RU2684942C1 - Low-noise technical room - Google Patents

Abstract

FIELD: acoustics.SUBSTANCE: invention relates to the field of the environment acoustic safety ensuring technical means, used for the noise emissions suppression (reduction) produced by industrial, technological and engineering equipment, presented, in particular, by the pumping, compressor stations, power plants (internal combustion engines, diesel generator sets), ventilation and air conditioning systems, electrical machines (electric motors, electrical transformers) mounted inside the noise-emitting (noise-active) technical premises (construction buildings). Technical device is presented in the form of low-noise technical room, equipped mounted with air gaps between the opposite end faces and relative to the opposed mounting surfaces of wall and ceiling enclosing structures of the technical room, separated by the all-molded combined sound-absorbing panels, made up of a porous air-blown crushed sound-absorbing structure of the substance, lined with the material sound-transparent layer and integrated therein cavernous frequency tuned noise-suppressing structural elements, presented in the form of low-frequency half-wave acoustic resonators R. Half-wave acoustic resonators Rare formed by the bearing inner air-blowing film elastic sound-transparent shell, made in the form of the cavernous sound-transparent element curved hollow U-shaped tubular profile, its tubular part certain dimensions, with open neck parts, which may be overlapped by the material protective lining damping air-blowing layer. Low-noise technical room technical device is endowed with the broad-band by the frequency composition sound absorption effect, with the sound pressure reducing pronounced selective low-frequency effect on released in the sound spectrum sound radiation fworking dominant functional frequencies discrete values, of mounted therein noise-generating technical objects. Also, the frequency-tuned sound absorption effect of the used half-wave acoustic resonators Rcan be extended to the resonant sound radiation suppression, excited by the technical room internal three-dimensional cavity air volume mass-elastic body own acoustic modes, characterized by the sound vibrations frequencies fand sound wavelengths λ.EFFECT: invention allows to increase the environment acoustic safety by the used technical device sound-absorbing characteristics improvement.18 cl, 44 dwg

Description

The invention relates to the field of technical means of ensuring acoustic safety of the environment due to the suppression (reduction) of noise emissions produced by production and technological and engineering equipment, represented, in particular, pumping, compressor stations, power plants (internal combustion engines, diesel generator installations), ventilation and air conditioning systems, electrical machines (electric motors, electrical transformers), inside the noise-generating (noise-active) technical premises (building buildings). It can also be used to improve acoustic comfort in adjacent residential, industrial, and public premises of buildings and structures that are integrated (adjacent, closely spaced) with the specified noise-generating technical premises (construction buildings).

It is known that to protect the environment from intense acoustic pollution (high noise levels) produced by various types of noise-generating technical objects, various types of sound-insulating (noise-insulating) enclosures of noisy technical premises are widely used (screen partitions, housings, panel linings of carrier and / or enclosure structures) equipped with additional layers of viscoelastic vibration-damping and / or porous air mounted on their surfaces oproduvaemyh sound-absorbing and / or dense vozduhoneproduvaemyh soundproofing materials, and / or various combinations of all matching addition may include carriers, reinforcing, sound transmission, protective, adhesive, decorative material layers or corresponding structural elements. Also, for the same purpose can be used isolated single or interlocked, presented in the form of aggregated modular batteries, various types of acoustic resonators - quarter-wave (R ^I ), half-wave (R ^II ), Helmholtz (R ^III ). Volumetric expansion chambers connected to the sound transmitting (waveguide) channels (openings) of the corresponding type can also be used, blocking (weakening) the transmission of acoustic energy due to the sound reflecting air (gas filled) “acoustic plugs” formed in them, which are characterized by abrupt changes (differences) wave acoustic impedances. In the overwhelming majority of cases, various combined combinations of the above types of noise suppressing (noise reducing) methods and technical devices for their implementation are used, and their specific choice is predetermined by both technical and economic factors. The use of such a wide variety of noise-attenuating techniques (methods), technical devices and substances (materials) for their implementation allows, in one way or another, to provide an acoustically safe noise-comfortable environment for people and animals. In particular, various types of hybrid noise reduction structures are widely used, using the combined realization of the physical processes of sound absorption and sound insulation, when the total noise reduction effect of a used technical device can be based on both the effects of reflection of sound energy and the combined combination of sound absorption and sound reflection. This type of technical noise-suppressing devices may not include porous air-conditioned sound-absorbing or sound-proof sound-proofing structures of materials, and the resulting sound attenuation effect can be realized exclusively by the operation of individual frequency-tuned acoustic resonator elements (quarter-wave R ^I , half-wave R ^II , Helmholtz R ^III), including the common use of the perforated plate structures with a given disposable WHO ear gap relative rigid sound-reflecting surfaces, to form the corresponding cavity resonator devices (acoustic Helmholtz resonators R ^III). This type of cavity resonator sound-damping devices can be hollow or partially filled with a porous sound-absorbing substance.

As well-known examples of the use of technical devices for damping acoustic energy that function according to the physical principles noted above, in particular, various types of panel-cavity sound-damping (noise-reducing) structures can be mentioned:

- international application for invention WO 2009/131855 A2 (published 10.29.2009);

- international application for invention WO 2008/138840 A1 (published 11/20/2008);

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

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

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

- RF patent for invention RU 2206458 (published June 20, 2003);

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

- Japanese application for the invention of JP 2008-96826 A (published October 13, 2006);

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

- RF patent for utility model RU 61353 (published February 27, 2007);

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

The pronounced useful advantages of using the above technical devices for damping acoustic energy should include the possibility of their use, including under the influence of corrosive media, high temperatures and intense dynamic loads, due to the exclusion of the use of porous air (gas) fibrous and / or foam in their composition open-cell structures of organic or synthetic origin, characterized, as a rule, insufficiently high thermal moisture o-biological stability characteristics. In their composition, extremely dense structures of perforated metal or heat-resistant polymeric materials are used, with the possible inclusion of heat-resistant porous fibrous (basalt, glass, metal), and / or foamed open-cell metallic and / or ceramic materials. At the same time, the narrow technical characteristics of this type of noise-suppressing devices should include their narrow working frequency sound range of effective functioning, high sensitivity to frequency detuning and loss of sound-damping effect when the physical parameters of the sound wave propagation medium change, and the sound attenuation effect is not high enough required wide frequency range, high cost, poor overall performance and increased aterialoemkost. At the present level of development of technology, these negative factors may limit their wide distribution in the effective solution of actual practical problems of suppressing the energy of acoustic radiation produced by various noise-generating technical objects.

Accordingly, panel-cavity noise-reducing structures are known and widely distributed, the cavities of which are completely or partially filled with porous air-breathing sound-absorbing material of fibrous and / or open-cell foam type (of organic, mineral, synthetic origin), characterized by higher sound-absorbing (noise reducing) characteristics, however sufficiently effective only in a limited range of medium and high frequencies of the sound range it (over 500 Hz). In this type of known noise-reducing structures, the front (front) wall of the acoustic panel is usually perforated and is characterized by a rather high value of the perforation coefficient exceeding the value of 0.2. This gives it the properties of acceptable sound transparency and provides, in fact, unhindered (with an insignificant, not exceeding 10% effect of sound reflection) the passage of sound waves into the cavity filled with porous sound-absorbing material. Through, mostly round holes or narrow slotted notches with bends, is the most common type of perforation of this type of front wall of the acoustic panel. As examples of this type of known noise reduction technical devices, the following should be noted:

- French patent for invention FR 2899919 (published 10.19.2007);

- French patent for invention FR 2899992 (published 10.19.2007);

- US patent for invention US 3991848 (published 09/16/1974);

- US patent for the invention of US 5422466 (published 11.03.1994);

- Japan patent for the invention of JP 11104898 (published April 20, 1999);

- international application for invention WO 2007/017317 (published February 15, 2007);

- Japan patent for the invention of JP 62165043 (published 07.21.1987);

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

- European patent for invention EP 1477302 A1 (published 11/17/2004);

- Japanese application for the invention JP 2000034937 (published 02.02.2000);

- German application for invention DE 202004018241 (published 11/24/2004);

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

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

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

- international application for invention WO 2004/013427 A1 (published February 12, 2004);

- RF patent for invention RU 2042547 (published 08/27/1995).

The above-mentioned known noise reduction technical devices, along with achievable satisfactory acoustic characteristics that are realized in the mid and high frequencies of the sound range, are nevertheless characterized by a certain loss of potential noise-attenuating properties due to the formation of an abrupt change (difference) in the acoustic wave resistance on the flat demarcation boundary ) elastic layered media propagation of sound waves in the considered zone of the air environment, adjacent to a solid flat-sheet layered structure, with different values of acoustic wave impedances, in the composition of adjacent air medium, both in the form of a solid flat wall of a perforated face panel, and a flat sheet structure of a porous sound-absorbing substance. This causes not only the corresponding potential loss of the sound-absorbing effect, but the perforation holes contained, distributed over the entire solid surface of the flat wall, also cause a certain loss of sound-insulating (in particular, sound-reflecting) properties of the said multilayer structure of the wall partition as a whole. Also, there is a relative high cost of polymer porous sound-absorbing substances used in this type of construction, produced mainly from non-renewable expensive hydrocarbon raw materials (oil, gas). They also (polymer materials) are characterized by quite complex, time-consuming and “environmentally dirty” technologies such as their production, and the final utilization of various types of heterogeneous construction materials used in parts and assemblies of the specified type of noise-reducing technical devices after they complete their life cycle.

To increase the noise-reducing properties of a similar type of construction, by providing a smoother (not abrupt jump-like) matching of acoustic wave impedances, on the sound wave propagation paths, in the boundary zones of the elastic air separation environment, the sound waves propagation, including adjacent boundary surfaces of the technical device panel with external and internal cavity zones of contiguity of the air environment, the contours of the outer shell (wall) of persons howl acoustical panel attached gofrovidnaya non-planar geometric shape (wedge-shaped, wavy, echelon), as is particularly shown in the following prior art devices:

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

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

- the application of Germany for the invention DE 4237513 (published 07.11.1992);

- US application for invention US 2003207086 (published 11.06.2003);

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

- RF patent for invention RU 2161825 (published Jan. 10, 2001);

- Australian application for invention AU 2007100636 (published 08.16.2007).

The above-mentioned noise reduction constructions of technical devices are characterized, first of all, by a significant complication of their technological performance and relatively high cost, while the sound insulation capacity is not sufficiently high (due to the presence of prominent “soundproofing dips” in separate sound frequency ranges of the sound energy suppression characteristic due to the formation of its own "Parasitic" cavity air acoustic resonances), as well as forced accompanying perceptible reduction (“ousting”) by the applied noise reduction structures of the useful working volume of the technical room, complicating the processes of their maintenance (cleaning, washing).

Another well-known technical direction for improving the design of technical devices for attenuating the spread of negative (“parasitic”) sound energy generated by vibro-noise technical objects mounted in technical rooms, associated with an increase in the fraction of absorbed sound energy, is the execution of a technical device directly perceiving falling sound waves, perforation holes with given technological tolerances geometrically specific shapes and dimensions. This type of noise-reducing technical devices are known from the following patent documents:

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

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

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

- European patent for invention EP 1950357 A1 (published 30.07.2000);

- US application for the invention of US 2007/0272472 A1 (published 11/29/2007);

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

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

These noise-reducing technical devices can be characterized by improved performance and decorative (improved exterior design) properties. However, their noise-reducing properties are, nevertheless, not high enough due to the limited potential used to improve the efficiency of a structural modification of a technical device based solely on the rationalization of geometric shapes and overall dimensions of perforation holes. Also, their production is associated with the need to use more complex and expensive high-tech equipment, ensuring compliance with narrow manufacturing tolerances for manufacturing.

Known noise-reducing technical devices, made in the form of composite node (modular) soundproofing fences, the structural elements of which combine combine several techniques (realizable several physical effects), borrowed from the above-considered groups of known technical devices, allowing in varying degrees (in This or that frequency range, with this or that achieved noise-suppressing effect) purposefully improve their acoustic properties. This type of hybrid hybrid noise reduction technical devices are described in the following patent documents:

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

- French patent for invention FR 2929749 (published 09/10/2009);

- UK patent for invention GB 822954 (published 11/04/1959);

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

- the application of Japan for the invention of JP 2002175083 (published June 21, 2002).

The disadvantages of the above-mentioned noise-reducing technical devices are their higher structural complexity and technological labor-intensiveness of production, when, in some cases, they are not sufficiently high (specified by the requirements of the design specification) environmental and cost indicators. In particular, this applies to the potentials realized for further improvement of their noise-attenuating characteristics in the low-frequency range of sound frequencies, which is the most intense and most relevant in solving typical problems of noise reduction of machines and equipment.

Known technical solution for the patent of the Russian Federation for the invention №2465390, published 01.20.2011, in. which describes the design of a soundproof fence, made in the form of an autonomous noise reduction screen, containing supporting elements such as transverse racks and longitudinal profiles, as well as a corresponding type of noise-absorbing element located in the cavity with a given air gap between the rear acoustic panel and perforated through holes of the front acoustic translucent the panel. Moreover, said noise-absorbing element contains a perforated or mesh type sheet carrier, fixed with mechanical fasteners to horizontal profiles and / or the base of a noise-reducing screen, lined at least from one of its sides, with separate sound-absorbing panels representing a set of crushed porous fiber fragments or foamed open-cell sound-absorbing materials, which are distributed in a certain way and fixedly mounted on the surface STI base substrate to form a corresponding clearances between them. At least on the placement side of the separate sound-absorbing panels, the surface of the noise-absorbing element is lined with a layer of sound-transparent gas-proof film or fabric. The disadvantage of the analyzed known technical solution is the limited possibility of its effective use, carried out not inside the closed limited volumes of technical premises, but mainly in the open spaces of the environment to ensure the protection of residential areas of settlements from the impacting negative acoustic radiation propagating from noise-generating technical objects - vehicles and industrial equipment installed around road and railways, airfields, open sections of metro lines, test sites, noise-generating construction and production sites, or any other spatially distributed sources of increased noise radiation, producing intense acoustic pollution of the environment. This causes, in particular, the need to use in the composition of this type of sound insulation fencing additional bearing and supporting elements (autonomous foundation, supporting base, transverse racks and longitudinal profiles), which significantly complicates the problem of using the specified noise reduction structure, leads to an increase in its weight-dimensional parameters and cost. At the same time, the use of a carrier base in the form of a flat-sheet geometric shape, fixed in a vertical position on horizontal profiles or the base, complicates the technological process of subsequent placement of separate sound-absorbing panels, and also complicates the construction of sound-insulating complex spatial geometric shape. The limited choice of overall dimensions and geometrical forms, physico-mechanical parameters, if necessary to maintain the specified values of air gaps between individual samples of crushed fragments of separate sound-absorbing panels, predetermines the insufficiently effective absorption of sound energy realized in the conditions of a diffuse sound field of closed rooms and is noted in the narrowed working frequency range characteristic only of spatially distributed local sound energy emitters and in a free sound field of open spaces such as moving in the open spaces of motor vehicles flows (passenger cars, trucks, buses) or rail transport means. The use of this type of soundproofing construction, performed as an autonomous noise-reducing screen (several composite structures, for subsequent placement inside the technical room, close to its enclosing wall and ceiling structures), will significantly reduce (clutter) its useful working space, worsen the process of technological service mounted in it production and technological and engineering equipment.

Also known and used in engineering (architectural acoustics) is the technique of partially eliminating (partially weakening) the development of the physical process of forming pronounced half-wave acoustic resonances of elastic bodies of air volumes represented by internal three-dimensional air spaces of rooms that degrade their acoustic qualities, is the direct application of the original in design technical room, presented in the form of an appropriate measuring acoustics ches instrumentation made in the form of a measuring reverberation chamber, as described in particular in [1, 2, 3]:

[1] - ASTM with 423-02a. Standart Test Method for Sound Absorption and Sound Absorption Coefficients by Reverberation Room Method. American Society for Testing and Materials International. - West Conshohocken. - 2002. - 11 p .;

[2] - GOST 31274-2004 (ISO 3741: 199) “The noise of machines. Determination of sound power levels by sound pressure. Exact methods for reverberation chambers. ”

[3] - GOST 31704-2011 (ISO 354: 2003) “Sound-absorbing materials. A method for measuring sound absorption in a reverberation chamber ”.

The overall dimensions and geometric forms of this type of measuring reverberation chamber, the ratio of its composite dimensions and the realized physical characteristics of its wall structures make it possible to a certain extent eliminate (partially weaken) the development of the physical process of forming the in-phase resonant addition of half-length sound waves (λ / 2) and multiples of them to harmonics excited inside the air cavity of the measuring reverberation chamber placed in it by the studied noise-generating source AUC (or calibrated sound emitter), thereby preventing the formation of pronounced resonating natural acoustic modes of the air volume of the space measuring the reverberation chamber. This allows the part of the resulting diffuse (reverberation) acoustic field of the internal air cavity of this type of technical room to partially exclude (weaken) the development of the physical process of forming a pronounced uneven spatial density of the distribution of sound energy intensity localized in the closed air cavity of the measuring reverberation chamber. This type of measuring reverberation chambers are of limited use and are mainly used in the field of acoustic measurements of sound power of noise-generating technical objects, as well as evaluation of the sound-absorbing characteristics of samples of acoustic materials. They are also used for studies of the sound-absorbing characteristics of full-scale structures of parts, assemblies and systems of machines (their prototypes) performed in a diffuse (reverberation) sound field. In the regulatory requirements given in [1, 2, 3], instructions are given on the relevant design principles for measuring reverberation chambers, which impose requirements on the volume (overall dimensions) and the geometric shape of its air cavity, the physical characteristics of the wall structures used, which exclude the negative development of physical formation processes of resonantly expressed spatial zones of unequal density distribution of sound energy intensity, as well as eliminating undesirable processes and sound absorption, proizvodimomgo enclosing surfaces and wall constructions doorway measuring the reverberation room. However, the alternative use of this type of original constructions of measuring reverberation chambers, as possible typical variant versions of low-noise technical premises, with eliminated half-wave acoustic resonances, significantly complicates and increases the cost of construction of typical technical premises intended for subsequent installation of noise-generating technical objects (SGD) in their design, construction and subsequent operation. An obvious disadvantage of this type of technical room, made in the form of measuring reverberation chambers, is also unsatisfactory (incomplete and inconvenient in operation) use of their useful working space, due to the non-parallel opposite surfaces of wall fences, floor and ceiling (ceiling) implemented in them. Moreover, in some cases, to ensure the required diffusion of the sound field (realizable uniform spatial density of the sound pressure distribution throughout the measuring reverberation chamber volume), the use of the free working space of the room is difficult for the measuring reflector cameras used in the air cavity of the additional reflector elements mounted in it, additionally equalizing the spatial density of the intensity distribution of sound energy and in measuring the air cavity reverberation chamber due to the additional clutter undesirable its useful working space.

