RU2677621C1 - Low-noise technical room - Google Patents

Abstract

FIELD: acoustics.SUBSTANCE: invention relates to technical means for providing acoustic environmental safety by suppressing noise emissions, produced by industrial-technological and engineering equipment, represented, in particular, by pumping, compressor stations, power plants, ventilation and air conditioning systems, electric machines, mounted inside noise generating technical rooms. Low-noise technical room is equipped with air gaps between the opposite end faces and relatively opposed mounting surfaces of wall and ceiling fencing structures of the technical room, detached, single-molded combined sound-absorbing panels made up of a porous air-driven crushed sound-absorbing structure of a substance and integrated in it cavity frequency-tuned noise-suppressing structural elements, presented in the form of quarter-wave acoustic resonators. Quarter-wave acoustic resonators are formed by a carrier inner air-blowing film elastic shell made in the form of a dead-end tubular cavity sound-transparent element of a certain overall dimensions of its tubular part with an open neck part and a bottom part covered with a hard sound-reflecting bottom. Low-noise technical room is endowed with a broadband in terms of frequency composition sound absorption effect with an expressed low-frequency effect of reducing sound pressure at discrete values of the working dominant functional frequencies of sound radiation f, noise-generating technical objects mounted in it.EFFECT: invention can be used to improve acoustic comfort in adjacent residential, industrial, and public premises of buildings and constructions integrated adjacent to specified noise-generating technical rooms.16 cl, 25 dwg

Description

The invention relates to the field of technical means to ensure acoustic safety of the environment by suppressing (decreasing) noise emissions produced by production, technological and engineering equipment, presented, in particular, pumping, compressor stations, power plants (internal combustion engines, diesel generating installations), ventilation and air conditioning systems, electric machines (electric motors, electric transformers), mounter inside the noise-generating (noise-active) technical premises (building buildings). It can also be used to improve acoustic comfort in the adjacent residential, industrial and public premises of buildings and structures, integrated adjacent (closely located) with the specified 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 (soundproofing) fencing of noisy technical rooms (screen partitions, casings, panel linings of bearing and / or cabinet are widely used) structures equipped with additional layers of viscoelastic vibration-damping and / or porous air mounted on their surfaces sound-absorbing, and / or dense, air-tight, sound-insulating materials being blown out, and / or their various combinations combined with the additional inclusion of bearing, reinforcing, sound-transparent, protective, adhesive, decorative layers of materials or corresponding structural elements). Also, for the same purposes, isolated single or interlocked batteries, 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, or contained in the composition of technical rooms, volume expansion chambers attached to sound-transmitting (waveguide) channels (openings) of the corresponding type, blocking (weakening) the transmission of acoustic energy due to sound reflection formed in them guides air (gas filled) "acoustic tubes" characterized by abrupt changes (differences) acoustic wave resistances. 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), 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 found to be widely used, using the combined implementation of physical processes of sound absorption and sound insulation, where the total noise-reducing effect of the technical device used can be based both on the effects of 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 structures, or air-blown sound-insulating structures, 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 ^III), including the use of perforated lamellar structures, disposable with a predetermined air gap otno itelno rigid sound-reflecting surfaces, to form the corresponding cavity resonator devices (acoustic Helmholtz resonators R ^III). This type of cavity resonator 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, in particular, various types of panel-cavity noise-reducing structures can be indicated:

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

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

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

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

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

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

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

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

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

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

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

The expressed useful advantages of using the above technical devices for damping acoustic energy include the possibility of their use in aggressive environments, high temperatures and intense dynamic loads, due to the exclusion of the use of porous air-blown (gas-blown) fibrous and / or foamed open-cell structures of organic or synthetic origin characterized, as a rule, not high enough thermo-moisture-biostable and characteristics. They use exclusively dense structures of perforated metal or heat-resistant polymer 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 suppressing devices include their narrow working frequency sound range of effective functioning, high sensitivity to frequency detuning when changing the physical parameters of the sound wave propagation medium, and when the value of achieving noise suppression effect in a wide frequency range is not high enough, high cost, poor overall performance and increased material consumption. 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 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 the invention of US 5422466 (published 03/11/1994);

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

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

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

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

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

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

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

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

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

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

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

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

The above-mentioned well-known noise-reducing technical devices, along with satisfactory acoustic characteristics 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. Also, there is a relative high cost of polymer porous sound-absorbing substances used in this type of construction, produced mainly from non-renewable, expensive hydrocarbon feedstocks (oil, gas). Also, they (polymeric materials) are characterized by rather complex, labor-consuming and "environmentally dirty" problems of both their production and the final disposal of various types of dissimilar structural materials used in the components and assemblies of this type of noise-reducing technical devices, after they complete their life cycle.

To increase the noise-reducing properties of this type of structure, by providing smoother (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 the boundary contact zones of the external hard-shell surface of the panel of a technical device with external and with internal cavity zones of adjacency of the air environment, the contours of the outer shell (wall) of the front acoustic Coy gofrovidnaya panel attached to 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 the invention of US 4097633 (published on 06/27/1978);

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

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

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

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

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

The above noise-reducing constructions of technical devices are characterized, first of all, by 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 sound damping characteristic due to the formation of their own “Parasitic” cavity airborne acoustic resonances), as well as forced concomitant during knowing reduction ("crowding out") of the useful working volume of the technical room, complicating the processes of their maintenance (cleaning, washing).

Another well-known technical direction for improving the design of technical devices for attenuating the spread of negative ("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 in the front face panel of a technical device that directly perceives 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 the invention DE 4315759 C1 (published on 05/11/1993);

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

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

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

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

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

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

These noise reducing technical devices can be characterized 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 of the perforation holes. Also, their production is associated with the need to use more sophisticated high-tech equipment, ensuring compliance with narrow manufacturing tolerances.

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 one degree or another (in one or another frequency range, with one or another sound-damping effect) to purposefully improve their acoustic properties. This type of hybrid hybrid noise reduction technical devices are described in the following patent documents:

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

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

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

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

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

The disadvantages of the above noise-reducing technical devices are their higher structural complexity and technological complexity of manufacturing, with achieved in some cases, insufficiently high (unsatisfactory) environmental and cost indicators. There are also insufficient potentials to further improve their noise-damping characteristics in the low-frequency range of sound frequencies, which is the most intense and relevant in solving typical problems of reducing noise in machinery and equipment.

A technical solution is known according to the RF patent for the 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 with a predetermined air gap in the cavity between the rear sound-reflecting panel and the front sound-transparent panel perforated through the holes, while the specified noise the absorbing element contains a supporting base of sheet perforated or mesh type, fixed by mechanical fasteners to horizontal profiles and / or the base of the noise-reducing screen, lined with at least one of its sides, separated by sound-absorbing panels representing a set of crushed fragments of porous fibrous or foamed open-mesh sound-absorbing materials that are distributed in a certain way and fixedly mounted on the surface of the carrier base, with the formation of the corresponding air gaps between them. At least from the standpoint of the placement of separate sound-absorbing panels, the surface of the noise-reducing element is lined with a layer of a soundproof gas-impermeable film or fabric. The disadvantage of the known known technical solution is the limited possibility of its effective use, which is carried out mainly not in closed limited volumes of technical rooms, but in open spaces of the environment to protect residential areas of settlements from negative acoustic radiation propagating from noise-generating technical objects - vehicles and industrial equipment installed near automobile and railroad Orog, airfields, open sections of subway lines, test sites, noise-active construction and production sites, or any other spatially distributed sources of increased noise radiation that produce intense acoustic pollution. In particular, this necessitates the use of additional load-bearing and supporting elements (foundations, supporting bases, 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 soundproof fencing of complex spatial geometric shapes. 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 insufficient 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 type moving in 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, in the areas of its enclosing wall and ceiling structures), will significantly reduce (clutter) its useful workspace and worsen the process of technological maintenance of the mounted in it production and technological and engineering equipment.

