RU2715727C1 - Low-noise technical room - Google Patents

Abstract

FIELD: construction.

SUBSTANCE: technical device is presented in the form of low-noise technical room equipped with mounted with air gaps between opposite end faces (γ) and relatively opposite mounting surfaces of wall and ceiling enclosing structures (k) of the technical room, separated by integral moulded composite sound-absorbing panels made of a porous air-defrosting sound-absorbing structure of the substance, lined with a sound-transparent layer of material, and integrated in it cavitary frequency-tuned noise-cancelling structural elements, presented in the form of low-frequency acoustic resonators Helmholtz R^III. Cavities of throat and chamber parts of Helmholtz R^III acoustic resonators are formed by bearing inner air-proof film elastic soundproof shell. Throat portion of the Helmholtz R ^III acoustic resonators can also be made from a solid air-insulated sound-insulating polymer material structure in the form of a hollow tubular element. Throat parts of the Helmholtz R^III acoustic resonators are placed on end faces of separate shaped-piece combined sound-absorbing panels. Technical device of low-noise technical room is endowed with broadband frequency composition sound absorption due to use of porous air-borne sound-absorbing structures of structural materials. At the same time, the high-frequency selective low-frequency suppression of sound energy is carried out on the discrete values of the dominant functional frequencies of sound radiation f_ms of the noise generating technical equipment, which are mounted in the technical room, which are released in the sound spectrum, which is realized using low-frequency acoustic resonators of Helmholtz R^III _ms. Similarly, selective frequency-tuned effect of acoustic absorption of acoustic resonators of Helmholtz R^III extends to suppression of arising resonant amplification of sound radiation by excited own acoustic modes of mass-elastic body of air volume of internal three-dimensional cavity of technical room, characterized by frequencies of acoustic oscillations f_mA and lengths of sound waves λ_mA , using corresponding low-frequency acoustic resonators of Helmholtz R^III _mA.

EFFECT: low-noise technical room is disclosed.

8 cl, 31 dwg

Description

The invention relates to the field of technical means to ensure acoustic safety of the environment by suppressing (reducing) negative (spurious) noise emissions produced by production, technological and engineering equipment, presented, in particular, pumping, compressor stations, power plants (internal combustion engines , diesel generator sets), ventilation and air conditioning systems, electric machines (electric motors, electric traction nsformatorami) mounted inside shumogeneriruyuschih (shumoaktivnyh) technical facilities (construction of buildings). It can also be used to improve acoustic comfort in the spatial zones of adjacent residential, industrial and public premises of buildings and structures integrated (adjacent, closely spaced) with the indicated noise-generating technical rooms (construction buildings).

It is known that in order to protect the environment from intense acoustic pollution (high noise levels) produced by various types of noise-generating technical objects, various types of soundproofing (noise-insulating) fencing of noisy technical rooms (screen partitions, casings, panel linings of bearing and / or cabinet are widely used) constructions) 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 purposes, 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 ) can be used. Volumetric expansion chambers connected to 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, characterized by sharp changes ( differences) of wave acoustic impedances. In the vast majority of cases, a variety of combined combinations of the above types of sound-damping (noise-reducing) methods and technical devices for their implementation are used, and their specific choice is determined by both technical and economic factors. The use of such a wide diverse type of noise-suppressing techniques (methods), technical devices and substances (materials) for their implementation, allows one way or another to provide an acoustically safe noise-comfortable living environment for people and animals. In particular, various types of hybrid noise-reducing structures are widely used, using the combined implementation of the physical processes of sound absorption and sound insulation, when the total noise-reducing effect of the technical device used can be based both on the effects of reflection of sound energy and on the combined combination of sound absorption and sound reflection effects. This type of technical sound-damping devices may, in particular, not contain porous air-blown sound-absorbing or air-blown sound-insulating structures of materials, and the arising sound attenuation effect can be realized solely by the operation of individual frequency-tuned acoustic resonator elements (quarter-wave R ^I , half-wave R ^II , Helmholtz R ^{II 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 resonant sound damping device can be either hollow or partially filled with a porous sound-absorbing substance.

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

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

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

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

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

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

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

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

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

- Japanese application for invention JP 2007-186186 (published on July 26, 2007);

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

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

The expressed useful advantages of using the above technical devices for damping acoustic energy include the possibility of their use, including under conditions of exposure to aggressive environments, high temperatures and intense dynamic loads, due to the exclusion of the use of their composition of porous air-blown (gas-blown) fibrous and / or foamed open-cell structures of organic or synthetic origin characterized, as a rule, by insufficiently high thermal o-biological stability characteristics. They use exclusively dense structures of perforated metal or heat-resistant polymeric materials, with the possible inclusion of heat-resistant porous fibrous (basalt, glass, metal), and / or foamed open-cell metal, and / or ceramic materials. At the same time, the negative technical characteristics of this type of noise-attenuating devices include their narrow working frequency sound range of effective functioning, high sensitivity to frequency detuning and loss of sound-attenuating effect when the physical parameters of the propagation medium of sound waves are changed, if the noise attenuation effect is not high enough the necessary wide frequency range, high cost, poor overall performance and increased aterialoemkost. At the current level of technological development, these negative factors can limit their widespread distribution in the effective solution of urgent 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 formed cavities of which are completely or partially filled with a porous air-generated sound-absorbing substance of fibrous and / or open-cell foam type (organic, mineral, synthetic origin), characterized by higher sound-absorbing (noise-reducing) characteristics, but which are quite effective only in a limited area 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, as a rule, perforated and has a rather high perforation coefficient in excess of 0.2. This gives her the properties of acceptable sound transparency and ensures, in fact, unhindered (with an insignificant, not exceeding 10% sound reflection effect) passage of sound waves into a cavity filled with porous sound-absorbing material. Through, mainly round holes or narrow slotted grooves with bends are the most common type of perforation of this type of front wall of an acoustic panel. As examples of this type of known noise reduction technical devices, it should be noted:

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

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

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

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

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

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

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

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

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

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

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

- UK patent for invention GB 1579897 (published 03.06.1976);

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

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

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

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

The above-mentioned well-known noise-reducing technical devices, along with satisfactory acoustic characteristics achieved in the medium 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 (drop) in the wave acoustic resistance on a flat demarcation boundary (section ) elastic layered propagation media of sound waves in the considered zone of the air environment, adjacent to a solid plane-sheet layered structure, with different values of wave acoustic impedances, as part of the adjacent air environment, both in the form of a solid flat wall of a perforated front panel and a flat-sheet structure of a porous sound-absorbing substance. This causes not only a corresponding potential loss of sound-absorbing effect, but also the contained perforation holes distributed over the entire solid surface of the flat wall, also cause a certain loss of soundproofing (in particular, sound-reflecting) properties of the specified multilayer structure of the wall partition as a whole.

To increase the noise-reducing properties of this type of structure, by providing smoother (not abrupt, jerky) coordination of wave acoustic impedances along the propagation paths of sound waves in the boundary zones of separation of the elastic air medium of propagation of sound waves, including adjacent boundary contact zones of the external hard shell surface of the panel of the technical device 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 the invention RU 2249258 (published September 27, 2004);

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

- German application for invention DE 4237513 (published 07.11.1992);

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

- European patent for the invention EP 0253376 A2 (published on 01/20/1988);

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

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

The above noise-reducing constructions of technical devices are characterized, first of all, by a significant complication of their technological design and relatively high cost, when the sound insulating ability is not high enough (due to the presence of “sound-insulating dips” in separate sound frequency ranges of the damping characteristic of sound energy, due to the formation of their own “Parasitic” cavity airborne acoustic resonances), as well as forced concomitant knowing reduction (“crowding out”) of the applied noise-reducing 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 propagation of negative (“spurious”) sound energy generated by vibro-noise-active technical objects mounted in technical rooms associated with an increase in the proportion of absorbed sound energy is the implementation of a technical device directly perceiving incident sound waves, perforation holes with specified narrow technological tolerances for geometric sky forms and certain overall dimensions. This type of noise reducing technical devices are known from the following patent documents:

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

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

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

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

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

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

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

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

Known noise-reducing technical devices made in the form of composite nodal (modular) soundproof fencing, the structural elements of which combine several techniques (realized by several physical effects), borrowed from the above groups of well-known technical devices, allowing to varying degrees ( one or another frequency range, with one or another achieved sound-damping effect) to purposefully improve their acoustic properties. This type of combined hybrid noise reduction technical devices are described in the following patent documents:

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

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

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

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

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

The disadvantages of the noise-reducing technical devices presented above are their higher structural complexity and the technological complexity of manufacturing, while in some cases they are not high enough (specified by the requirements of the design specification) environmental and cost indicators. In particular, this refers to the realized potentials of further improving their sound-damping characteristics in the low-frequency range of sound frequencies, which is the most intense and most relevant in solving typical problems of reducing noise in machinery and equipment.

A technical solution is known according to the RF patent for invention No. 2465390, published on January 20, 2011, which describes the design of a soundproof fence made in the form of an autonomous noise-reducing screen containing load-bearing elements such as transverse struts and longitudinal profiles, as well as a corresponding type of sound-absorbing element, located in a cavity with a predetermined air gap between the rear sound-reflecting panel and the front sound-permeable panel perforated through holes. At the same time, said sound-absorbing element comprises a supporting base of sheet perforated or mesh type, fastened by mechanical fasteners to horizontal profiles and / or the base of the noise-reducing screen, lined with at least one of its sides, separate sound-absorbing panels representing a set of crushed fragments of porous fibrous or foamed open-cell sound-absorbing materials that are distributed in a certain way and fixedly mounted on the surface STI base substrate to form a corresponding clearances between them. At least from the location of the separate sound-absorbing panels, the surface of the sound-absorbing element is lined with a layer of a soundproof gas-impermeable film or fabric. The disadvantage of the known known technical solution is the limited possibility of its effective use, carried out not within closed limited volumes of technical rooms, but mainly in open spaces of the environment to ensure the protection of residential areas of settlements from the negative acoustic radiation propagating from noise-generating technical objects - vehicles and industrial equipment installed near zi automobile and railways, aerodromes, open sections of subway lines, test sites, noise-active construction and production sites, or any other spatially distributed sources of increased noise emissions that produce intense acoustic pollution of the environment. This necessitates, in particular, the need to use additional load-bearing and supporting elements (an autonomous foundation, supporting base, transverse struts and longitudinal profiles) as part of this type of soundproofing fence, which significantly complicates the problem of using this noise reduction structure, leading to an increase in its weight and overall parameters and cost. At the same time, the use of a supporting base in the form of a flat-sheet geometric shape, fixed in a vertical position on horizontal profiles or the base, complicates the process of subsequent placement of separate sound-absorbing panels, and also complicates the implementation of sound-insulating fencing of complex spatial geometric shape. A limited choice of overall dimensions and geometric shapes, physical and mechanical parameters, if necessary, compliance with the specified values of air gaps between individual samples of crushed fragments of separate sound-absorbing panels, determines the insufficiently effective absorption of sound energy, which is realized in a diffuse sound field of enclosed spaces and is noted in a narrowed working frequency the range characteristic only of spatially distributed local emitters of sound energy 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 design of soundproof fencing, made in the form of an autonomous noise-reducing screen (several composite structures, for subsequent placement inside the technical room, near its enclosing wall and ceiling structures), will significantly reduce (clutter) its useful working space, worsen the process of technological maintenance of the installed in him production, technological and engineering equipment.

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

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

[2] - GOST 31274-2004 (ISO 3741: 199) “Machine noise. Determination of sound power levels by sound pressure. Exact methods for reverb cameras. ”

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

The overall dimensions and geometric shapes of this type of measuring reverberation chamber, the ratios of its composite overall dimensions, and the physical characteristics of its wall structures that are being implemented allow us to a certain extent to exclude (partially weaken) the development of the physical process of forming in-phase resonant addition of half-lengths of sound waves (λ / 2) and multiples of them 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 us to partially exclude (weaken) the development of the physical process of the formation of a pronounced uneven spatial density of the intensity distribution of sound energy localized in a closed air cavity of the measuring reverberation chamber from the structure of the diffuse (reverberation) acoustic field of the internal air cavity of this type of technical room. This type of measuring reverberation chambers are of limited use and are mainly used in the field of acoustic research and measurement of the sound power of noise-generating technical objects, as well as evaluating the sound-absorbing characteristics of samples of acoustic materials. They are also used to study the sound-absorbing characteristics of full-scale structures of parts, components and systems of machines (their prototypes), performed in a diffuse (reverberation) sound field. The regulatory requirements given in [1, 2, 3] provide guidance on the relevant design principles for the design of measuring reverberation chambers, imposing requirements on the volume (overall dimensions) and geometric shape of its air cavity, the physical characteristics of the wall structures used, excluding (weakening) negative development of physical processes of the formation of resonantly expressed spatial zones of unequal distribution of sound energy intensity, as well as exceptions (weakened ii) the undesirable process of sound absorption produced by the enclosing surfaces of wall structures and the doorway of the measuring reverberation chamber. However, the alternative use of this type of original design of measuring reverberation chambers, as possible typical variant designs of low-noise technical rooms, with eliminated (attenuated) half-wave acoustic resonances, significantly complicates and increases the cost of the design of typical technical rooms intended for subsequent installation of noise-generating technical objects in them ( SHGTO) during their design, construction and subsequent operation. An obvious drawback of this type of technical premises, made in the form of measuring reverberation chambers, is also the unsatisfactory (incomplete and inconvenient to use) use of their useful working space, due to the non-parallel opposite surfaces of the wall fencing, floor and ceiling (ceiling) implemented in them. Moreover, in some cases, to ensure the required diffusion of the sound field (a uniform spatial density of sound pressure distribution over the room volume of the measuring reverberation chamber is realized), the use of the free working space of the room is complicated by the use of additional reflex screen elements mounted in it in the air cavity of the measuring reverberation chamber, additionally aligning the spatial density of the distribution of sound energy and in measuring the air cavity reverberation chamber due to the additional clutter undesirable its useful working space.

A technical solution is known according to the RF patent for invention No. 2579104, published on December 20, 2015, adopted as a PROTOTYPE, which presents a technical room equipped with soundproofing sewing made in the form of a soundproofing face plate and / or soundproofing molded non-flat panel, with an air gap mounted relatively the surface of the opposing 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 to suppress arising air acoustic voids in the formed air cavities, are appropriately fixed to the indicated soundproofing faceplates and / or supporting wall (ceiling) structures of the technical room resonances formed on their own transverse, longitudinal and altitudinal acoustic modes. Also, an additional function of partially suppressing the amplitude values of intrinsic acoustic resonances in air cavities formed between the opposite walls of the soundproofing front panel of the soundproofing sewing and the supporting wall (ceiling) structure of the technical room can be performed by separate briquetted sound-absorbing modules made up of crushed porous sound-absorbing substances, appropriately placed in specified spatial zones in stuffy cavities.

A disadvantage of the known technical solution presented in the prototype is the complexity of its technological design, as well as the high cost, the complexity of installation and maintenance, due primarily to the need for separate installation of various types of noise-canceling (sound-absorbing) structural elements (quarter-wave acoustic resonators R ^I and / or half-wave acoustic resonators R ^II ), and / or separate briquetted sound-absorbing modules using the appropriate their fasteners and a separate front panel. At the same time, the use of a flat-plate front panel as part of the considered technical solution causes a corresponding abrupt change (drop) in the wave acoustic resistance in the path of propagation of sound waves. In addition, it should be noted the insufficient (weak) use of the mechanism (physical effect) of edge diffraction absorption of sound energy, due to the small total perimeter of the edge zones being realized with a small number of used briquetted sound-absorbing modules, and / or the absence of through holes in the porous structure of the briquetted sound-absorbing modules (through channels), potentially capable of further enhancing the effect of diffraction absorption of the propagation energy of sound ovyh waves.