Known technical solution according to the patent of the Russian Federation for invention No. 2579104, published 12/20/2015, taken as a PROTOTYPE, in which a technical room is presented, equipped with a soundproofing lining made in the form of a soundproofing face plate and / or soundproofing molded non-plane panel, with an air gap mounted the surface of the opposedly located bearing wall (ceiling) structure of the technical room, with the formation of the corresponding closed air cavities. At the same time, quarter-wave acoustic resonators R ^I and / or half-wave acoustic resonators R ^II , frequency-tuned and temperature-adapted for suppression of air acoustic arising in the air cavities formed, are appropriately fixed to the specified soundproofing front panels and / or supporting wall (ceiling) structures of the technical room. resonances formed on their own transverse, longitudinal, and elevated acoustic modes. Also, an isolated briquetted sound-absorbing modules composed of crushed porous sound-absorbing substances can perform an additional function of partial efficiency of the suppression of the amplitude values of the intrinsic acoustic resonances in the air cavities formed between the oppositely located walls of the soundproofing front panel of the soundproofing skin and the carrier wall appropriately placed in specified spatial areas in stuffy cavities.

The disadvantage of the known technical solutions presented in the prototype, is the complexity of its technological performance, as well as the high cost, complexity of installation and maintenance, due primarily to the need for separate installation of various types of noise suppressing (sound-absorbing) structural elements R ^I and / or half-wave acoustic resonators R ^II ), and / or separate briquetted sound-absorbing modules using the appropriate their fasteners and separate faceplates. At the same time, the use of the front panel in the composition of the considered technical solution causes a corresponding abrupt change (difference) of the acoustic wave resistance on the sound wave propagation path. In addition, one should point out the insufficient (weak) use of the mechanism (physical effect) of the edge diffraction absorption of sound energy due to the small total perimeter of the edge zones and the small number of briquetted sound-absorbing modules used, and / or the absence of perforation through holes in through channels), potentially capable of further enhancing the effect of diffraction absorption of the propagation energy of sound waves.

The technical device “Low noise technical room” declared as an invention is aimed at eliminating identified and analyzed shortcomings of analogues and prototypes in terms of simplicity of its technical implementation, manufacturability, environmental friendliness, cost and operating efficiency, while ensuring the effect of extending the frequency range to reduce the level of sound radiation produced as ShSTO established in the technical room, and aimed at the exclusion (prevention) of the implementation of zvitiya physical processes resonant interaction and appropriate amplification acoustic emission levels and the occurrence of the physical process beats interacting acoustic signals (sound waves) with close values of frequency of acoustic oscillations f _ms and f _mA, manufactured located therein SHGTO (several SHGTO) and carries them potentially possible dynamic excitation of resonant acoustic oscillations of a mass-elastic body of air volume contained in an internal three-dimensional air cavity chenical premises. The need to prevent the development of the physical process of the beating of interacting acoustic signals (sound waves) with similar frequencies of sound vibrations f _ms and f _mA is caused by the expediency of eliminating the resulting pulsating noise signal with a rise and fall frequency of its levels equal to the difference between the values of interacting sound vibrations f _ms and f _mA . For the actual low-frequency acoustic range of radiation considered in the application materials (see Fig. 1-4), not exceeding 500 Hz, the resulting acoustic signal of these physical interactions, manifested as beats of acoustic signals, is perceived by the subjective perceptions of human hearing as a sharp unpleasant irritating effects that worsen the psycho-physiological state of a person and is a negative factor in ensuring the acoustic safety of the environment.

On the relevance and possible ways (methods, devices) of solving the problems of reducing low-frequency sound radiation on the dominant values of individual discrete frequency components f _ms , emitted in the broadband spectra of sound pressure of various types of SHGTO operated (mounted) in technical rooms, in particular, piston ICE, mechanical gearboxes, rotors, fan units, electric generators, electrical transformers, traction machines, smoke exhausters (axial, centrifugal type), pumps compressors (reciprocating, centrifugal) - indicated in the known information sources [4 ... 10] and confirmed by the results of experimental investigations of the authors set forth in FIG. 1 ... 4.

Springer-Verlag Berlin Heidelberg, 2007 - 546 p.;[4] - Helmut V. Fuchs. Schallabsorber und

Springer-Verlag Berlin Heidelberg, 2007 - 546 p .;

[5] - N.I. Ivanov. Engineering acoustics. The theory and practice of dealing with noise. - M .: Logos, 2010. - 424 p .;

[6] - V.B. Stupid Reducing noise from power equipment. - M .: Publishing house MEI, 2005. - 232 p .;

[7] - D.F. Lazaroiu, N.L. Bikir The noise of electrical machines and transformers. Translated from room., - M .: "Energy", 1973. - 271 p .;

[8] - Fighting industrial noise. Directory. Ed. E.Y. Yudina, Mashinostroenie, M., 1985, 400 pp .;

[9] - Handbook for the control of industrial noise. Translation from English L.B. Scriabina and N.I. Shabanova, M., Mechanical Engineering, 1979, 447 pp .;

[10] - Technical Acoustics Reference. Ed. M. Hekla and Kh.A. Muller L., Shipbuilding, 1980, 440 pp .;

[11] - G.L. Osipov, V.N. Bobylev, L.A. Borisov et al. Sound insulation and sound absorption. Ed. G.L. Osipova, V.N. Bobylev. - M .: LLC AST Publishing House: Astrel Publishing LLC, 2004. - 450 p.

Taking into account the functioning constant (steady-state) speed and load modes of operation of the above-used SHGTOs, the dominant discrete low-frequency components f _ms emitted in the broadband spectral sound pressure are also constant (with constant sound frequency values f _ms ), as follows from the given FIG. . 1, 2, 3, 4. This applies, in particular, to the ShGTO presented by a power electric transformer, with prominent frequency harmonics f _1s , f _2s , f _3s equal to 100, 200 and 300 Hz, multiples of the constant value of the industrial frequency of the AC network f _c = 50 Hz (see Fig. 1 and 2). Similarly, this may refer to constant steady-state values of nominal rotational frequencies n _s (f _ms ) of the shafts of piston machines (internal combustion engines, compressors, pumps), electric generators, mechanical or electric fans, mechanical gearboxes, as well as periodic unbalanced unbalanced masses unbalanced forces and moments of crank mechanisms of piston machines (see, in particular, Fig. 3 and Fig. 4). Sources (dynamic pathogens) of intense sound radiation on these evolving dominant discrete components f _ms , with the corresponding acoustic fields being formed, are, in particular, gas (air) pulsations in the processes of air suction into the cylinders of piston machines, periodic dynamic movements of air by blades (blades) fan impellers, dynamic imbalances of rotating shafts, unbalanced forces and unbalanced moments of reciprocating moving masses of pores nevyh machines (connecting rod-piston masses of the crank mechanism, the crank shaft), alternating dynamic loads working processes intermating teeth in the toothing of gear units, dynamic alternating electromagnetic and magnetostrictive forces are different types of electrical machines and installations. The numerical values of the frequencies of sound vibrations of the considered dominant discrete components f _{ms are} known in the form of a specific result (value) determined experimentally, performed using appropriate recording and analyzing vibroacoustic equipment (as illustrated by examples in Figs. 1, 2, 3). , 4), or known in the form of a result (value) determined by calculation, taking into account the known initial data - the known given constant steady-state speed th (load) of the operating mode n _s machine or system and the known design characteristics (technical parameters), the constituent elements under consideration SHGTO (e.g., the rotational speed of the crankshaft, number of cylinders and taktnosti workflow piston engine rotational speed and the number of vanes (blades) of the impeller the fan, the number of teeth of the mating gear teeth of the gearing at a known frequency of rotation of the gear wheels, frequency of the alternating current network), as determined, including from known above information sources [4 ... 10].

The technical result of the claimed device in the form of the invention is to provide (improve) the acoustic safety of the environment by improving the sound-absorbing (noise-reducing) characteristics of the used technical device, implemented mainly in the current low-frequency sound range, with the concomitant reduction of the broad-band frequency composition of the sound radiation generated by SHGTO . The claimed technical device is represented by a low-noise technical room, equipped with technical means of effective suppression, mounted in this technical room, mainly, low-frequency acoustic radiation generated by ShGTO (Fig. 5 ... 7). These technical means (components of a technical device) are intended, first of all, to suppress sound radiation produced by the ShGTO, including the elimination (prevention) of the development of physical processes of low-frequency resonant interaction and the subsequent resulting amplification of sound pressure levels, as well as to prevent the occurrence of physical processes of the beating of interacting acoustic signals (sound waves), which have rather close values of the levels of sound x pressures (ultrasonic sounding) and frequencies of sound oscillations f _ms and f _mA , produced by SHGTO (f _ms ) located in it and possible excitation of resonant dynamic reactions carried out by it - responses, manifested in the form of acoustic oscillations of a mass-elastic body of air volume enclosed in an internal three-dimensional air cavity technical room (f _mA ). The technical result is achieved due to the appropriate application (installation with predetermined air gaps) on the wall and ceiling overlays of the technical room of the corresponding structural and technological versions of isolated all-molded combined sound-absorbing panels made of solid substances characterized by a porous air-blown crushed sound-absorbing structure in which they are placed (integrated) frequency-tuned cavity noise-suppressing structural elements s, presented in the form of a half-wave acoustic resonators R ^II _ms (see. FIGS. 8, 9, 10a, 10b, 11a, 11b, 11c, 12a, 12b, 12c, 13a, 13b, 14a, 14b, 15a, 15b, 16a, 16b, 17a, 17b, 18a, 18b, 19a, 19b, 20, 21, 22, 23, 24, 25, 26).

The effective reduction of the level of sound energy emitted by the ShGTO, achieved, in this case, is realized in the extended frequency range of the sound spectrum, which includes both low-frequency and medium-and high-frequency sound radiation. This is due to the corresponding design and technological combined combining and parallel operation of composite technical elements designed for selective frequency-tuned suppression of low-frequency sound energy (energy of propagated low-frequency sound waves) on the prominent (dominant) frequency spectrums of noise weakly damped low-frequency acoustic resonances, as well as providing broadband dissipative absorption used porous crushed in zduhoproduvaemym sound absorbing material, medium and high frequency sound energy. In this case, the physical effect is based on the realized selective frequency-tuned sound-suppressing processes of a functioning acoustic oscillatory system, excited by sound waves incident on it, which selectively (selectively) absorb acoustic energy (converts it into thermal energy) emitted at sound frequencies close to (coincident) to the natural (resonant) oscillation frequency f ^II _R used in the composition of a separate, whole-shaped, combined sound-absorbing panel of a half-wave a bush resonator R ^II . At the same time, in parallel, a broadband (medium and high frequency) sound absorption is carried out, produced directly by the substance of the crushed porous air-blown sound-absorbing structure (see Fig. 25). At the same time, additional sound-absorbing surface zones formed by the free surfaces of the faces of each of the separate crushed fragmented sound-absorbing elements are effectively included in the physical process of absorption of sound energy. There is also the occurrence of additional mechanisms for intensifying the physical process of absorption of sound energy caused by realizable diffraction dissipative losses arising in the edge edge zones and rib sections of isolated crushed fragmented sound-absorbing elements, when sound waves travel along and bend around them in formed, randomly distributed, interconnecting wind waves, which are formed and bend around their sound waves along formed, randomly distributed, winding waves, and bending around them. channels formed by loose adjoining and / or adhesive mating contacting edges and edges of detached crushed fragmented sound-absorbing elements, which occur along with the typical physical processes of sound absorption, carried out directly by the porous structures of sound-absorbing substances of each of the detached fragmented fragmented elements. The hollow volumetric U-shaped profile of the tubular cavities of the half-wave acoustic resonators R ^II , formed in the structures of the isolated all-molded combined sound-absorbing panels, are limited (formed) by the sound-transparent layers of the exposed glass elastic shells, which contribute to the formation of the anisotropic acoustic structure of the separate glass-shaped glass bands sound absorption en Energy (see Fig. 11a, 11b, 11b, 12a, 12b, 12b, 13a, 13b, 14a, 15a, 15b, 16a, 16b, 17a, 17b, 18a, 18b, 19a, 19b, 20, 21, 22, 22, 23, 24, 25, 26, 27). Also, additional edge diffraction dissipative absorption of sound energy also occurs in the processes of bending around the perimetric zones of the open throat parts of the half-wave acoustic resonators R ^II (as shown in Fig. 27, 30) and free end faces of separate, fully-formed combined sound-absorbing panels with narrow gaps shameful placement relative to each other (see diagrams in figs 6, 7, 8, 9, 10a, 10b, 29, 31.).

The same physical phenomena (the formation of acoustic anisotropy, which enhances the dissipative absorption of sound energy), can also be facilitated by the deliberate additional introduction of crushed sound-absorbing material composed of porous air-absorbing sound-absorbing materials, represented by separate crushed fragmented porous sound-absorbing elements, corresponding to structural patterns. and dimensions of crushed fragments made of dense (Nonporous) vozduhoneproduvaemyh polymeric substances (see. Fig. 28). At the same time, their specified limited quantitative dosed composition can be observed, with the necessary volume distribution, if necessary, carried out in the formed mixture of heterogeneous (porous and non-porous) crushed fragments. The installation of separate solid-molded combined sound-absorbing panels with narrow-gap air gaps between the opposite end parts leads to the realization of dissipative diffraction absorption of sound energy by their free edge zones of the porous sound-absorbing structure, while bending free propagating sound waves, see

As a result of achieving higher resultant sound-absorbing effects, in some cases, if necessary, this allows to reduce the amount of porous sound-absorbing substance used, provided that the required magnitude of the effect of noise suppression is satisfied (determined by the technical task for development or technical specifications for manufacturing). For similar reasons, it is possible (permissible) to use cheaper and environmentally friendly starting semi-finished raw materials for the production of sound-absorbing material (hereinafter referred to as ZPM) produced from industrial-technological waste, industrial waste, or from dismantled porous sound-absorbing structures of materials contained in the technical insulation packages. objects that have completed their life cycle and are forced to be disposed of. Ultimately, this contributes to the improvement of the safety environmental characteristics of the proposed technical device (and the concomitant "healing" of the environment), realized by reducing the number of unproductively utilized sound-absorbing substances, which are subject to forced disposal, including disposal processes (for example, dismantled noise-reducing packages). included in parts and assemblies of PBXs that have completed their life cycle), which do not allow their direct energy utilization incineration, due to their release of harmful and dangerous products of combustion and / or destructive, including the ozone layer (CO ₂ emissions). This is even more relevant economic and environmental efficiency and the feasibility of the use of technical devices using recyclable waste as a raw material source, made according to the proposed technical solution (invention). Also in these cases, more economically efficient use is made of resource-saving resource-saving non-renewable hydrocarbon raw materials (oil, natural gas), in smaller quantities spent on the original (initial) production of synthetic sound-absorbing materials from them.

As a source of semi-finished raw materials used for the manufacture of fragmented crushed fragmented sound-absorbing elements, products of secondary recycled recycling of technological waste and technological defect of production of fibrous, foamed open cell ZPM and / or technological waste and scrap of various types of parts from ZPM can be used. The original semi-finished raw materials also include already manufactured parts and components (panels, upholstery, gaskets - from porous ZPM), selected from the composition of the dismantled noise insulation packages of various technical objects such as noise-sensitive means of transport (road, rail, aircraft, tractors, combines, mobile utility and road-building equipment, etc.), and / or other noise-generating units and systems of power plants (stationary internal combustion engines, stationary and mobile compressor installations, etc.), and / or used in various types of construction projects (sound-insulating fibrous or foamed open-cell cladding panels for wall linings, floor decks, elevator shafts, ventilation systems). Ultimately, this allows reducing the cost of the technical device being produced and ensures the reduction of environmental pollution by already formed waste products and accumulated unused products of the utilization of acoustic materials. Thus, it contributes to the improvement of the environmental characteristics of the device, including by reducing the number of sound-absorbing substances to be forcedly buried (for example, noise-reducing packages in ATC parts that have served their time), which do not allow their direct energy utilization by burning. For a controlled simplification of the implementation of technological operations of mechanical crushing (cutting / cutting) and their subsequent volumetric distribution with the provision of predetermined dosing according to the structural composition and weight-dimensional parameters, in some cases, as the initial semi-finished raw material used for the manufacture of separate low-noise technical sound-absorbing panels premises, can also be used produced "new" isolated crushed fragments Bathrooms sound-absorbing elements. The term "new" refers to fragmented fragmented sound-absorbing elements made from "new" (not recyclable) raw materials, for example, from a semi-finished product of flat sheet type (flat sheets or rolls of ZPM). Combined mixtures can also be used, defined in certain proportions of metered combinations of isolated crushed fragmented sound-absorbing elements, obtained from recycled recycling materials of parts and assemblies, to which a certain amount of produced "new" isolated crushed fragmented sound-absorbing elements of given geometrical shapes and dimensions are made. from the "new" source semi-finished raw materials for the production of porous ZPM (sheet, rolled). In a number of cases, this allows more flexible control over the final physical (acoustic) parameters of the sound-absorbing substance formed by the mixed combined structural mass (acoustic, weight, density, hardness, performance) by introducing a given quantitative, dosed additive “new” into the required proportions. detached crushed fragmented sound-absorbing elements characterized by narrow scatter fields of controlled acoustic parameters of pores sound absorbing substance. Thereby, technological procedures can be implemented, in one way or another, to the required extent, improving the physical (acoustic) characteristics of the structure of isolated, whole-shaped, combined sound-absorbing panels as part of the proposed low-noise technical room.

Comparison of scientific, technical and patent documents on the priority date in the main and adjacent headings of the MKI shows that the set of essential features of the claimed technical solution was not previously known, therefore, it meets the condition of patentability "novelty."

