls, ceiling, internal partition of the technical room 12. Soundproofing sewing-up of a technical room according to claim 1, characterized in that the separate briquetted sound-absorbing modules are mounted on sound-reflecting enclosing panels of load-bearing elements and / or sound-insulating flat-sheet and / or sound-insulating front molded panels using appropriate mechanical fasteners and / or a sticky layer adhesive adhesive substance and / or layer of film thermoactive adhesive substance and / or intermediate layer of adhesive viscoelastic in noise damping material 13. Soundproofing sewing of a technical room according to claim 1, characterized in that the soundproofing front flat-sheeted or soundproofing front molded non-planar panels are mated to the surfaces of the sound-reflecting enclosing panels of the supporting elements (walls, ceiling, internal partition) and fixed with them using appropriate mechanical fasteners , and / or layers of sticky adhesive, film thermoactive adhesive substances, and / or an intermediate layer of adhesive viscoelastic vibro modempfiruyuschego material, wherein in the individual zones of direct contact pairing corresponding construction additionally mounted soundproof sealing elements. 14. Soundproofing sewing of a technical room according to claim 1, characterized in that the soundproofing front molded non-planar panels are represented by corrugated geometric designs with cross sections of a triangle, trapezoid, flat segment 15. Soundproofing sewing of a technical room according to claim 1, characterized in that the soundproofing front flat sheets and / or soundproofing front molded non-flat panels are made of metal or polymeric materials and / or their composite puff combinations with a total wall thickness of 0.5 ... 15 mm. 16. Soundproofing sewing-up of a technical room according to claim 1, characterized in that the isolated crushed fragmented sound-absorbing elements are made of identical or different types of structures and grades of porous sound-absorbing materials, characterized by identical or different physical characteristics, chemical composition, porosity, tortuosity of pores, quantity and / or a different combination of the used types of structures of the porous layers in the composition of single and / or their multilayer combinations, identical or different geometrical shape and overall dimensions, produced mainly from solid recyclable polymer waste, presented in the form of parts that were technologically processed by crushing, mainly porous sound-absorbing structures, mainly dismantled from recyclable technical objects, mainly parts of noise insulation packages of vehicles that have completed their life cycle, and / or from technological waste and rejects the production of porous sound-absorbing materials and parts one of them, while the volume of each of the isolated fragmented fragmented sound-absorbing elements is mainly in the range of V _f = 4.2 · (10 ^-9 ... 10 ^-2 ) m ³ , and the filling density of the separate capacities of the bearing sound-transparent shells of the briquetted sound-absorbing modules ρ _f = 10 ... 655 kg / m ^3, with 30% of the total filling separate containers bearing shells comprise separate sound transmission crushed fragmented sound absorbing elements made of dense, non-porous polymer structures m materials under. 17. Soundproofing sewing of a technical room according to claim 16, characterized in that the separate crushed fragmented sound-absorbing elements and their supporting sound-transparent shells are fastened into the formed monolithic structures of the isolated briquetted sound-absorbing modules using appropriate sound-transparent adhesive substances represented by hot-melt adhesive materials / adhesive fibers or adhesive adhesives hot-melt powdery adhesive substance and / or a layer of sticky adhesive adhesive substance, and / or a layer of film thermosetting adhesive substance. 18. Soundproofing sewing-up of a technical room according to claim 1, characterized in that the quarter-wave acoustic resonators R ^I and / or half-wave acoustic resonators R ^{II used are} fixed with corresponding mechanical and / or adhesive joints on the supporting elements - walls, ceiling, internal partition of the technical room, and / or walls of soundproofing front flat sheets, and / or on soundproofing front molded non-flat panels of soundproofing sewing 19. Soundproofing sewing-up of a technical room according to claim 1, characterized in that the quarter-wave acoustic resonators R ^{I used are} integrated into the structures of the load-bearing elements - walls, ceiling, internal partition of the technical room by formed blind blind holes with a bottom part and a predetermined depth, form the corresponding geometric length tubular part $${\text{l}}_{\text{rd}}{}^{\text{I}}$$

quarter wave acoustic resonator R ^I. 20. Soundproofing sewing of a technical room according to claim 1, characterized in that the geometric length of the tubular part $${\text{l}}_{\text{rd}}{}^{\text{I}}$$

quarter-wave acoustic resonators R ^I is determined by the expression:

Where $${\text{l}}_{\text{rd}}{}^{\text{I}}$$

- the geometric length in m of the tubular part of the quarter-wave acoustic resonator R ^I , designed to suppress the resonant amplitudes of sound pressure at the first (m = 1) transverse intrinsic acoustic mode f _d , which is formed along the thickness (width) d of the air gap formed by the surface of the sound-reflecting enclosing panel of the carrier element - wall, ceiling, internal partition of the technical room and the corresponding opposed surface of the soundproofing face plate or flat whom section of the soundproofing front non-planar panel of soundproofing sewing;
d is the thickness (width) in m of the air gap formed by the surface of the sound-reflecting enclosing panel of the bearing element - the wall, ceiling, internal partition of the technical room and the corresponding opposed surface of the sound-insulating front flat-panel panel or flat section of the sound-insulating front molded non-flat sound-insulating panel;
S _T is the flow area in m ^{2 of the} tubular part of the quarter-wave acoustic resonator R ^I ;
π = 3.14. 21. Soundproofing sewn technical premises according to claim 1, characterized in that the geometric length of the tubular part $${\text{l}}_{\text{rd}}{}^{\text{II}}$$

half wave acoustic resonator R ^II is determined by the expression:

Where $${\text{l}}_{\text{rd}}{}^{\text{II}}$$

- the geometric length in m of the tubular part of the half-wave acoustic resonator R ^II , designed to suppress the resonant amplitudes of sound pressure at the first (m = 1) transverse intrinsic acoustic mode f _d , which is formed along the thickness (width) d of the air gap formed by the surface of the sound-reflecting enclosing panel of the carrier element - wall, ceiling, internal partition of the technical room and the corresponding opposed surface of the sound-insulating face flat panel or flat the front portion of the sound insulating panel nonplanar shaped soundproofing linings;
d is the thickness (width) in m of the air gap formed by the surface of the sound-reflecting enclosing panel of the bearing element - the wall, ceiling, internal partition of the technical room and the corresponding opposed surface of the sound-insulating face flat panel or a flat section of the sound-insulating front molded non-flat soundproofing panel;
S _T is the flow area in m ^{2 of the} tubular part of the half-wave acoustic resonator R ^II ;
π = 3.14. 22. Soundproofing sewn technical premises according to claim 1, characterized in that the geometric lengths of the tubular parts $${\text{l}}_{\text{rL}}{}^{\text{I}}$$

, $${\text{l}}_{\text{rB}}{}^{\text{I}}$$

, $${\text{l}}_{\text{rH}}{}^{\text{I}}$$

used quarter-wave acoustic resonators R ^{I are} determined by the expressions:

and the geometric lengths of the tubular parts $${\text{l}}_{\text{rL}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rB}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rH}}{}^{\text{II}}$$

used half-wave acoustic resonators R ^{II are} determined by the expressions:

Where $${\text{l}}_{\text{rL}}{}^{\text{I}}$$

, $${\text{l}}_{\text{rB}}{}^{\text{I}}$$

, $${\text{l}}_{\text{rH}}{}^{\text{I}}$$

- the geometric lengths in m of the tubular parts of the quarter-wave acoustic resonators R ^I , designed to suppress the resonant amplitudes of sound pressures of the first (m = 1) longitudinal intrinsic acoustic modes f _L , f _B , f _H , formed along the overall lengths of the ribs L, B and H, determined by the overall dimensions L, B, H of the three-dimensional air cavities of the technical room, formed by the gap, at a distance d, the location of the soundproofing face flat sheets, and / or soundproofing front molded non-flat panels insulating linings relative to oppositely disposed surfaces of the respective sound reflecting panels enclosing - walls, ceiling, interior partition technical room;
$${\text{l}}_{\text{rL}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rB}}{}^{\text{II}}$$

, $${\text{l}}_{\text{rH}}{}^{\text{II}}$$

- the geometric lengths in m of the tubular parts of the half-wave acoustic resonators R ^II , designed to suppress the resonant amplitudes of the sound pressures of the first (m = 1) longitudinal intrinsic acoustic modes f _L , f _B , f _H , formed along the overall lengths of the ribs L, B and H, determined by the overall dimensions L, B, H of the three-dimensional air cavities of the technical room, formed by the gap at a distance d from the location of the soundproofing face plate panels and / or soundproofing face molded non-planar soundproof panels ruyuschey patching on appropriate oppositely disposed surfaces enclosing sound reflecting panels - the walls, ceiling, interior partition technical room;
L, B, N - overall lengths of the ribs in m, determined by the overall dimensions of the three-dimensional air cavity of the technical room along the length L, width B and height H;
S _T is the flow area in m ^{2 of the} tubular part of the half-wave acoustic resonator R ^II ;
π = 3.14. 23. Soundproofing sewing of the technical room according to claim 22, characterized in that the tubular and throat parts of the quarter-wave acoustic resonators R ^I and / or half-wave acoustic resonators R ^II contain corresponding damping elements represented by perforation holes and / or porous air-blown plugs, and / or an air-blown layer of fabric material and / or non-woven fabric, and / or a microperforated polymer film, and / or a microperforated metal foil 24. Soundproofing sewing of the technical room according to claim 19, characterized in that the quarter-wave acoustic resonators R ^{I used are} integrated into the structural structures of the supporting elements - walls, ceiling, internal partition of the technical room and are presented as embedded dead-end tubular elements of a dead end type, the bottom of which placed inside the structure of the structures of the indicated load-bearing elements - walls, ceiling, internal partition of the technical room, and the open neck is located on the sides an air cavity formed shameful disposed a reflecting panels enclosing the carrier elements - walls, ceiling and internal partitions and technical room respective oppositely arranged facial ploskolistovymi soundproofing and / or sound-insulating non-planar shaped panels of sound absorbing linings. 25. Soundproofing sewing of a technical room according to claim 1, characterized in that the R ^II half-wave acoustic resonators used are integrated into the structural structures of the load-bearing elements - walls, ceiling, internal partition of the technical room and are presented as embedded U-shaped hollow tubular elements corresponding to the geometric tubular lengths $${\text{l}}_{\text{rd}}{}^{\text{II}}$$

half-wave acoustic resonators R ^II .

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