The technique of partial exclusion (partial attenuation) of 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 rooms is a well-known and used technique in technology (architectural acoustics), which is the use of a technical building specialized in structural design presented in the form appropriate measuring acoustic instruments made in the form of a meter reverberation chamber, as described, in particular in [1, 2, 3]:

[1] - ASTM 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 the measuring reverberation chamber, the ratios of its composite overall dimensions and the physical characteristics of its wall structures make it possible to exclude (partially weaken) the development of the physical process of the formation of the in-phase resonant addition of half-lengths of sound waves λ / 2) excited inside the air cavity of the measuring reverberation cameras with the studied sound-generating sound source (or calibrated sound emitter), thereby preventing m the formation of pronounced resonant intrinsic acoustic modes of the air volume of the room measuring reverberation chamber. Thus, this makes it possible to partially exclude (partially weaken) the development of the physical process of the formation of a pronounced uneven spatial density distribution of the intensity of sound energy localized in the air cavity of the measuring reverberation chamber from the composition of the diffuse 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 used in the field of acoustic measurements of samples of acoustic materials, and are also used to study the sound-absorbing characteristics of the structures of parts, components and systems of machines, 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, eliminating the negative development of physical the formation of resonantly expressed spatial zones of unequal distribution of the intensity of sound energy, as well as the exclusion of the sound absorption process Oia, proizvodimomgo enclosing surfaces and wall constructions doorway measuring the reverberation room. 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 partially eliminated 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 (SHGTO) in them during their design, construction and subsequent operation. The 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 opposing surfaces of the wall fencing, floor and ceiling (ceiling) performed in them. Moreover, in some cases, to ensure the required diffusion of the sound field (uniform spatial density of sound pressure distribution over the room volume of the measuring reverberation chamber), 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 distribution of the intensity of sound energy in the air the first cavity of the measuring reverberation chamber, which is associated with an undesirable additional clutter of its useful working space.

There is a known technical solution according to the RF patent for invention No. 2579104, published on December 20, 2015, adopted as a PROTOTYPE, which presents a noisy technical room equipped with soundproofing sewing, made in the form of a soundproofing face plate and / or soundproofing molded non-flat panel, which is gapingly mounted relative to the surface 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 front panels and / or supporting wall (ceiling) structures of the technical room resonances formed on their own transverse, longitudinal and altitudinal acoustic modes. The function of partially suppressing the amplitude values of the 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 is performed by separate briquetted sound-absorbing modules composed of crushed porous sound-absorbing substances, suitably placed in given. spatial zones of air 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 structural elements (quarter-wave acoustic resonators R ^I and / or half-wave acoustic resonators R ^II ), using appropriate fasteners and a separate front panel. The use of the front panel as part of the considered technical solution causes a corresponding abrupt change (drop) in the wave acoustic resistance along the propagation path of sound waves. In addition, it should be noted the insufficient (weak) weak use of the mechanism (physical effect) of the edge diffraction absorption of sound energy, due to the small total perimeter of the edge zones of the insignificant number of used briquetted sound-absorbing modules, and / or the absence of through holes in the porous structure of the briquetted sound-absorbing modules, potentially capable of enhancing the effect of diffraction absorption of the propagation energy of sound 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 simplicity of its technical implementation, manufacturability, environmental friendliness, cost and efficiency of operation, while ensuring the effect of expanding the frequency range of reducing the level of sound radiation produced as by SHGTO, installed in the technical room, and aimed at eliminating (preventing) the implementation of zvitiya physical processes resonant interaction and enhancing the sound radiation levels and the occurrence of beats interacting acoustic signals (sound waves) with close values of frequency of acoustic oscillations f _ms and f _mA, manufactured located therein SHGTO (several SHGTO) and carries them potentially allow dynamic excitation resonant acoustic vibrations of a mass-elastic body of an air volume enclosed in an internal three-dimensional air cavity of a technical room. The need to prevent the development of the physical process of beating of interacting acoustic signals (sound waves) with close values of the frequencies of sound vibrations f _ms and f _mA 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 f _ms and f _mA . 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 effects that worsen the psycho-physiological state of a person and is a negative factor in ensuring the acoustic safety of the environment.

On the relevance and possible ways (methods, devices) of solving the problems of reducing low-frequency sound emissions at the dominant values of individual discrete frequency components f _ms , which are distinguished in the broadband spectra of sound pressures of various types of SHGTO, operated (mounted) 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 .;

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 released in the broadband sound pressure spectra 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 shown Electric power, with prominent harmonics of the frequency _{f 1s, f 2s, f 3s} , equal to 100, 200 and 300 Hz, constant multiples zna eniyu network power frequency AC f _c = 50 Hz (see. Figs. 1 and 2). Similarly, this may apply 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, pulsations of gas (air) in the processes of air intake into the cylinders of piston machines, periodic dynamic movements of air 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 with 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 the broadband frequency composition of the sound radiation generated by SHGTO . The inventive technical device is represented by a low-noise technical room equipped with technical means for effectively suppressing, 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 exclude (prevent) the implementation of the development of physical processes of low-frequency resonant interaction and subsequent resulting amplification of sound pressure levels, as well as to prevent the occurrence of physical processes of beating of interacting acoustic signals (sound waves) having sufficiently close values of sound pressure levels (SPL) and sound frequencies f _ms and f _mA produced SHGTO (f _ms ) located in it and possible dynamic excitation of resonant reactions - responses, manifested in the form of acoustic vibrations of a mass-elastic body of an air volume enclosed in an internal three-dimensional air cavity of a technical room (f _mA ). The technical result is achieved due to the appropriate application (installation with predetermined air gaps) on the wall and ceiling floors of the technical premises of the corresponding structural and technological versions of separate integral molded sound-absorbing panels made mainly of solid materials characterized by a porous air-blown crushed sound-absorbing structure in which are placed (integrated) frequency-tuned cavity cavity sound-absorbing consoles ruktivnye elements presented in the form of quarter-wave acoustic resonators R ^I _ms (see. FIGS. 8, 9, 10a, 10b, 11a, 11b, 11c, 12a, 12b, 12c, 13a, 13b, 14a, 14b, 15a, 15b, 16a , 16b, 17a, 17b, 18a, 18b, 19a, 19b).