Analysis of the known technical solutions in this field of technology has shown that the claimed low-noise technical room has signs that are not present in the known technical solutions, and using them in the claimed combination of features makes it possible to obtain a new technical result, therefore, the proposed technical solution involves an inventive step compared to with the current level of technology.

The proposed technical solution is industrially applicable, because can be manufactured industrially, workable, feasible and reproducible, therefore, meets the condition of patentability "industrial applicability".

The features and advantages of the claimed invention will become clear from the presented drawings and the following detailed description of the device, where:

- in fig. 1 shows the experimental results of measurements of the sound pressure spectrum (FFT spectrum) emitted by the ShGTO 9, represented by a closed type electrical transformer substation (ETPZT) located in the technical room 1 of the basement floor of the test center building of an industrial enterprise. The measuring microphone was located outside the technical room 1 at a height of 1.2 m from the surface of its floor, at a distance of 1 m from the doorway 5 of the technical room 1 ETPZT blocked by the entrance door 6;

- in fig. 2 shows the experimental results of measurements of the spectrum of the sound pressure (1/3 octave spectrum) emitted by the ShGTO 9, presented by a PLATTHAUS 3MK 260-1 type electric transformer (Germany) located in the technical room of the 1st test center of an industrial enterprise. The measuring microphone was located inside the technical room 1 at a distance of 0.5 m from the body of the electrical transformer, at a height of 1.2 m from the floor of the floor 4 of the technical room 1;

- in fig. 3 shows the experimental results of measurements of the sound pressure spectrum (1/3 octave spectrum) emitted by ShGTO 9, presented by an Aksipal FTDA-050-3 industrial fan (Russia) mounted in the technical room 1, represented by the test room of an acoustic testing laboratory of an industrial enterprise. The measuring microphone was located inside the technical room 1 along the axis of rotation of the fan impeller at a distance of 0.25 m from the surface of its hub;

- in fig. 4 shows the experimental results of measurements of the sound pressure spectrum (1/3 octave spectrum) emitted by ShGTO 9, represented by a piston compressor produced by STAL (Sweden), mounted inside the technical room 1, represented by the refrigeration compressor station of the testing center of an industrial enterprise. The measurements were carried out inside the technical room 1, at a distance of 3 m from the wall surface of the front part of the compressor housing, at a height of 1.2 m from the floor surface 4 of the technical room 1;

- in fig. 5 shows a schematic depiction of a technical room 1, as well as basic directions and transmission paths of air and structural noise emitted by ShGTO 9, mounted in a closed (closed) technical room 1;

- in fig. 6 shows an illustrative, concretized example of a technical room 1 with ShGTO 9 installed in it, represented as a power electric transformer, mounted on enclosing wall (pos. 2) and ceiling 3 (not shown) overlaps by separate, single-shaped combined sound-absorbing panels 10, integrated into their porous structure of the half-wave acoustic resonators R ^II _ms (pos. 11) formed using the carrier inner elastic film vozduhoneproduvaemoy vukoprozrachnoy shell 20;

- in fig. 7 shows an illustrative example of a technical room 1 installed in it SHGTO 9, presented in the form of a diesel generator set, mounted on enclosing wall (pos. 2) and ceiling 3 (in Fig. Not shown) ceilings with separate joint-shaped combined sound absorbing panels 10 , with integrated into their porous structure, half-wave acoustic resonators R ^II _ms (pos. 11), formed using a carrier internal air-blowing film elastic sound-transparent band 20;

- in fig. 8 schematically depicts a fragment of a wall fencing (pos. 2) of the technical room 1 with mounted on its surface separate, single-shaped, combined sound-absorbing panels 10 installed with narrow-gap air gaps γ between their opposite end surfaces;

- in fig. 9 schematically shows a fragment of a wall fencing (pos. 2) of the technical room 1 with mounted detached, whole-molded combined sound-absorbing panels 10, installed with a remote air gap k relative to the wall surface (pos. 2);

- in fig. 10a is a schematic representation of a wall fence (ceiling) 2 of a technical room 1 with combined, without mutual overlapping, installation of separate, fully-formed combined sound-absorbing panels 10, mounted without backlash, directly on the surface of a wall overlap (pos. 2) of technical room 1, and installed with a predetermined air distance clearance k relative to the opposite surface of the wall fence (floor), pos. 2;

- in fig. 10b schematically shows a wall fence (overlap) 2 of a technical room 1 with combined, overlapping, and assembly of separate all-shaped combined sound-absorbing panels 10 mounted without backlash, directly on the surface of a wall overlap (pos. 2) of technical room 1, and installed with a given air distance clearance k relative to the opposite surface of the wall fence (floor), pos. 2, while the lining of the isolated, whole-shaped, combined sound-absorbing panels 10 is additionally overlapped with a sound-proof protective and decorative perforated panel 25;

- in fig. 11a shows an example of a possible structurally-technological execution of technical means of securing in a horizontal position the isolated all-molded combined sound-absorbing panels 10 through the use of appropriate suspension units mounted on the horizontal surface of the ceiling 3 of the technical room 1, made in the form of the appropriate type of remote mechanical fasteners 12;

- in fig. 11b shows an example of a possible structural and technological execution of technical means of securing in a horizontal position the isolated all-molded combined sound-absorbing panels 10 through the use of appropriate suspension units mounted on the horizontal surface of the ceiling 3 of the technical room 1, made in the form of the appropriate type of suspension cable elements 13 connected to an external carrier sound-transparent shell 19;

- in fig. 11b presents an example of a possible structural and technological execution of technical means of securing in a horizontal position the isolated all-molded combined sound-absorbing panels 10 through the use of appropriate suspension units mounted on the horizontal surface of the ceiling 3 of the technical room 1, made in the form of a corresponding type of suspension cable elements 13 connected to a reinforcement reinforcement a sound-transparent element 24 of a detached whole-molded combination oh sound-absorbing panel 10;

- in fig. 12a shows an example of a possible structural and technological implementation of technical means of securing in an upright position separate semifinished composite sound-absorbing panels 10 by using the appropriate type of mounting studs 14, passing through the structure of a continuous supporting support base 22;

- in fig. 12b shows an example of a possible structural and technological execution of technical means of securing in an upright position separate semifinished combined sound-absorbing panels 10 by using an appropriate type of mounting frame 15 that holds the detached whole-shaped combined sound-absorbing panel 10 in its upper and lower parts;

- in fig. 12B presents an example of a possible structural and technological execution of technical means of securing in an upright position separate septum-shaped combined sound-absorbing panels 10 by using the appropriate type of mounting resilient (vibration-insulating) elements 16 integrated into the structure of an external thin-walled acoustic-transparent shell 19;

- in fig. 13a presents an example of a possible structural and technological execution of technical means of securing in a vertical position separate seal-shaped combined sound-absorbing panels 10 by using the appropriate type of mounting profiles 17 fixed to the mounting surface by means of mechanical fasteners;

- in fig. 13b presents an example of a possible structural and technological execution of technical means of securing in a horizontal position the detached single-shaped combined sound-absorbing panels 10, by using the appropriate type of mounting profiles 17 fixed to the mounting surface by means of mechanical fasteners;

- in fig. 14a is a longitudinal sectional view of an isolated tselnoformovannoy combined sound absorption of the panel 10, in the porous vozduhoproduvaemoy sound absorbing structure which composed of separate crushed fragmented sound absorbing elements 18 are integrated U-shaped hollow tubular profile of circular cross-section abdominal half wave acoustic resonators R ^II _ms (pos. 11) formed using the carrier inner air-carrying film elastic acoustic-transparent shell 20;

- in fig. 14b shows a side view of the end face of a separate, single-shaped, combined sound-absorbing panel 10 from the side of the throat parts (pos. 29) of a half-wave acoustic resonator R ^II _ms (pos. 11), the tubular part 28 of which is made in the form of a curved circular cylinder; A separate, single-formed, combined sound-absorbing panel 10 is composed of two composite modules 27 connected by an adhesive coating 26 with mating surfaces;

- in fig. 15a is a longitudinal sectional view of an isolated tselnoformovannoy combined sound absorption of the panel 10, in the porous vozduhoproduvaemoy sound absorbing structure which composed of separate crushed fragmented sound absorbing elements 18 are integrated U-shaped hollow tubular profile of rectangular cross-section abdominal half wave acoustic resonators R ^II _ms (pos. 11) formed with the use of a carrier inner air-blowing film elastic sound-transparent strip 20;

- in fig. 15b shows a side view of the end face of a separate, single-shaped, combined sound-absorbing panel 10 from the side of the throat parts (pos. 29) of a half-wave acoustic resonator R ^II _ms (pos. 11), the hollow tubular part 28 of which is made in the form of a curved rectangular cylinder; A separate, single-formed, combined sound-absorbing panel 10 is composed of two composite modules 27 connected by an adhesive coating 26 with mating surfaces;

- in fig. 16a shows a longitudinal section of a detached one-shaped combined sound-absorbing panel 10, in a porous sound-absorbing structure of which, composed of separate crushed fragmented sound-absorbing elements 18, are integrated U-shaped hollow tubular profile, the cavity elements made in the form of curved circular and rectangular cylinders formed using hollow circular and rectangular cylinders formed using bearing carriers that are formed with curved circular and rectangular cylinders formed using hollow circular and rectangular cylinders formed using a hollow circular profile and rectangular cylindrical, formed using curved circular and rectangular cylinders formed using hollow circular and rectangular cylinders formed using hollow circular and rectangular cylindrical shaped air-tight film elastic sound-transparent shell 20, forming a half-wave kusticheskie resonators R ^II _ms (11 pos.) differing resonant frequency setting (parameter f ^II _Rms), determined by their geometric l ^II _r and dynamic l ^II _R lengths;

- in fig. 16b is a side view of the end face of a separate, single-shaped combined sound-absorbing panel 10 from the side of the throat parts 30 (pos. 29) of a half-wave acoustic resonator R ^II _ms (pos. 11), the hollow tubular part 28 of which is made in the form of a curved circular and rectangular cylinder; A separate, single-formed, combined sound-absorbing panel 10 is composed of two composite modules 27 connected by an adhesive coating 26 with mating surfaces;

- in fig. 17a shows a longitudinal section of a detached single-shaped composite sound-absorbing panel 10, in a porous air-absorbing sound absorbing structure of which, composed of separate crushed fragmented sound-absorbing elements 18, are integrated U-shaped hollow tubular profile, cavity elements formed using an internal air-absorbing element of a plastic element of a plastic element of a plastic board. in the form of a non-smooth (rough) wall surface forming my cavity of the tubular part 28 of a half-wave acoustic resonator R ^II _ms (pos. 11);

- in fig. 17b shows a side view of the end face of a separate, single-shaped, combined sound-absorbing panel 10 from the side of the throat parts (pos. 29) of a half-wave acoustic resonator R ^II _ms (pos. 11), the hollow tubular part 28 of which is made in the form of a curved circular cylinder; A separate, single-formed, combined sound-absorbing panel 10 is composed of two composite modules 27 connected by an adhesive coating 26 with mating surfaces;

- in fig. 18a is a longitudinal sectional view of an isolated tselnoformovannoy combined sound absorption of the panel 10, in the porous vozduhoproduvaemoy sound absorbing structure which composed of separate, crushed fragmented sound absorbing elements 18 are integrated U-shaped hollow tubular member cavitary elements formed using the carrier inner vozduhoneproduvaemoy film flexible sound transmission casing 20, in the form of two half-wave acoustic resonators R ^II _ms (pos. 11), with oppositi tnym positioned pairs of open neck portions (29 pos.) disposed at opposite end faces 32 separate tselnoformovannoy combined sound absorption of the panel 10;

- in fig. 18b shows a side view of the end face of a separate, single-shaped combined sound-absorbing panel 10 from the side of the throat parts (pos. 29) of a half-wave acoustic resonator R ^II _ms (pos. 11), the hollow tubular part 28 of which is made in the form of a curved circular cylinder; A separate, single-formed, combined sound-absorbing panel 10 is composed of two composite modules 27 connected by an adhesive coating 26 with mating surfaces;

- in fig. 19a depicts a longitudinal section of a detached whole-shaped combined sound-absorbing panel 10 mounted on the ceiling 3 of a technical room 1, in the structure of which are integrated vertically arranged hollow half-wave acoustic resonators R ^II _ms (pos. 11), which are formed using an internal air-supported air duct film elastic sound-transparent shell 20; the open throat parts (pos. 29) of the tubular parts 28 of the half-wave acoustic resonators R ^II _{ms are} directed downwards, towards the floor of the technical room 1;

- in fig. 19b shows a side view of an end face of a separate, single-shaped, combined sound-absorbing panel 10, which is formed of two composite modules 27 connected by mating surfaces with an adhesive coating 26;

- in fig. 20 shows a diagram of geometrical-dimensional parameters of a half-wave acoustic resonator R ^II (pos. 11) integrated as part of a separate, single-shaped, combined sound-absorbing panel 10;

- in fig. 21 shows a longitudinal section of a separate structural and technological design of a separate, single-shaped combined sound-absorbing panel 10 comprising a longitudinal dividing wall 30 of a tubular 28 and throat 29 parts of a half-wave acoustic resonator R ^II (pos. 11), made in the form of a rigid sound-reflecting plate;

in fig. 22 shows a cross section of a separate structural and technological design of a separate, single-shaped, combined sound-absorbing panel 10 containing a longitudinal partition wall 30 of the tubular 28 and throat 29 parts of a half-wave acoustic resonator R ^II (pos. 11), in the form of a rigid sound-reflecting plate, with the tubular part 28 made of round geometric shape;

in fig. 23 shows a cross-section of a separate structural and technological design of a separate, single-shaped, combined sound-absorbing panel 10 containing a longitudinal partition wall 30 of a tubular 28 and throat 29 parts of a half-wave acoustic resonator R ^II (pos. 11), in the form of a rigid sound-reflecting plate, with the tubular part 28 made oval geometric shape;

in fig. 24 shows a cross section of a separate structural and technological design of a separate, single-shaped, combined sound-absorbing panel 10 containing a longitudinal partition wall 30 of a tubular 28 and throat 29 parts of a half-wave acoustic resonator R ^II (pos. 11), with a rigid sound-reflecting plate, and the section of the tubular part 28 is made of an oval geometric shape, and the dividing partition 30 with its end sections is embedded in the structure of isolated crushed fragments centered sound absorbing elements 18;

in fig. 25 shows an illustrative schematic depiction of the physical mechanisms for the absorption of the energy of sound waves, realized by the use of a separate, single-shaped, combined sound-absorbing panel 10;

in fig. 26 shows an illustrative schematic depiction of the physical process of the propagation and absorption of sound energy in the composite structural elements of a separate, single-shaped, combined sound-absorbing panel 10, which is emitted by the STEP (pos. 9) at individual discrete values of the operating dominant functional frequencies of acoustic radiation f _1s , f _2s , f _3s with sound wavelengths λ _1s , λ _2s , λ _3s , and absorbed by half-wave acoustic resonators R ^II _1ms , R ^II _2ms , R ^II _3ms (pos. 11), characterized by their dynamic lengths I _{R 1} , I _R2 , I _R3 (geometric lengths I _r1 , I _r2 , I _{r3 of the} tubular parts 28);

- in fig. 26a shows an illustrative diagram of the formation of an acoustic quadrupole in the spatial zone of the throat portions (pos. 29) of a half-wave acoustic resonator (pos. 11);

- in fig. 27 shows the implementation scheme of the physical mechanisms of diffraction absorption of the energy of the incident sound waves at the edge perimetric zones of the open throat parts (pos. 29) of a half-wave acoustic resonator R ^II _ms (pos. 11);

- in fig. 28 shows the implementation of the physical mechanism for diffractive absorption of the energy of sound waves propagating in a porous sound-absorbing structure of a fragment of a closed internal cavity 31 of a separate, fully-formed combined sound-absorbing panel 10 containing, in a specified structure, a porous sound-absorbing substance, represented by separate crushed fragmented sound-absorbing elements 18, which have been draped by a piece of a piece of a piece of a piece of a piece of a piece of sound absorbing material. and / or dense eporistye structure of polymeric materials;

- in fig. 29 shows a diagram of the implementation of the physical process of diffraction bending by sound waves in narrow-gap air gaps of the edge (end, end) zones of the end faces 32 of porous sound-absorbing air-blown structures of the substance of separate fully-formed combined sound-absorbing panels 10, with dissipative energy losses arising from them, dissipated energy losses, in addition to the amount of the additional discharges that have been applied.

- in fig. 30 shows a diagram of the implementation of the physical process of diffraction bending by sound waves of the edge perimetric sections of the throat parts (pos. 29) in the end zones of the cavities of the tubular parts 28 of the half-wave acoustic resonators R ^II _ms (pos. 11) integrated into the structure of the porous sound-absorbing air-blown substance represented by crushed crushed the fragmented sound-absorbing elements 18 contained in the composition of the isolated whole-shaped combined sound-absorbing panels 10, with ikayuschimi attendant dissipative energy losses;

- in fig. 31 is a diagram of the installation of clearance (γ, k) installations of separate, fully-formed, combined sound-absorbing panels 10 relative to the surface of the enclosing wall structure (pos. 2) of the technical room 1 (gap k) and between opposite end faces of 32 separate, whole-shaped combined sound-absorbing panels 10 (gap γ) with schematic images of direct incidence of sound waves (solid arrows) and reflected incidence of sound waves (dashed arrows).