The inventive technical device "Low noise technical room" is aimed at eliminating the identified and analyzed disadvantages of analogues and prototype with respect to the relative simplicity of its technical implementation, acceptable manufacturability, environmental friendliness, cost and efficiency of operation, with the effect of expanding the frequency range of reducing the level of sound radiation, produced both by SHGTO itself, installed in the technical room, and aimed at exclusion (pre prevention) of the implementation of the development of physical processes of resonant interaction and the corresponding amplification of sound radiation levels, as well as the occurrence of a physical process of beats of interacting acoustic signals (sound waves) with close frequencies of sound vibrations produced by the SHGTO (several SHGTOs) located in it and the possible dynamic excitation of resonant acoustic vibrations of a mass-elastic body of an air volume enclosed in an internal three-dimensional airway of the technical room. The need to prevent the development of the physical process of beats of interacting acoustic signals (sound waves) with close values of the frequencies of sound vibrations is caused by the advisability of eliminating the resulting resulting pulsating noise signal with a rise and fall rate of its levels equal to the difference in the values of the interacting frequencies of sound vibrations. For the actual low-frequency sound 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 in the form of beats of acoustic signals, is perceived by the subjective perceptions of the human hearing as a sharp unpleasant annoying impact worsening 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 emissions at the dominant values of individual discrete frequency components f _ms , which stand out in the broadband spectra of sound pressures of various types of SHGTOs, which are operated (installed) as part of technical rooms, in particular, piston rooms ICE, mechanical gearboxes, rotors, fan units, electric generators, electric transformers, draft 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. Theory and practice of dealing with noise. - M .: Logos, 2010 .-- 424 p .;

[6] - V.B. Stupid. Noise reduction from power equipment. - M .: Publishing House MPEI, 2005. - 232 p .;

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

[8] - Combating noise in production. Directory. Ed. E.Ya. Yudina, Engineering, M., 1985, 400 pp .;

[9] - Reference for industrial noise control. Translation from English L.B. Scriabinoy and N.I. Shabanova, M., Mechanical Engineering, 1979, 447 p .;

[10] - Reference on technical acoustics. Ed. M. Hekla and H.A. Mueller. L., Shipbuilding, 1980, 440 p .;

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

[12] - M.I. Fesina, I.V. Deryabin, L.N. Gorina. Some results of experimental studies of the physical processes of generating beats of sound vibrations in closed air volumes of technical rooms. Collection of reports of the fourth international scientific and technical conference "Dynamics and vibroacoustics of machines": July 18-20, 2018 - Samara: SNIU, 2018. - P. 34-35.

Given the functioning constant (steady-state) speed and load modes of operation of the above-mentioned operating SHGTOs, the dominant discrete low-frequency components f _ms that are released in the broadband spectra of sound pressures are also unchanged (with constant values of the sound frequency f _ms ), as follows from the figures . 1, 2, 3, 4. This applies, in particular, to SHGTO represented by a power electric transformer, with distinguished 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 mains f _c = 50 Hz (see FIGS. 1 and 2). Similarly, this may relate to constant steady-state values of nominal rotational speeds n _s (f _ms ) of piston machine shafts (ICE, compressors, pumps), electric generators, mechanical or electric fans, mechanical gearboxes, as well as to periodic reciprocating unbalanced masses unbalanced forces and moments of the crank mechanisms of piston machines (see, in particular, Fig. 3 and Fig. 4). Sources (dynamic pathogens) of intense sound emissions from the indicated emitted dominant discrete components f _ms , with corresponding acoustic fields being generated, are, in particular, gas (air) pulsations in the processes of air intake into the piston engine cylinders, periodic dynamic air movements by the blades (blades) fan impellers, dynamic imbalances of rotating shafts, unbalanced forces and unbalanced moments of reciprocating moving pore masses 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 as a specific result (value) determined experimentally using appropriate recording and analyzing vibroacoustic equipment (as illustrated by the authors in Figs. 1, 2, 3 , 4), or are known in the form of a result (value) determined by calculation, taking into account the known initial data - a 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 fan, the number of teeth of the mating gear pairs of gear mesh at a known frequency of rotation of the gears, the frequency of the AC network), as determined, including from known, indicated above, information sources [4 ... 10].

The technical result of the claimed device in the form of an invention is to ensure (increase) the acoustic safety of the environment by improving the sound-absorbing (noise-reducing) characteristics of the technical device used, which are realized mainly in the current low-frequency sound range, with a concomitant decrease in broadband (medium and high frequency) in frequency the composition of sound radiation generated by SHGTO. The inventive technical device is represented by a low-noise technical room, equipped with technical means to effectively suppress, mainly low-frequency acoustic radiation generated by SHGTO, mounted in this technical room (Fig. 5 ... 7). These technical means (components of a technical device) are intended, first of all, to suppress sound radiation produced directly by SHGTO, as well as to exclude (prevent) the implementation of the development of physical processes of low-frequency resonant interaction and the subsequent resulting amplification of sound pressure levels, with the prevention of the occurrence of physical processes of beats of interacting acoustic signals (sound waves) that are reasonably close (commensurate the actual) values of sound pressure levels (SPL) and frequencies of sound vibrations f _ms produced by the SHGTO located in it (f _ms ) and realized by it by possible excitation of resonant dynamic "reactions - responses" on discrete values of the natural frequencies of sound vibrations (f _mA ) formed on their own acoustic modes of the mass-elastic body of the air volume of the internal three-dimensional air cavity of the technical room, in the direction of its overall parameters A (L, B, H). The technical result is achieved due to the appropriate application (installation with predetermined air gaps) on wall and ceiling fences and floors of the technical room of the corresponding structural and technological versions of separate integral molded sound-absorbing panels made of solid-state porous air-borne sound-absorbing substances characterized by porous air-blown monolithic and / or sound-absorbing structure in which are placed (integr Rowan) cavitary chastotonastroennye soundproof constructive elements shown in the form of a Helmholtz resonator R ^III (R ^III _ms and / or R ^III _mA) (see. FIGS. 8, 9, 10, 11a, 11b, 11c, 12, 13a, 13b, 14a, 14b, 15a, 15b, 16a, 16b, 17). At the same time, the throat parts of Helmholtz R ^III acoustic resonators are assembled exclusively on the end faces of separate integral molded combined sound-absorbing panels and can be made in separate types of designs in the form of plug-in tubular elements made of dense air-tight materials.

The achieved, in this case, effective decrease in the level of sound energy generated by SHGTO is realized in the extended frequency range of the sound spectrum, mainly in the low-frequency, but also covers medium and high-frequency sound radiation. This is due to the corresponding structural and technological combined combination and parallel effective functioning of the constituent technical elements of the claimed device, intended for selective frequency-tuned suppression of low-frequency sound energy (energy of propagated low-frequency sound waves) generated in the technical room on the amplified and dominant noise in the frequency spectra of noise / or weakly damped low-frequency acoustic resonances, as well as both sintering of the accompanying broadband dissipative absorption used in the composition of the technical device porous monolithic or crushed breathable sound-absorbing substance, medium and high frequency sound energy. The physical effect of absorbing sound energy in this case is based on realized selective frequency-tuned sound-canceling processes of a functioning acoustic oscillating system in the form of an Helmholtz acoustic resonator R ^III , excited by sound waves incident on it (into the open throat parts of R ^III ), which is selectively (selectively) and sufficiently effectively absorbs acoustic energy (converts it into thermal energy) emitted at sound frequencies close (coincident) to its own (resonant) hour OTE oscillation f ^III _R used in the composition separate tselnoformovannoy combined acoustic panel Helmholtz resonator R ^III. At the same time, in parallel, broadband (medium and high frequency) absorption of sound energy is carried out, produced directly by the substance of the porous monolithic or crushed air-blown sound-absorbing structure. In the physical process of absorbing sound energy, additional sound-absorbing surface zones formed by the free surfaces of the faces of each of the isolated crushed fragmented elements of the crushed porous sound-absorbing substance are also effectively included in the physical process. There is also a concomitant occurrence of additional mechanisms of intensification of the physical process of absorption of sound energy caused by realized diffractive dissipative losses that occur in the zones of edge face and edge sections of separate crushed fragmented sound-absorbing elements, when they travel and bend around them by sound waves along shaped, randomly distributed, communicating tortuous air channels formed by contact and / or clearance loose leaks legs and / or adhesively contacting mating faces of the ribs and separate crushed fragmented sound absorbing elements that occur along with implements typical physical absorption processes implemented by directly monolithic porous structures sound absorbing material each separate from the crushed fragmented sound-absorbing elements. In turn, hollow volume chamber cavities of Helmholtz R ^III acoustic resonators formed in porous structures of separate integral molded combined sound-absorbing panels, limited (formed) by translucent air-deflectable film-elastic elastic shells, contribute to the formation of an anisotropic acoustic structure as a part of a separate whole-forming combined amplifying sound-absorbing panel physical processes of dissipative absorption i of sound energy (see Fig. 11a, 11b, 11c, 12, 13a, 13b, 14a, 14b, 15a, 15b, 16a, 16b, 18). An additional edge diffraction dissipative absorption of sound energy also arises in the processes of propagation by the propagating sound waves of the perimetric zones of the open cavity parts of the acoustic Helmholtz resonators R ^III (as shown in Figs. 18, 21) and the free end faces of the separate integral molded combined sound-absorbing panels with their narrow-gap gap placement relative to each other (see diagrams in FIGS. 6, 7, 8, 9, 10, 20, 22).

The same physical phenomena (the formation of acoustic anisotropy that enhances the dissipative absorption of sound energy) can be facilitated by the deliberate additional introduction of a sound-absorbing substance composed of porous air-blown sound-absorbing materials represented by separate fragmented porous sound-absorbing elements corresponding in structural composition and geometric dimensions of crushed fragments made of dense (non-porous ) airborne polymeric substances (see Fig. 19). In this case, their predetermined limited quantitative dosage composition can be observed, with the necessary appropriate volumetric distribution in the resulting mixture of heterogeneous (porous and non-porous) crushed fragments. The mounting installation of separate integrally formed combined sound-absorbing panels with narrow-gap air gaps between opposite end parts causes the dissipative diffraction absorption of sound energy to be realized by the free edge zones of the porous sound-absorbing structure, when they are freely enveloped by propagated sound waves (see Fig. 20).

As a result of achieving higher resulting sound-absorbing effects, in some cases (if necessary), this allows to reduce the amount of porous sound-absorbing substance used, provided that the specified value (determined by the technical design or development specifications) for the required sound damping effect is satisfied. For similar reasons, it is possible (permissible) to use cheaper and at the same time more environmentally friendly initial semi-finished raw materials for obtaining sound-absorbing material (hereinafter - ZPM), produced, for example, from industrial and technological waste, industrial scrap, or from dismantled porous sound-absorbing structures of materials contained as a part of noise insulation packages of technical facilities that have completed their life cycle and have to be recycled. Ultimately, all this contributes to the improvement of the safety ecological characteristics of the claimed technical device (and the concomitant "improvement" of the environment), which is realized by reducing the amount of unproductively recyclable solid sound-absorbing substances, which are forced to undergo, including disposal processes (for example, in the form of dismantled noise-reducing packages, which are part of parts and nodes of automatic telephone exchanges that have completed their life cycle), which do not allow their direct energy ilizatsii by burning, due to the evolution of harmful and dangerous combustion products and / or destructive, including ozone (CO ₂ emissions). This even more actualizes the economic and environmental efficiency of the feasibility of using technical devices using recyclable waste as the initial raw material product, made in accordance with the claimed technical solution (invention). Also, in these cases, economical substitute resource and energy conservation of non-renewable hydrocarbon raw materials (oil, natural gas), in lesser amounts spent on the initial (initial) production of synthetic sound-absorbing materials from them, is more productively implemented.

As the initial semi-finished raw material used for the manufacture of isolated crushed fragmented sound-absorbing elements, products of secondary recycled recycling processing of technological waste and technological marriage of the production of fibrous, foamed open-mesh ZPM and / or technological waste and marriage of the production of various types of parts from ZPM can be used. Also, the initial semi-finished raw material includes already manufactured parts and assemblies (panels, upholstery, gaskets from porous ZPM), selected from the dismantled soundproofing packages of various technical objects such as noise-active vehicles (automobile, railway, aviation, tractors, combines, mobile communal and road-building equipment, etc.), and / or other noise generating units and systems of power plants (stationary ICE, stationary and mobile compressor installations, etc.), and / or used in various types of construction projects (soundproofing fibrous or foamed open-cell facing panels for wall linings, floors, elevator shafts, ventilation systems). Ultimately, this allows to reduce the resulting cost of the produced technical device and ensures the reduction of environmental pollution by already generated production wastes and accumulated unused products of utilization of acoustic materials. Thus, this helps to improve the environmental characteristics of the device, which are realized, among other things, by reducing the number of sound-absorbing substances to be compelled to be buried (for example, noise-reducing packages in the components of automatic telephone exchanges that have expired), which prevent their direct energy utilization by burning. To manage the simplification of the technological operations of mechanical crushing (cutting / cutting) and their subsequent volumetric distribution with the provision of a predetermined dosage according to the structural composition and weight and size parameters, in some cases as the initial semi-finished raw material used for the manufacture of separate whole-molded combined sound-absorbing panels of low noise technical rooms, produced “new” isolated crushed fragmenter can also be used Bathrooms sound-absorbing elements. The term “new” means crushed fragmented sound-absorbing elements made from “new” (not recyclable) raw materials, for example, from a semi-finished flat-sheet type (flat sheets or ZPM rolls). Combined mixtures can also be used, given in certain proportions of dosed 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 predetermined geometric shapes and dimensions made from the "new" initial semi-finished raw materials of porous production ZPM (sheet, roll). In a number of cases, this makes it possible to more flexibly control the final physical (acoustic) parameters of the formed mixed combined structural mass of sound-absorbing substances (acoustic, weight, density, stiffness, operational) carried out by introducing the “quantitative” new quantitative dosed additives in the required proportions into it. isolated crushed fragmented sound-absorbing elements characterized by narrower scatter fields of controlled acoustic parameters of pores sound absorbing substance. Thus, technological procedures can be implemented, to one degree or another, to the extent that improves the physical (acoustic) characteristics of the resulting structure of the separate integral molded combined sound-absorbing panels in the inventive low-noise technical room.

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

Analysis of known technical solutions in the art showed that the inventive low-noise technical room device has features that are not found in the known technical solutions, and their use in the claimed combination of features makes it possible to obtain a new technical result, therefore, the proposed technical solution has an inventive step in comparison with the current level of technology.