Achievable, at the same time, effective reduction of sound energy level is realized in the extended frequency range of the sound spectrum, including both low-frequency and medium-and high-frequency sound radiation, which is due to the corresponding structural and technological combined combination with the parallel functioning of composite technical elements designed for frequency tuned suppression of low-frequency sound energy (energy of propagated low-frequency sound waves) to emitted (d leaf miner) in the frequency spectra of the noise of low-frequency acoustic resonances slabozadempfirovannyh and dissipative absorption vozduhoproduvaemym used crushed porous sound-absorbing material, medium and high frequency sound energy. In this case, the physical effect is based on realized frequency-tuned sound-canceling processes of a functioning acoustic oscillatory system excited by sound waves incident on it, which selectively absorbs acoustic energy (converts it into thermal energy) at sound frequencies close (coincident) to the natural (resonant) vibration frequency f ^I _{R of the} used quarter wave acoustic resonator R ^I. At the same time, in parallel, a highly effective broadband (medium and high frequency) sound absorption is carried out, produced directly by the substance of the crushed porous air-blown sound-absorbing structure (see Fig. 20, 21). At the same time, additional sound-absorbing surface zones formed by the free surfaces of the faces of each of the isolated crushed fragmented sound-absorbing elements are also effectively included in the physical process of absorption of sound energy. There are also 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 rib sections of separate crushed fragmented sound-absorbing elements, when they travel and bend around them by sound waves along formed, randomly distributed, communicating tortuous branched channels formed by loose adjacent and / or adhesive mating with contacting edges and faces of separate crushed fragmented sound-absorbing elements, along with the typical physical processes of sound absorption that are carried out directly by the porous structures of sound-absorbing substances of each of the separate crushed fragmented sound-absorbing elements. The hollow volumetric dead-end tubular cavities of the quarter-wave acoustic resonators R ¹ formed in the structures of separate integral molded combined sound-absorbing panels, bounded by sound-transparent air-deflectable film elastic shells, contribute to the formation of an anisotropic acoustic structure of a separate, fully-formed combined sound-absorbing panel that amplifies the absorbing energy-amplifying (energy-absorbing). Fig. 11a, 11b, 11 12a, 12b, 12c, 13a, 13b, 14a, 15a, 15b, 16a, 16b, 17a, 17b, 18a, 18b, 19a, 19b, 20, 21). An additional edge diffraction dissipative absorption of sound energy also arises in the processes of enveloping the incident sound waves of the perimetric zones of the cavity neck portions of the quarter-wave acoustic resonators R ^I (as shown in Figs. 21, 24) and the free end faces of the separate integrally formed combined sound-absorbing panels with their narrow gap gap placement relative to each other (see diagrams in FIGS. 6, 7, 8, 9, 10a, 10b, 23, 25.).

The same physical phenomena (the formation of acoustic anisotropy that improves dissipative absorption of sound energy) can be facilitated by the deliberate additional introduction of crushed sound-absorbing substances composed of porous air-blown sound-absorbing materials represented by separate crushed fragmented porous sound-absorbing elements corresponding in structural composition and geometric dimensions of crushed fragments made of dense ( nonporous) airborne polymeric substances (see Fig. 22). At the same time, 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. A similar type of physical effect of dissipative dissipation of sound energy in the edge (end) zones of sound waves passing around opposing solid-state obstacles takes place when they round the hard sound-reflecting bottom of the bottom of the quarter-wave acoustic resonator R ^I , as shown in FIG. 21. The mounting installation of separate integral molded 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 their free edge zones of the porous sound-absorbing structure, when they are freely enveloped by propagated sound waves (see Fig. 23).

As a result of achieving higher resulting sound-absorbing effects, in some cases this allows, if necessary, to reduce the amount of porous sound-absorbing substance used, while satisfying the specified (defined by the technical task for the development or technical conditions for manufacturing) required value of the sound damping effect. For similar reasons, it is possible to use cheaper and environmentally friendly starting semi-finished raw materials to obtain sound-absorbing material (hereinafter - ZPM), produced from industrial and technological waste, industrial scrap, or dismantled porous sound-absorbing structures of materials contained in soundproof packages of technical objects that have completed their life cycle and forced recycling. Ultimately, this helps to improve the environmental safety characteristics of the inventive technical device (and the concomitant "improvement" of the environment), which is realized by reducing the amount of unproductively disposed sound-absorbing substances, which are forced to undergo, including burial processes (for example, in the form of dismantled noise-reducing packages included in the parts and components of automatic telephone exchanges that have completed their life cycle), which do not allow their direct energy disposal by incineration, so releasing hazardous and dangerous combustion products and / or destructive, including ozone (CO ₂ emissions). This even more actualizes the economic and environmental efficiency and feasibility of using technical devices that use recyclable waste as a 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 materials include the relevant parts (panels, upholstery, gaskets made of porous ZPM) already selected, selected from the dismantled soundproofing packages of various technical objects such as noiseless 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 rooms of spring units and the like), and / or used in various types of building objects (zvukoteploizolyatsionnye fibrous or open cell foam facing panels for wall linings, floors, elevator shafts, ventilation systems). Ultimately, this allows to reduce the 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, including 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 technological operations of mechanical crushing (cutting / slicing) 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 integral molded sound-absorbing panels of a low-noise technical room, can also be used produced "new" isolated crushed fragmented sound absorbing bathtubs. The term “new” means crushed fragmented sound-absorbing elements made from “new” (not recyclable) raw materials, for example, from a semi-finished product of a flat-sheet type (flat sheets or ZPM rolls). Combined mixtures can also be used, given in certain proportions of dosed combinations of separate crushed fragmented sound-absorbing elements obtained from recycled recycling materials of parts and assemblies, to which a certain amount of produced “new” separate crushed fragmented sound-absorbing elements of a given geometric shapes and overall dimensions made from the "new" initial semi-finished porous raw materials 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 acoustic parameters of the porous sound absorber glazing substance. In this way, technological procedures can be implemented, to one degree or another, to improve the physical (acoustic) characteristics of the 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 the 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, which is represented by a closed-type electric transformer substation (ETPZT) located in the technical room on 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 type power transformer from PLATTHAUS company (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 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. 4 shows the experimental results of measurements of the sound pressure spectrum (1/3 octave spectrum) emitted by SHGTO 9, presented by a piston compressor company STAL (Sweden), mounted inside the technical room 1, represented by a compressor-refrigeration station of the 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 casing, at a height of 1.2 m from the floor surface 4 of the technical room 1;

- in FIG. 5 shows a schematic illustration of the technical room 1 and the basic directions and transmission paths of air and structural noise emitted by SHGTO 9 mounted in a closed (closed) technical room 1;

- in FIG. 6 shows an illustrative, specific example of a technical room 1 with a ShGTO 9 installed in it, presented in the form of a power electric transformer, with ceiling mounted on a wall (pos. 2) and ceiling 3 (not shown in Fig.), Separate separate, all-molded combined sound-absorbing panels 10, integrated into their porous structure of the quarter-wave acoustic resonators R ^I _ms (pos. 11) formed using the carrier inner elastic film vozduhoneproduvaemoy th sound transmission casing 20 and the rigid bottom of a reflecting bedplate 29;

- 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 mounted on a wall (pos. 2) and ceiling 3 (not shown in Fig.), separate, fully formed combined sound-absorbing panels 10, with quarter-wave acoustic resonators R ^I _ms (pos. 11) integrated into their porous structure, formed using a carrier internal air-blown film elastic soundproof the shell 20 and the hard, sound-reflecting bottom of the bottom 29;

- in FIG. 8 schematically depicts a fragment of a wall enclosing ceiling (pos. 2) of a 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 surfaces;

- 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. 10a, a wall fencing (overlapping) 2 of a technical room 1 with combined, without mutual overlapping, installation of separate integrally formed combined sound-absorbing panels 10, mounted unobtrusively directly on the surface of a wall floor (pos. 2) of a technical room 1, and installed with a given air remote clearance k relative to the opposite surface of the wall fence (floor), pos. 2;