Digital positions on the presented figures indicate:

1 - technical room;

2 - walls of the technical room 1 (hereinafter referred to as walls 2);

3 - ceiling (ceiling) of the technical room 1 (hereinafter - ceiling 3);

4 - the floor of the technical room 1 (hereinafter - floor 4);

5 - the doorway wall 2 (hereinafter - the doorway 5);

6 - the entrance door of the doorway 5 (hereinafter - the entrance door 6);

7 - supply and exhaust ventilation openings of the technical room 1 (hereinafter referred to as ventilation openings 7);

8 - internal three-dimensional air cavity of the technical room 1, bounded by the enclosing surfaces of the ceiling 3, floor 4, side walls 2 and closed entrance door 6 (hereinafter - the internal three-dimensional air cavity 8);

9 - noise-generating technical object (hereinafter - ShGTO 9);

10 - detached one-piece combined sound-absorbing panel;

11 - half-wave acoustic resonators R ^II (R ^II _ms , R ^II _mA );

12 - remote mechanical fasteners;

13 - suspended cable elements;

14 - mounting spikes;

15 - mounting frames;

16 - mounting elastic elements;

17 - mounting profile;

18 - isolated crushed fragmented sound-absorbing elements;

19 - bearing outer surface facing sound-transparent sheath;

20 - supporting internal air-blown film elastic sound-transparent sheath forming the tubular part 28 of a half-wave acoustic resonator R ^II (R ^II _ms , R ^II _mA ), pos. eleven;

21 - outer surface facing sound-transparent layer of material;

22 - supporting base, made of solid dense air-conductive sound reflecting material (hereinafter - the supporting base 22);

23 — air-tight closed cell foamed and / or dense non-porous structures of polymeric materials;

24 —the internal embedded sound-transparent reinforcing elements of the rod, mesh or plate-perforated types of the isolated whole-shaped combined sound-absorbing panel 10, (hereinafter referred to as the internal embedded acoustic-transparent reinforcing elements 24);

25 - sound-transparent facing protective and decorative perforated panel (k _perf ≥0.25);

26 - adhesive continuous continuous (film) or intermittent (fibrous, powdery, perforated film) sound-transparent coating, represented accordingly by the surface and / or volumetrically distributed adhesive adhesive or thermo-melting adhesive material (hereinafter - adhesive coating 26);

27 — composite prefabricated modules of a detached, whole-shaped, combined sound-absorbing panel 10;

28 - tubular part of a half-wave acoustic resonator R ^II (pos. 11);

29 - throat part of a half-wave acoustic resonator R ^II (pos. 11);

30 - longitudinal dividing wall of a tubular 28 and throat 29 parts of a half-wave acoustic resonator R ^II (pos. 11);

31 —a closed internal cavity of a separate, single-shaped, combined sound-absorbing panel 10;

32 — end faces of a separate, single-molded, combined sound-absorbing panel 10;

33 —a protective lining damping air-blown layer of material mounted on the throat portion 29 of a half-wave acoustic resonator R ^II (pos. 11);

34 — narrow-gap air gaps formed between the opposite end faces 32 of the isolated, whole-shaped combined sound-absorbing panels 10 mounted on the supporting enclosing elements of the walls 2 and the ceiling 3 of the technical room 1;

A is one of the basic dimensional parameters (L, B, H), characterizing the dimensions of the internal three-dimensional space of the internal three-dimensional air cavity 8 of the technical room 1;

L is the overall length of the internal space of the internal three-dimensional air cavity 8 of the technical room 1;

B is the overall width of the internal space of the internal three-dimensional air cavity 8 of the technical room 1;

H is the overall height of the internal space of the internal three-dimensional air cavity 8 of the technical room 1;

R ^II - half-wave acoustic resonator;

R ^II _ms - a half-wave acoustic resonator designed to mute the noise generated by ShGTO 9 produced by it at the working dominant functional frequencies of acoustic radiation f _ms ;

R ^II _1s is a half-wave acoustic resonator designed to mute the noise generated by ShGTO 9 produced by it at the operating dominant functional frequency of acoustic radiation f _1s ;

R ^II _2s is a half-wave acoustic resonator designed to mute the noise generated by ShGTO 9 produced by it at the working dominant functional frequency of acoustic radiation f _2s ;

R ^II _3s is a half-wave acoustic resonator designed to mute the noise generated by ShGTO 9 produced by it at the operating dominant functional frequency of acoustic radiation f _3s ;

n _s - specified (passport) steady-state operating speed mode of ShGTO 9, characterized by sound radiation, containing in the spectrum prominent working dominant functional frequencies of sound oscillations f _ms , min ^-1 , s ^-1 ;

R ^II _mA is a half-wave acoustic resonator designed to suppress resonant sound radiation in the internal three-dimensional air cavity 8 of the technical room 1, in the direction of its overall parameter A (L, B, H) caused by the excitation of its own acoustic modes of a mass-elastic body of air volume, with wavelengths λ _mA (λ _mL , λ _mB , λ _mH ) at discrete values of the natural frequencies f _mA (f _mL , f _mB , f _mH );

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

f _mA (f _mL , f _mB , f _mH ) - discrete values of the natural frequencies of sound oscillations in Hz on the own acoustic modes of the mass-elastic body of the air volume of the internal three-dimensional air cavity 8 of the technical room 1, in the direction of its overall parameters A (L, B , H), characterized by sound wavelengths λ _mA (λ _mL , λ _mB , λ _mH );

f _ms - discrete values of the working dominant functional frequencies of the sound radiation of ShGTO 9, Hz;

(f _1s , f _2s , f _3s ) - discrete values of the operating dominant functional frequencies of sound vibrations, represented by three multiple lower harmonic components of the spectrum of sound radiation of the ShGTO 9, Hz;

f _R - own (resonant) frequency of sound waves in Hz of an acoustic resonator R;

f ^II _R - own (resonant) frequency of sound vibrations in Hz of a half-wave acoustic resonator R ^II ;

f ^II _R1s , f ^II _R2s , f ^II _R3s , - own (resonant) frequencies of sound oscillations in Hz of half-wave acoustic resonators R ^II _1s , R ^II _2s , R ^II _3s (pos. 11), intended for damping the noise generated by SHGTO 9 produced by him on his discrete values of the working dominant functional frequencies of acoustic radiation f _1s , f _2s , f _3s ;

Δf _R is the width of the frequency band of sound oscillations in Hz, at the boundaries of which the acoustic energy with forced resonant sound vibrations is twice (3 dB) less than the acoustic energy at the resonance frequency of sound vibrations of the acoustic resonator f _R ;

ϕ is the phase of the sound wave (rad.);

с - sound speed (speed of sound waves propagation), m / s;

c (t ° C _st ) - the speed of sound waves in m / s, distributed in the air of the technical room 1 at the air temperature regime established in it, at t ° C _st ;

λ - sound wavelength, m;

λ (t ° C) is the length of the sound wave in m, propagating at a speed c (t ° C _st ) in m / s in the air environment of the technical room 1 at the temperature regime established in it in ° C;

λ _R ^II is the length of the sound wave in m, half the distance of which (0.5λ _R ^II ) is within the limits of the dynamic length l _R ^{II of the} half-wave acoustic resonator R ^II (pos. 11)

Δ _λ is the range of change of the sound wavelength λ in m, caused by the operational range of change in air temperature Δ _t in the technical room 1, in whose air the sound wave propagates;

λ _ms is the length of the sound wave, in m, at the working dominant functional frequency f _{ms of the} sound radiation of the ShGTO 9 operating at a given steady-state operating mode n _s ;

(λ _1s , λ _2s , λ _3s ) are the sound wavelengths in m of three multiple dominant frequency harmonics (f _1s , f _2s , f _3s ) of the operating dominant functional frequencies f _{ms of the} sound radiation of ShGTO 9 operating at a given steady-state operating mode _s ;

λ _mA (λ _mL , λ _mB , λ _mH ) are the sound wavelengths in m at the lowest natural acoustic modes, represented by the own acoustic oscillations of the mass-elastic body of the air volume of the internal three-dimensional air cavity 8 of the technical room 1;

t ° C - ambient temperature (air), in degrees. Celsius;

t ° C _st - stabilized value of air temperature in ° С, established in the internal three-dimensional air cavity 8 of the technical room 1;

Δ _t is the operational range of changes in air temperature, in ° C;

P _pad - the amplitude values of the incident (incoming) sound waves in the open sections of the throat parts of the 29 half-wave acoustic resonators R ^II (R ^II _ms , R ^II _mA ), pos. eleven;

R _out - amplitude of sound waves emanating from the tubular part 28 in zones of open sections of the throat parts 29 of half-wave acoustic resonators R ^II (R ^II _ms , R ^II _mA ), pos. eleven;

P _s1 , P _s2 , P _s3 are the amplitude values of the incident (incoming) sound waves to (c) the open throat portions 29 and (c) the porous sound-absorbing substance, represented by separate crushed fragmented elements 18, which are part of a separate, fully-formed combined sound-absorbing panel 10 ;

d _ol is the reduced hydraulic diameter, in m, of an arbitrary geometrical shape of the flow area of the tubular part 28 (for a circular flow section, d _dpr = d _kr , where d _kr is the circle diameter) of a half-wave acoustic resonator R ^II (R ^II _ms , R ^II _mA ) , pos. eleven;

S _t is the flow area, in m ² , of the tubular part 28 of the half-wave acoustic resonator R ^II (R ^II _ms , R ^II _mA ), pos. eleven;

l ^II _r (l ^II _r1 , l ^II _r2 , l ^II _r3 ) is the geometric length, in m, of the tubular part 28 of the half-wave acoustic resonators R ^II (R ^II ₁ , R ^II ₂ , R ^II ₃ ) - pos. 11, frequency tuned to the process of suppressing sound radiation at frequencies f _1s , f _2s , f _3s ;

l ^II _R (l ^II _R1 , l ^II _R2 , l ^II _R3 ) - dynamic length, in m, half-wave acoustic resonators R ^II (R ^II ₁ , R ^II ₂ , R ^II ₃ ) - pos. 11, frequency tuned to the process of suppressing sound radiation at frequencies f _1s , f _2s , f _3s ;

m, m _L , m _B , m _H are integers of the natural number (1, 2, 3, ...).

k is a remote air gap between the rear surface of a separate all-molded combined sound-absorbing panel 10 and the opposite surface of the wall (ceiling) ceiling (pos. 2, 3) of the technical room 1;

γ is a remote air gap between the opposite surfaces of the end faces of 32 separate, single-shaped, combined sound-absorbing panels 10 mounted on the enclosing wall and ceiling ceilings (pos. 2, 3) of the technical room 1;

α _rev - reverberation coefficient of sound absorption;

α _N - normal sound absorption coefficient;

A _ekv is the area of equivalent sound absorption;

K _perf - perforation coefficient;

ρ _f is the density in kg / m ^{3 of} filling with detached crushed fragmented sound-absorbing elements 18 of the closed internal cavity 31 of the detached whole-shaped combined sound-absorbing panel 10;

j is the shortest distance in m formed between the flow sections in the plane of open sections of the composite throat parts 29 of each individual sample of a half-wave acoustic resonator R ^II (pos. 11), made in the form of a bent hollow U-shaped tubular profile.

Terminology used in the description of the application for invention

Acoustic resonators (R) - frequency-tuned sound-damping devices (Helmholtz acoustic resonators R ^III , quarter-wave R ^I and half-wave R ^II acoustic resonators R) intended for dissipative absorption (dissipation, damping, antiphase compensation) of sound (acoustic) energy distributed in a given gas. (aerodynamic) system to which they are connected; The most effective use of acoustic resonators R refers to the absorption of resonant sound waves emitted in the spectra of sound radiation of a gas-dynamic (aerodynamic) system.

The standing wave - the state of the elastic medium in the process of propagation of sound waves, in which the location of the maxima and minima of the elastic displacements of oscillating particles of the medium does not change with time; formed as a result of the interference of two opposite (out-of-phase) harmonic oscillations with identical frequencies; noted, in particular, in a closed room between opposed rigid surfaces of the walls, as well as the floor and ceiling; recorded, in particular, at the frequencies of the own half-wave acoustic resonances of the natural acoustic modes of a mass-elastic body of the air volume (cavity) of a technical room.

Diffraction of sound waves is a physical phenomenon associated with the deviation of sound waves from their straight-line propagation when interacting with a counter solid obstacle (located in the path of their propagation); the occurrence of the diffraction effect of sound absorption due to the physical process of dissipation of the energy of a sound wave on a solid (porous) obstacle with a final value of the input acoustic resistance of the surface of a solid obstacle (porous fibrous or foamed open-cell structure); A new diffuse sound wave formed by the diffraction process of propagation at the edges (edges) of a finite-sized porous element (forming the edge diffraction effect) causes an additional flow of sound energy directed (propagating) into the porous structure of this element, which leads to an increase in the total sound-absorbing effect.

Diffuse sound field - a sound field, at each point of which the sound pressure level is the same; it is formed mainly in the high-frequency sound range in enclosed volumes (technical rooms) limited by rigid sound reflecting walls.

The quality factor of the acoustic resonator frequency characteristic R is a parametric characteristic of the acoustic resonator R, indicating the magnitude of internal dissipative losses arising both in the composite structures (elements) of the acoustic resonator R and due to external energy losses directly related to the process of sound emission into the environment, which also consumes a certain part of the vibrational (acoustic) energy of the acoustic resonator R.

Sound absorption is the physical process of weakening part of the energy of sound vibrations distributed in the porous structure of a sound-absorbing material, with the arising irreversible dissipative conversion of sound energy into thermal energy dissipated exclusively by the medium of the porous structure in which the sound wave propagates; It is characterized by sound absorption coefficient (normal α _N , reverberation α _rev ) or equivalent absorption area A _ekv .

The area of equivalent sound absorption (A _ekv ) is an estimated technical parameter of the sound-absorbing properties of flat-sheet samples of materials or full-scale non-planar volumetric noise-absorbing parts, determined under the influence of a diffuse sound field on them, which is compared with the corresponding equivalent area of an abstract flat sound-absorbing surface having 100% absorption of sound energy ; in this case, the reverberation absorption coefficient α _rev = 1.0 sr. units quantitatively estimated in m ² of flat plate sample with 100% absorption of sound energy.

The reverberation sound absorption coefficient (α _rev ) is the ratio of the energy of a diffuse sound field absorbed by the surface of a material sample under investigation (a full-scale part under study) to the energy of a diffuse sound field falling on it; is determined by the changeable recorded reverberation time t _rev in the working cavity of the measuring reverberation chamber based on the results of placing the material sample under study (the full-scale part under study) in its cavity.

The sound absorption coefficient is normal (α _N ) - the sound absorption coefficient of a small-sized sample of a material, determined with a normal incidence of a sinusoidal sound wave on it; determined by the results of recording the localization of the amplitudes of the maximum and minimum values of sound pressures of standing waves, artificially created in an acoustic interferometer (Kundt Tube), with subsequent calculation of the values at each frequency of the sound wave studied.

Sound transparency is a property of structural elements of structures (plates, shells, films, fabrics) that are in the propagation path of a sound wave, to pass a sound wave propagated in an elastic medium without significant (no more than 10%) attenuation (without a significant reflection effect in the opposite propagation of sound waves from the radiation source); characterized by the coefficient of sound propagation through the structure, representing the ratio of the sound pressure amplitudes in the wave transmitted through the structure (P _Ave), to the sound pressure of the incident sound wave (P _pad).

Interference of waves - the physical process of addition in unlimited space (or in a limited waveguide) of two or more two waves having the same oscillation periods T, as a result of which in different zones of unlimited space (or limited space of the waveguide) the amplitude value of the resulting wave increases or decreases depending from the phase relationships of the oscillations ϕ of the folding (interacting) waves, thus forming uneven spatial amplitude distributions resulting boiling waves.

The beats of sound (acoustic) oscillations are the result of the interference addition of two interacting harmonic sound waves with similar frequencies, manifested as alternating ramp ups and drops of amplitude maxima and minima (pulsations of sound pressure) recorded at a frequency equal to the frequency difference of the interacting sound waves.

Adhesives, adhesives - compositions based on organic or inorganic substances capable of combining (sticking together) various materials; their action is due to the formation of a strong adhesive bond between the adhesive layer and the surfaces to be joined; the cohesiveness of the adhesive layer and the mating surfaces also affect the strength of the adhesive joint; The basis of organic adhesives are mainly synthetic oligomers and polymers (phenol-formaldehyde, epoxy, polyester resins, polyamides, polyurethanes, silicon-organic polymers, rubbers, etc.), which form an adhesive film as a result of solidification upon cooling (thermoplastic adhesives), curing ( thermoactive adhesives) or vulcanization (rubber adhesives); Inorganic adhesives include aluminophosphate, ceramic, silicate, and metal.

Fire retardants - substances or mixtures of substances that protect wood, fabrics and other materials of organic origin (including sound-absorbing or sound insulating) from ignition and self-combustion; decompose with the formation of non-combustible substances and / or prevent the decomposition of the material with the release of combustible gases; flame retardants are applied to the surface of the products in the composition of paints and (or) used in the form of solutions that impregnate the material; common flame retardants - aluminum hydroxide, compounds of boron, antimony, chlorides, organic and inorganic phosphorus compounds.

The perforation coefficient is the ratio of the total area of the holes (projections of the holes) to the total area (local area) of the wall surface of the structural element subjected to the perforation process (until its perforation).

Sound-absorbing material - an acoustic material with a sound absorption reverberation coefficient α _rev not less than 0.2.

A sound-absorbing fibrous material is a porous acoustic material, the structure of which is represented by an elastic deformable skeleton formed by a multitude of fibers that are dynamically connected and interacting with each other; the air pores formed between the surfaces of the fibers in such elastic structures of fibrous materials have the form of narrow interconnecting capillary channels; performed on the basis of natural (cotton, silk, jute, sisal, flax, hemp, etc., or animal protein), synthetic (acrylic, polyester, polyoxadiazole, polyimide, carbon, aramid, polypropylene, nylon, etc.) , mineral fibers (basalt, ceramic, glass, etc.), metal fibers (in the form of specially prepared metal structures such as porous fibrous material - PVM, porous mesh material - PSM, metal rubber - MP).

Sound-absorbing foam material (spongy) is a porous open-cell acoustic material, the elastically deformable skeleton of which is formed by means of technological foaming and subsequent polymerization of a solution of a polymeric material or by means of an appropriate chemical reaction; Foamed sound-absorbing materials are made on the basis of urethane, nitrile, vinyl, styrene-butadiene polymer compositions.

Porous sound-absorbing material is an acoustic material in which solid matter occupies part of the total volume, forming a spatial porous skeleton, and the remaining volume falls into numerous communicating cavities and channels (for foamed open-cell materials) or communicating capillary channels (for fibrous materials) that are open to the outside. and filled with elastic air.