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

Features and advantages of the claimed invention will become apparent from the drawings and the following detailed description of the device, where:

- in FIG. Figure 1 shows the experimental results of measurements of the sound pressure spectrum (FFT spectrum) emitted by SHGTO 9, represented by a closed-type electric transformer substation (ETPZT) located in the technical room of the basement floor of the building of the test center 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 front door;

- in FIG. 2 shows the experimental results of measurements of the sound pressure spectrum (1/3 octave spectrum) emitted by SHGTO 9, presented by a 3MK 260-1 power transformer of the PLATTHAUS firm (Germany), located in the technical room of 1 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 case of the electric transformer, at a height of 1.2 m from the surface of the floor 4 of the technical room 1;

- in FIG. Figure 3 shows the experimental results of measurements of the sound pressure spectrum (1/3 of an octave spectrum) emitted by SHGTO 9, represented by an Axipal FTDA-050-3 industrial fan (Russia), mounted in technical room 1, represented by the premises of the acoustic testing laboratory of the testing center 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. Figure 4 shows the experimental results of measurements of the sound pressure spectrum (1/3 octave spectrum) emitted by SHGTO 9, presented by a STAL piston compressor (Sweden), mounted inside the technical room 1, represented by a compressor-refrigeration station of a test 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 of the compressor housing, at a height of 1.2 m from the floor surface 4 of the technical room 1;

- in FIG. 5 is a schematic illustration of the technical room 1, as well as the basic spatial directions and transmission paths of air and structural noise emitted by the SHGTO 9 mounted in a closed (closed) technical room 1. The arrows in FIG. 5 are indicated:

- in FIG. 6 shows an illustrative, specific example of a technical room 1 with a ShGTO 9 installed in it, presented in the form of a power electric transformer, with air gaps between opposite end faces on the enclosing wall (pos. 2) and ceiling 3 (not shown in Fig.) Ceilings separate integral molded combined sound-absorbing panels 10, with Helmholtz acoustic resonators R ^III _ms integrated into their porous structure (item 11), formed using not a real inner air-blown film elastic soundproof sheath 17, the neck parts (pos. 25) of which are arranged on the end faces 28 of the separate integral molded combined sound-absorbing panels 10;

- in FIG. 7 shows an illustrative example of a technical room 1 with a ShGTO 9 installed in it, presented in the form of a diesel generator set, with ceiling ceilings (pos. 2) and ceilings 3 (not shown), mounted on enclosing walls, with separate integral molded combined sound-absorbing panels 10 , with Helmholtz R ^III acoustic resonators integrated into their porous structure (pos. 11), formed using a carrier internal air-blown film elastic soundproof shell 17, the neck portions (key 25) of which are arranged on the end faces of 28 separate, integrally formed, combined sound-absorbing panels 10;

- in FIG. 8 schematically shows a fragment of the wall enclosing ceiling (pos. 2) of the technical room 1 with separate, integral molded combined sound-absorbing panels 10 mounted on its surface, installed with narrow-gap air distance clearances γ between their opposite end faces 28, in which the throat parts 25 of acoustic resonator G are arranged R ^III (item 11);

- in FIG. 9 schematically shows a fragment of a wall enclosing ceiling (pos. 2) of a technical room 1 with mounted separate integral molded combined sound-absorbing panels 10 installed with a remote air gap k relative to the wall surface (pos. 2);

- in FIG. 10 schematically shows a wall fencing (overlapping) 2 of the technical room 1 with the installation of separate integral molded combined sound-absorbing panels 10 with a given air distance clearance k relative to the opposite surface of the wall fencing (overlapping), pos. 2, while the lining of separate integral molded combined sound-absorbing panels 10 is additionally blocked by a sound-transparent facing protective and decorative perforated panel 21;

- in FIG. 11a, an example of a possible structural and technological embodiment of technical means for securing in a horizontal position separate detached integral formed sound-absorbing panels 10 by using appropriate suspension units mounted on the horizontal surface of the ceiling 3 of the technical room 1, made in the form of the corresponding type of remote mechanical fasteners 12;

- in FIG. 11b presents an example of a possible structural and technological embodiment of technical means for securing in a horizontal position separate detached integrally formed sound-absorbing panels 10 by using the corresponding 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 suspended cable elements 13 connected to an external carrier translucent sheath 16;

- in FIG. 11c, an example of a possible structural and technological embodiment of technical means for securing in a horizontal position separate detached integrally formed sound-absorbing panels 10 by using 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 suspended cable elements 13 connected to a reinforcing mortgage, is presented sound translucent element 20 separate integral molded combined oh sound absorbing panel 10;

- in FIG. 12a shows a longitudinal section of a separate, integral molded combined sound-absorbing panel 10, in the porous sound-absorbing structure of which is composed of separate crushed fragmented sound-absorbing elements 15 of the porous air-blown sound-absorbing substance 31, Helmholtz cavity resonators R ^III _ms (pos. 11) of circular cross section are integrated the use of a carrier inner air-blown film elastic soundproof shell 17;

- in FIG. 12b shows a side view of the end face of a separate integral molded combined sound-absorbing panel 10 from the neck side (key 25) of the Helmholtz acoustic resonator R ^III _ms (key 11), the chamber part 24 of which is made in the form of a circular cylinder; a separate, one-piece, combined sound-absorbing panel 10 is composed of two composite modules 23 connected by an adhesive coating 22 to mating surfaces;

- in FIG. 13a shows a longitudinal section of a separate, integrally molded combined sound-absorbing panel 10, in which the porous sound-absorbing structure is composed of the monolithic structure of foamed open-cell polyurethane foam and / or the whole-molded fibrous material of the porous air-blown sound-absorbing substance 31, cavity resonant cavity resonators ^III ( ^III ) are integrated. cross section formed using a carrier inner air-blown ple night elastic soundproof shell 17;

- in FIG. 13b shows a side view of the end face of a separate integral molded combined sound-absorbing panel 10 from the neck side (key 25) of the Helmholtz acoustic resonator R ^III (key 11), the hollow chamber part 24 of which is made in the form of a rectangular cylinder; a separate whole-molded combined sound-absorbing panel 10 is composed of two composite modules 23 connected by the mating surfaces of the monolithic structure of the porous air-blown sound-absorbing substance 31 with an adhesive coating 22;

- in FIG. 14a shows a longitudinal section of a separate, integrally molded combined sound-absorbing panel 10, in the porous sound-absorbing structure of which is composed of separate crushed fragmented sound-absorbing elements 15 of a porous air-blown sound-absorbing substance 31, molded cavity containers formed using a load-bearing inner air-tight, sound-absorbing film-elastomeric sheath are integrated Helmholtz resonators R ^III (pos. 11), from differing in frequency resonance tuning (parameter f ^III _R );

- in FIG. 14b shows a side view of the end face of a separate integral molded combined sound-absorbing panel 10 from the side of the neck portions (key 25) of the Helmholtz acoustic resonator R^III (item 11); a separate whole-molded combined sound-absorbing panel 10 is composed of two composite modules 23 connected by mating surfaces with an adhesive coating 22;

- in FIG. 15a shows a longitudinal section of a separate, integrally molded combined sound-absorbing panel 10, in the porous sound-absorbing structure of which is composed of separate crushed fragmented sound-absorbing elements of a porous air-blown sound-absorbing substance 31, molded cavity containers formed using a load-bearing inner air-tight, sound-absorbing transparent two-layer film membrane are integrated Helmholtz acoustic resonators R ^III (pos. 11), with about by the positive arrangement of open throat parts (pos. 25) located in opposite (opposite) end faces 28 of a separate integral molded combined sound-absorbing panel 10;

- in FIG. 15b shows a side view of the end face of a separate, integral molded combined sound-absorbing panel 10 from the neck side (key 25) of the Helmholtz acoustic resonator R ^III (key 11); a separate whole-molded combined sound-absorbing panel 10 is composed of two composite modules 23 connected by mating surfaces with an adhesive coating 22;

- in FIG. 16a shows a longitudinal section of a separate, integral molded combined sound-absorbing panel 10 mounted on the ceiling 3 of a technical room 1, in the porous structure of which vertically located Helmholtz cavity acoustic resonators R ^III (pos. 11) are formed, using a carrier internal air-blown film elastic soundproof sheath 17; open throat parts (pos. 25) of Helmholtz acoustic resonators R ^{III are} directed downward towards the floor of the technical room 1;

- in FIG. 16b shows a side view of the end face of a separate, integral molded combined sound-absorbing panel 10, which is formed of two composite modules 23 connected by an adhesive coating 22 to the mating surfaces;

- in FIG. 17 is a longitudinal sectional view of a separate, integral molded combined sound-absorbing panel 10, in which a porous air-blown sound-absorbing structure 31 of which is composed of separate fragmented fragmented sound-absorbing elements 15, molded cavity containers in the form of Helmholtz R ^III acoustic resonators (key 11) are integrated, chamber parts 24 of which are formed using a supporting internal air-blown film elastic soundproof sheath 17, and the neck portions 25 avleny as removable cavity of tubular elements 26 with different parameters _{h r1, h r2, h r3} , S r1, S r2, S r3, made of a dense sound-reflecting material;

- in FIG. Figure 18 shows a diagram of the implementation of the physical mechanisms of diffraction envelope and energy absorption of incident sound waves at the peripheral edge zones of the open throat parts (pos. 25, 26) of the Helmholtz R ^III acoustic resonator (pos. 11). The arrows in FIG. 18 is indicated:

Направление падающих, распространяемых на обособленную цельноформованную комбинированную звукопоглощающую панель (поз. 10), звуковых волн

Direction of sound waves incident on a separate, integrally formed combined sound-absorbing panel (item 10)

Направление дифракционных огибаний звуковыми волнами краевых периметрических зон горловых частей 25 акустических резонаторов Гельмгольца R^III (поз. 11);

The direction of the diffraction envelopes by sound waves of the edge perimetric zones of the throat parts of 25 Helmholtz acoustic resonators R ^III (pos. 11);

- in FIG. 19 is a diagram of a physical diffraction envelope mechanism with concomitant absorption of energy of sound waves propagating in a porous air-blown sound-absorbing structure of a substance 31 of a fragment of a closed inner cavity 27 of a separate integrally formed combined sound-absorbing panel 10 containing in this structure of a porous air-produced sound-absorbing substance 31, represented by isolated isolated fragmented fragmented elements 15 made s, including, from the sound reflecting vozduhoneproduvaemyh closed cell foam and / or dense, non-porous structure of polymer materials. The arrows in FIG. 19 is indicated by:

Направление падающих звуковых волн на обособленную цельноформованную комбинированную звукопоглощающую панель (поз. 10)

Direction of incident sound waves at a separate, all-molded combined sound-absorbing panel (item 10)

Направление дифракционных огибаний звуковыми волнами плотных воздухонепродуваемых звукоотражающих элементов 19, помещенных в структуру пористого воздухопродуваемого звукопоглощающего вещества 31, представленного в виде обособленных дробленных фрагментированных звукопоглощающих элементов 15, расположенных во внутренней полости 27;

The direction of the diffraction envelopes by sound waves of dense air-borne sound-reflecting elements 19, placed in the structure of a porous air-blown sound-absorbing substance 31, presented in the form of separate fragmented fragmented sound-absorbing elements 15 located in the inner cavity 27;

- in FIG. 20 shows a diagram of the implementation of the physical process of diffraction envelopes of propagated sound waves in narrow-gap air gaps formed by opposite edge (end, end) zones of end faces 28 porous sound-absorbing air-blowing structures of matter 31 separate integrally formed combined sound-absorbing panels 10, with the resulting accompanying dissipative irreversible with the resulting additional absorption of sound energy). The arrows in FIG. 20 is indicated:

Направление падающих звуковых волн на обособленные цельноформованные комбинированные звукопоглощающие панели (поз. 10)

Direction of incident sound waves at separate, fully formed, combined sound-absorbing panels (key 10)

Направление дифракционных огибаний распространяемыми звуковыми волнами узкощелевых воздушных зазоров краевых (концевых, торцевых) зонах (торцевых гранях 28) обособленных цельноформованных комбинированных звукопоглощающих панелей (поз. 10);

The direction of the diffraction envelopes by the propagated sound waves of narrow-gap air gaps in the edge (end, end) zones (end faces 28) of separate, integrally formed combined sound-absorbing panels (pos. 10);

- in FIG. 21 is a diagram of the implementation of the physical process of diffraction envelopes by sound waves of the edge perimeter sections of the throat parts (key 25) of Helmholtz acoustic resonators R ^III (key 11) integrated into the structure of the porous air-blown sound-absorbing substance 31, represented by separate fragmented fragmented sound-absorbing elements 15 contained in the composition of the separate integral molded combined sound-absorbing panels 10, with the accompanying dissipative e ergeticheskimi losses. The arrows in FIG. 21 is indicated:

Направление падающих звуковых волн на обособленные цельноформованные комбинированные звукопоглощающие панели (поз. 10)

Direction of incident sound waves at separate, fully formed, combined sound-absorbing panels (key 10)

Направление дифракционных огибаний звуковыми волнами краевых периметрических зон горловых частей (поз. 25) полостей акустических резонаторов Гельмгольца R^III _ms (поз. 11);

The direction of the diffraction envelopes by sound waves of the edge perimetric zones of the throat parts (pos. 25) of the cavities of Helmholtz acoustic resonators R ^III _ms (pos. 11);

- in FIG. 22 is a diagram of the mounting clearance (γ, k) layouts of the separate integral molded combined sound-absorbing panels 10 relative to the surface of the enclosing wall structure (item 2) of the technical room 1 (clearance k) and between the opposite end faces 28 of the separate integral molded combined sound-absorbing panels 10 (clearance γ) with schematic images of direct incidence of sound waves (solid arrows) and reflected incidence of sound waves (dashed arrows). The arrows in FIG. 22 is indicated:

Направление падающих (прямых и отраженных) звуковых волн на обособленные цельноформованные комбинированные звукопоглощающие панели (поз. 10)

Direction of incident (direct and reflected) sound waves to separate, integral molded, sound-absorbing panels (item 10)

Прямые падающие звуковые волны на обособленные цельноформованные комбинированные звукопоглощающие панели (поз. 10)

Direct incident sound waves onto separate, fully formed, combined sound-absorbing panels (key 10)

Отраженные звуковые волны от поверхности ограждающей стеновой конструкции (поз. 2) технического помещения;

Reflected sound waves from the surface of the enclosing wall structure (item 2) of the technical room;

- in FIG. 23 shows the results of measurements of the reverberation coefficient of sound absorption α _rev (in arb. Units) of the investigated prototypes of separate whole-molded combined sound-absorbing panels (pos. 10) made of a monolithic structure of a porous air-blown sound-absorbing substance (foamed open-cell polyurethane foam) - pos. 31, the outer front surfaces of which are lined with an elastic sound-transparent air-blown polyester aluminized film with a thickness of 0.012 mm, which form the supporting external surface sound-clad transparent sheaths 16, the internal internal air-blown film sound-transparent elastic sheaths 17 and the external surface protective sound-transparent cladding layer 18 of which are embedded into the bulk composition 18 chamber parts 24 and arranged on the end faces of 28 separate integral forms nnyh combined sound absorbing panels 10, the neck portion 25 of a Helmholtz resonator R ^III (pos. 11) in comparison with the monolithic model sample measurements similar procedures, made of a porous vozduhoproduvaemogo sound absorbing material 31 in the form of foamed open-cell polyurethane foam without integrated into its porous sound absorbing structure of acoustic resonators Helmholtz R ^III ;

в вариантах его беззазорного (k=0) и зазорного (k=300 мм) монтажа относительно поверхности пола малой реверберационной камеры «Кабина Альфа», а также в вариантах его фрагментированного дробления на 8 образцов идентичных габаритных размеров, с последующим беззазорным (γ=0) и зазорным (γ=10 мм) расположением противолежащих торцевых граней 28 образцов обособленных цельноформованных звукопоглощающих панелей 10. Буквенными позициями на фиг. 24 обозначено:- in FIG. 24 shows the results of comparative measurements of the reverberation coefficient of sound absorption α _rev (acc. Units) of the initial state of a prototype monolithic sample of a separate integrally formed panel 10, a porous air-generated sound-absorbing substance (pos. 31) of which is represented by a fully-formed fibrous porous air-generated sound-absorbing material, overall dimensions

in variants of its gapless (k = 0) and gap (k = 300 mm) mounting relative to the floor surface of the Cab Alfa small reverberation chamber, as well as in variants of its fragmented crushing into 8 samples of identical overall dimensions, followed by gapless (γ = 0 ) and the gap (γ = 10 mm) of the opposed end faces 28 of the samples of the separate, one-piece sound-absorbing panels 10. The letter positions in FIG. 24 is indicated:

a - a monolithic prototype of a separate, integrally molded combined sound-absorbing panel (pos. 10) is installed gaplessly on the floor surface of the Cab Alfa small reverberation chamber with open (non-soundproof) end faces; b - a monolithic prototype of a separate integral molded combined sound-absorbing panel (item 10) is mounted on a soundproof mounting platform with an air gap of k = 300 mm relative to the sound-reflecting surface of the floor of the Cab Alfa small reverberation chamber with open (non-soundproof) end faces; c - a monolithic prototype of a separate, integral molded combined sound-absorbing panel (pos. 10) is mounted on the sound-reflecting floor surface of the Cab Alfa small reverberation chamber with soundproof end faces; d - a monolithic prototype of a separate integral molded combined sound-absorbing panel (pos. 10) mounted on a soundproof mounting platform with an air gap of k = 300 mm relative to the sound-reflecting surface of the floor of the Cab Alfa small reverberation chamber with soundproof end faces; f - a monolithic prototype of a separate, integral molded combined sound-reflecting panel (item 10) is divided into 8 identical square fragments mounted with end-to-end inter-facet gaps relative to each other at a distance of γ = 10 mm and with air gaps of their rear surfaces relative to the floor of the small reverberation chamber “Cabin Alpha ”(end faces of 8 fragments of prototype samples are not soundproofed).