- in FIG. 10b schematically shows a wall fencing (overlapping) 2 of the technical room 1 with combined, mutually overlapping, mounting separate integral molded combined sound-absorbing panels 10 mounted gaplessly directly on the wall surface (pos. 2) of the technical room 1, and installed with a given air remote clearance k relative to the opposite surface of the wall fence (floor), pos. 2, the lining of the separate integral molded combined sound-absorbing panels 10 is blocked by a sound-transparent facing protective and decorative perforated panel 25;

- 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 19;

- 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 a sound-transparent element 24 of a separate whole-molded combined oh sound absorbing panel 10;

- in FIG. 12a shows an example of a possible structural and technological embodiment of technical means for securing in a vertical position separate detached integrally formed sound-absorbing panels 10 by using the corresponding type of mounting spikes 14 passing through the structure of a continuous supporting support base 22;

- in FIG. 12b shows an example of a possible structural and technological embodiment of technical means for securing in a vertical position separate detached integrally formed sound-absorbing panels 10 by using an appropriate type of mounting frame 15 holding the detached integrally formed combined sound-absorbing panel 10 in the upper and lower parts;

- in FIG. 12c shows an example of a possible structural and technological implementation of technical means for securing in a vertical position separate detached integrally formed sound-absorbing panels 10 by using the corresponding type of mounting elastic (vibration-isolating) elements 16 integrated into the structure of the external thin-walled soundproof sheath 19;

- in FIG. 13a presents an example of a possible structural and technological embodiment of technical means for securing in an upright position separate detached integral formed sound-absorbing panels 10 by using the appropriate type of mounting profiles 17 fixed to the mounting surface by means of mechanical fasteners;

- in FIG. 13b presents an example of a possible structural and technological embodiment of technical means for securing in a horizontal position separate detached integral formed sound-absorbing panels 10 by using the appropriate type of mounting profiles 17 fixed to the mounting surface by means of mechanical fasteners;

- in FIG. 14a shows a longitudinal section of a detached integrally formed combined sound-absorbing panel 10, in which a porous air-blown sound-absorbing structure composed of separate fragmented fragmented sound-absorbing elements 18 integrates dead-end tubular, round cross-section, cavity quarter-wave acoustic resonators R ^I _{ms formed} (pos. 11). the use of a carrier inner air-blown film elastic soundproof shell 20 and hard sound azhayuschego bottoms bottom portion 29;

- in FIG. 14b shows a side view of the end face of a separate integral molded combined sound-absorbing panel 10 from the neck portion 30 (pos. 29) of the quarter-wave acoustic resonator R ^I _ms (pos. 11), the tubular part 28 of which is made in the form of a circular cylinder, a separate integral molded combined sound-absorbing panel 10 is composed of two composite modules 27 connected by an adhesive coating 26 to the mating surfaces;

- in FIG. 15a shows a longitudinal section of a separate, integral molded combined sound-absorbing panel 10, in which a porous air-blown sound-absorbing structure composed of separate fragmented fragmented sound-absorbing elements 18 integrates dead-end tubular, rectangular cross-section, cavity quarter-wave acoustic resonators R ^I _{ms formed} (pos. 11). the use of a carrier inner air-blown film elastic soundproof shell 20 and hard ukootrazhayuschego bottoms bottom portion 29;

- in FIG. 15b shows a side view of the end face of a separate integral molded combined sound-absorbing panel 10 from the neck portion 30 (pos. 29) of the quarter-wave acoustic resonator R ^I _ms (pos. 11), the tubular portion 28 of which is made in the form of a rectangular cylinder, a separate integral molded combined sound-absorbing panel 10 is composed of two composite modules 27 joined by an adhesive coating 26;

- in FIG. 16a 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 18, dead-end tubular, cavity elements, in the form of circular and rectangular cylinders formed using a load-bearing inner air-tight opaque elastic membrane, are integrated 20 and a hard sound-reflecting bottom of the bottom 29, forming a quarter acoustic wave resonators R ^I _ms (pos. 11), characterized by a frequency resonance tuning (parameter f ^I _Rms ), determined by their geometric l ^I _r and dynamic l ^I _R lengths;

- in FIG. 16b shows a side view of the end face of a separate integral molded combined sound-absorbing panel 10 from the throat portion 30 (pos. 29) of the quarter-wave acoustic resonator R ^I _ms (pos. 11), the tubular part 28 of which is made in the form of a circular and rectangular cylinder, a separate integrally molded combined the sound-absorbing panel 10 is composed of two composite modules 27 connected by an adhesive coating 26;

- in FIG. 17a shows a longitudinal section of a separate, integral molded combined sound-absorbing panel 10, in which a porous air-blown sound-absorbing structure, composed of separate fragmented fragmented sound-absorbing elements 18, are integrated dead-end tubular, cavity elements formed using a bearing inner air-tight, soundproof transparent film casing 20 parts 29, made in the form of non-smooth (rough ) the wall surface of the formed cavity of the tubular part 28 of the quarter-wave acoustic resonator R ^I _ms (item 11);

- in FIG. 17b shows a side view of the end face of a separate integral molded combined sound-absorbing panel 10 from the throat portion 30 (pos. 29) of the quarter-wave acoustic resonator R ^I _ms (pos. 11), the tubular part 28 of which is made in the form of a circular cylinder, a separate integral molded combined sound-absorbing panel 10 is composed of two composite modules 27 joined by an adhesive coating 26;

- in FIG. 18a shows a longitudinal section of a separate, integrally molded combined sound-absorbing panel 10, in which a porous air-blown sound-absorbing structure composed of separate fragmented fragmented sound-absorbing elements integrates dead-end tubular, cavity elements formed using a load-bearing inner air-tight, film-like, sound-transparent, opaque, translucent, opaque, translucent sheath 29, in the form of six (three pairs) quarter-wave aku of resonators R ^I _ms (pos. 11), which differ in frequency resonance tuning (parameter f ^I _Rms ), determined by their geometric l ^I _r and dynamic l ^I _R lengths, with the opposite arrangement of pairs of open neck parts (pos. 30) located in opposite end faces 32, and common hard sound-reflecting bottoms of the bottom part 29 as part of a separate, integral molded combined sound-absorbing panel 10;

- in FIG. 18b shows a side view of the end face of a separate integral molded combined sound-absorbing panel 10 from the neck portion 30 (pos. 29) of the quarter-wave acoustic resonator R ^I _ms (pos. 11), the tubular portion 28 of which is made in the form of a circular cylinder, a separate integral molded combined sound-absorbing panel 10 is composed of two composite modules 27 joined by an adhesive coating 26;

- in FIG. 19a is a longitudinal sectional view of an isolated, fully molded, combined sound absorbing; panel 10 mounted on the ceiling 3 of the technical room 1, in the structure of which vertically located deadlock tubular, cavity quarter-wave acoustic resonators R ^I _ms (pos. 11) are formed, formed using a carrier inner air-blown film elastic soundproof shell 20 and a hard sound-reflecting bottom of the bottom 29, (open throat parts 30 of the tubular parts 28 of the quarter-wave acoustic resonators R ^I _{ms are} directed downward, towards the floor of the technical room 1);

- in FIG. 19b shows a side view of the end face of a separate integral molded combined sound-absorbing panel 10, a separate integral molded combined sound-absorbing panel 10 is composed of two composite surfaces 27 connected by an adhesive coating 26 to the mating surfaces;