Crushed porous air-absorbing sound-absorbing substance is the original raw material of recycled recycling of acoustic materials, mainly porous air-blown sound-absorbing fibrous and / or foamed open-cell, contained in parts and assemblies that have completed their life cycle, as well as in the production and technological marriage of production and waste of specified types of acoustic materials, reused as the initial production of raw materials in the manufacture of a variety of technical devices reducing noise emissions produced by different objects shumogeneriruyuschimi (sound barriers, sound-absorbing panels, noise insulation upholstery engine compartments, luggage compartments and passenger spaces of vehicles and other technical devices provide acoustic environment safety); used isolated crushed fragmented sound-absorbing elements made from the specified type of recyclable materials are made of identical or different types and grades of porous sound-absorbing materials with identical or different physical characteristics, chemical composition, porosity, number and combination of types of structures of porous layers in the composition of single and / or multi-layer combinations, identical or different geometric shape and overall dimensions, which are substantially in the linear overall range of 5 ... 100 mm, while the volume of each of the isolated crushed fragmented sound-absorbing elements is in the range of 4.2 × (10 ^-9 ... 10 ^-2 ) m ³ .

A sound-transparent material (film, foil-coated micro-perforated, woven, non-woven fabric) is a structural material that, when installed on the surface of a porous sound-absorbing layer (including, “technological stitching” of their mating surfaces) causes an acceptable drop in the reverberation coefficient of sound absorption (α _rev ) more than 10%; the sound transmission properties provided are substantially characterized by selected appropriate values of the parameters of resistance to blowing by air flow (fabric or micro-perforated film or micro-perforated foil layers), and / or the established values of thickness, flexural rigidity and specific surface mass, determined by the mass of the material per 1 m ² surface (non-sold by the air flow continuous film or foil layers); the values of resistance to blowing airborne sound-transparent air-blown fabrics or air-blown non-woven fabrics (perforated polymer film or perforated foil metal layers) should be in the range of 20 ... 500 n 3s / m ³ , with the thickness of the fibrous layer of fabric material, fibrous non-woven cloth, microperforated film polymer or micro-perforated metal foil layer, comprising 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 are in the range of 20 ... 70 g / m ² , with a film thickness of 0.01 ... 0.1 mm; the sound-transparent material can be made of various structural materials - polyethylene terephthalate, polyester aluminized, urethane, polyvinyl chloride films, or of a similar type of other acceptable polymeric materials; the use of micro-perforated metal foil material involves the use of aluminum, copper, brass as a structural material; A continuous layer of air-blown fabric (non-woven cloth) can be made of materials such as "Malifliz", "Filts", fiberglass, cloth based on superthin basalt fibers.

Flat sheet material is a structural material, produced in the form of individual flat sheets of a given geometric size.

Molded (all-molded) material is a structural material formed as a result of the implementation of technological molding operations, with subsequent obtaining, as a rule, non-planar parts of complex geometric shape that implements the geometric topology of different curvature, porosity, density, etc.

Oscillation modes resonant (own acoustic modes) - the characteristic of vibro-acoustic properties of a mechanical or gas-dynamic system, directly related to its own resonant frequency; resonance vibroacoustic mode (acoustic mode) illustrates the type (shape) of the system oscillations at its own (resonant) frequency (at natural resonant frequencies) when the values of the natural frequencies of the system and the frequencies of forced oscillations (external excitation) coincide (at close values).

Waste is any substance or object that the owner throws out, or intends to throw it away, or it is subject to release (as defined in Directive 75/442 EEC).

Perforated holes (perforation holes) - several (at least two) holes of a given identical geometric shape and area, located relative to each other and / or relative to another structural element of the part (assembly) at a specified distance; perforations - from the Latin perforato - pierce, pierce - the technological process of making holes of a given size, arranged appropriately in the structure of the manufactured part (assembly).

Microperforated holes (microperforation holes) - several (at least two) holes of a given identical geometric shape and area, located relative to each other and / or relative to another structural element of the part (assembly) at a specified distance, the diameter of which does not exceed 1 mm (≤0.001 m ).

Porosity - the ratio of the volume of voids in the porous structure of the sample material to the total volume of the sample.

Dissipative losses - irreversible dissipation (loss) of energy (in this case in question - the vibrational energy).

Recycling - the return to the production of recyclable waste materials (in this case - acoustic materials), by recycling; recycling is one of the types of utilization (unlike other types of utilization, associated, for example, with the reuse of parts and assemblies, as they are, or after their recovery, and also associated with energy production by burning part of the waste ( energy recovery).

The intrinsic (resonant) frequency ƒ _m is the oscillation frequency at which the resonance phenomenon takes place (in this case, the sound frequency f at which there is an acoustic resonance characterized by a significant increase in the amplitudes of the sound pressure).

Own (resonant) acoustic modes - a characteristic of the vibro-acoustic properties of a mechanical or gas-dynamic system, directly related to its own (resonant) frequency of its oscillations f _m ; natural (resonant) acoustic mode illustrates the type (spatial form) of the acoustic oscillations of the system at its own (resonant) oscillation frequencies f _m , realized when the natural frequencies of the system f _m coincide with the frequencies of its forced oscillations (external dynamic excitation frequencies), f _s .

The temperature field of the technical room is the set of values of the temperature distribution in the spatial domain of the internal three-dimensional air cavity of the technical room at a given time.

The sonic (acoustic) field of the technical room is the resulting steady-state distribution of the energy of the incident and reflected sound waves, with realizable accompanying physical processes of its propagation, amplification and absorption in the three-dimensional air volume of the technical room limited by rigid wall structures; one of the basic components of the acoustic field of a technical room is the expression (1), see [4]:

where c is the speed of propagation of sound waves in the air environment of the internal space of the internal three-dimensional air cavity 8 of the technical room 1, m / s (c = 344.057 m / s at + 20 ° C);

L is the overall length of the internal space of the internal three-dimensional air cavity 8 of the technical room 1, m;

B - overall width of the internal space of the internal three-dimensional air cavity 8 of the technical room 1, m;

H - the overall height of the internal space of the internal three-dimensional air cavity 8 of the technical room 1, m;

m _L is the ordinal number of the acoustic mode of sound oscillations of the mass-elastic body of the air volume of the internal three-dimensional air cavity 8 of the technical room 1 in the direction of its overall length L, expressed by an integer number of the natural number (m = 1, 2, 3 ...);

m _B is the ordinal number of the acoustic mode of sound oscillations of the mass-elastic body of the air volume of the internal three-dimensional air cavity 8 of the technical room 1 in the direction of its overall width B, expressed by an integer number of the natural row (m = 1, 2, 3 ...);

m _H is the ordinal number of the acoustic mode of sound oscillations of the mass-elastic body of the air volume of the internal three-dimensional air cavity 8 of the technical room 1 in the direction of its overall height H, expressed by an integer number of the natural number (m = 1, 2, 3 ...);

Monopole acoustic is a classic emitter of the pulsating sphere type;

Acoustic dipole is a classic sound emitter consisting of two closely spaced (paired), antiphase, non-directional pulsating spherical type emitters (acoustic monopoles);

Acoustic quadrupole - a classic sound emitter, formed from a pair of closely spaced acoustic dipoles.

The essential features of the proposed technical solution are also illustrated by figures 1 ... 31.

Schematically shown in FIG. 5 technical room 1, contains rigid supporting fencing elements, made in the form of walls 2, ceiling 3, floor 4, doorway 5 with the entrance door 6 closed and ventilation openings 7. Formed internal three-dimensional air cavity 8 of technical room 1 is represented by a hollow rectangular cylinder of the type a hollow rectangular parallelepiped with overall dimensions A (L, B, H), in which ShGTO 9 is mounted, producing “parasitic” acoustic (noise) radiation, presented in the form of propagated sound waves, noise, shown on the figure with the corresponding arrows. At the same time, during operation of ShGTO 9, thermal energy is generated, which also spreads in the internal three-dimensional air cavity 8 of the technical room 1. Thus, the corresponding sound and temperature fields are formed (spatially distributed) in the internal three-dimensional air cavity 8. Rigid carrier enclosing sound-reflecting elements of the technical room 1 can be represented by prefabricated large-panel (reinforced concrete, frame-metal), large-block monolithic or hand-made brickwork constructive-technological designs.

ShGTO 9 (for example, a piston internal combustion engine, a mechanical gearbox, a fan unit, an electric generator, a power electric transformer, a blower machine, an axial or centrifugal type exhaust fan, a piston or centrifugal pump, a piston compressor, or several of them simultaneously operated in the technical room 1 of the ShGTO 9); given by the passport (given technical conditions of operation) steady state high-speed operating mode n _s . The specific dimensions of the overall dimensions A of the internal three-dimensional air cavity 8 (L, B, H) of the technical room 1 predetermine the specific physical parameters of the mass-elastic body of the air volume formed in it, characterized, in particular, by certain values of the lowest natural acoustic modes formed on the corresponding discrete values natural (resonant) frequency sound oscillations _{f mA (f mL, f mB} , f mH), with their corresponding lengths of sound waves _{λ mA (λ mL, λ mB} , λ mH), excited as a result of f the dynamic process of dynamic excitation and the response dynamic oscillatory response of an elastic air medium (mass-elastic body of air volume) as a result of propagation of sound waves in it, represented as natural acoustic oscillations of a mass-elastic body of air volume enclosed within an internal three-dimensional air cavity 8 one.

A distinctive feature of the proposed technical device, presented in the form of a low-noise technical room 1, is the equipment (lining of wall and ceiling structures) of the technical room 1, mounted with air gaps between the opposite end faces and relatively opposed mounting surfaces (walls 2 and ceiling 3) of the technical room 1 , isolated single-molded combined sound-absorbing panels 10 (see Fig. 6, 7, 8, 9, 10a, 10b, 11b, 11b, 12a, 12b, 12b, 13a, 13b), composed of pores a sound, air-breathed, crushed sound-absorbing structure of a substance and cavity frequency-tuned noise-suppressing structural elements integrated into it, presented in the form of half-wave acoustic resonators R ^II (pos. 11).

The installation in the technical room 1 of the isolated all-molded combined sound-absorbing panels 10 can be carried out, in particular, by hanging them to the ceiling 3 using the appropriate type of remote mechanical fasteners 12 (see Fig. 11a), hanging cable elements 13 (see Fig. 11b and 11b), mounted on the walls 2 by means of the mounting profile 17 (see Fig. 13a and Fig. 13b), with the formation of vertically suspended volumetric absorbers of sound energy, mounted with a remote air gap k between the obos a bended, single-shaped, combined sound-absorbing panel 10 and a wall 2 of the technical room 1 (see Fig. 9, 10a, 10b, 13a, 13b), or be mounted without a backlash (see Fig. 12a, 12b, 12c) on the surface of the wall enclosures (technical) rooms 1, with the use of appropriate mechanical fasteners in the form of mounting studs 14, passing through the structure of a continuous supporting base 22, frames 15, holding a separate one-piece combined combined sound-absorbing panel 10 in the upper and lower parts, elastic elements 16 integrated into the structure of the outer thin-walled sound-transparent sheath 19. The remote air gap γ between the opposite end surfaces of the faces of the mounted samples of the isolated solid-molded combined sound-absorbing panels 10 is no more than a quarter of the overall thickness (dimensions) of the opposite end faces 32 of the separate forms of the distribution forms 32 10 (γ≤0.25h). Mounted detached, single-formed, combined sound-absorbing panels 10 can overlap with an additionally installed acoustic-transparent protective-decorative perforated panel 25 (K _perf ≥ 0.25), freely (without substantial reflection) transmitting the emitted sound waves in the direction of the mounted separate all-shaped combined acoustic panels 10, which is in particular, shown in FIG. 10b. A translucent facing protective and decorative perforated panel 25 can be mounted without backlash to the surfaces of separate, fully-formed, combined sound-absorbing panels 10 or with a predetermined air gap (non-contact). The permissible reduction of the reverberation sound absorption coefficient α _rev from the installation of a sound-transparent facing protective-decorative perforated panel 25 does not exceed 0.1.

Installation of separate solid-molded combined sound-absorbing panels 10 with a given air gap k of their back surfaces relative to the sound-reflecting surfaces of the ceiling 3 or wall 2 floors of the technical room 1 that are close to them (if this does not limit the requirements of the development specification), as shown in FIG. 9, 10b, 11a, 11b, 11b, 13a, 13b, 31, allows deliberately controlled to influence the increase in sound-absorbing effect in the low frequency range of the sound spectrum - with a corresponding increase in the parameter k, and also leads to an additional effect of dissipative diffraction absorption of sound energy arising on free perimetric edges (end zones) of isolated all-molded combined sound-absorbing panels 10 with their diffraction bending around by reflected sound waves (see FIGS. 29, 31). The sound wave enveloped during its propagation and dissipated in the porous sound-absorbing substance at the free peripheral edges of each separate whole-shaped combined sound-absorbing panel 10 is accompanied by a process of additional flow of sound energy from its front face to the back porous surface. For a sound wave reflected from the surface of a wall or ceiling overlap, there is a similar diffraction dissipative effect of the flow of sound energy from the back surface of a separate whole-shaped combined sound-absorbing panel 10 onto its front surface, followed by its propagation deep into the porous air-blown sound-absorbing structure of a separate whole-shaped pattern. in turn leads to the corresponding additional cuts. the losing effect of increasing the dissipative absorption of sound energy.

Each of their mounted, with predetermined air gaps (γ, k), isolated whole-shaped combined sound-absorbing panels 10, can be considered as an autonomous surround sound-absorbing element, characterized according to the source [11] with significantly higher sound-absorbing characteristics (parameters α _rev , A _ekv ) comparing with backlash-mounted flat sound-absorbing panels made of identical mass of identical structure and physical characteristics of the sound-absorbing substance va.

Separate one-piece combined sound-absorbing panel 10, made in the form of one-piece volume casing design, which has been found to be a sub-structured by default. and the inner airflow lenochnoy flexible sound transmission casing 20 formed in a tubular portion 28 of the half-wave acoustic resonator R ^II (pos. 11), separate tselnoformovannoy combined sound absorption of the panel 10, is filled with porous vozduhoproduvaemym sound absorbing material formed distinct crushed fragmented sound absorbing members 18, with their contacting each other ribs and edges, resulting in the formation of numerous additional interconnecting winding intercostal and intergranular Sound-breathing waveguide sound-propagating (sound transmitting) and, accordingly, sound-absorbing channels. The type of sound absorbing material used includes predominantly used identical or different types, structures and brands of porous air-blown sound-absorbing materials, characterized by identical or different physical characteristics, chemical and structural composition, the number and combination of the types of structures of porous layers used in the composition of multilayer combinations of sound-absorbing materials, identical different geometric shapes and dimensions, made from t Hard recyclable, mainly polymeric wastes, presented in the form of sound-absorbing structures technologically processed by mechanical crushing, dismantled from recyclable technical objects, mainly parts of noise insulation packages of vehicles that have completed their life cycle, and / or from technological wastes and rejects of sound-absorbing materials and parts and components made from them. Said closed inner cavity 31 isolated tselnoformovannoy combined sound absorption of the panel 10, with the carrier inside vozduhoneproduvaemoy film flexible sound transmission casing 20 communicates with the attached thereto cavitary hollow molded zvkopogloschayuschimi (noise-suppressing) structural elements (at least - one cavitary hollow molded sound-absorbing member) provided in the form of half-wave acoustic resonators R ^II (pos. 11). The tubular parts 28 of the said half-wave acoustic resonators R ^II (pos. 11) are formed using the carrier internal air-blowing film elastic sound-transparent shell 20 (see Fig. 11a, 1b, 11b, 12a, 12b, 12b, 13a, 13b, 14a, 14b, 15a, 15b, 16a, 16b, 17a, 17b, 18a, 18b, 19a, 19b, 20, 21, 22, 23, 24, 25) from inside the lining of the surface of the adjacent (in contact) facets and edges of isolated crushed fragmented sound-absorbing elements 18 placed in a closed internal cavity 31 of a separate, single-molded combination sound ogloschayuschey panel 10. The closed inner cavity 31 isolated tselnoformovannoy combined sound absorption of the panel 10 is filled with crushed fragmented distinct sound-absorbing elements 18 which are made mainly of recyclable acoustic materials. Also they (isolated crushed fragmented sound-absorbing elements 18) can be made according to typical technologies of their production from "new" semi-finished sheet (roll) acoustic materials subjected to the subsequent technological process of their mechanical crushing into fragments of predetermined geometric shapes and overall dimensions, in addition to placed in a closed internal cavity 31 of a detached whole-shaped combined sound-absorbing panel 10, detached crushed fragments annym sound absorbing member 18 made of recyclable acoustic materials listed above. As possible constructive-technological variants of the execution of a separate all-molded combined sound-absorbing panel 10, its closed internal cavity 31 can also be partially, but not more than 30% of its cavitary volume, filled with fragmented-fragmented air-tight closed cell foam and / or dense non-porous polymer structures materials 23.

The provided sound transmission properties of the carrier outer surface cladding translucent shell 19, as part of a separate, single-molded combined sound-absorbing panel 10, are substantially characterized by selected corresponding values of the parameters of resistance to blowing air flow of layers of materials — woven or non-woven fabric, or micro-perforated film or micro-perforated foil layers). and / or established values of thickness, bending stiffness and their specific th surface weight determined by mass per 1 m ² surface (windproof airflow continuous film or foil layers). The values of resistance values for blowing airborne sound-transparent air-blown fabrics or sound-transparent air-blown nonwoven fabrics (micro-perforated polymer film or micro-perforated foil metal layers) are within 20 ... 500 ns / m ³ , with thicknesses of the fibrous layer of fabric material, fibrous non-woven fabric, micro-perforations, Polymer film or microperforated metal foil layer, comprising 0.025 ... 0.25 mm with a specific surface m assoy 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 are in the range of 20 ... 70 g / m ² , with a film thickness of 0.01 ... 0.1 mm. The outer surface cladding sound-transparent layer of the material 21 bearing the outer surface cladding sound-transparent film-type casing 19 can be made of various structural materials - aluminized polyester, urethane, polyvinyl chloride film, or a similar type of other acceptable polymeric film materials.

The outer surface cladding sound-transparent layer of the material 21 carrying the outer surface cladding sound-transparent sheath 19 can be made solid or perforated. For example, it can be made of microperforated (with a perforation opening diameter not exceeding 1 mm) a foil material, using aluminum, copper, brass as a construction material. The outer surface facing sound-transparent layer of the material 21 bearing the outer surface facing sound-transparent shell 19 may also be made of a continuous layer of air-blown fabric (non-woven cloth) material, may be represented by materials such as "mallfliz", "filts", fiberglass, basalt fabric of super thin basalt the fibers. The use of these types of structural materials for the manufacture of an external surface cladding sound-transparent layer of the material 21 bearing the external surface cladding sound-transparent shell 19 used in the composition of a separate, single-shaped combined sound-absorbing panel 10, provides for a given packing density (ρ _f = 10 ... 655 kg / m ³ ) closed the inner cavity 31 of a separate all-molded combined sound-absorbing panel 10 corresponding to the isolated crushed fragment otirovannyh sound-absorbing elements 18, the elimination of unwanted ingress and accumulation (absorption) in porous open-cell foamed or porous fibrous structures of isolated crushed fragmented sound-absorbing elements 18, various types of technological and / or operating fluids (moisture, fuel, coolant), as well as small amorphous particles or insects during the operation of the proposed technical object.