The digital positions in the figures shown 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 referred to as ceiling 3);

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

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

6 - the front door of the doorway 5 (hereinafter - the front 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, limited by the enclosing surfaces of the ceiling 3, floor 4, side walls 2 and the closed entrance door 6 (hereinafter - the internal three-dimensional air cavity 8);

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

10 - separate whole-molded combined sound-absorbing panel;

11 - Helmholtz acoustic resonators R ^III (R ^III _ms , R ^III _mA );

12 - remote mechanical fasteners;

13 - suspended cable elements;

14 - mounting profile (not shown in FIG.);

15 - separate fragmented fragmented sound-absorbing elements;

16 - bearing external surface cladding translucent sheath;

17 - carrier internal air-blown film elastic soundproof shell, forming the chamber 24 and the throat 25 of the Helmholtz acoustic resonator R ^III (R ^III _ms , R ^III _mA ), pos. eleven;

18 - external surface protective cladding translucent material layer;

19 - air-blown closed-cell foam and / or dense non-porous structures of polymeric materials;

20 - internal embedded soundproof reinforcing elements of the rod, mesh or plate-perforated types of a separate integrally formed combined sound-absorbing panel 10, (hereinafter referred to as internal embedded soundproof translucent reinforcing elements 20);

21 - soundproof facing protective and decorative perforated panel (k _perf ≥ 0.25);

22 - adhesive continuous layered (film) or intermittent (fibrous, powdery, perforated film) sound-transparent coating, represented by a correspondingly surface and / or volumetric distributed sticky adhesive or thermosetting hot-melt adhesive material (hereinafter referred to as adhesive coating 22);

23 - composite prefabricated modules of a stand-alone integrally formed combined sound-absorbing panel 10;

24 - chamber part of the Helmholtz acoustic resonator R ^III (pos. 11);

25 - throat portion of the Helmholtz acoustic resonator R ^III (pos. 11);

26 - removable cavity tube element formed by the neck portion 29 of the Helmholtz acoustic resonator R ^III (pos. 11);

27 - a closed internal cavity of a separate integrally formed combined sound-absorbing panel 10;

28 - end faces of a separate, integral molded combined sound-absorbing panel 10;

29 - protective lining damping air-blown layer of material overlapping the neck portion 25 of the Helmholtz acoustic resonator R ^III (pos. 11);

30 - narrow-gap air gaps formed between the opposite end faces 28 of the separate integral molded combined sound-absorbing panels 10 mounted on the supporting wall elements of the walls 2 and ceiling 3 of the technical room 1;

31 - porous air-generated sound-absorbing substance (separate crushed fragmented sound-absorbing elements, and / or monolithic mounting foamed open-cell polyurethane foam, and / or monolithic whole-molded fibrous material).

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

In - the overall width of the inner space of the inner three-dimensional air cavity 8 of the technical room 1;

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

R ^III - Helmholtz acoustic resonator;

R ^III _ms - Helmholtz acoustic resonator designed to damp the noise generated by SHGTO 9 produced by it at the working dominant functional frequencies of acoustic radiation f _ms ;

R ^III _1s - Helmholtz acoustic resonator designed to damp the noise generated by SHGTO 9 produced by it at the working dominant functional frequency of acoustic radiation f _1s ;

R ^III _2s - Helmholtz acoustic resonator designed to damp the noise generated by SHGTO 9 produced by it at the working dominant functional frequency of acoustic radiation f _2s ;

R ^III _3s - Helmholtz acoustic resonator designed to damp the noise generated by SHGTO 9 produced by it at the working dominant functional frequency of acoustic radiation f _3s ;

n _s is the specified (passport) steady-state operational mode of operation of SHGTO 9, characterized by the corresponding sound radiation containing in its spectrum the distinguished working dominant functional frequencies of sound vibrations f _ms , min ^-1 , s ^-1 ;

R ^III _mA - Helmholtz acoustic resonator designed to suppress resonant sound radiation generated in the internal three-dimensional air cavity 8 of the technical room 1, propagated in the direction of its overall parameter A (L, B, H), due to the dynamic excitation of its own acoustic mass-elastic acoustic modes bodies of the air volume of the technical room 1, with emerging wavelengths λ _mA (λ _mL , λ _mB , λ _mH ) at the corresponding discrete values of the natural frequencies of sound vibrations 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 vibrations in Hz, which are formed on the natural 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 the sound wavelengths λ _mA (λ _mL , λ _mB , λ _mH );

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

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

f _R is the intrinsic (resonant) frequency of sound vibrations in Hz of the acoustic resonator R;

f ^III _R is the intrinsic (resonant) frequency of sound vibrations in Hz of the Helmholtz acoustic resonator R ^III ;

f ^III _R1s , f ^III _R2s , f ^III _R3s , are the natural (resonant) frequencies of sound vibrations in Hz of Helmholtz acoustic resonators R ^III _1s , R ^III _R2s , R ^III _R3s (pos. 11), designed to damp noise (absorption of sound energy ) generated by SHGTO 9, produced by it on its first three 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 the spectrum of sound vibrations in Hz, at the boundaries of which the acoustic energy during stimulated resonant sound vibrations is half (3 dB) less than the acoustic energy at the discrete value of the resonant frequency of the sound vibrations of the acoustic resonator f _R ;

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

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

s (t ° С _st ) - the speed of sound waves in m / s, propagated in the air of the technical room 1 with the temperature regime of air established in it, in t ° C _ct ;

λ is the sound wavelength, m;

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

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

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

λ _mA (λ _mL , λ _mB , λ _mH ) - the lengths of sound waves in m, formed on the lower eigen acoustic modes, represented by the own acoustic vibrations of the mass-elastic body of the air volume of the internal three-dimensional air cavity 8 of the technical room 1;

t ° C - temperature of the medium (air), in deg. Celsius

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

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

V _k is the volume of the chamber portion 24 of the Helmholtz acoustic resonator 11, m ³ ;

k _p - conductivity of the neck portion 25 of the Helmholtz acoustic resonator 11, m;

S _g - the cross-sectional area of the neck portion 25 of the Helmholtz acoustic resonator 11, in m ² ;

d _g - the diameter of the circular passage section of the neck portion 25 of the Helmholtz acoustic resonator 11, m;

h _g - geometric (overall) length of the neck portion 25 of the Helmholtz acoustic resonator 11, m;

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

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

γ is the remote air gap between the opposing opposite surfaces of the end faces 28 of the separate integral molded combined sound-absorbing panels 10 mounted on the enclosing wall and ceiling floors (items 2, 3) of the technical room 1;

α _rev - reverberation coefficient of sound absorption (conventional units);

α _N - normal sound absorption coefficient (conventional units);

A _ekv is the area of equivalent sound absorption (m ² );

K _perf - perforation coefficient (conventional units);

ρ _f is the density in kg / m ^{3 of} filling with separate crushed fragmented sound-absorbing elements 15 of the porous air-blown sound-absorbing substance 31 of the closed inner cavity 27 of the separate integral molded combined sound-absorbing panel 10;

Terminological definitions used in the text of 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), designed for dissipative absorption (scattering, damping, antiphase compensation) of sound (acoustic) energy propagated in the gas-dynamic under consideration the (aerodynamic) system to which they are connected; the most efficient use of acoustic resonators R refers to the absorption of resonant sound vibrations released in the spectra of sound radiation of a gas-dynamic (aerodynamic) system.

Standing wave - the state of an elastic medium during the propagation of sound waves, in which the location of the maxima and minima of the elastic displacements of the oscillating particles of the medium does not change in time; it is formed as a result of the interference of two counterpropagating (antiphase directed) harmonic oscillations with identical frequencies; it is noted, in particular, in an enclosed space between the opposed rigid surfaces of the walls, as well as the floor and ceiling; it is recorded, in particular, at the frequencies of intrinsic half-wave acoustic resonances of intrinsic acoustic modes of the mass-elastic body of the air volume (cavity) of the technical room.

Diffraction of sound waves - a physical phenomenon associated with the deviation of sound waves from their straight-line propagation when interacting with an oncoming solid-body obstacle (located on the path of their propagation); the occurrence of the diffraction effect of sound absorption is due to the physical process of dissipating the energy of the sound wave on a solid (porous) obstacle with a finite value of the input acoustic resistance of the surface of a solid obstacle (porous fibrous or foamed open-cell structure); a new scattered sound wave formed by the diffraction process of propagation at the edges (faces) of a solid-state porous element of finite dimensions (forming an edge diffraction effect) causes an additional flow of sound energy directed (propagating) into the porous solid-state 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 closed volumes (technical rooms), limited by rigid sound-reflecting walls.

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

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

Equivalent sound absorption area (A _ekv ) is the estimated technical parameter of the sound-absorbing properties of flat-sheet samples of materials or full-scale non-planar volumetric sound-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 with 100% sound energy absorption ; in this case, the reverberation coefficient of sound absorption α _rev = 1,0 srvc quantitatively estimated in m ^{2 the} area of a flat-sheet sample having 100% absorption of sound energy.

Reverberation sound absorption coefficient (α _rev ) is the ratio of the energy of the diffuse sound field absorbed by the surface of the material sample under study (the full-scale part being studied) to the energy of the diffuse sound field incident on it; it is determined by the variable recorded reverberation time t _rev in the working cavity of the measuring reverberation chamber according to the results of placing the material sample under study (the full-scale part being studied) in its cavity.

Normal sound absorption coefficient (α _N ) - sound absorption coefficient of a small sample of material, determined by normal incidence of a sinusoidal sound wave on it; is determined by recording the localization of the amplitudes of the maximum and minimum values of the sound pressure of standing waves artificially created in an acoustic interferometer (Kundt tube), followed by calculation of the values at each frequency of the sound wave under study.

Sound transparency is a property of structural elements of structures (plates, shells, films, fabrics) that are in the path of propagation 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 direction propagation of sound waves from a radiation source); characterized by the coefficient of sound transmission through the structure, representing the ratio of the amplitudes of sound pressure in the wave that passed through the structure (P _CR ), to the sound pressure in the incident sound wave (P _pad ).

Wave interference is a physical process of adding two or more two waves having the same oscillation periods T in an unlimited space (or in a limited waveguide), as a result of which the amplitude value of the resulting wave increases or decreases in different zones of unlimited space (or a limited waveguide space) depending from the ratio of the phases of the oscillations ϕ of the folding (interacting) waves, thus forming the uneven spatial distribution of the amplitude as a result boiling waves.

The beating of sound (acoustic) vibrations is the result of the interference addition of two interacting harmonic sound vibrations with close (not exceeding 4 Hz) frequencies, manifested in the form of alternating increases and decreases in amplitude maxima and minima (sound pressure pulsations) recorded at a frequency equal to the frequency difference ( not exceeding 2 Hz) of interacting sound vibrations [12].

Glues, adhesives - compositions based on organic or inorganic substances capable of joining (gluing) various materials; their action is due to the formation of a strong adhesive bond between the adhesive layer and the joined surfaces; the strength of the adhesive joint is also affected by the cohesion of the adhesive layer and mating surfaces; The basis of organic adhesives are mainly synthetic oligomers and polymers (phenol-formaldehyde, epoxy, polyester resins, polyamides, polyurethanes, silicon-organic polymers, rubbers, etc.) that form the adhesive film as a result of hardening upon cooling (thermoplastic adhesives), curing ( thermoactive adhesives) or vulcanization (rubber adhesives); inorganic adhesives include aluminophosphate, ceramic, silicate, 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; disintegrate 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 products as part of paints or (and) are used in the form of solutions that impregnate the material; common flame retardants - aluminum hydroxide, boron compounds, antimony, chlorides, organic and inorganic phosphorus compounds.

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 it is perforated).

Sound-absorbing material - an acoustic material with a reverberation coefficient of sound absorption α _{rev of} at least 0.2.

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 dynamically connected and interacting with each other; the air pores formed between the surfaces of the fibers in such elastic structures of the fibrous materials have the form of narrow interconnected capillary channels; It is made on the basis of natural (cotton, silk, jute, sisal, linen, 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 foamed (spongy) material is a porous open-cell acoustic material, the elastically deformable skeleton of which is formed by technological foaming and subsequent polymerization of a solution of a polymeric material or by conducting an appropriate chemical reaction; foamed sound-absorbing materials are based on urethane, nitrile, vinyl, butadiene-styrene polymer compositions.

Sound-absorbing porous material is an acoustic material in which a solid substance occupies a part of the total volume, forming a spatial porous skeleton, and the remaining volume falls on 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 resilient air.

Crushed porous air-borne sound-absorbing substance is an original raw material (semi-finished) product of recycled recycling processing of acoustic materials, mainly porous, air-blown sound-absorbing fibrous and / or foamed open-cell materials contained in parts and assemblies that have completed their life cycle, as well as in production and technological marriage and waste products of the specified types of acoustic materials, used a second time as a source production 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 separate crushed fragmented sound-absorbing elements made from the indicated type of utilized raw materials are made of identical or different types and brands of porous sound-absorbing materials having identical or different physical characteristics, chemical composition, porosity, quantity and combination of types of structures of porous layers in the composition of one and / or multi-layer combinations, identical or different geometric shapes and overall dimensions, which are in front significantly in the linear overall range of 5 ... 100 mm, while the volume of each of the isolated fragmented fragmented sound-absorbing elements is in the range of 4.2 × (10 ^-9 ... 10 ^-2 ) m ³ .