- in FIG. 20 is a schematic representation of the implementation of the physical process by partial amplitude interference compensation of the incident (P _pad ) sound wave with the reflected (P _OTR ) sound wave in the throat region 30 of the quarter-wave acoustic resonator R ^I _ms (pos. 11), with a variant of its structural and technological design the side wall in the form of a supporting internal air-blown film elastic shell 20, which ensures the passage of a sound wave (P _CR ) into the structure of a porous sound-absorbing substance, comprising one of the isolated fragmented fragmented sound-absorbing elements 18, with the corresponding effect of absorption of a part of the sound energy of the incident (P _pad ) and reflected P _er sound wave;

- in FIG. 21 is a diagram of the implementation of the mechanisms of diffraction absorption of energy of incident sound waves at the peripheral peripheral zones of the open neck 30 and the end perimetric zones of the hard sound-reflecting bottom of the bottom part 29 of the quarter-wave acoustic resonator R ^I _ms (item 11);

- in FIG. 22 shows a diagram of the implementation of the mechanism of diffraction absorption of energy of propagating sound waves in the porous sound-absorbing structure of a substance of a fragment of a closed internal cavity 31 of a separate integrally formed combined sound-absorbing panel 10, comprising in the structure of a porous sound-absorbing substance represented by separate fragmented sound-absorbing elements 18, sound-reflecting or non-air-breathing or closed dense non-porous structures measuring materials;

- in FIG. 23 shows a diagram of the implementation of the physical process of diffraction envelopes by sound waves in narrow-gap air gaps of the edge (end, end) zones of the end faces of 32 porous sound-absorbing air-blowing structures of matter of separate integral molded sound-absorbing panels 10, with associated dissipative energy losses (additional absorption) associated with them (additional absorption);

- in FIG. 24 is a diagram of the implementation of the physical process of diffraction envelopes by sound waves of the edge perimetric zones of the throat parts 30 cavities of the tubular parts 28 quarter-wave acoustic resonators R ^I _ms (item 11) integrated into the structure of the porous sound-absorbing air-blown substance represented by separate fragmented fragmented sound-absorbing elements 18, in the composition separate whole-molded combined sound-absorbing panels 10, with the associated dissipate an apparent energy losses;

- in FIG. 25 is a diagram of the mounting clearance (γ, k) installations of the separate integral molded sound-absorbing panels 10 relative to the surface of the enclosing wall structure (pos. 2) of the technical room 1 (clearance k) and between the opposite end faces 32 of the separate integral molded 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 digital positions in the figures shown indicate:

1 - technical room;

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

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

4 - floor of the 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 air cavity 8);

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

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

11 - quarter-wave acoustic resonators R ^I (R ^I _ms , R ^I _mA );

12 - remote mechanical fasteners;

13 - suspended cable elements;

14 - mounting spikes;

15 - mounting frames;

16 - mounting elastic elements;

17 - mounting profile;

18 - separate fragmented fragmented sound-absorbing elements;

19 - supporting external surface cladding translucent;

20 - carrier internal air-blown film elastic soundproof shell forming the tubular part 28 of the quarter-wave acoustic resonator R ^I (R ^I _ms , R ^I _mA ), pos. eleven;

21 is an external surface cladding translucent material layer;

22 - a support base made of a solid dense air-blown sound-reflecting material (hereinafter - the support base 22);

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

24 - 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 24);

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

26 - adhesive continuous layered (film) or intermittent (fibrous, powder, perforated film) sound-transparent coating, represented by a correspondingly surface and / or volumetric distributed adhesive adhesive or thermosetting hot-melt adhesive material (hereinafter referred to as adhesive coating 26);

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

28 - the tubular part of the quarter-wave acoustic resonator R ^I (pos. 11);

29 - hard sound-reflecting bottom of the bottom part (bottom part) of the quarter-wave acoustic resonator R ^I (pos. 11);

30 - throat part of a quarter-wave acoustic resonator R ^I (pos. 11);

31 - a closed inner cavity of a separate integrally formed combined sound-absorbing panel 10;

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

33 - protective lining damping air-blown layer of material mounted on the throat portion 30 of the quarter-wave acoustic resonator R ^I (pos. 11);

34 - narrow-gap air gaps formed between the opposite end faces 32 of the separate separate molded combined sound-absorbing panels 10 mounted on the supporting wall elements of the walls 2 and ceiling 3 of the technical room 1;

35 - a rigid sound-reflecting end part of an integrally formed combined sound-absorbing panel 10 used to form a single bottom part 29 of quarter-wave acoustic resonators R ^I (pos. 11);

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

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

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

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

R ^I - quarter-wave acoustic resonator;

R ^I _ms is a quarter-wave acoustic resonator designed to damp the noise generated by SHGTO 9 produced by it at the working functional frequencies of acoustic radiation f _ms ;

R ^I _1s is a quarter-wave acoustic resonator designed to damp the noise generated by SHGTO 9 produced by it at the working functional frequency of acoustic radiation f _1s ;

R ^I _2s is a quarter-wave acoustic resonator designed to damp the noise generated by SHGTO 9 produced by it at the working functional frequency of acoustic radiation f _2s ;

R ^I _3s is a quarter-wave acoustic resonator designed to damp the noise generated by SHGTO 9 produced by it at the working functional frequency of acoustic radiation f _3s ;

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

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

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

f _mA (f _mL , f _mB , f _mH ) - discrete values of the eigenfrequencies of sound vibrations on the eigen acoustic modes of a mass-elastic body of 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, in the direction of its overall parameters A (L, B, H), Hz;

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 natural (resonant) frequency in Hz of the acoustic resonator R;

f ^I _R is the natural (resonant) frequency in Hz of the quarter-wave acoustic resonator R ^I ;

f ^I _R1s , f ^I _R2s , f ^I _R3s, are the natural (resonant) frequencies in Hz of the quarter-wave acoustic resonators R ^I _1s , R ^I _2s , R ^I _3s (pos. 11), designed to damp the noise generated by SHGTO 9 produced him on his discrete values of the working dominant functional frequencies of the acoustic radiation f _1s , f _2s , f _3s ;

Δf _R is the width of the frequency band 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 resonant frequency of the acoustic resonator f _R ;

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

s is the speed of sound, m / s;

c (t ° C _st ) - the speed of sound waves in m / s, propagated in the air of technical room 1 at a steady temperature of air, in t ° C _st ;

λ is the sound wavelength, m;

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

λ _R ^I - the length of the sound wave, a quarter of the distance of which (0.25λ _R ^I ) fits within the dimensions of the dynamic length I _R ^{I of the} quarter-wave acoustic resonator R ^I ;

Δ _λ is the range of changes in the length of the sound wave λ in m, caused by the operational range of changes in air temperature Δ _t in the technical room 1, in which the sound wave propagates;

λ _ms - the sound wavelength of the working dominant functional frequency f _ms sound radiation SHGTO 9, operating at a given steady state operating mode n _s , m;

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

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

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

t ° C _st - steady-state (stabilized) value of air temperature in ° C in the internal three-dimensional air cavity 8 of the technical room 1;

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

P _pad - the amplitude of the sound wave incident on a solid obstacle;

P _neg - the amplitude of the sound wave reflected from a solid obstacle;

P _ol - the amplitude of the sound wave passing through a solid obstacle in the path of its propagation (passing into the structure of a porous sound-absorbing substance composed of isolated fragmented fragmented sound-absorbing elements 18);