For the formation of the corresponding sound-transparent connections (sound-transparent technological "cross-links") of the constituent elements of an isolated whole-shaped combined sound-absorbing panel 10, various types of sound-transparent adhesive coatings 26 can be used, realized, for example, by appropriate temperature heating and melting of the used hot-melt polymer films or fibers placed on the surface of the structure outer surface cladding sound-transparent layer of material 21 (carrying external surface sound-transparent cladding 19), or a carrier internal air-blown film elastic sound-transparent cladding 20, or between contacting fins and edges of detached crushed fragmented sound-absorbing elements 18 in the course of the implementation of the technological process of manufacturing a separate composite shaped sound-absorbing panel 10. technological variants of execution of a separate whole form when combined with a polymeric material of the outer surface cladding sound-transparent layer of material 21 (bearing outer surface cladding sound-transparent sheath 19) or carrying an internal air-tight film elastic sound-transparent sheath 20, which does not provide the required adhesive bonding by melting it (with proper heating) structure), satisfying the adhesive compound can be provided by introducing additional sound translucent (not significantly negative, no more than 10%, to reduce the sound absorption coefficient of sound energy) of a certain type of adhesive adhesive layers (in the form of sticky adhesive or thermo-hot-melt substances), technologically realized by surface-spaced separate thin solid lines, or surface separated by thin, discontinuous lines, or in the form of a thin continuous surface layer perforated by through holes Achy adhesive substance, either in the form of a continuous thin acoustic translucent adhesive layer with a low specific surface weight (not exceeding 100 g / m ² ), or in the form of a continuous thin acoustic transparent thermally active thermo-melting layer of an adhesive substance with a low specific surface weight (not more than 50 g / m ² ).

In the closed internal cavity 31 of the detached whole-shaped combined sound-absorbing panel 10, filled with sound-absorbing substance, formed by separate crushed fragmented sound-absorbing elements 18, the corresponding internal core-acoustic or reinforcing elements 24 of the rod-type or mesh-like or plate-perforated type can be contained.

The bearing outer surface cladding sound-transparent casing 19 of a separate all-molded combined sound-absorbing panel 10 can additionally overlap with a metal or polymer sound-transparent cladding protective-decorative mesh or perforated panel 25 (as shown in Fig. 10b, 26), with a perforation ratio K _perf ≥0,25 .

During operation of ShGTO 9 containing thermally loaded nodes and systems mounted in close proximity to the surface areas of the installation of separate all-shaped combined sound-absorbing panels 10 and acoustic translucent protective-decorative perforated panels 25 of the technical room 1, the specified structural elements (pos. 10 and 25) can be performed taking into account ensuring their heat-resistant fire-safe structural and technological performance. In these cases, in particular, substances can be used - flame retardants for their structural impregnation and / or thin-layer surface deposition. Thus, in addition, individual substances or mixtures of substances can be used, protecting materials of organic or synthetic origin from ignition and independent burning. In particular, aluminum hydroxide, compounds of boron, antimony, chlorides, organic and inorganic phosphorus compounds can be used as flame retardants. The bearing outer surface cladding sound-transparent sheath 19 and the protective lining damping air-blown layer of material 33 mounted on the throat part 29 of the half-wave acoustic resonator R ^II (pos. 11) can be made of microperforated metallic materials in these cases. Similar fire and safety requirements for the use of fire retardants can, if necessary, apply to sound-transparent adhesive coatings 26 and to separate crushed fragmented sound-absorbing elements 18. In the considered design-technological versions, the use of this type of fire-resistant elements can mainly relate only to local areas of their application, and as part of a complete set of sound-absorbing lining of supporting building envelopes of a technical room 1. Removed The wall (post. 2) and / or ceiling (post. 3) structures of the specified acoustic elements (pos. 10, 25, 19, 26, 18) from ShGTO 9 can be made of other types of materials that do not require flame retardant treatment or not requiring a metal version, as described in the description of the proposed technical device.

Constructive-technological performance of individual components of a separate all-molded combined sound-absorbing panel 10, as well as grouped from separate parts (half-forms) mating together in monolithic structures of composite prefabricated modules 27 (see Fig. 14b, 15b, 16b, 17b, 18b, 19b) , can be presented in the form of prefabricated one-piece connections, using appropriate sound-transparent adhesive coatings 26, made in the form of continuous or perforated film, or intermittent fibrous or pores Optical acoustic translucent coatings. They can be represented accordingly by the surface and / or volumetric distribution of sticky adhesive or thermoactive adhesive substances, with the formation in the internal cavity 31 of a separate whole-shaped combined sound-absorbing panel 10 of fixed structural sound-absorbing (noise suppressing) elements, represented as porous-crushed sound-absorbing substance in the form of fastened a crushed fragmented sound-absorbing elements 18 and half-wave acoustic resonator tori R ^II (pos. 11).

The outer surface layer formed by adhesively bonded to each other by the contacting edges and edges of individual samples of isolated crushed fragmented sound-absorbing elements 18, as part of a separate all-molded combined sound-absorbing panel 10, can form a corresponding monolithic air-blown sound-absorbing briquetted structure, which, in turn, will be applied. counter surface bearing external surface facing sound-transparent shell 19 in the composition of a separate all-molded combined sound-absorbing panel 10.

The outer surface layer of the porous air-permeable sound-absorbing structure, composed of separate crushed fragmented sound-absorbing elements 18, which are appropriately distributed in the spatial zones of the internal cavity 31, adjacent (mating) with the carrier internal air-blowing film elastic acoustic-transparent shell 20, forms corresponding dimensions of the tubular body 28 resonators R ^II (pos. 11) is integrated into a porous vozduhoproduvae second substance isolated structure tselnoformovannoy combined sound absorption of the panel 10.

Hollow molded cavity capacitances, represented by tubular 28 and throat (pos. 29) parts of a half-wave acoustic resonator R ^II (pos. 11), composed of a separate whole-molded combined sound-absorbing panel 10, may include, as identical overall dimensions and geometric shapes, acoustic half-wave resonators R ^II (pos. 11), as shown in FIG. 11a, 11b, 11c, 14a, 15a, 17a, 18a 19a, characterized by identical frequency setting for given specific values (set of sound frequency values grouped into a narrow frequency band) of natural (resonant) sound vibrations (f ^II _R ) formed by acoustic R ^II half-wave resonators (pos. 11), as well as the overall dimensions and geometric shapes of the R ^II half-wave acoustic resonators (pos. 11), which differ from each other, as shown in FIG. 16a, 16b, 26, which ensure their different frequency setting for given different values (given sets of sound frequency values grouped into a narrow frequency band) of their own (resonant) frequencies of sound oscillations (f ^II _R ) of half-wave acoustic resonators R ^II (pos. 11 ).

Constructive-technological versions of half-wave acoustic resonators R ^II (pos. 11) are represented by curved hollow cavity U-shaped tubular elements (tubular part 28) limited by a carrying internal air-blowing film elastic acoustic-transparent shell 20 (see Fig. 11a, 11b, 11c, 12a , 12b, 12b, 13a, 13b, 14a, 14b, 15a, 15b, 16a, 16b, 17a, 17b, 18a, 18b, 19a, 19b, 20, 21, 22, 23, 24, 25, 26). The open end zones of the tubular part 28 with a part of the air mass oscillating in the tubular part 28 of the air column (located behind the plane of the open sections of the tubular part 28) that forms the attached oscillating air mass in the form of a dynamic increment to the oscillating air mass concentrated in the tubular parts 28 form two throat parts (pos. 29) of a half-wave acoustic resonator R ^II (pos. 11), see fig. 20 and FIG. 21. The longitudinal dividing wall 30 of the tubular 28 and the throat 29 parts can be represented as in the form of the used structure of the porous sound-absorbing substance of isolated crushed fragmented sound-absorbing elements (see Fig. 11a, 11b, 11b, 12a, 12b, 12b, 13a, 13b, 14a , 14b, 15a, 15b, 16a, 16b, 17a, 17b, 18a, 18b, 19a, 19b, 20) and in the form of a different structure of a dense, air-breathing sound-reflecting substance, mainly from a solid polymeric material (see Fig. 21, 22, 23, 24).

The formation of the specified values of the physical and structural parameters of the half-wave acoustic resonators R ^II (pos. 11) is carried out by concretely calculating the values of their own (resonant) frequency f ^II _R , taking into account the choice of the geometric length of the tubular part 28 (l ^II _r ) and the calculated value of the dynamic length ( l ^II _R), taking into account the value of the dynamic increment, which is formed with the reduced flow cross section of the hydraulic diameter of the tubular portion 28 - d _etc., as well as the effect on its potential value used I footer protective damping material layers 33, mounted on the neck portion - Pos. 29 (overlapping the flow area of the throat portions 29 on their open end sections). Technical design of the tubular part 28, made of an air-blown material structure, with a predetermined approach to the throat parts 29, which is carried out by selecting a curved U-shaped geometric shape of the tubular part 28, ensuring the realization of the allowable distance j between the contours of the throat bore (position 29) The tubular 28 part of the half-wave acoustic resonators R ^II causes the common-mode hit (entry) and the subsequent corresponding waveguide propagation of sound waves with frequencies oh f _ms and wavelength λ _ms to both open throat parts 29 of the tubular part 28 of each individual sample of a half-wave acoustic resonator R ^II (pos. 11) for their further counter-penetrating energy damping occurring in the middle zone of the tubular part 28 when the sound pulses pressure towards each other in both composite quarter-wave sections of their half-wave tubular part 28 (see FIG. 25, 26). At the same time, in the zone of the open throat parts 29, the antiphase energy compensation of the pressure fields of the falling (incoming) P _pad and outgoing throat parts P _out sound waves is realized. In this zone, the near hydrodynamic field of pulsating pairs of acoustic monopoles is realized, which form acoustic dipoles that emit a weakly radiating sound. The shortest distance j formed between the flow sections in the plane of open sections of the composite throat parts (pos. 29) of each individual sample of a half-wave acoustic resonator R ^II (pos. 11), made in the form of a bent U-shaped tubular profile, should not exceed 0.068 m that thereby, in particular, does not exceed 0.1 sound wavelength λ (≤0.1λλ) at a frequency of 500 Hz (at t ° C = 20 ° C), adopted as the upper limit of the actual low-frequency sound range being considered 50 ... 500 Hz. Acoustical pairs of acoustic dipoles (two horizontal and two vertical acoustic dipoles) at the open sections of the composite throat parts (pos. 29) form higher-order acoustic emitters — acoustic quadrupoles, characterized, other things being equal, by significantly weaker emission of acoustic energy compared to emitters of monopole and dipole types, which indicates the realizable effects of its suppression due to the mutual antiphase compensation of the field generated by them (throat parts) sound pressures (see. FIGS. 25, 26 and 26a). The frequency setting of the effective functioning of the half-wave acoustic resonator R ^II (pos. 11) is carried out taking into account the specified known (determined by calculation or experimentally, or known according to the passport characteristics of the operating SHGTO 9, or known according to the requirements of the selected design specification or specified technical specifications production ShGTO 9) spectral acoustic characteristics ShGTO 9, mounted in the technical room 1, as well as known tnyh (measured) overall and geometric dimensional parameters of the inner air cavity 8 is known (detected) values of the operational air temperature in the technical room 1 (already exploited or projected).

The functioning of half-wave acoustic resonators R ^II (pos. 11), as technical devices for attenuation (suppression, damping) of acoustic energy in given narrow frequency ranges of the sound spectrum, is determined (characterized) by the corresponding discrete values of their own (resonant) oscillation frequencies f ^II _R and parametric Q-factors (determined by the width of the resonance characteristics of the amplitude responses generated by the frequency domain of the sound spectrum relative to the discrete value own (resonant) oscillation frequency f ^II _R ) specified used half-wave acoustic resonators R ^II (POS. 11). The Q parameter is equal to the ratio of the value of the natural (resonant) oscillation frequency f ^II _{R of a} half-wave acoustic resonator R ^II (pos. 11) to the width of the adjacent frequency band Δf _R , at the boundaries of which the acoustic energy with forced resonant oscillations is twice (3 dB) less acoustic energy at the resonant frequency f ^II _R. The Q-characteristic of a half-wave acoustic resonator R ^II (pos. 11) is determined (formed) by the amount of internal dissipative losses realized in it, arising both directly in the composite structures (elements) of the half-wave acoustic resonator R ^II (pos. 11), and by external energy losses, directly related to the process of sound emission into the environment, which also consumes the vibrational energy of a half-wave acoustic resonator R ^II (pos. 11). The operation, with frequency tuning on its own (resonant) oscillation frequency f ^II _{R of} half-wave acoustic resonators R ^II (pos. 11), is based on the corresponding wave (wavelength λ, phase ϕ) interaction with the resulting effect of compensatory suppression of the energy distributed in the elastic (air) medium of sound waves (λ _ms , f _ms ), emitted by ShGTO 9, coinciding (close in values) with the natural (resonant) frequencies f ^II _{R of} half-wave acoustic resonators R ^II (pos. 11). As is known, in general, the frequency f and the wavelength λ of sound vibrations are related to the speed from their propagation in an elastic (air) medium by the following known [4] relation (2)

where λ is the length of the sound wave, m;

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

с - speed of sound waves propagation (sound speed), m / s;

In turn, the speed of propagation of sound waves with in air is related to a known functional dependence [4] with the temperature state of this medium t ° C, according to the expression (3)

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

t ° C - air temperature in ° С

излучаемой ШГТО (поз. 9), помещающейся в габаритах пустотелой полости трубчатой части 28 полуволнового акустического резонатора R^II _ms (поз. 11) -

включающая его горловую часть 29 с вязкоприсоединенными к ней динамическими удлинениями на концевых частях геометрической длины трубчатой части 28 - l^II _rms на величину (0,2…0,6)d_пр (здесь d_пр - приведенный гидравлический диаметр, в м, произвольной геометрической формы проходного сечения трубчатой части 28 (для круглого проходного сечения d_пр=d_кр, где d_кр - диаметр круга) полуволнового акустического резонатора R^I _ms, поз. 11), характеризуемого физическим параметром динамическая длина l^II _Rms полуволнового акустического резонатора R^II _ms (поз. 11), удлиняющим его геометрическую длину l^II _rms на величину (0,2…0,6)d_пр, может быть представлена в виде соотношения (4):Thus, taking into account the known expressions (2) and (3), half the length of the sound wave

radiated SHGTO (pos. 9), located in the dimensions of the hollow cavity of the tubular part 28 of a half-wave acoustic resonator R ^II _ms (pos. 11) -

including its throat part 29 with dynamic elongations viscous to it on the end parts of the geometric length of the tubular part 28 - l ^II _rms by the value (0.2 ... 0.6) d _pr (here d _pr is the reduced hydraulic diameter, in m, arbitrary geometric forms of a flow section of the tubular part 28 (for a circular flow section d _ol = d _kr , where d _kr is the circle diameter) of a half-wave acoustic resonator R ^I _ms , pos. 11) characterized by a physical parameter dynamic length l ^II _{Rms of a} half-wave acoustic resonator R ^II _ms (pos. 11), lengthening conductive its geometrical length l ^II _rms value to (0,2 ... 0,6) d, _etc., may be represented as equation (4):

or

Taking into account expressions (6) and (7):

Where

π = 3.14;

S _t - the area of the bore, m ² , the tubular part 28 of a half-wave acoustic resonator R ^II _ms , pos. eleven,

geometrical length l ^II _{rms of a} half-wave acoustic resonator R ^II _ms , pos. 11, used at the design stage, can be determined from the known geometric and physical parameters under consideration according to the following expressions:

In final form, after transformations

Similarly (similar considerations), an expression can be represented to determine the geometric length l ^II _{rmA of a} half-wave acoustic resonator R ^II _mA (pos. 11), designed to suppress resonant sound radiation in technical room 1 caused by the excitation of its own acoustic modes of a mass-elastic body its three-dimensional air volume, characterized by the acoustic wavelength _{λ mA (λ mL, λ mB} , λ mH) at discrete values of the natural frequencies of sound vibrations _{f mA (f mL, f mB} , f mH), distributed in three-dimensional inner air cavity 8 technical room 1, in the direction of its dimension parameters A (L, B, H):

Thus, the choice of the range of variation of the value of the additionally viscous attached oscillating air mass to the oscillating air mass column bounded by the cavity of its tubular part (pos. 28) forms the specified value of the dynamic length l ^II _{R of the} half-wave acoustic resonator R ^II (pos. 11), which includes its geometrical length l ^II _r and attached to the open cuts of the throat portions (pos. 29) is the dynamic increment (0.2 ... 0.6) d _pr according to expression (6), which is predetermined as the given geometric shape used The cross section of the tubular part of the half-wave acoustic resonator R ^II (pos. 11) is round, elliptical, rectangular, trapezoidal, and possible mounting in the zone of the throat portions (pos. 29) of the half-wave acoustic resonator R ^II (pos. 11), other types of protective lining damping air-blown layers of materials (pos. 33), with overlapping bore section of the tubular part (pos. 28), which can be characterized by a wide range of variation of the values of resistance values of blowing by air flow (20 ... 500 ns / m ³ ), wake These are represented by various types of air-blown fabric materials (technical gauze, air-blown fibrous nonwoven cloths, micro-perforated polymer films or air-blown micro-perforated foil metal materials, differing in layer thicknesses of 0.025 ... 0.25 mm and surface density in the form of specific surface mass of 20 ... 300 g m ² ). As nonwoven fibrous webs, materials such as “marifliz”, “filts”, fiberglass, cloth based on super thin basalt fibers can be considered. Micro-perforated layers of air-blown polymeric film materials can be aluminized polyester, urethane, polyvinyl chloride, polyethylene terephthalate films. Micro-perforated metal layers of air-blown materials can be represented by steel, aluminum, copper, brass.