Sound-transparent material (film, foil, microperforated, fabric, non-woven fabric) is a structural material, the installation of which on the surface of the porous sound-absorbing layer (by performing, including contact “technological stitching” of their mating surfaces) causes an acceptable drop in the reverberation sound absorption coefficient (α _rev ) no more than 10%; the provided sound transparency properties are substantially characterized by the selected respective values of the parameters of resistance to blowing by the air flow (fabric or microperforated film or microperforated foil layers), and / or the established values of thickness, bending stiffness and specific surface mass, determined by the mass of material per 1 m ^{2 of the} surface (continuous film or foil layers not blown by the air flow); the values of the resistance to blowing through the air stream of sound-transparent air-blown fabrics or air-blown non-woven fabrics (perforated polymer film or perforated foil metal layers) should be within 20 ... 500 ns / m ³ , with the thicknesses of the fibrous layer of fabric material, fibrous non-woven fabric, microperforated film polymer or microperforated foil metal layer constituting 0.025 ... 0.25 mm and their surface density of 20 ... 300 g / m ² ; values of 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; sound-transparent material can be made of various structural materials - polyethylene terephthalate, polyester aluminized, urethane, polyvinyl chloride films, or from a similar type of other polymeric materials acceptable for these purposes; the use of microperforated foil metal material involves the use of aluminum, copper, brass as a structural material; a continuous layer of an air-blown fabric (non-woven fabric) can be made of materials such as maliflis, filts, fiberglass, and fabrics based on superthin basalt fibers.

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

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

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

Waste is any substance or object that the owner throws away, or intends to throw away, or it is to be thrown away (according to the definition of Directive 75/442 of the 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 given distance; perforations - from the Latin perforato - punch, puncture - the technological process of making holes of specified sizes, located accordingly 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 given distance; the diameter of the round holes does not exceed 1 mm (≤0.001 m).

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

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

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

- частота колебаний, на которой имеет место явление резонанса (в данном случае, частота звука f на которой наблюдается акустический резонанс, характеризуемый существенным усилением амплитуд звукового давления).Natural (resonant) frequency

- the oscillation frequency at which the resonance phenomenon takes place (in this case, the sound frequency f at which acoustic resonance is observed, characterized by a significant amplification of the sound pressure amplitudes).

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

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

The sound (acoustic) field of the technical room is the resulting steady-state energy distribution of the incident and reflected sound waves, with the accompanying physical processes of its propagation, amplification and absorption in the three-dimensional cavity 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 expression (1), see [4]:

where c is the speed of propagation of sound waves in the air of the internal space of the internal three-dimensional air cavity 8 of the technical room 1, m / s (s = 344,057 m / s at + 20 ° C);

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

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

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

m _A - serial number of the own acoustic mode of sound vibrations of the mass-elastic body of the air volume of the internal three-dimensional air cavity 8 of the technical room 1, propagating in the direction of its overall parameter A (length L, width B, height H), expressed as an integer of the natural number (m _A = 1, 2, 3 ...);

The essential features of the claimed technical solution are also illustrated by figures 1 ... 24.

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

SHGTO 9 (for example, a reciprocating internal combustion engine, a mechanical reducer, a fan unit, an electric generator, a power electric transformer, a blowing machine, an axial or centrifugal type smoke exhaust, a piston or centrifugal pump, a piston compressor, or several engines operating in a technical room 1 of SHGTO 9 at the same time), operates given by the passport (given by the technical operating conditions) steady steady high-speed operational mode of operation 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 determine the specific physical parameters of the mass-elastic body of the air volume formed in it, characterized, in particular, by certain values of the lower intrinsic acoustic modes formed at 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 of the dynamic dynamic excitation process and the response dynamic vibrational reaction of an elastic air medium (mass-elastic body of an air volume) as a result of the propagation of sound waves in it, represented as natural acoustic vibrations of a mass-elastic body of an air volume enclosed inside an internal three-dimensional air cavity 8 of the technical room 1.

A distinctive feature of the claimed technical device, presented in the form of a low-noise technical room 1, is the corresponding equipment (lining of wall and ceiling structures) of the technical room 1, mounted with air gaps between opposing (opposite) end faces 28 and relatively opposing (opposite) mounting surfaces (walls 2 and the ceiling 3) of the technical room 1, separate integral molded combined sound-absorbing panels 10 (see. Fig. 6, 7, 8, 9, 10, 11b, 11c) made up of a porous air-blown sound-absorbing substance 31 (separate crushed fragmented sound-absorbing elements 15, and / or a monolithic mounting foamed open-cell polyurethane foam, and / or a monolithic whole-molded fibrous material) and integrated cavity-shaped cavity-shaped noise canceling elements in it Helmholtz acoustic resonators R ^III (pos. eleven).

The installation in the technical room 1 of separate integral molded combined sound-absorbing panels 10 can be carried out, in particular, by hanging them on the ceiling 3 using the appropriate type of remote mechanical fasteners 12 (see Fig. 11a), suspended cable elements 13 (see Fig. 11b and 11c), mounted on the walls 2 by means of a mounting profile 14 (not shown in FIG.), with the formation of vertically suspended volumetric absorbers of sound energy, as well as with a distance between to a separate integral molded combined sound-absorbing panel 10 and wall 2 of the technical room 1 (see Fig. 9, 10, 11a, 116, 11b). The remote air gap γ, which is formed between the opposite (opposite) end surfaces of the faces of 28 assembled samples of separate integral molded sound-absorbing panels 10, makes up no more than a quarter of the overall thickness (dimensions h) of the opposite end faces 28 of the separate separate integral molded sound-absorbing panels 10 ≤0.25h). The mounted separate integral molded combined sound-absorbing panels 10 may overlap with the additionally installed sound-transparent cladding protective and decorative perforated panel 21 (K _perf ≥ 0.25) that freely (without significant ≤ 10% reflection) transmits propagating sound waves in the direction of the mounted separate separate integral molded combined sound-absorbing panels 10, as shown in particular in FIG. 10. Sound-transparent facing protective and decorative perforated panel 21 can be mounted gaplessly to the surfaces of separate integral molded combined sound-absorbing panels 10 or with a predetermined air gap (non-contact). The permissible decrease in the reverberation coefficient of sound absorption α _rev from the installation of a sound-transparent facing protective and decorative perforated panel 21 should not exceed 0.1.

Installation of separate integral molded combined sound-absorbing panels 10 with a predetermined air gap k of their rear surfaces relative to the opposite sound-reflecting surfaces of the ceiling 3 or wall (walls 2) floors of the technical room 1, which are nearby (if this is not limited by the requirements of the technical specification for development), as presented on FIG. 9, 10, 11a, 11b, 11c, 22, allows to a certain degree to deliberately controllably influence the increase in the 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 amplification of the dissipative diffractive absorption of sound energy arising on free perimetric edges (end zones) of separate integral molded combined sound-absorbing panels 10 when they are diffractively enveloped by reflected sound waves (see Fig. 20, 2 2). Enveloped during its propagation and scattered in a porous air-produced sound-absorbing substance 31 on the free peripheral edges of each separate integral molded combined sound-absorbing panel 10, the sound wave, due to the realized edge diffraction effect and the accompanying dissipative absorption of its energy, is accompanied by the process of additional flow of sound energy from its face back porous surface. For the reflected sound wave from the surface of the wall or ceiling, a similar diffractive dissipative effect of the flow of sound energy from the back surface of the separate integrally formed combined sound-absorbing panel 10 to its front surface takes place, with its subsequent penetration into the porous air-produced sound-absorbing structure 31 of the separate whole-formed combined-shaped panel 10. This, in turn, leads to the corresponding additional ozhitelnomu effect resulting increase dissipative absorption of sound energy.

Each of the mounted, with given air gaps (γ, k), separate integrally formed combined sound-absorbing panels 10, can be considered as an autonomous volumetric sound-absorbing element, characterized according to the source [11] by significantly higher sound-absorbing characteristics (parameters α _rev , A _ekv ) in Compared to gaplessly mounted flat sound-absorbing panels made of identical surface area, mass, identical structure and physical characteristics of sound opogloschayuschego substances.

The separate integrally molded combined sound-absorbing panel 10, made in the form of an integrally molded three-dimensional shell structure, comprises, as a composite internal element, a supporting external surface sound-transparent, air-insensitive or air-blowing shell 16. A closed internal cavity 27, formed by a mating adhesive adhesive-insulated air-insulating, non-transparent, air-insulating shell 16 and inner air roduvaemoy film flexible sound transmission casing 17 formed in a chamber 24 and throat 25 portions Helmholtz resonator R ^III (pos. 11) composed of CDP tselnoformovannoy combined sound absorption of the panel 10, is filled with porous vozduhoproduvaemym sound absorbing monolithic type substance 31 or preferably formed distinct crushed fragmented sound-absorbing elements 15, with their gap-contacting ribs and faces, as a result of which many communicating the numerical additional winding and intercostal mezhgranevye vozduhoproduvaemye zvukorasprostranyaemye waveguide (zvukoperedayuschie) and respectively absorbing channels. This type of crushed sound-absorbing material used includes predominantly identical or different types, structures and brands of porous air-blown sound-absorbing materials, identical or different physical characteristics, chemical and structural composition, amount and combination of types of porous layers used in multilayer combinations of sound-absorbing materials, identical or different geometric shapes and dimensions, produced data from solid recyclable, mainly polymeric wastes, presented in the form of parts and assemblies dismantled from utilizable technical objects, technologically processed by mechanical crushing method of sound-absorbing structures, mainly parts of noise insulation packages of vehicles that have completed their life cycle, and / or from technological wastes and production defects sound-absorbing materials and parts and assemblies made from them. The specified closed internal cavity 27 of a separate integral molded combined sound-absorbing panel 10, by means of a bearing internal air-blown film elastic sound-transparent shell 17 communicates with attached cavity hollow molded sound-absorbing (noise-canceling) structural elements (at least one cavity hollow-shaped element) in the form of Helmholtz acoustic resonators R ^III (pos. 11). The throat 25 and chamber 24 parts of these Helmholtz acoustic resonators R ^III (pos. 11) are formed using a supporting internal air-blown film elastic soundproof shell 17 (see Figs. 11a, 11b, 11c, 12a, 12b, 13a, 13b, 14a, 14b , 15a, 15b, 16a, 16b), lining inside the surface of the faces (edges) of edges and edges of separate crushed fragmented sound-absorbing elements 15 located in a closed inner cavity 27 of a separate integral molded combined sound-absorbing panel 10. Gore the rear part 25 of Helmholtz acoustic resonators R ^III (pos. 11) can also be formed (formed) by an insertable removable hollow tubular element (pos. 26) made of a rigid dense (solid) material structure (mainly from a polymeric material) of specified length dimensions (h _g ) and the passage area (S _g ) attached to the air cavity of the chamber portion 24, as shown in FIG. 17.

The closed inner cavity 27 of the separate integral molded combined sound-absorbing panel 10 is filled with porous air-generated sound-absorbing substance 31 (separate crushed fragmented sound-absorbing elements 15, and / or monolithic foamed open-cell polyurethane foam, and / or monolithic integral molded fibrous material). It is preferable, in this case, from a technical, environmental and economic point of view, filling it with separate crushed fragmented sound-absorbing elements 15, which are made mainly of recyclable acoustic materials. Also, they (separate crushed fragmented sound-absorbing elements 15) can be manufactured according to typical technologies for their production from “new” semi-finished sheet (roll) acoustic materials subjected to the subsequent technological process of their mechanical crushing into fragments of given geometric shapes and dimensions, in addition to placed in a closed inner cavity 27 of a separate integrally formed combined sound-absorbing panel 10, a separate crushed fragment bathrooms sound-absorbing members 15 made of recyclable acoustic materials listed above. As possible structural and technological options for the implementation of a separate integral molded combined sound-absorbing panel 10, its closed internal cavity 27 can also be partially, but not more than 30% of its cavity volume, filled with crushed, fragmented, air-tight closed-cell foam and / or dense non-porous polymer structures materials 19.

The provided sound transparency properties of the supporting outer surface cladding soundproof shell 16, as a part of a separate integrally formed combined sound-absorbing panel 10, are substantially characterized by the selected respective values of the parameters of the resistance to blowing through the air flow of the layers of materials - fabric 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 the resistance to blowing through the air stream of translucent air-permeable fabrics or translucent air-permeable non-woven fabrics (microperforated polymer film or microperforated foil metal layers) are in the range of 20 ... 500 n 3s / m ³ , with the thickness of the fibrous layer of fabric material, fibrous non-woven fabric, microperforated film polymer or microperforated foil metal layer constituting 0.025 ... 0.25 mm with specific surface m assoy 20 ... 300 g / m ² .

The values of 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 translucent material layer 18 of the supporting outer surface cladding translucent film sheath 16 of the film type can be made of various structural materials - polyester aluminized, urethane, polyvinyl chloride film, or from a similar type of other suitable polymeric film materials.

The outer surface cladding translucent material layer 18 of the supporting outer surface cladding translucent sheath 16 can be solid or perforated. For example, it can be made of micro-perforated (with a diameter of the passage section of perforation holes not exceeding 1 mm) of a foil material that provides for the use of aluminum, copper, and brass as a structural material. The outer surface cladding translucent material layer 28 of the supporting outer surface cladding translucent shell 16, can also be made of a continuous layer of air-blown fabric (non-woven fabric) material, can be represented by materials such as "maliflise", "filts", fiberglass, basalt fabric from superthin basalt fiber. The use of these types of structural materials for the manufacture of an external surface soundproofing material layer 18 of a supporting external surface soundproofing cladding shell 16 used as part of a separate integral molded combined sound-absorbing panel 10 provides a closed packing at a given packing density (ρ _f = 10 ... 655 kg / m ³ ) the inner cavity 27 of a separate integral molded combined sound-absorbing panel 10, the corresponding separate crushed fragments with sound absorbing elements 15, elimination of unwanted ingress and accumulation (absorption) into porous open-cell foam or porous fibrous structures of separate crushed fragmented sound-absorbing elements 15, various types of process and / or operating fluids (moisture, fuel, cutting fluids), as well as small amorphous particles or insects during operation of the claimed technical object.

For the formation of the corresponding sound-transparent compounds (the implementation of sound-transparent technological “cross-linking”) of the constituent elements into the monolithic structure of a separate integral molded combined sound-absorbing panel 10, various types of sound-transparent adhesive coatings 22 can be used, realized, for example, by the appropriate temperature heating and melting of used hot-melt polymer films or fibers, placed on the surface of the structure of the outer surface cladding a translucent material layer 18 (supporting the outer surface cladding soundproof shell 16), or for pairing the constituent elements of the prefabricated modules 23 of a separate integrally formed combined sound-absorbing panel 10, or a supporting inner air-blown film elastic soundproof shell 17, or between contacting ribs and faces of the isolated fragmented fragmented fragments 15 in the process of implementing the manufacturing process (manufacture) of a separate price flax-shaped combined sound-absorbing panel 10. For possible implementations of a variety of structural and technological options for a separate, whole-molded combined sound-absorbing panel 10, when the polymeric material of the outer surface cladding is an opaque layer of material 18 (supporting outer surface cladding is an opaque sheath 16) or the bearing is an inner air-impermeable film sheath elastic 17, which does not provide bonded adhesive bond by melting it (with appropriate heating of its structure), a satisfactory adhesive bond can be achieved by introducing additional soundproof (not significantly negative, not more than 10%, decrease the sound absorption coefficient of sound energy) of a certain type of adhesive adhesive layers (in the form of sticky glue or thermoactive hot-melt substances), technologically realized by surface-separated separate thin solid lines or spaced apart by separate thin dashed lines, either in the form of a thin continuous surface layer of sound-transparent adhesive substance perforated through holes, or in the form of a continuous thin sound-transparent adhesive adhesive layer with a low specific surface weight (not exceeding 100 g / m ² ), or as a continuous thin sound-transparent thermoactive hot-melt adhesive layer with a low specific surface weight (not more than 50 g / m ² ).