P _rez - the amplitude of the resulting sound wave, formed in the process of dynamic (amplitude, phase) interaction of the incident, reflected and transmitted through the obstacle sound waves;

d _pp is the reduced hydraulic diameter, in m, of an arbitrary geometric shape of the bore of the tubular part 28 (for a circular _bore , d _p = d _kp , where d _kp is the diameter of the circle) of the quarter-wave acoustic resonator R ^I (R ^I _ms , R ^I _mA ) , pos. eleven;

S _t - the area of the bore, in m ² , of the tubular part 28 of the quarter-wave acoustic resonator R ^I (R ^I _ms , R ^I _ma ), pos. eleven;

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

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

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

k is 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 opposite surfaces of the end faces 32 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;

α _N is the normal coefficient of sound absorption;

A _ekv is the area of equivalent sound absorption;

K _perf - perforation coefficient;

ρ _f - density in kg / m ³ filling the closed inner cavity 31 of the separate integral molded combined sound-absorbing panel 10 separate crushed fragmented sound-absorbing elements 18;

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, the floor and the ceiling; recorded at the frequencies of their own half-wave acoustic resonances of their own acoustic modes of the mass-elastic body of the air volume (cavity) of the room.

Diffraction of sound waves is a physical phenomenon associated with the deviation of waves from their linear propagation when interacting with a solid 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 porous element of finite dimensions (forming an edge diffraction effect) causes an additional flow of sound energy directed (propagating) into the porous structure of this element, which leads to an increase in the total sound-absorbing effect.

A diffuse sound field is a sound field at each point of which the sound pressure level is the same; formed in enclosed spaces (rooms) bounded 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 a sound-absorbing material, with 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 .

The equivalent sound absorption area 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. Reverberation coefficient of sound absorption α _rev = 1,0 srvc. units 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; determined by the results of recording the localization of the amplitudes of the maximum and minimum values of the sound pressures of standing waves artificially created in an acoustic interferometer (Kundt tube), with subsequent calculation of the values at each frequency of the sound wave under study.

Sound transparency is the 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 the 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 the 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 an unlimited space (or limited space) of the waveguide 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 harmonic sound vibrations with close frequencies, manifested in the form of alternating amplitude maxima and minima.

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.), forming an 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 that protect wood, fabrics and other materials of organic origin (including sound absorbing or sound insulating) from ignition and self-combustion. They decompose with the formation of non-combustible and / or prevent the decomposition of the material with the release of combustible gases. Fire 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 are aluminum hydroxide, boron, antimony, chloride compounds, and 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 zone) 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 dynamically connected and interacting fibers; 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 based on 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, styrene-butadiene 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-generated sound-absorbing substance is an original raw material of recycled recycling processing of acoustic materials, mainly; porous air-blown sound-absorbing fibrous and / or: foamed open-cell, contained in parts and assemblies that have completed their life cycle, as well as in industrial and technological marriage of production and production waste of these types of acoustic materials, used second time as the initial production raw material in the manufacture of various technical devices for reducing noise emissions produced by various noise-generating objects (noise screens, noise absorbing panels, noise insulating upholstery of engine compartments, luggage compartments and passenger rooms of vehicles and other technical devices for ensuring acoustic environmental safety); used isolated crushed fragmented sound-absorbing elements made from the indicated type of utilized raw materials are made from 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 multilayer combinations of identical or different geometric shapes and dimensions that are advantageous essentially in a 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 “technological stitching” of their mating surfaces) causes an acceptable drop in the reverberation sound absorption coefficient (α _rev ) of not 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 per 1 m ^{2 of the} surface (non-blown continuous film or foil layers). The values of the resistance to blowing through the air stream of translucent air-permeable fabrics or air-permeable 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 polymeric or microperforated foil metal layer constituting 0.025 ... 0.25 mm and their surface density 20 ... 300 g / m ² . The values of the surface density (specific surface mass) of continuous sound-transparent films not blown by the air flow should be in the range of 20 ... 70 g / m ² , with a film thickness of 0.01 ... 0.1 mm. Sound-transparent material can be made of various structural materials - 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, followed by the production of, as a rule, non-planar parts of complex geometric shape that implements a geometric topology of various curvature, porosity, density, etc.

Resonance oscillation modes (intrinsic acoustic modes) are 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 resonant 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 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 a part (assembly) at a given distance, the diameter of which 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 losses - irreversible dispersion (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 related, for example, to 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).

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

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

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

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

m _L - 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 in the direction of its overall length L, expressed as an integer of the natural number (m = 1, 2, 3 ...);

m _in - 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 in the direction of its overall width B, expressed as an integer of the natural number (m = 1, 2, 3 ...);

m _n - 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 in the direction of its overall height H, expressed as an integer of the natural number (m = 1, 2, 3 ...).

The essential features of the claimed technical solution are also illustrated by figures 1 ... 25.

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, in the form of propagated sound waves qualified by noise, and depicted in the indicated figure by 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, the corresponding sound and temperature fields are formed (spatially distributed) in the internal three-dimensional air cavity 8. 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 installation, an electric generator, a power electric transformer, a blowing machine, an axial or centrifugal type exhaust fan, 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 characteristics of the resulting mass-elastic body of the air volume characterized, in particular, by certain values of the lower eigen acoustic modes that form on the corresponding discrete eigenvalues ( 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 phe- process of dynamic excitation and response of the dynamic vibrational response of an elastic air environment as a result of propagation of sound waves present in the form of acoustic vibrations own weight and the elastic body of the air volume enclosed within the inner cavity of the three-dimensional air 8 technical room 1.

A distinctive feature of the proposed technical device, presented in the form of a low-noise technical room 1, is the equipment (lining of wall and ceiling structures) of the technical room 1, mounted with air gaps between opposite end faces and relative to the opposing mounting surfaces (wall 2 and ceiling 3) of the technical room 1 , separate integral molded combined sound-absorbing panels 10 (see Fig. 6, 7, 8, 9, 10a, 10b, 11b, 11c, 12a, 12b, 12c, 13a, 13b), composed of pores true air-blown crushed sound-absorbing structure of the substance and integrated cavity frequency-tuned noise-canceling structural elements, represented in the form of quarter-wave acoustic resonators R ^I (pos. 11).