Reduce the sensitivity (reduce temperature dependence) of unregulated (non-tunable), characterized by ease of manufacture, structures of half-wave acoustic resonators R ^II (pos. 11), to ensure their sufficiently effective operation in some variable operating temperature Δt of the surrounding air environment, possibly by a corresponding change in the parametric characteristics of the "quality factor" half-wave acoustic resonators R ^II (POS. 11), with some allowable (acceptable) loss th muting efficiency in terms of suppressing the maximum amplitude level of acoustic energy (reducing the sound pressure level) at discrete values of natural (resonant) frequencies f ^II _R , while ensuring the expansion of the frequency range of its effective functioning. This, in particular, can be achieved by introducing into the resonating oscillatory (acoustic) system, containing half-wave acoustic resonators R ^II (pos. 11), the corresponding constructive-technological elements, which have additional dissipative losses, which additionally dissipate sound energy and, thus, provide the corresponding expansion of the frequency range of the achievable acceptable efficiency of half-wave acoustic resonators R ^II (pos. 11). In these cases, the expansion of the frequency range of efficiency implies a possible increase in the damped number of sound frequencies located (grouped) near the discrete value of the natural (resonant) frequency f ^II _R and, correspondingly, groupings of lengths λ ^II _R (half the lengths of λ ^II _R / 2) sound waves, stacked with their propagation in the cavity of the tubular part 28 and attached to it dynamic elongation, taken into account the dynamic length l ^II _R , half-wave acoustic resonator R ^II (pos. 11), with the realization achieved, interferential compensation effects of suppression (damping) of sound fields with weakening of acoustic energy, achieved in an already extended frequency range, taking into account the occurring (possible, acceptable) operational temperature changes acceptable for solving the technical problem.

If necessary (according to the technical requirements for design), a possible use of complementary or alternative use of technical devices can be considered (not excluded), for example, in the form of a typical automated temperature control system (climate control) of the air environment of a technical room 1 operating in an internal three-dimensional air cavity. 8, equipped with adjustable performance performance (discrete "on - off", or smoothly p adjust- able speed operation mode) elektroventilyatornoy (climate) installing ventilating cooling device (Fig. not shown). In this case, it can provide support for a given operating thermal mode of operation of ShGTO 9 in a narrower temperature range of the air environment Δt. This, accordingly, can additionally exclude (attenuate) the unacceptable frequency detuning of the effective frequency-tuned noise-suppressing operation of the used half-wave acoustic resonators R ^II (pos. 11), endowed with discrete (narrowband) frequency-tuned operation, with particular consideration for the change in sound wavelength λ ^II _R (one-half of the sound wavelengths λ ^II _R / 2), under given physical conditions and speeds of propagation of sound waves c (t) at steady-state air temperatures t ° C _st . This type of technical solutions in the inventive device are not considered.

As is known, technical rooms 1, wall enclosing structures of which are made in the form of rigid sound-reflecting elements, can also create problems of amplification of noise radiation generated by ShGTO 9 arising from the formation (excitation) of their own low-frequency acoustic resonances of their internal three-dimensional air cavities 8 (1). The generated (excited) own acoustic resonances of the internal three-dimensional air cavity 8 of the technical room 1 arising on its own x acoustic modes with frequencies of sound vibrations _{f mA (f mL, f mB} , f mH, wherein m = 1, 2, 3, ...) can also substantially enhance the resonant transfer of acoustic energy from the closed inner dimensional air cavity 8 technical room 1 in its console room or in other adjacent premises of the building (building), as well as in open space, with a corresponding increase in the degree of acoustic pollution of the environment (see the circuit in FIG. five). This even more actualizes the solution of the problem of applying appropriate technical means to eliminate (suppress, attenuate) this type of resonant amplification of acoustic radiation in noise-generating technical premises 1. Along with the physical process of resonant amplification of acoustic radiation in technical room 1, the development of the physical process can also take place beats interacting acoustic signals (sound waves) with close values of frequency of acoustic oscillations f _ms and f _mA, manifested in a de pulsating noise signal with the frequency of the rise and fall of the level equal to the difference values of sound vibrations interacting f _ms and frequencies f _mA. For the pronounced dominant low-frequency acoustic radiation range not exceeding 500 Hz (see Figs. 1–4) considered in the application materials, the resulting acoustic signal of these physical interactions, manifested as beats of acoustic signals, is perceived as sharply unpleasant by the subjective perceptions of human hearing. irritating effect of a pulsating low-frequency hum that worsens the psycho-physiological state of a person, which is a negative factor in ensuring sound th acoustic comfort and safety of the environment, including health and productivity of the staff (employees) 1 technical room.

In addition to the half-wave acoustic resonators R ^II _ms (pos. 11) tuned to the operating dominant functional frequencies f _{ms of the} sound spectra of acoustic radiation of ShGTO 9, samples of half-wave acoustic resonators R ^II can also be complementary or alternatively integrated into the structure of the single-shaped combined sound-absorbing panel 10 ( pos. 11) configured to suppress the acoustic radiation in other (different from the functional values of working frequency f _ms) frequency ranges of the audio spectrum, to Or they can also be formed by numerous other various sources of acoustic radiation that are part of the technical technical room 1. Such, in particular, can be noise-generating devices for ventilation cooling, as well as individual resonant amplifications of sound radiation arising on the own acoustic modes of the air volume of the internal three-dimensional air cavity 8 technical room 1 _{- f mA (f mL, f} mB, f mH), determined experimentally or by calculation according to expression Submission Form (1). These may include, in particular, low-frequency sound emissions generated by dynamically excited own structural vibrations, separate thin-walled metal hulls of the equipment or highly excitable thin-walled metal partition walls of the technical room 1, making an additional contribution to the total noise radiation of the multi-component sound field, which is formed as part of the claimed technical object. Suppression of resonant amplifications of sound radiation arising on the own acoustic modes of the air volume of the internal three-dimensional air cavity 8 of the technical room 1, with its own (resonant) frequencies f _mA (f _mL , f _mB , f _mH ), determined experimentally or by calculation, according to the expression ( 1) can also be carried out using separate, single-shaped, combined sound-absorbing panels 10 through the use of appropriately frequency-tuned half-wave acoustic resonators s R ^II _mA, physical and geometrical parameters are determined according to the expressions (4) ... (11). In these cases, the calculated value of the geometric length of a half-wave acoustic resonator R ^II _mA , designed to suppress the sound radiation generated in the excited natural acoustic modes of the internal three-dimensional air cavity 8 of the technical room 1, characterized by overall parameters A (L, B, H), with frequencies sound vibrations f _mA (f _mL , f _mB , f _mH ), determined according to expression (1), can be determined according to expression (11).

в которой осуществляется физический процесс встречного взаимного проникающего демпфирования энергии распространяющихся навстречу друг другу падающих (входящих) P_пад и выходящих P_вых звуковых волн с идентичными амплитудами звуковых давлений. Вторая пространственная зона сосредоточена вблизи (в зоне ближнего гидродинамического поля) открытых горловых частей 29, в которой осуществляется физический процесс противофазной компенсации полей давлений - падающих (входящих в трубчатую часть 28) - Р_пад и выходящих из трубчатой части 28 - Р_вых полуволнового акустического резонатора R^II (R^II _ms, R^II _mA) - поз. 11. На фиг. 26 указанные физические процессы схематично иллюстрируются для трех дискретных значений рабочих доминирующих функциональных частот звуковых колебаний, представленных тремя кратными низшими гармоническими составляющими спектра звукового излучения ШГТО 9 - f_1s, f_2s, f_3s. Средне- и высокочастотное поглощение звуковой энергии, генерируемой ШГТО 9, при этом схематично иллюстрируется стрелками (звуковыми волнами), проникающими в пористое звукопоглощающее вещество, представленное обособленными дробленными фрагментированными звукопоглощающими элементами 18, образующими твердую структуру обособленной цельноформованной комбинированной звукопоглощающей панели 10 (см. фиг. 22, 23, 24, 25, 27, 28, 29, 30, 31).FIG. 25 and 26 illustrative schematic representations of the mechanisms (physical processes) of selective selective absorption of the energy of propagated low-frequency sound waves by half-wave acoustic resonators R ^II (R ^II _ms , R ^II _mA ) - pos. 11, represented by curved hollow U-shaped hollow tubular parts 28 with closely-spaced (j≤0.068 m) open throat portions 29, which indicate the two reduced zones of frequency-tuned low-frequency acoustic energy. One zone is concentrated in the middle of the geometric length (I ^II _r ) or dynamic length (I ^II _R ) of a half-wave acoustic resonator R ^II (R ^II _ms , R ^II _mA ) - pos. 11, i.e. in the zone of a quarter wavelength localization

in which the physical process of the oncoming mutual penetrating damping of the energy of incident (incoming) P _pad and outgoing P _out sound waves with identical amplitudes of sound pressure is carried out. The second spatial zone is concentrated near (in the near hydrodynamic field zone) of open throat parts 29, in which the physical process of antiphase compensation of pressure fields — falling (entering the tubular part 28) —P _pad and going out of the tubular part 28 — P _out half-wave acoustic resonator is performed R ^II (R ^II _ms , R ^II _mA ) - pos. 11. In FIG. 26 these physical processes are schematically illustrated for the three discrete values of the operating dominant functional frequencies of sound vibrations, represented by the three multiple lower harmonic components of the sound emission spectrum of the ShGTO 9 - f _1s , f _2s , f _3s . The medium and high-frequency absorption of sound energy generated by the ShGTO 9 is schematically illustrated with arrows (sound waves) penetrating into the porous sound-absorbing substance, represented by detached crushed fragmented sound-absorbing elements 18, forming the solid structure of the detached whole-shaped combined sound-absorbing panel 10 (see FIG. 22, 23, 24, 25, 27, 28, 29, 30, 31).

The use of a curved U-shaped sound-transparent thin-film waveguide tubular channel in the form of a tubular part 28 of a half-wave acoustic resonator R ^II (pos. 11) makes it possible to realize, in this connection, the numerous physical principles of suppressing the propagation of sound energy generated by ShGTO (pos. 9). This allows you to implement a more effective resultant dissipative absorption of sound energy through the implementation of physical phenomena noted above in the description of the application, such as:

- arising diffraction of propagated sound waves in the marginal zones of the open throat parts (pos. 29) and longitudinal dividing partition 30 of the tubular 28 and throat 29 parts, with their deviating (bending) penetration (passage) in the opposite direction to the direct propagation of sound waves, with subsequent dissipative the dissipation of energy in the porous sound-absorbing structure of a substance composed of isolated crushed fragmented sound-absorbing elements 18 (see. 22, 23, 24, 27, 30);

- an additional increase in the counter surface area of the fall and, accordingly, dissipative absorption of sound energy, due to the introduction of tubular air cavities lined with a carrier internal air-blowing film elastic sound-transparent membrane 20 formed by a tubular part 28 of a half-wave acoustic resonator R ^II (pos. 11) into the porous sound-absorbing structure see fig. 25, 27;

- introduction of tubular air cavities, represented by tubular parts of 28 half-wave acoustic resonators R ^II (pos. 11), into the porous sound-absorbing structure of a separate, single-shaped combined sound-absorbing panel 10, contributes to a smoother (less discontinuous) matching of wave acoustic impedances in the zones of boundary separation of elastic layered media propagation of sound waves (air and solid porous crushed sound-absorbing substance, represented by separate crushers Fragmented sound-absorbing elements 18 enclosed in a closed internal cavity 31 formed by a carrier outer surface cladding sound-transparent shell 19 and a bearing inner air-tight film elastic sound-transparent sheath 20), in comparison with a flat surface variant of a typical flat sheet structure of an sound absorbing panel (not containing alternating body elements). dimples and intercavitary jumpers), which contributes to a quantitative reduction in A wave of reflected sound waves and an increase in sound-absorbing effect;

- reduction of dynamic stiffness (increase in dynamic compliance) of the used porous skeleton formed by the crushed sound-absorbing substance, due to the additional integration of hollow air cavities into the structures of a separate, fully-formed combined sound-absorbing panel 10 facilitates the process of acoustic energy dissipation (see Fig. 25, 27, 30);

- formation of structural-cavity acoustic anisotropy, with the realization of amplification of the physical process of dissipative dissipation of the energy of propagated sound waves, due to the sound-transparent introduction (connection) integrated into the three-dimensional structure of a separate whole-shaped combined sound-absorbing panel 10 half-wave acoustic resonators R ^II (pos. 11) see fig. 25, 27, 30, 11a, 11b, 11b, 12a, 12b, 12b, 13a, 13b, 14a, 14b, 15a, 15b, 16a, 16b, 17a, 17b, 18a, 18b, 19a;

- the formation of structural acoustic anisotropy with additional dissipative diffraction absorbed sound energy due to the additional introduction of a three-dimensional structure of porous crushed sound absorbing material isolated tselnoformovannoy combined acoustic panel 10 different types (different) solid-state vozduhoneproduvaemyh closed cell foam and / or dense, non-porous structures of the polymeric materials 23 (see FIG. 28);

- implementation of the physical effects of additional absorption of sound energy arising in narrow-gap air gaps formed between the opposite end parts of the mounted detached whole-shaped combined sound-absorbing panels 10, causing additional dissipative diffraction absorption of sound energy by the free edge zones of the porous sound-absorbing body and the body that is out the part of the body and the body that is outlined Fig. 29);

- implementation of the physical effects of enhancing the low-frequency absorption of sound energy from the introduction of predetermined air gaps between the back sides of the surfaces of the isolated all-shaped combined sound-absorbing panels 10 and the opposite acoustic surfaces of the enclosing wall structures (walls 2, ceiling 3), see FIG. 31;

укладывается в габаритных размерах динамической длины l^II _R полуволнового акустического резонатора R^II (поз. 11), как это имеет место в конструкции классического полуволнового акустического резонатора R^II (поз. 11), оборудованного трубчатой частью 28, представленной звукоизолирующей (звуконепрозрачной, звукооотражающей) твердотелой конструкцией, исключающей прохождение звуковых волн из ее полости в замкнутую внутреннюю полость 31, заполненной звукопоглощающим веществом.- the use of constructive-technological performance of the tubular channel of the tubular part 28 in the form of a sound-transparent thin-film element, represented as a half-wave acoustic resonator R ^II (pos. 11), allows physical processes not only anti-phase compensation of the amplitude-phase interactions of the incoming (P _pad ) to the throat portion 29 and out of them (P _O) of sound waves, but also simultaneously provide their passage from the hollow tubular cavity formed inside the carrier vozduhoneproduv film elastic sound-transparent casing 20, into the structure of a porous sound-absorbing substance located in a closed internal cavity 31 of an isolated whole-shaped combined sound-absorbing panel 10, represented by separate crushed fragmented sound-absorbing elements 18, with the implementation of the physical process of a wideband sound frequency dissipation sound pattern. selective selective absorption of low-frequency sound energy on discrete frequencies of sound waves, half the length of which

fits in the overall dimensions of the dynamic length l ^II _{R of a} half-wave acoustic resonator R ^II (pos. 11), as is the case in the design of the classical half-wave acoustic resonator R ^II (pos. 11), equipped with a tubular part 28, represented by acoustic insulation (sound-transparent, sound-reflective) solid construction, excluding the passage of sound waves from its cavity into a closed internal cavity 31, filled with sound-absorbing substance.

Direct sound waves propagated and penetrating into the structures of the composite sound-absorbing elements of a separate, single-shaped, combined sound-absorbing panel 10, falling on their facial sound-transparent surfaces and penetrating into porous air-producing sound-absorbing structures made up of separate crushed fragmented elements 18, are effectively dissipated, and there will be a way to be,), is altogether, there is to be too-active, so the pattern is altogether, there is a way, a blueprof is set,), is not too much; energy to warmth. This applies both to the microporous structures of detached crushed fragmented elements 18, and to interconnecting macroporous winding air channels and cavities formed between their loose (shameful) contact faces and edges. The process of dissipative absorption of sound energy includes, among other things, molded cavity capacitances formed by the carrier internal air-carrying film elastic sound-transparent shells of 20 half-wave acoustic resonators R ^II (pos. 11).

As illustrative examples of the actual need to suppress discrete low-frequency components that dominate the sound spectra of the working spaces of a technical room 1, presented in the form of working dominant functional frequencies f _ms , the corresponding results of experimental studies of sound fields of various types of technical rooms 1 are given. In particular, in FIG. 1-4 shows the experimental results of measuring the sound pressure spectra (FFT spectra, 1/3 octave spectra) emitted by various types of ShGTO 9 (a power electric transformer, an industrial fan, a piston compressor) placed in the corresponding technical rooms 1. The results of the indicated experimental studies indicate released in the presence of low-frequency spectra of identified dominant functional working frequency f _ms sound radiation investigated SHGTO 9 forming the sound ol technical room 1. In particular, measurements of the narrowband FFT-sound spectrum emitted ETPZT placed in the basement of the building construction industrial plant test center (see. FIG. 1) indicate evolved in the sound spectrum prevailing discrete functional operating frequency f _ms in the form of three low-frequency harmonic components of the sound pressure spectrum f _1s = 100 Hz, f _2s = 200 Hz, f _3s = 300 Hz, multiple frequency AC f _c = 50 Hz SHGTO 9 represented force elektrotransform torus. Ultrasonic sounding at registered discrete frequencies (f _1s , f _2s , f _3s ) exceeds by more than 20 dB (10 times in linear units of measurement) the levels of sound pressure (ultrasonic) of the remaining frequency components of the ETPZT sound radiation. Thus, this indicates their complete dominance both in the closed spatial sound field of the technical room 1, presented in the form of an ETPZT, and in the territory adjacent to it (due to the fact that the measuring microphone was located outside room 1 in the closed doorway area) and current the need to suppress them.

Measurements of 1/3 octave sound pressure spectrum emitted by a PLATTHAUS 3MK 260-1 type electric power transformer (Germany) with a microphone located in the technical room 1 of the test center of an industrial enterprise (see Fig. 2) were also recorded by the working dominant functional frequencies f _ms sound radiation SHGTO 9, subjectively perceived as a pronounced low-frequency "electric transformer rumble" power electric transformer with radiated sound frequencies: f _1s = 100 Hz, f _2s = 200 Hz, f _3s = 300 Hz (included in leaving the frequency band width centered at 315 Hz). Ultrasonic sounding at registered discrete frequencies (f _1s , f _2s , f _3s ) exceeds by more than 15 dB (5.6 times in linear units of measurement). Ultrasonic sounding of other frequency components of the presented sound pressure spectrum of the studied electric transformer, which also indicates their dominant contribution to the formation of the internal sound field of the technical room 1 with its negative impact on the environment.