In the closed inner cavity 27 of the separate integral molded combined sound-absorbing panel 10, filled with a porous air-generated sound-absorbing substance 31 formed by separate crushed fragmented sound-absorbing elements 15, the corresponding internal embedded sound-transparent reinforcing elements 20 of the rod, or mesh, or plate-perforated types may additionally be contained.

The supporting outer surface sound-cladding cladding 16 of a separate integrally formed combined sound-absorbing panel 10 may additionally overlap a metal or polymer sound-transparent cladding protective or decorative mesh or perforated panel 21 (as shown in Fig. 10), with a perforation coefficient K _perf ≥ 0.25.

During operation of SHGTO 9, which contains thermally loaded units and systems mounted in the immediate vicinity of the surface areas of the installation of separate integral molded combined sound-absorbing panels 10 and sound-transparent facing protective and decorative perforated panels 21 of the technical room 1, the indicated structural elements (pos. 10 and 21) can be performed taking into account the provision of their heat-resistant fire-safe structural and technological design. In these cases, in particular, flame retardants can be used for their structural impregnation and / or thin-layer surface application. Thus, additional substances or mixtures of substances that protect materials of organic or synthetic origin from ignition and self-combustion can additionally be used. As flame retardants, aluminum hydroxide, boron, antimony, chloride, organic and inorganic phosphorus compounds can be used in particular. The supporting external surface cladding translucent soundproof shell 16 and a protective lining damping air-blown material layer 29, overlapping the neck portion 25 of the Helmholtz acoustic resonator R ^III (pos. 11), in these cases can be made of microperforated metal materials. Similar fire safety requirements for the use of flame retardants can, if necessary, apply to sound-transparent adhesive coatings 22 and to separate crushed fragmented sound-absorbing elements 15. In the considered structural and technological designs, the use of this type of fire-resistant elements can mainly relate only to their local areas of application, and not as part of a complete set of sound-absorbing lining of load-bearing enclosing structures of a technical room 1. Removed the structures of the specified acoustic elements (items 10, 21, 16, 22, 15) from SHGTO 9 can be made of other types of materials that do not require additional treatment with flame retardants or do not require metal construction, as described in the description of the claimed technical device .

Structural and technological versions of the individual components of a separate integral molded combined sound-absorbing panel 10, as well as grouped from separate parts (half-forms) mated together in monolithic structures of composite prefabricated modules 23 (see Fig. 12b, 13b, 14b, 15b, 16b), can be presented in the form of prefabricated one-piece joints, using the appropriate sound-transparent adhesive coatings 22, made in the form of continuous, or perforated film, or intermittent fibrous or powder decorative soundproof coatings. They can be represented by the corresponding surface and / or volume distribution of sticky adhesive or thermoactive adhesive substances, with the formation in a closed internal cavity 27 of a separate integral molded combined sound-absorbing panel 10 of stationary structural sound-absorbing (noise-canceling) elements, presented as porous-crushed sound-absorbing substance in the form of bonded sound-absorbing substance between themselves crushed fragmented sound-absorbing elements 15, and acoustic resonators Helmholtz and R ^III (pos. 11).

The outer surface layer, formed by adhesively bonded contacting faces and ribs of individual samples of separate crushed fragmented sound-absorbing elements 15, as part of a separate integral molded combined sound-absorbing panel 10, can form a corresponding monolithic air-generated sound-absorbing briquetted structure, which, in turn, can be adhesive-bonded counter surface supporting outer surface cladding soundproof th shell 16 as part of a separate integral molded combined sound-absorbing panel 10.

The outer surface layer of the structure of the porous air-blown sound-absorbing substance 31, composed of a monolithic mounting foamed open-cell polyurethane foam, and / or a monolithic integral molded fibrous material, or separate crushed fragmented sound-absorbing elements 15, which are appropriately distributed in the spatial zones of the inner cavity 27 adjacent to the mating carrier internal air-blown film elastic soundproof sheath 17, forms the corresponding dimensions of the chamber 24 and throat 25 parts of Helmholtz R ^III acoustic resonators (pos. 11) integrated in the porous air-blown structure of the substance 31 of a separate integrally formed combined sound-absorbing panel 10.

Hollow molded cavity tanks represented by chamber 24 and neck 25 parts of the Helmholtz acoustic resonator R^III (Pos. 11), as part of a separate integrally formed combined sound-absorbing panel 10, may include Helmholtz acoustic resonators R of identical overall dimensions and geometric shapes^III (key 11), as shown in FIG. 11a, 11b, 11c, 12a, 12b, 13a, 15a 16a, characterized by identical frequency tuning to specific specific values (a set of values of sound frequencies grouped into a narrow frequency band) of natural (resonant) frequencies of sound vibrations (f^III _R) formed by Helmholtz acoustic resonators R^III (pos. 11), as well as different overall dimensions and geometric shapes of Helmholtz acoustic resonators R^III (key 11), as shown in FIG. 14a, 14b, 17 providing their different frequency tuning to specified different values (given sets of values of sound frequencies grouped into a narrow frequency band) of natural (resonant) frequencies of sound vibrations (f^III _R) formed Helmholtz acoustic resonators R^III (item 11).

The frequency tuning of the effective functioning of the Helmholtz acoustic resonator R ^III (pos. 11) is carried out taking into account predetermined known (determined by calculation or experimentally, or known according to the passport characteristics of the operated SHGTO 9, or known according to the requirements of the selected design specification or given values of the current technical conditions production of SHGTO 9) spectral acoustic characteristics of SHGTO 9 mounted in a technical room 1, and also known (defined) dimensional and geometric parameters of its internal three-dimensional air cavity 8, known (recorded) values of the operating temperature of the air in the technical room 1 (already in operation or planned).

The frequency-resonance settings for the given values of the natural resonant frequencies (f ^III _R ) of Helmholtz acoustic resonators R ^III (pos. 11) are determined by the corresponding design of their composite structural elements formed by cavity shaped containers - the air volume of the cavity of the chamber part 24 (V _k ), geometric length h _g and the area of the passage section S _g (diameter of the circular passage section - d _g ) of the neck portion 25, calculated taking into account the air temperature t ° C _article , established in the internal three-dimensional air cavity and 8 technical premises 1 according to the expression (2):

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

f ^III _R is the value of the resonant frequency in Hz of the Helmholtz acoustic resonator R ^III (pos. 11);

π = 3.14

V _k - the volume of the chamber part 24 of the Helmholtz acoustic resonator R ^III (pos. 11), m ³ ;

k _p - the conductivity of the neck portion 25 of the Helmholtz acoustic resonator R ^III (pos. 11), m, determined according to the expression (3):

where S _g is the passage area in m ^{2 of the} neck portion 25 of the Helmholtz acoustic resonator R ^III (pos. 11), for the circular passage section of the parameter S _g is determined according to expression (4):

where d _g is the diameter of the circular bore of the neck portion 25 of the Helmholtz acoustic resonator R ^III (pos. 11), m;

l _R is the dynamic length of the neck portion 25 of the Helmholtz acoustic resonator R ^III (pos. 11), m, determined according to expression (5):

where h _g is the geometric (overall) length of the neck portion 25 of the Helmholtz acoustic resonator R ^III (pos. 11), m

The functioning of Helmholtz acoustic resonators R ^III (pos. 11), as technical devices for attenuating (suppressing, damping) acoustic energy in given narrow frequency ranges of the sound spectrum, is determined (characterized) by the corresponding discrete values of their natural (resonant) vibration frequencies f ^III _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 intrinsic (resonant) oscillation frequency f ^III _R ) of the used Helmholtz acoustic resonators R ^III (pos. 11). The Q factor is equal to the ratio of the intrinsic (resonant) frequency of the oscillations f ^III _{R of the} Helmholtz acoustic resonator R ^III (pos. 11) to the width of the adjacent frequency band Δf _R , at the boundaries of which the acoustic energy is twice less (by 3 dB) for forced resonant vibrations (3 dB) acoustic energy at a resonant frequency f ^III _R. The quality factor of the Helmholtz acoustic resonator R ^III (pos. 11) is determined (formed) by the internal dissipative losses realized in it, which arise both directly in the composite structures (elements) of the Helmholtz acoustic resonator R ^III (pos. 11) and external energy losses, directly related to the process of emission of sound into the environment, which also uses the vibrational energy of the Helmholtz acoustic resonator R ^III (pos. 11).

Thus, using expressions (2) ... (5), it is possible to design the overall geometric parameters as Helmholtz acoustic resonators R ^III _ms integrated in a separate integral molded combined sound-absorbing panel 10 with the ability to attenuate low-frequency sound radiation SHGTO (item 9) on the dominant values of individual discrete frequency components f _ms, and the Helmholtz resonator R ^III _mA, intended to suppress the resonance amplification of sound radiation by the technical eschenii 1 due to the dynamic excitation in its natural acoustic modes in the form of an oscillating mass and an elastic body of 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 the internal three-dimensional air cavity 8 of the technical room 1, in the spatial directions of its overall parameters A (L, B, H), determined according to the expression (6):

where f ^III _RmA is the value of the resonant frequency in Hz of the Helmholtz acoustic resonator R ^III , which coincides with the discrete value of one of the natural frequencies of sound vibrations f _mA (f _mL , f _mB , f _mH ), excited natural modes of the mass-elastic body of the air volume of the internal three-dimensional air cavity of a technical room of overall dimensions A (L, B, H);

To weaken the sensitivity (reduce the temperature dependence) of non-adjustable (non-tunable) designs of Helmholtz R ^III acoustic resonators (pos. 11), which are distinguished by simplicity of manufacture, to ensure their sufficiently effective functioning in some variable operational temperature regime Δt of the ambient air environment, is achieved by a corresponding change in the parametric characteristics "quality factor" of Helmholtz acoustic resonators R ^III (pos. 11), with some permissible (acceptable) sweat muffling efficiency in terms of suppressing the maximum amplitude level of acoustic energy (decreasing sound pressure level) at discrete values of natural (resonant) frequencies f ^III _R , while ensuring the expansion of the frequency range of its effective functioning. This, in particular, can be achieved by introducing into the resonating vibrational (acoustic) system containing Helmholtz acoustic resonators R ^III (pos. 11), the corresponding structural and technological elements having dissipative losses, additionally dissipating sound energy and, thereby, providing a corresponding expansion the frequency range of the acceptable performance of Helmholtz acoustic resonators R ^III (pos. 11). In these cases, the expansion of the effective frequency range implies an increase in the damped number of sound frequencies located (grouped) near the discrete value of the natural (resonant) frequency f ^III _R , with the implementation of the achieved, acceptable for solving the technical problem, interference compensation effects of the suppression (damping) of sound fields with a corresponding attenuation of the level of acoustic energy achieved in the extended frequency range, taking into account the arising (possible, additional stim) operational temperature changes.

If necessary (according to, for example, technical design requirements), the possible use of complementary use of alternative technical devices can be considered, for example, in the form of a typical automated temperature control system (climate control) of the air of a technical room 1, functioning in an internal three-dimensional air cavity 8, equipped with appropriate adjustable performance of its functioning (discrete "on-off", or continuously adjustable high-speed operation mode) by an electric fan (climatic) installation of a ventilation cooling device (not shown in Fig.). In this case, it can ensure the maintenance of a given operating operational thermal operating mode of SHGTO 9 in a narrower temperature range of the air environment Δt. This, accordingly, can additionally exclude (weaken) the unacceptable frequency detuning of the effective frequency-tuned noise-canceling function of the used Helmholtz R ^III acoustic resonators (pos. 11), endowed with discrete (more narrow-band) frequency-tuned operation, with specific consideration of a less significant change in the sound wavelengths λ ^III _R , under given physical conditions and propagation velocities of sound waves c (t) at steady-state operating air temperatures t ° C _st . This type of temperature-controlled (thermostatic) technical solutions are not considered in the claimed device.

As you know, technical rooms 1, the 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 (dynamic excitation) of their own low-frequency acoustic resonances in their internal three-dimensional air cavities 8 (see expression (1). The resulting (dynamically excited) intrinsic acoustic resonances of the mass-elastic air volume of the internal three-dimensional air olosti 8 technical room 1, resulting in its natural 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 a closed internal three-dimensional air cavity 8 of the technical room 1 to its console room or to other adjacent rooms of the building structure (building), as well as through open supply and exhaust ventilation openings 7 into the open space, with a corresponding increase in the degree of acoustics eskogo pollution (see. the circuit of FIG. 5). This additionally actualizes the solution of the problems of ensuring the acoustic safety of the environment using appropriate technical means of eliminating (suppressing, attenuating) this type of resonant amplification of acoustic radiation generated in noise-generating technical rooms 1.

Thus, in addition to Helmholtz acoustic resonators R ^III _ms (pos. 11) tuned to the working dominant functional frequencies f _{ms of} sound spectra of acoustic radiation of SHGTO 9, samples of acoustic resonators can also be supplemented or alternatively integrated into the structural compositions of a separate integrally formed combined sound-absorbing panel 10 Helmholtz R ^III (pos. 11) configured to suppress the acoustic radiation in other (different from the function f _ms working frequency values) of the frequency range x the sound spectrum, which can also be formed by numerous other various sources of acoustic radiation, which are part of the technical room 1. Such, in particular, can be noise-generating ventilation cooling devices, as well as individual resonant amplifications of sound radiation arising on the intrinsic acoustic modes of the internal 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, cor asno expression (1). These may include, in particular, low-frequency sound emissions generated by dynamically excited intrinsic structural vibrations, individual thin-walled metal housing elements of the equipment, or highly excitable thin-walled metal enclosing panels of the walls 2 (internal wall partitions) of the technical room 1, making an additional contribution to the total noise radiation of multicomponent sound field formed as part of the claimed technical object. Suppression of resonant amplifications of sound emissions arising from natural acoustic modes of the air volume of the internal three-dimensional air cavity 8 of the technical room 1, with natural (resonant) frequencies of sound vibrations f _mA (f _mL , f _mB , f _mH ), determined experimentally or by calculation, according to expression (1) can also be carried out using separate integrally formed combined sound-absorbing panels 10 through the use of appropriately frequency-tuned acoustic res Helmholtz onators R ^III _mA , the physical and geometric parameters of which are determined according to the expressions (2) ... (5).