Installation in a technical room 1 of separate, individually formed, combined sound-absorbing panels 10 can, in particular, be carried out by hanging them from the ceiling 3 using the appropriate type of remote mechanical fasteners 12 (see Fig. 11a), hanging cable elements 13 (see Fig. 11b and 11c), mounted on walls 2 by means of a mounting profile 17 (see Fig. 13a and Fig. 13b), with the formation of vertically suspended volumetric absorbers of sound energy, mounted with a remote air gap k between blenny integral molded sound-absorbing panel 10 and the wall 2 of the technical room 1 (see Fig. 9, 10a, 10b, 13a, 13b), or mounted seamlessly (see Fig. 12a, 12b, 12c) on the surface of the wall fences (floors) technical rooms 1, with the use of mechanical fasteners in the form of mounting spikes 14 passing through the structure of a continuous supporting support base 22, frames 15, holding a separate integrally formed combined sound-absorbing panel 10 in the upper and lower parts, elastic elements 16, integ formed into the structure of the external thin-walled translucent shell 19. The remote air gap γ between the opposite end surfaces of the faces of the mounted samples of separate integral molded sound-absorbing panels 10 is at the same time not more than a quarter of the overall thickness (dimensions) of the opposite end faces of 32 separate separate molded combined sound-absorbing 10. stand-alone whole-molded combined sound-absorbing panels 10 mo they can be covered by an additionally installed sound-transparent facing protective and decorative perforated panel 25 (K _perf ≥ 0.25), which freely transmits emitted sound waves in the direction of the mounted separate integral molded combined sound-absorbing panels 10, as, in particular, shown in FIG. 10b. Sound-transparent facing protective and decorative perforated panel 25 can be mounted gaplessly (contactlessly) to the surfaces of separate integral molded combined sound-absorbing panels 10 or with a given air gap. 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 25 does 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 sound-reflecting surfaces of ceiling 3 or wall 2 floors of the technical room 1 located close to them (if this does not limit the requirements of the technical specification for development), as shown in FIG. 9, 10b, 11a, 11b, 11c, 13a, 13b, 25, allows you to intentionally 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 diffraction absorption of sound energy arising on free perimetric edges (end zones) of separate integrally formed combined sound-absorbing panels 10 when they are diffractively enveloped by reflected sound waves (see Figs. 23, 25). Enveloped during its propagation and scattered in a porous sound-absorbing substance on the free peripheral edges of each separate integrally formed combined sound-absorbing panel 10, the sound wave due to the realized edge diffraction effect of dissipative absorption of its energy is accompanied by the process of additional flow of sound energy from its front to the rear porous surface. For the reflected sound wave from the surface of the wall or ceiling, a similar diffraction dissipation 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 propagation deep into the porous air-produced sound-absorbing structure of the isolated whole-shaped combined 10 panel. , in turn, leads to the corresponding additional cut the ultimate effect of increasing dissipative absorption of sound energy.

The separate integrally molded combined sound-absorbing panel 10 is made in the form of an integrally molded three-dimensional shell structure containing, as a component, carrying an external surface cladding sound-transmissive air-tight or air-blowing shell 19. A closed inner cavity 31 formed by the bearing outer surface of the cladding sound-transparent translucent or air-tight air-tight coupled with an adhesive joint carrying internal air windproof film flexible sound transmission sheath 20 forming a tubular portion 28 quarterwave acoustic resonator R ^I (pos. 11), separate tselnoformovannoy combined sound absorption of the panel 10, is filled with porous vozduhoproduvaemym sound absorbing material formed distinct crushed fragmented sound absorbing members 18, with contacting each other ribs and edges as a result of which numerous additional communicating sinuous intercostal and inter wound air-blown waveguide sound-propagating (sound-transmitting) and, accordingly, sound-absorbing channels. This type of sound absorbing material used includes predominantly identical or different types, structures and brands of porous air-blown sound-absorbing materials, characterized by identical or different physical characteristics, chemical and structural composition, amount and combination of used types of structures of porous layers in multilayer combinations of sound-absorbing materials, identical or different geometric shape and overall; sizes made from solid utilizable, 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 defective production of sound-absorbing materials and parts and assemblies made from them. The specified closed internal cavity 31 of a separate integral molded combined sound-absorbing panel 10, by means of a bearing internal air-blown film elastic soundproof sheath 20 communicates with attached hollow hollow molded sound-absorbing (noise-canceling) structural elements (at least one hollow hollow hollow element) in the form of quarter-wave acoustic resonators R ^I (pos. 11). The tubular parts 28 of these quarter-wave acoustic resonators R ^I (pos. 11) are formed using a supporting internal air-blown film elastic soundproof shell 20 (see Fig. 11a, 1b, 11c, 12a, 12b, 12c, 13a, 13b, 14a, 14b, 15a, 15b, 16a, 16b, 17a, 17b, 18a, 18b, 19a, 19b), lining inside the surface of the faces (edges) of the edges and edges of the separate crushed fragmented sound-absorbing elements 18 located in the inner cavity 31 of the separate integral molded sound-absorbing panel 10. Adhesively attached to the tubular parts 28, the hard, sound-reflecting bottoms of the bottom parts 29 of the quarter-wave acoustic resonators R ^I (pos. 11) are made of a rigid plate-like type of polymeric material (for example, f polyamide, polyvinyl chloride, polyethylene, polypropylene). The closed} internal cavity 31 of the separate integral molded combined sound-absorbing panel 10 is filled with separate crushed fragmented sound-absorbing elements 18, which are made mainly of recyclable acoustic materials. Also, they (isolated fragmented fragmented sound-absorbing elements 18) can be manufactured according to typical production technologies from “new” semi-finished sheet (roll) acoustic materials subjected to the subsequent technological process of their mechanical crushing into fragments of a given geometric shapes and overall dimensions, in addition to placed in a closed inner cavity 31 of a separate integrally formed combined sound-absorbing panel 10, separated by crushed fragmentary annym sound absorbing member 18 made of recyclable acoustic waves; the 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 31 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 23.

The ensured sound transparency properties of the supporting outer surface cladding soundproof sheath 19, as a part of a separate integrally formed combined sound-absorbing panel 10, are substantially characterized by the selected respective values of the resistance parameters to blowing through the fabric or non-woven fabric or microperforated film or microperforated foil layers), and / or established values of thickness, bending stiffness and specific surface mass s, determined by the mass per 1 m ² surface (not blown by the air stream of continuous film or foil layers). The values of the resistance to blowing through the air stream of translucent air-borne fabrics or translucent breathable non-woven fabrics (micro-perforated polymer film or micro-perforated foil metal layers) should be within 20 ... 500 ns / m ³ , with the thickness of the fibrous layer of fabric material, fibrous non-woven fabric, microperforated film polymer or microperforated foil metal layer, components of 0.025 ... 0.25 mm and their surface density 20 ... 300 g / m ² .

The values of the surface density (specific surface mass) of continuous sound-transparent films not blown by the air flow should be in the range of 20 ... 70 g / m ² , with a film thickness of 0.01 ... 0.1 mm. The outer surface cladding translucent material layer 21 of the supporting outer surface cladding translucent sheath 19 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 21 of the supporting outer surface cladding translucent sheath 19 can be solid or perforated. For example, it can be made of micro-perforated (with a bore diameter of the 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 21 of the supporting outer surface cladding translucent shell 19, 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 types of structural materials for the manufacture of an external surface cladding sound-transparent layer of material 21 of the supporting external surface This veneered soundproof sheath 19, used as part of a separate integral molded combined sound-absorbing panel 10, provides for a given packing density (ρ _f = 10 ... 655 kg / m ³ ) of the closed inner cavity 31 of a separate integral molded combined sound-absorbing panel 10, corresponding isolated crushed fragmented sound-absorbing elements 18, the elimination of unwanted ingress and accumulation (absorption) in porous open-cell foam or porous fibrous structures of separate crushed fragmented sound-absorbing elements 18, 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 (sound-transparent technological “cross-links”) of the constituent elements of a separate integral molded combined sound-absorbing panel 10, various types of sound-transparent adhesive coatings 26 can be used, realized, for example, by appropriate temperature heating and melting of the used hot-melt polymer films or fibers placed on the surface of the structure outer surface cladding translucent material layer 21 (bearing to it an external surface cladding soundproof sheath 19), or a supporting inner air-blown film elastic soundproof sheath 20, or between contacting ribs and faces of separate crushed fragmented sound-absorbing elements 18 during the implementation of the manufacturing process of manufacturing a separate whole-molded combined sound-absorbing panel 10. For possible implementations of various constructive technological options for the execution of a stand-alone whole-mold a combined sound-absorbing panel 10, when the polymeric material of the outer surface cladding is an opaque layer of material 21 (the supporting outer surface cladding is an opaque sheath 19) or the carrier is an internal air-blown film elastic soundproof sheath 20, which does not provide the required adhesive bond by melting it (with appropriate heating structure), a satisfactory adhesive compound can be provided by the introduction of additional sound translucent (not significantly negative, by no more than 10%, for decreasing the sound absorption coefficient of sound energy) of a certain type of adhesive adhesive layers (in the form of sticky adhesive or thermoactive hot-melt substances), technologically realized by surface separated separate thin solid lines, or surface spaced apart by separate thin dashed lines, or in the form of a thin continuous surface layer of perforated perforated through holes or as a continuous thin sound-transparent adhesive adhesive layer with a low specific surface weight (not exceeding 100 g / m ² ), or in the form of a continuous thin sound-transparent heat-sensitive hot-melt adhesive layer of an adhesive substance with a low specific surface weight (not more than 50 g / m ² ).