The 1/3 octave sound spectrum emitted by the AXIPAL FTDA-050-3 industrial fan (Russia) mounted in the technical room 1, represented by the acoustic test laboratory room (see Fig. 3), identifies the two low-frequency spectral components the dominant functional frequencies of sound radiation of ShGTO 9, which manifest themselves in the form of a blade (blade) impeller rotation frequency f _1s = 50 Hz and a multiple harmonic f _2s = 100 Hz. Ultrasonic sounding at marked discrete frequencies (f _1s , f _2s ) by more than 25 dB (17.8 times - in linear units of measure) exceed the ultrasonic sounding of the medium and high frequency range of the studied spectrum of the sound radiation of the SHTO 9 under investigation. This allows to qualify the indicated frequencies f _1s and f _2s as pronounced dominant low-frequency sound emitters that form the sound field of a technical room 1.

The measurement results of a 1/3 octave sound spectrum emitted by a piston compressor produced by STAL (Sweden), mounted in the technical room 1 of the refrigeration compressor station of the testing center of an industrial enterprise, are shown in FIG. 4 also identify two pronounced discrete working dominant functional frequencies of sound radiation of ShGTO 9 - f _1s = 200 Hz and f _2s = 400 Hz. Ultrasonic sounding at registered discrete values of sound frequencies (f _1s , f _2s ) by more than 10 dB (3.16 times in linear units of measure) exceed the ultrasonic sound frequency of the other frequency components of the sound emission spectrum recorded in technical room 1 of the refrigeration compressor station under study .

), укладывающимися между противолежащими (оппозитно расположенными) жесткими звукоотражающими поверхностями стеновых 2 (а также пола 4 и потолка 3) ограждений технического помещения 1. Таким образом, указанные факторы актуализируют необходимость решения проблемы подавления звуковых излучений, производимыми ШГТО 9, как в подавляющем широкополосном звуковом диапазоне спектра, так и с первостепенной (исключительной) задачей уменьшения его доминирующих низкочастотных составляющих звукового спектра. В связи с этим, поставленные задачи могут быть эффективно решены использованием комбинированных технических устройств заглушения звуковой энергии, включающих как частотонастроенные элементы ее избирательного селективного заглушения, наделенные повышенной эффективностью в низкочастотном диапазоне, так и широкополосные шумозаглушающие устройства, приемлемо эффективные в средне- и высокочастотном звуковом диапазоне, которые представлены используемыми пористыми звукопоглощающими структурами акустических материалов и соответствующих звукопоглощающих конструкций. Следует указать, что футеровка ограждающих стеновых и потолочных конструкций технического помещения 1 обособленными цельноформованными комбинированными звукопоглощающими панелями 10, содержащими пористые звукопоглощающие вещества, будет дополнительно способствовать устранению выраженных полостных воздушных резонансов внутренней трехмерной воздушной полости 8 технического помещения 1, проявляющихся на собственных акустических модах, характеризуемых длинами звуковых волн λ_mA (полудлинами

), с собственными частотами звуковых колебаний f_mA (f_mL, f_mB, f_mH). В это же время, для усиления эффективности их подавления, в необходимых случаях, в составе обособленных цельноформованных комбинированных звукопоглощающих панелей 10 могут применяться заданные частотнонастроенные устройства избирательного селективного заглушения звукового излучения на выраженных дискретных спектральных составляющих (в виде предложенных к использованию полуволновых акустических резонаторов R^II _mA (поз. 11)), настроенных на заглушение акустической энергии на дискретных значениях собственных частот звуковых колебаний f_mA (f_mL, f_mB, f_mH), проявляющиеся на слабозадемпфированных собственных акустических модах массо-упругого тела воздушного объема, характеризуемых длинами звуковых волн λ_mA (λ_mL, λ_mB, λ_mH), формирующихся во внутренней трехмерной воздушной полости 8 технического помещения 1, и распространяющихся в направлении его габаритных параметров A (L, В, Н).Thus, as follows from the above results of the studies performed in FIG. 1-4, identified as discrete values, the working dominant functional frequencies of sound radiation f _{ms of} various types of the studied ShGTO 9 mounted in the corresponding technical rooms 1, differing overall dimensions L, B, H, are concentrated in the low-frequency region of the sound spectrum (50 ... 500 Hz ), sound wavelengths λ _ms which are in the meter range of sound frequencies. This, in turn, can contribute to their multiple frequency-wave resonance coincidence with the overall dimensions A (L, B, H) of the mass-elastic air volume of the internal three-dimensional air cavity 8 of the technical room 1, as well as being in meter ranges of measurements and characterized by the corresponding own acoustic modes with sound wavelengths λ _mA (half-lengths

) that fit between opposite (opposed) rigid sound-reflecting surfaces of wall 2 (as well as floor 4 and ceiling 3) fencing of a technical room 1. Thus, these factors make it necessary to solve the problem of suppressing sound radiation produced by ShGTO 9, as in the overwhelming broadband sound range of the spectrum, and with the primary (exceptional) task of reducing its dominant low-frequency components of the sound spectrum. In this regard, the tasks can be effectively solved using combined technical devices for muffling sound energy, including both frequency-tuned elements of its selective selective muffling, endowed with increased efficiency in the low-frequency range, and broadband noise suppressors, which are acceptably effective in the medium and high-frequency sound range which are represented by the used porous sound-absorbing structures of acoustic materials and the corresponding sound absorbing structures. It should be pointed out that the lining of the enclosing wall and ceiling structures of the technical room 1 with separate all-molded combined sound-absorbing panels 10 containing porous sound-absorbing substances will further help to eliminate pronounced cavitary air resonances of the internal three-dimensional air cavity 8 of the technical room 1, which appear on their own acoustic modes characterized by lengths sound waves λ _mA (half-length

), with own frequencies of sound vibrations f _mA (f _mL , f _mB , f _mH ). At the same time, to enhance the effectiveness of their suppression, where necessary, the specified frequency-tuned devices for selective selective damping of sound radiation on pronounced discrete spectral components (in the form of half-wave acoustic resonators R ^II _mA proposed for use) can be used as part of separate all-molded combined sound-absorbing panels 10. (pos. 11)), configured to mute the acoustic energy at discrete values of the natural frequencies of sound vibrations f _mA (f _mL , f _mB , f _mH ), which manifest themselves on weakly damped eigen acoustic modes of an air-mass-elastic body characterized by sound wavelengths λ _mA (λ _mL , λ _mB , λ _mH ), which are formed in the internal three-dimensional air cavity 8 of the technical premises 1, and extending in the direction of its overall parameters A (L, B, H).

As follows from the description, the technical device of a low-noise technical room presented as an invention is endowed with a broadband effect of sound absorption in terms of frequency composition, with a pronounced, increased efficiency, a selective and selective low-frequency effect of suppressing acoustic energy at discrete values of the operating dominant functional frequencies of sound radiation f _{ms of} various types of CTGT 9 mounted in the corresponding technical premises 1. In this case, generated by ShGTO 9 medium and high-frequency sound is suppressed by the use of the porous sound-absorbing structures used in the structure of the detached subdivided framed elements 18 of the isolated edge-shaped combined sound-absorbing panel 10. The sound-damping effects jet separate crushed fragmented elements 18 formed by air-blown porous sound-absorbing particles of recyclable materials, including the introduction of a certain dosed quantity, with its corresponding volumetric distribution of crushed fragments of dense air-blown elements of solid polymeric materials in a mixture with crushed fragments of porous air blowable sound-absorbing elements of solid polymeric materials. Physical processes of acoustic anisotropy formed by the hollow air cavities of the tubular parts of 28 half-wave acoustic resonators R ^II (pos. 11) integrated into the bulk structure of separate all-shaped combined sound-absorbing panels 10 are also included in the process of absorption of sound energy. Besides, diffraction dissipative absorption of sound energy it is realized in the marginal zones of the throat parts (pos. 29), including the longitudinal dividing wall 30 of the tubular 28 and the throat 29 parts and the edge zones of the end faces 32 of shamefully mounted separate integrally-formed combined sound-absorbing panels 10. The air gaps formed between the back sides of the surface of the isolated integrally-formed combined sound-absorbing panels 10 and opposite sound-reflecting surfaces of the enclosing wall structures (walls 2, ceiling 3) are also provided by the acoustic walls. sound absorption efficiency in the low-frequency sound range. The most effective resonant sound radiation at low frequencies forming on expressed in the sound spectra of discrete working dominant functional frequencies f _ms, generated SHGTO 9 dulled due integrated within the structure of the porous sound-absorbing material isolated tselnoformovannoy combined acoustic panel 10 chastotonastroennyh half-wave acoustic resonators R ^II _ms ( pos. 11), as illustrated graphically illustrated in FIG. 25, 26 and 26a.

The claimed technical solution in the form of the invention is not limited to specific design examples of its implementation, described in the text and shown in the attached diagrams. Some (insignificant) changes to the various constituent elements or structural materials from which these elements are made, or replacing them with technically equivalent ones that do not go beyond the scope of the claims indicated by the claims, remain possible.

Claims (30)

1. A low-noise technical room, characterized by the physical parameters of the sound and temperature field established in its internal three-dimensional air cavity and at least one noise-generating technical object operated in it, containing supporting enclosing elements in the form of the floor, walls and ceiling, on which are mounted separate sound-absorbing panels, composed of detached crushed fragmented sound-absorbing elements, as well as detached structures of half-wave mounted x acoustic resonators R ^II , while the noise-generating technical object in operation operates at a given steady-state high-speed operational mode of operation n _s accompanied by steady-state physical processes of radiation of sound and thermal energy, the spectral sound composition of which contains prominent discrete values of the working dominant functional sound frequencies f _ms characterized by corresponding sound wavelengths λ _ms , characterized in that the separate sound waves oschayuschie panel presented sheath design-technological performance, executed in the form of preferably rectangular cross section separate tselnoformovannyh combined sound-absorbing panels comprising a carrier vozduhoneproduvaemuyu or vozduhoproduvaemuyu exterior surface facing sound transmission casing, adhesively mating with bearing inner vozduhoneproduvaemoy film flexible sound transmission shell, forming a closed inner cavity consisting of isolated This single-molded combined sound-absorbing panel, filled with detached crushed fragmented sound-absorbing elements, while carrying internal air-blowing film elastic sound-transparent sheath made in the form of at least one curved hollow U-shaped tubular profile of the abdominal acoustic-transparent element of a certain size of the overall dimensions of a hollowed acoustic-transparent element, a certain size of the overall size of the hollowed acoustic U-shaped tubular profile of the abdominal translucent element, a certain size of the overall size of the abdominal transparent, transparent, transparent throat parts, forming a half-wave acoustic resonator R ^II _ms , own The resonant frequency of which f _Rms coincides with at least one of the discrete values of the working dominant functional frequencies of the sound radiation of at least one noise-generating technical object f _ms characterized by the corresponding sound wave length λ _ms determined by the physical parameters of the temperature and sound field established in the internal three-dimensional air cavity of the technical room (s, t ° C). 2. Low-noise technical room under item 1, characterized in that the overall dimensions of the tubular part of the half-wave acoustic resonator R ^II _ms , characterized by its geometric length l ^II _rms , determining its frequency setting suppressing the sound radiation of given discrete values of the working dominant functional frequencies f _ms , with corresponding sound wavelengths λ _ms , is determined from the expression

, where d _ol - reduced hydraulic diameter of the bore of the tubular part of the used half-wave acoustic resonator R ^II _ms , m; f _ms - discrete value of a given dominant functional frequency of sound radiation of a noise-generating technical object, Hz (s ^-1 ); t ° C is the air temperature established in the internal three-dimensional air cavity of the technical room, ° C. 3. Low-noise technical room under item 1, characterized in that the overall dimensions of the tubular part of a half-wave acoustic resonator R ^II _mA , characterized by its geometric length l ^II _rmA , determining its frequency setting suppression of resonant sound radiation excited by its own acoustic modes of a mass-elastic body air volume of an internal three-dimensional air cavity of a technical room of overall dimensions A (L, B, H), characterized by sound wavelengths λ _mA (λ _mL , λ _mB , λ _mH ) with discrete values eigenfrequencies of sound vibrations f _mA (f _mL , f _mB , f _mH ) are determined from the expression

, where d _ol - reduced hydraulic diameter of the bore of the tubular part of the used half-wave acoustic resonator R ^II _mA , m; t ° C is the air temperature in the internal three-dimensional air cavity of the technical room, ° C; λ _mA (λ _mL , λ _mB , λ _mH ) are the sound wavelengths of the lowest natural acoustic modes, represented by the intrinsic acoustic oscillations of the mass-elastic body of the air volume of the internal three-dimensional air cavity of the technical room, m; f _mA (f _mL , f _mB , f _mH ) - discrete values of the natural frequencies of sound vibrations on the natural acoustic modes of a mass-elastic body of air volume, characterized by sound wave lengths λ _mA (λ _mL , λ _mB , λ _mH ), formed in the internal three-dimensional air cavity technical room, Hz (s ^-1 ); A (L, B, H) - overall dimensions of the internal three-dimensional air cavity of the technical room, m. 4. The low-noise technical room according to claim 1, characterized in that the shortest distance j in m formed between the flow sections in the plane of the open sections of the throat part of each individual half-wave acoustic resonator R ^II _ms , made in the form of a bent hollow U-shaped tubular profile does not exceed the value of 0.068 m; 5. The low-noise technical room according to claim 1, characterized in that the throat parts of the half-wave acoustic resonators R ^II _ms are placed on the end faces of the separate, fully-formed combined sound-absorbing panels. 6. Low-noise technical room according to claim 1, characterized in that on the open throat parts of the half-wave acoustic resonator R ^II _ms a protective lining damping air-blown layer of material, which is characterized by ranges of values of blow resistance by air flow, equal to 20 ... 500 N⋅s / cm ³ , with a layer thickness of 0.025 ... 0.25 mm and a specific surface weight of 20 ... 300 g / m ² . 7. The low-noise technical room according to claim 1, characterized in that, on the side of the front surfaces of the faces of the isolated all-molded combined sound-absorbing panels, the acoustic-transparent facing protective-decorative perforated panels are additionally mounted, whose perforation coefficient corresponds to the expression K _perf ≥ 0.25. 8. The low-noise technical room according to claim 1, characterized in that the separate, single-shaped, combined sound-absorbing panels are fixed to the supporting enclosing elements of the walls and ceiling with corresponding fastening elements, represented by remote mechanical fastening elements, or suspension cable elements, or mounting studs, or mounting frames, either by mounting resilient elements, or mounting profiles. 9. The low noise technical room according to Claim. 1, characterized in that the sound transmission adhesive coating the mating surfaces of components separate tselnoformovannoy combined acoustic panel presented thermofusible adhesive filaments and / or pulverulent hot melt adhesive and / or a sticky adhesive layer adhesive, and / or continuous or perforated layer of thermoactive adhesive film substance. 10. Low-noise technical room according to claim 1, characterized in that the bearing outer surface facing sound-transparent sheath is made of micro-perforated, with perforation holes with a diameter not exceeding 1 mm, of a foil material - aluminum, copper, brass, or from a continuous layer of air blowing fabric (non-woven cloth) construction material such as "mallfliz", "filts", fiberglass, basalt fiber fabric. 11. Low-noise technical room according to claim 1, characterized in that the carrier inner air-blowing film elastic sound-transparent membrane forming the tubular part of the half-wave acoustic resonators R ^II _ms is made of the corresponding polymeric materials - polyethylene terephthalate, polyvinyl chloride, aluminized polyester, urethane, with a thickness of 0 , 01 ... 0.1 mm with a specific surface weight of 20 ... 70 g / m ² . 12. Low-noise technical room under item 1, characterized in that the isolated crushed fragmented elements are made of solid recyclable, mainly polymeric, waste, presented in the form of sound-absorbing structures of parts and assemblies dismantled from recyclable technical objects, mainly parts, technologically processed by mechanical crushing. noise insulation packages of vehicles that have completed their life cycle, and / or from technological waste and rejects of production kopogloschayuschih materials and products made from these parts and assemblies. 13. Low-noise technical room according to claim 1, characterized in that the formed narrow-gap air gaps γ installed between the opposite end faces of the isolated integrally formed combined sound-absorbing panels mounted on the supporting enclosing elements of the walls and ceiling do not exceed the values indicated in the expression γ≤0,25h, where h is the overall thickness of the opposite end faces of the isolated all-shaped combined sound-absorbing panels. 14. The low-noise technical room according to claim 7, characterized in that the sound-proof facing protective and decorative perforated panels are made of the corresponding metallic or polymeric material - steel, aluminum, polypropylene, polyamide. 15. The low-noise technical room according to claim 1, characterized in that the supporting outer surface cladding sound-transparent shells of the isolated all-shaped combined sound-absorbing panels are made of a layer of structural material with a thickness of 0.025 ... 0.25 mm and a specific surface weight of 20 ... 300 g / m ² , presented air-blown polymer film, metal foil or made of air-blown layer of fabric, nonwoven fabric, micro-perforated polymer film, micro-perforated metal netocrystalline foil resistance which is blowing air flow in the range of 20 ... 500 N⋅s / m ^3. 16. The low-noise technical room according to claim 1, characterized in that the longitudinal dividing partition of the tubular and throat parts formed as part of a half-wave acoustic resonator R ^II _ms is represented by the structure of a porous sound-absorbing substance made up of fragmented crushed fragmented sound-absorbing elements. 17. The low-noise technical room according to claim 1, characterized in that the material formed in the half-wave acoustic resonator R ^II _{ms of the} longitudinal partition of the tubular and throat parts is represented by the structure of a dense air-conductive acoustic reflecting substance. 18. A low noise technical room according to Claim. 1, characterized in that in the inner closed space isolated tselnoformovannoy combined acoustic panel filled with crushed fragmented distinct sound-absorbing elements contained metered quantity of crushed-fragmented vozduhoneproduvaemyh closed cell foam and / or solid non-porous polymeric materials structures occupying no more than 30% of the cavity volume of the internal closed cavity of an isolated whole-molded bone combined sound-absorbing panel.

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