The use of a hollow molded cavity container in the structure of a whole-molded combined sound-absorbing panel 10 formed by a supporting internal air-blown film elastic soundproof sheath (pos. 17), in the form of a chamber 24 and a throat 25 parts of the Helmholtz R ^III acoustic resonator (pos. 11), allows In this regard, the numerous physical principles of suppressing the propagation of sound energy. Thus, a more efficient resulting dissipative absorption of sound energy is achieved due to the implementation of physical phenomena noted above in the text of the application description, such as:

- the resulting diffraction of the propagated sound waves in the boundary zones of the open throat parts (key 25) with their deflecting (bending) penetration (passage) in the opposite direction to the direct propagation of sound waves, followed by dissipative thermal dissipation of energy in a porous air-generated sound-absorbing substance composed of a monolithic sound-absorbing material or isolated crushed fragmented sound-absorbing elements 15 (see Fig. 18, 21);

- an additional increase in the opposite surface area of the incidence and, accordingly, the dissipative absorption of sound energy, due to the introduction of a separate integrally formed combined sound-absorbing panel 10 in hollow molded cavity containers lined with a supporting internal air-blown film soundproof transparent sheath 17 (forming acoustic resonators ^III) into the porous sound-absorbing structure Pos. 11), see FIG. 18;

- the introduction of hollow molded cavity containers, represented by Helmholtz acoustic resonators R ^III (pos. 11), into a porous air-produced sound-absorbing structure (pos. 31) of a separate integrally formed combined sound-absorbing panel 10, contributes to a smoother (less spasmodic) coordination of wave acoustic impedances in the boundary acoustic zones separation of elastic layered media propagating sound waves (air and solid porous crushed sound-absorbing substance, presented separate crushed fragmented sound-absorbing elements 15 enclosed in a closed inner cavity 27 formed by a supporting external surface cladding sound-transparent sheath 16 and a bearing internal air-blown film elastic sound-transparent shell 17), in comparison with a plane-surface version of a monolithic typical plane-sheet construction of an air-absorbing panel (not containing cavities, recesses and inter-cavity jumpers), which contributes to quantitative reduction of the energy of the reflected acoustic waves and to increase the sound dampening effect;

- a decrease in dynamic stiffness (an increase in dynamic compliance) of the porous skeleton used, formed by a crushed sound-absorbing substance (separate crushed fragmented sound-absorbing elements 15), due to the additional integration of hollow air cavities into the structures of a separate, fully-molded combined sound-absorbing panel 10 contributes to the process of additional dissipation of propagated acoustic energy. Fig. 18, 21);

- the formation of structural-cavity acoustic anisotropy, with the implementation of enhancing the physical process of dissipative dissipation of the energy of propagated sound waves, due to the sound-transparent introduction (connection) of 10 hollow molded cavity containers that form Helmholtz R ^III acoustic cavities integrated into the bulk structure of a separate integrally formed sound-absorbing panel (pos. 11), see FIG. 18, 21, 11a, 11b, 11c, 12a, 12b, 13a, 13b, 14a, 14b, 15a, 15b, 16a;

- the formation of structural acoustic anisotropy with additional dissipative diffraction absorption of sound energy due to the additional introduction into the volumetric structure of the porous air-blown crushed sound-absorbing substance 31 of a separate integrally formed combined sound-absorbing panel 10 of various types (various) solid-state air-blown closed-cell non-porous non-porous and / or Fig. 19);

- the implementation of the physical effects of additional absorption of sound energy arising in narrow-gap air gaps formed between the opposite end parts of 28 mounted separate integrally formed combined sound-absorbing panels 10, which cause the accompanying additional dissipative diffraction absorption of sound energy by free edge zones of the porous sound-absorbing sound-absorbing structure (with their sound-absorbing porous sound-absorbing structures) see Fig. 20);

- the implementation of the physical effects of amplification of low-frequency absorption reflected from solid wall (walls - pos. 2) and ceiling (ceiling - pos. 3) panels of the technical room 1 of sound energy from the introduction of predetermined air gaps formed between the rear sides of the surfaces of separate integrally formed combined sound-absorbing panels 10 and opposite opposite sound-reflecting front surfaces of the enclosing wall structures (walls 2, ceiling 3), see FIG. 22;

- the use of the structural and technological design of hollow molded cavity containers using a sound-transparent thin-film element (supporting an internal air-blown film elastic elastic translucent shell 17), presented in the form of an Helmholtz acoustic resonator R ^III (pos. 11), allows physical processes of the passage of sound waves from a molded cavity capacity formed by the carrier of the inner air-blown film elastic soundproof sheath 17, in st the structure of a porous air-blown sound-absorbing substance 31 located in a closed inner cavity 27 of a separate integrally formed combined sound-absorbing panel 10, represented by separate fragmented sound-absorbing elements 15, with the implementation of the physical process of a broadband frequency-composition dissipative absorption of sound energy, and not just selective selective low-frequency selective energy absorption on discrete values of the frequencies of sound waves f ^III _R , as is the case in the design of the classical Helmholtz acoustic resonator R ^III (pos. 11), represented (made in the form) of a sound-insulating (soundproof, sound-reflecting) solid-state structure, excluding the passage of sound waves from a hollow resonator cavity into a closed internal cavity 27 filled with sound-absorbing substance.

Direct sound waves emitted by SHGTO 9 and propagating and penetrating into the structures of composite sound-absorbing elements of a separate integral molded sound-absorbing panel 10, falling onto their front sound-transparent surfaces and penetrating into porous air-blowing sound-absorbing structures 31, of a monolithic type or, more preferably, made up of fragments composed of elements 15, they are effectively dissipatively dissipated in them with an irreversible conversion of sound energy into heat y. This applies directly to both the microporous structures of the separate crushed fragmented elements 15, and to the communicating macroporous sinuous air channels and cavities formed between their loosely (gap) placed or contacting faces and ribs. The dissipative absorption of sound energy includes, among other things, molded cavity containers formed by supporting internal air-deflecting film elastic soundproof sheaths of 17 Helmholtz R ^III acoustic resonators (pos. 11).

As illustrative examples of the urgent need to suppress discrete low-frequency components that dominate the sound spectra of the working spaces of the technical room 1, presented in the form of the working dominant functional frequencies f _ms , the corresponding results of experimental recordings of sound fields inside various types of technical rooms 1 are shown. In particular, in FIG. . Figures 1-4 show the experimental results of measurements of sound pressure spectra (FFT spectra, 1/3 octave spectra) emitted by various types of SHGTO 9 (power electric transformer, industrial fan, reciprocating compressor) located in the corresponding technical rooms 1. The results of these experimental studies indicate released in the presence of low-frequency spectra of identified dominant working f _ms sound radiation frequencies investigated functional SHGTO 9 forming the sound technical room ol 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 the first three low-frequency harmonic components of the sound pressure spectrum f _1s = 100 Hz, f _2s = 200 Hz, f _3s = 300 Hz, multiples of the frequency of the alternating current network f _c = 50 Hz SHGTO 9, represented by power electrotra informant. SPL at recorded discrete frequencies (f _1s , f _2s , f _3s ) equal to, respectively, 100, 200 and 300 Hz. At the same time, they exceed by more than 20 dB (10 times - in linear units of measurement) the sound pressure levels (SPL) of the remaining frequency components of the sound radiation of the ETPZT. Thus, this indicates their complete dominance both in the closed spatial sound field of the technical room 1, presented in the form of ETPZT, and in the adjacent territory (due to the fact that the measuring microphone was located outside of room 1 in the spatial zone of the closed doorway), which actualizes the need to suppress them.

Measurements of the 1/3 octave spectrum of sound pressure emitted by a type 3MK 260-1 power transformer from PLATTHAUS (Germany), a microphone located inside the technical room 1 of the industrial testing center (see Fig. 2), also recorded dominant operating functional frequencies f _ms sound radiation SHGTO 9, on the first three harmonic components of the sound spectrum f _1s , f _2s , f _3s , subjectively perceived as a pronounced low-frequency "electric transformer hum" power electrotransfo rator with radiated sound frequencies: f _1s = 100 Hz, f _2s = 200 Hz, f _3s = 300 Hz (included in the frequency band with a center of 315 Hz). The SPL at recorded discrete frequencies (f _1s , f _2s , f _3s ) exceeds by more than 15 dB (5.6 times - in linear units of sound pressure in N / m ² ) SPL of other frequency components of the presented sound pressure spectrum of the investigated electric transformer , which also indicates their dominant contribution to the process of forming the internal sound field of the technical room 1 with its subsequent negative impact on the acoustic safety of the environment.

The reduced 1/3 octave spectrum of sound emitted by the industrial fan of the Axipal FTDA-050-3 model (Russia), mounted in technical room 1, represented by the premises of the acoustic testing laboratory (see Fig. 3), identifies two working as expressed low-frequency spectral components the dominant functional frequencies of sound radiation SHGTO 9, manifested in the form of a blade (scapular) frequency of rotation of the impeller f _1s = 50 Hz and its multiple harmonics f _2s = 100 Hz. The SPL at the indicated discrete frequency values (f _1s , f _2s ) is more than 25 dB (17.8 times higher in linear units of sound pressure in N / m ² ) than the SPL of the adjacent medium and high frequency range of the studied sound spectrum radiation SHGTO 9. This allows you to qualify the indicated frequencies f _1s and f _2s as expressed dominant low-frequency sound emitters, responsible for the formation of the sound field of the technical room 1.

The measurement results of the 1/3 octave sound spectrum emitted by the STAL piston compressor (Sweden) mounted in the technical room 1 of the compressor-refrigeration station of the industrial facility test center, shown in FIG. 4 also identify two distinct discrete dominant working functional frequencies of sound radiation SHGTO 9 - f _1s = 200 Hz and f _2s = 400 Hz. The SPL on recorded discrete values of sound frequencies (f _1s , f _2s ) is more than 10 dB (3.16 times higher in linear units of sound pressure in N / m ² ) than the SPL of the remaining frequency components of the spectrum of sound radiation recorded in technical room 1 of the studied compressor and refrigeration station.

), укладывающимися между противолежащими (оппозитно расположенными) жесткими звукоотражающими поверхностями стен 2 (а также пола 4 и потолка 3) ограждений технического помещения 1. Таким образом, указанные экспериментально установленные факторы актуализируют необходимость решения проблемы подавления звуковых излучений, производимыми ШГТО 9, как в подавляющем широкополосном звуковом диапазоне спектра, так и с первостепенной (приоритетной) задачей уменьшения его доминирующих низкочастотных составляющих звукового спектра. В связи с этим, поставленные технические задачи и проблемы предлагается эффективно решать использованием комбинированных технических устройств заглушения звуковой энергии, включающих как частотонастроенные шумозаглушающие элементы ее избирательного селективного заглушения, наделенные повышенной эффективностью в низкочастотном звуковом диапазоне, так и широкополосные шумозаглушающие устройства, приемлемо эффективные в средне- и высокочастотном звуковом диапазоне, которые осуществляются используемыми пористыми воздухопродуваемыми 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 воздухопродуваемые звукопоглощающие вещества 31, будет дополнительно способствовать ослаблению 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 направленного усиления эффективности их подавления, в необходимых случаях, в составе обособленных цельноформованных комбинированных звукопоглощающих панелей 10 дополнительно применяются частотнонастроенные устройства избирательного селективного заглушения звукового излучения на выделяющихся дискретных спектральных составляющих (в виде предложенных к использованию интегрированных в состав обособленных цельноформованных комбинированных звукопоглощающих панелей 10 акустических резонаторов Гельмгольца R^III _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 пространственно распространяющихся в направлении его габаритных параметров A (L, В, Н).Thus, as follows from the above in FIG. 1-4 results of studies performed, identifying as discrete values the dominant working functional frequencies of sound radiation f _ms (f _1s , f _2s , f _3s ) of various types of investigated SHGTO 9 mounted in the corresponding technical rooms 1, differing in overall dimensions L, B, N, are concentrated in the low-frequency region of the sound spectrum (50 ... 500 Hz), the sound wavelengths λ _{ms of} 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, also located in meter measurement ranges and characterized by their own acoustic modes with sound wavelengths λ _mA (half-lengths

), stacked between the opposite (opposite) hard sound-reflecting surfaces of the walls 2 (as well as floor 4 and ceiling 3) of the fences of the technical room 1. Thus, these experimentally established factors actualize the need to solve the problem of suppressing sound radiation produced by SHGTO 9, as in the overwhelming the broadband sound range of the spectrum, and with the primary (priority) task of reducing its dominant low-frequency components of the sound spectrum. In this regard, it is proposed to effectively solve the technical problems and problems using combined technical devices for damping sound energy, including both frequency-tuned sound-damping elements of its selective selective damping, endowed with increased efficiency in the low-frequency sound range, and broadband noise-damping devices that are reasonably effective in medium- and high-frequency sound range, which are carried out by the used porous air blowing bubbled sound-absorbing acoustic materials and structures of the respective sound-absorbing structures. It should be noted that the lining of the enclosing wall and ceiling structures of the technical room 1 with separate integral molded combined sound-absorbing panels 10 containing porous air-blown sound-absorbing substances 31 will further contribute to the weakening of the pronounced cavity air resonances of the internal three-dimensional air cavity 8 of the technical room 1, manifested in their own acoustic modes, characterized by sound wavelengths λ _mA (half-lengths

), with natural frequencies of sound vibrations f _mA (f _mL , f _mB , f _mH ). At the same time, to directionally enhance the efficiency of their suppression, if necessary, frequency-tuned devices for selective selective damping of sound radiation on the discrete discrete spectral components (in the form of integrated separate composite-shaped combined components proposed for use) are additionally used as part of separate integral molded combined sound-absorbing panels 10 sound-absorbing panels 10 Helmholtz acoustic resonators R ^III _mA (according 11)) tuned to damp 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 natural acoustic modes of a mass-elastic body of an air volume characterized by sound wavelengths λ _mA (λ _mL , λ _mB , λ _mH ), formed in the internal three-dimensional air cavity 8 of the technical room 1, and spatially propagating in the direction of its overall parameters A (L, B, H).

As follows from the description, the technical device of the low-noise technical room presented as an application for the invention is endowed with a broadband frequency composition of the sound absorption effect, with a priority (enhanced efficiency), selective selective low-frequency effect of suppressing acoustic energy at discrete values of the working dominant functional frequencies of sound radiation f _ms various types of SHGTO 9 mounted in the corresponding technical rooms 1. In this case, ShGTO 9, broadband medium- and high-frequency sound radiation is suppressed by the porous sound-absorbing dissipative structures used in the technical device of the porous air-blown sound-absorbing substance 31, composed of separate crushed fragmented elements 15, and / or a monolithic mounting foamed open-cell polyurethane foam and polyurethane foam, and integral molded sound-absorbing panel 10. Implement The sound-damping effects that are being effected are further enhanced by the arising edge diffraction dissipative sound-absorbing effects, as well as the arising dissipative acoustic anisotropy effect due to the inclusion in the porous air-produced sound-absorbing substance 31 in the form of a monolithic sound-absorbing substance and / or in a sound-absorbing structure made up of fragments composed of 15 isolated fragments air-generated porous sound-absorbing particles of recyclable materials terials, including due to the introduction of a certain dosage amount and its corresponding volume distribution of crushed fragments made of air-blown closed-cell foamed and / or dense non-porous structures of polymeric materials 19 in a mixture with separate crushed fragmented sound-absorbing elements 15. Also to enhance the sound absorption process energy includes the physical phenomena of acoustic anisotropy formed by hollow shaped air cavity cavities Helmholtz acoustic resonators R ^III (pos. 11) integrated into the bulk structure of the porous air-blown sound-absorbing substance 31 (monolithic type and / or composed of separate crushed fragmented elements 15) separate integral molded combined sound-absorbing panels 10. In addition, the accompanying diffractive dissipative absorption of sound energy is realized in the edge zones of the throat parts ( pos. 25) of Helmholtz acoustic resonators R ^III (pos. 11) and the edge zones of the end faces 28 of the gaplessly mounted separate circuits flax-shaped combined sound-absorbing panels 10. The implementation of the air gaps formed between the rear sides of the surfaces of the separate integral-shaped combined sound-absorbing panels 10 and opposed opposed sound-reflecting surfaces of the wall structures (walls 2, ceiling 3) also provides an increase in sound absorption effects 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 f _ms functional frequencies generated SHGTO 9 is suppressed due to integrated inside the porous sound absorbing structure of the substance isolated tselnoformovannoy acoustic combined panel 10 chastotonastroennyh acoustic Helmholtz resonators R ^III _ms ( Pos. 11).

содержали встроенные в их объемных структурах полостные акустические резонаторы Гельмгольца R^III (поз. 11) в количестве 8 шт. Габаритно-геометрические размеры пустотелых формованных полостных резонаторных емкостей, образующих акустические резонаторы Гельмгольца R^III (поз. 11), были определены с использованием выражений (2)…(5), исходя из необходимости уменьшения звукового излучения в частотном диапазоне 1/3 октавных полос частот с центрами 400 и 500 Гц. Для оценки достигаемых эффектов изменения значений реверберационного коэффициента звукопоглощения α_rev, в качестве опорной сопоставительной базы был использован макетный образец, изготовленный из монолитного пористого воздухопродуваемого звукопоглощающего материала идентичного структурного состава и габаритных размеров без интегрированных в нем акустических резонаторов Гельмгольца R^III (поз. 11). На фиг. 23 приведены результаты измерений реверберационного коэффициента звукопоглощения α_rev исследованных макетных образцов обособленных цельноформованных комбинированных звукопоглощающих панелей (поз. 10), изготовленных из монолитного типа пористого воздухопродуваемого звукопоглощающего вещества (вспененного открытоячеистого пенополиуретана) - поз. 31, внешние лицевые поверхности которого футерованы эластичной звукопрозрачной воздухонепродуваемой полиэстеровой алюминизированной пленкой толщиной 0,012 мм, образующей несущую внешнюю 16 и несущую внутреннюю 17 поверхностные облицовочные воздухонепродуваемые пленочные эластичные звукопрозрачные оболочки, в объемный состав которого встроены (скомпонованы) полостные камерные 24 и горловые 25 части акустических резонаторов Гельмгольца R^III (поз. 11), а также сопоставляемого монолитного макетного образца звукопоглощающей панели без интегрированных акустических резонаторов.The effectiveness of the proposed technical solution is confirmed by the results of experimental studies. Presented in FIG. 23 and 24, the results of experimental studies of the sound-absorbing characteristics of prototypes of isolated, whole-molded combined sound-absorbing panels (pos. 10) containing porous air-produced sound-absorbing substance (pos. 31) with integrated Helmholtz acoustic resonators R ^III (pos. 11), chamber 24 and throat 25 parts which are partially formed by the supporting inner air-blown film elastic soundproof sheath (pos. 17). The experiments were carried out using the “Cab Alpha” small-sized reverberation chamber, the volume of the air cavity of which was 6.45 m ³ , and the working frequency range of measurements covered 1/3 octave frequency bands with centers 400 ... 10000 Hz. As the constituent elements of mock-up samples of separate, integral molded combined sound-absorbing panels (pos. 10), flat sheets of a monolithic porous air-blown sound-absorbing substance (foamed open-cell polyurethane foam) - pos. 31, the outer front surfaces of which contained layers of a resilient soundproof air-blown polyester aluminized film with a thickness of 0.012 mm. Separate whole-molded combined sound-absorbing panels (pos. 10) with overall dimensions

contained 8 Helmholtz cavity cavity acoustic resonators R ^III (pos. 11) embedded in their bulk structures. The overall geometric dimensions of hollow molded cavity resonator tanks forming Helmholtz acoustic resonators R ^III (pos. 11) were determined using expressions (2) ... (5) based on the need to reduce sound radiation in the frequency range of 1/3 octave frequency bands with centers of 400 and 500 Hz. To evaluate the effects of changing the values of the reverberation sound absorption coefficient α _rev , we used a prototype sample made of a monolithic porous air-blown sound-absorbing material of identical structural composition and overall dimensions without Helmholtz R ^III acoustic resonators integrated in it (reference 11). In FIG. 23 shows the results of measurements of the reverberation coefficient of sound absorption α _{rev of the} studied prototypes of isolated whole-molded combined sound-absorbing panels (pos. 10) made of a monolithic type of porous air-blown sound-absorbing substance (foamed open-cell polyurethane foam) - pos. 31, the outer front surfaces of which are lined with an elastic sound-transparent air-blown polyester aluminized film with a thickness of 0.012 mm, forming a supporting outer 16 and a bearing inner 17 surface cladding air-blown film elastic sound-transparent shells, in the volumetric composition of which cavity cavity parts 24 and neck are built-in (arranged) Helmholtz R ^III (pos. 11) and mapped monolithic model sample without integrating the acoustic panel ovannyh acoustic resonators.

As follows from the results of an experimental study, the introduction of a separate integrally formed combined sound-absorbing panel (pos. 10) of Helmholtz acoustic resonators R ^III (pos. 11) in the volumetric composition of the prototype allows increasing the reverberation coefficient of sound absorption α _rev in a controlled the working frequency range of 1/3 octave bands of the sound spectrum with centers of 400 and 500 Hz.

. Имитация беззазорного монтажа обособленных цельноформованных звукопоглощающих панелей предусматривала их непосредственную установку на поверхность пола малой реверберационной камеры «Кабина Альфа». Имитация зазорного монтажа обособленных цельноформованных звукопоглощающих панелей осуществлялась дополнительным использованием звукопрозрачной установочной платформы, выполненной в виде плоской крупноячеистой (габариты ячеек -

) металлической сетки, поверхность которой находилась с заданным воздушным зазором (k=300 мм) над звукоотражающей поверхностью пола малой реверберационной камеры «Кабина Альфа». Эксперименты выполнялись при вариантах открытых и дополнительно звукоизолированных торцевых граней (поз. 28) исходного макетного образца цельноформованной звукопоглощающей панели, а также при ее фрагментированном дроблении на 8 идентичных частей габаритными размерами

. Задаваемые воздушные зазоры между противолежащими торцевыми гранями 28 фрагментированных частей обособленных цельноформованных звукопоглощающих панелей составляли величину γ=10 мм. Как иллюстрируют приведенные результаты измерений, возрастание эффектов поглощения звуковой энергии достигается как при зазорной компоновке обособленных цельноформованных звукопоглощающих панелей относительно звукоотражающих поверхностей ограждающих конструкций (k), так и с сопутствующей узкощелевой зазорной установкой (γ), образующейся между их противолежащими торцевыми гранями (поз. 28).The potential effects achieved by increasing the sound-absorbing properties of the used separate whole-molded combined sound-absorbing panels (pos. 10) during their mounting air-gap arrangements with respect to the gap-free installations on the sound-reflecting floor surface of the test chamber are confirmed by those shown in FIG. 24 relevant experimental results. The measurements of the reverberation coefficient of sound absorption α _{rev were} carried out in a small-sized reverberation chamber “Cab Alpha” using mock-ups of separate, whole-molded sound-absorbing panels made of a monolithic porous air-blown sound-absorbing substance (key 31) made of a plane-sheet porous, whole-shaped, fibrous sound-absorbing fibrous

. Simulation of the gap-free installation of separate whole-molded sound-absorbing panels provided for their direct installation on the floor surface of the small reverberation chamber “Cabin Alpha”. Simulation of the gap installation of separate, fully formed sound-absorbing panels was carried out by the additional use of a sound-transparent installation platform, made in the form of a flat coarse-mesh (cell dimensions -

) a metal mesh, the surface of which was with a given air gap (k = 300 mm) above the sound-reflecting surface of the floor of the Cab Alfa small reverberation chamber. The experiments were performed with options for open and additionally soundproof end faces (pos. 28) of the original prototype of a whole-formed sound-absorbing panel, as well as when it was fragmented into 8 identical parts with overall dimensions

. The preset air gaps between the opposite end faces of the 28 fragmented parts of the separate integral molded sound-absorbing panels were γ = 10 mm. As the results of measurements illustrate, an increase in the effects of absorption of sound energy is achieved both with the gap arrangement of separate whole-molded sound-absorbing panels relative to the sound-reflecting surfaces of the building envelope (k), and with the accompanying narrow-gap gap installation (γ) formed between their opposite end faces (pos. 28 )

The claimed technical solution in the form of the invention is not limited to specific structural examples of its implementation, described in the text and shown in the attached diagrams. It remains possible and some (non-essential) changes in various constituent elements or structural materials from which these elements are made, or their replacement with technically equivalent, not beyond the scope of the claims indicated by the claims.

Claims (27)

1. A low-noise technical room, characterized by the physical parameters of the sound and temperature fields of at least one noise-generating technical object that has been established in its internal three-dimensional air cavity and contains load-bearing enclosing elements in the form of a floor, walls and ceiling, on which separate, fully formed combined sound-absorbing panels containing cavity structures of acoustic resonators, while operating sound-generating technology sky object operates at a predetermined steady constant speed operational mode n _s, which is accompanied by the established physical processes of radiation of sound and heat energy in a spectral sound structure which contains evolved discrete values of operating dominant functional sound frequency f _ms, characterized by respective lengths of sound waves λ _ms, wherein the fact that the separate whole-molded combined sound-absorbing panels are mounted with specified air with clearances k relative to the supporting wall and ceiling enclosing elements of the low-noise technical room, as well as with predetermined air gaps γ formed by opposite end faces of separate integral molded sound-absorbing panels mounted on the supporting wall and ceiling enclosing elements of the low-noise technical room; separate sound-absorbing panels are represented by shell structural and technological versions made in the form of a predominantly rectangular cross-section of separate whole-molded combined sound-absorbing panels containing load-bearing air-blown or air-blown external surface cladding sound-transparent shells that are adhesively mated with load-bearing inner film-transparent, opaque The hollow cavities in the composition of the separate integral molded combined sound-absorbing panels filled with a monolithic porous breathable sound-absorbing substance or composed of separate fragmented fragmented elements, while the bearing internal breathable elastic sound-transparent film sheaths are made in the form of certain overall dimensions of the cavity sound-transparent elements and contain chamber parts containing Helmholtz forming acoustic resonators R ^III , with the natural resonant frequencies of which f _R coincide with at least one of the discrete values of the working dominant functional frequencies of sound radiation of at least one exploited noise-generating technical object f _ms characterized by the corresponding sound wavelength 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), while the throat parts of Helmholtz acoustic resonators R ^III ra placed on the end faces of separate, individually formed, combined sound-absorbing panels. 2. The low-noise technical room according to claim 1, characterized in that the frequency-resonant settings f ^III _{Rms of} Helmholtz acoustic resonators R ^III to the given discrete values of the resonant frequencies of the sound radiation of the noise generating technical object of the working dominant functional frequencies f _ms , with corresponding sound wavelengths λ _ms , are determined by the corresponding structural and technological execution of its component elements, based on the expressions:

, where f ^III _Rms is the value of the resonant frequency in Hz of the Helmholtz acoustic resonator R ^III , which coincides with the discrete value of one of the working dominant functional frequencies f _ms ; t ° C _article - stabilized value of air temperature in ° C, established in the internal three-dimensional air cavity 8 of the technical room 1; π = 3.14; V _k is the volume of the chamber part of the Helmholtz acoustic resonator R ^III , m ³ ; k _p - conductivity of the throat portion of the Helmholtz acoustic resonator R ^III _ms , m;

, where S _g - the passage area of the neck of the acoustic Helmholtz resonator R ^III _ms , m ² ;

, where d _g is the diameter of the circular bore of the throat portion of the Helmholtz acoustic resonator R ^III _ms , m; l _Rms is the dynamic length of the throat portion of the Helmholtz acoustic resonator R ^III _ms , m;

, where h _g is the geometric (overall) length of the neck of the Helmholtz acoustic resonator R ^III _ms , m 3. The low-noise technical room according to claim 1, characterized in that the frequency-resonant settings f ^III _{RmA of the} Helmholtz acoustic resonators R ^III to suppress the amplification of the resonant sound radiation of the excited natural acoustic modes of the mass-elastic body of the air volume of the internal three-dimensional air cavity of the technical room of overall dimensions a (L, B, H), characterized by the acoustic wavelength _{λ mA (λ mL, λ mB} , λ mH) with the discrete values of the natural frequencies of sound vibrations _{f mA (f mL, f mB} , f mH), determined based on the exp Nia:

, where f ^III _RmA is the value of the resonant frequency in Hz of the Helmholtz acoustic resonator R ^III , which coincides with the discrete value of one of the natural frequencies of sound vibrations f _mA (f _mL , f _mB , f _mH ), excited natural modes of the mass-elastic body of the air volume of the internal three-dimensional air cavity of a technical room of overall dimensions A (L, B, H); f _mA (f _mL , f _mB , f _mH ) - discrete values of the natural frequencies of sound vibrations in Hz, formed on the natural acoustic modes of the mass-elastic body of the air volume of the internal three-dimensional air cavity of the technical room, in the direction of its overall parameters A (L, B , Н), characterized by the sound wavelengths λ _mA (λ _mL , λ _mB , λ _mH ), determined on the basis of the expression:

, where m _A is the serial number of the natural acoustic mode of sound vibrations of the mass-elastic body of the air volume of the internal three-dimensional air cavity of the technical room in the direction of its overall parameter A (length L, width B, height H), expressed as an integer of the natural number (m _A = 1 , 2, 3 ...); s - the speed of propagation of sound waves in the air of the internal space of the internal three-dimensional air cavity of the technical room, m / s (s = 344,057 m / s at + 20 ° С). 4. Low-noise technical room according to claim 1, characterized in that on the open throat parts of the Helmholtz acoustic resonator R ^III, a protective lining damping air-blown layer of material is mounted, characterized by ranges of resistance to blowing by an air flow equal to 20 ... 500 N⋅s / cm ³ , a layer thickness of 0.025 ... 0.25 mm and a specific surface weight of 20 ... 300 g / m ² . 5. The low-noise technical room according to claim 1, characterized in that the throat portion of the Helmholtz acoustic resonator R ^{III is} formed by a removable hollow tubular element made of a rigid, dense, air-tight material structure. 6. The low-noise technical room according to claim 1, characterized in that from the front surfaces of the faces of the separate integral molded sound-absorbing panels, sound-transparent cladding protective and decorative perforated panels are additionally mounted, the perforation coefficient of the walls of which corresponds to the expression K _perf ≥ 0.25. 7. The low-noise technical room according to claim 1, characterized in that the separate integral molded combined sound-absorbing panels are fixed to the supporting wall and ceiling enclosing elements by corresponding fasteners, represented by remote mechanical fasteners, or suspended cable elements, or mounting spikes, or mounting frames, or mounting elastic elements, or mounting profiles. 8. The low-noise technical room according to claim 1, characterized in that the remote air gap γ between the opposite end surfaces of the faces of the mounted separate integral molded sound-absorbing panels is not more than a quarter of the overall thickness of the opposite end faces of the isolated integral molded sound-absorbing panels.

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