In a closed inner cavity 31 of a separate integral molded combined sound-absorbing panel 10 filled with sound-absorbing material formed by separate crushed fragmented sound-absorbing elements 18, corresponding internal embedded sound-transparent reinforcing elements 24 of the rod, or mesh, or plate-perforated types may be contained.

The supporting outer surface soundproofing cladding shell 19 of the separate integral molded combined soundproofing panel 10 may additionally be overlapped by a metal or polymer soundproofing decorative and decorative mesh or perforated panel 25 (as shown in Fig. 106), with a perforation coefficient K _perf ≥ 0.25.

The tubular parts 28 of the quarter-wave acoustic resonators R ^I (pos. 11) can be aligned and contain a common sound-reflecting bottom of the bottom part 29, in the form of an attached rigid sound-reflecting end part 35, attached to a separate integral molded combined sound-absorbing panel 10, as shown in FIG. 17a.

During operation of SHGTO 9, which contains thermally loaded units and systems mounted in the immediate vicinity of the surface zones of separate integral molded combined sound-absorbing panels 10 and sound-transparent facing protective and decorative perforated panels 25 of the technical room 1, the indicated structural elements (pos. 10 and 25) can be performed with given their heat-resistant fire-safe design and technological performance. In these cases, in particular, flame retardants can be used for their structural impregnation and / or thin-layer surface filling. 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 outer surface soundproofing cladding 19 and the protective lining damping air-blown material layer 33 mounted on the neck portion 28 of the quarter-wave acoustic resonator R ^I (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 26 and to separate crushed fragmented sound-absorbing elements 18. 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 Wall (pos. 2) and / or ceiling (pos. 3) constructions of the specified acoustic elements (pos. 10, 25, 19, 26, 18), obtained from SHGTO, can be made from other types of materials that do not require flame retardant treatment or not requiring a metal design, 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-shapes) mated together in a monolithic construction of composite prefabricated modules 27 (see Fig. 14b, 15b, 16b, 17b, 18b, 19b) can be presented in the form of prefabricated one-piece joints, using the corresponding sound-transparent adhesive coatings 26, made in the form of continuous, or perforated film, or intermittent fibrous or pore erratic soundproof coatings. They can be represented by an appropriate surface and / or volume distribution of sticky adhesive or thermoactive adhesive substances, with the formation in the inner cavity 31 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 between themselves crushed fragmented sound-absorbing elements 18, and quarter-wave acoustic p act as resonators R ^I (pos. 11).

The outer surface layer formed by adhesively bonded contacting faces and ribs of individual samples of separate crushed fragmented sound-absorbing elements 18, as a 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, adheres the surface of the supporting external surface cladding soundproof shell glasses 19 as part of a separate integral molded combined sound-absorbing panel 10.

The outer surface layer of the porous air-blown sound-absorbing structure, composed of separate crushed fragmented sound-absorbing elements 18, which are appropriately distributed in the spatial zones of the inner cavity 31, adjacent (mating) with the carrier inner air-blown film elastic sound-transparent shell 20 and a rigid sound-reflecting bottom 29, the bottom respective dimensions tubular parts 28 quarter-wave acoustic resonators R ^I (pos. 11) integrated in the porous air-blown structure of the substance of a separate whole-molded combined sound-absorbing panel 10.

Hollow molded cavity tanks represented by bottom 29, tubular 28 and throat 30 parts of the quarter-wave acoustic resonator R ^I (pos. 11), as part of a separate integral molded combined sound-absorbing panel 10, can include acoustic quarter-wave resonators R ^I (of identical overall dimensions and geometric shapes) ( Pos. 11), as shown in FIG. 11a, 11b, 11c, 14a, 15a, 17a, 19a, 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 ^I _R ) formed by acoustic quarter-wave resonators R ^I (pos. 11), as well as differing overall dimensions and geometric shapes of acoustic quarter-wave resonators R ^I (pos. 11), as shown in Figs. 16a, 16b, 18a, providing their different frequency tuning to preset from varying values (given a set of values of sound frequencies grouped into a narrow frequency band) of the natural (resonant) frequencies of sound vibrations (f ^I _R ) of the formed quarter-wave acoustic resonators R ^I (pos. 11).

обеспечивает компенсационное выравнивание полей давлении падающих глад и отраженных Р_отр звуковых волн в зоне горловой части 30 четвертьволнового акустического резонатора R^I (поз. 11). Указанная частотная настройка эффективного функционирования четвертьволнового акустического резонатора R^I (поз. 11) осуществляется с учетом заданных известных (определенных расчетным или экспериментальным путем, или известных согласно паспортным характеристикам эксплуатируемого ШГТО 9, или известных согласно технического задания на проектирование или техническим условиям производства ШГТО 9) спектральных акустических характеристик ШГТО 9, смонтированного в техническом помещении 1, известных габаритно-геометрических параметров его внутренней трехмерной воздушной полости 8, известных значений эксплуатационной температуры воздушной среды в техническом помещении 1 (уже эксплуатируемого или проектируемого).Structural and technological versions of the quarter-wave acoustic resonators R ^I (pos. 11) are represented by a hollow cavity dead-end tubular element (tubular part 28) bounded by a supporting internal air-blown film elastic soundproof sheath 20 and a hard sound-reflecting bottom of the bottom part 29, overlapping the passage section of the tubular part 28 on its end section (see Fig. 11a, 11b, 11c, 12a, 12b, 12c, 13a, 13b, 14a, 14b, 15a, 15b, 16a, 16b, 17a, 17b, 18a, 18b, 19a, 19b, 20, 21). The opposite open end zone of the tubular part 28 with the part of the air column oscillating in the tubular part 28 (located beyond the plane of the open cut of the tubular part 28) viscously attached to it, forming the attached oscillating air mass in the form of a dynamic increment to the air mass concentrated in the tubular part 28, forms the throat portion 30 of the quarter-wave acoustic resonator R ^I (key 11), see FIG. 20 and FIG. 21. The formation of the specified values of the physical and structural parameters of the quarter-wave acoustic resonators R ^I (pos. 11) is carried out by a specific calculation of the values of their own (resonant) frequency f ^I _R , taking into account the geometric length of the tubular part 28 (l ^I _r ), and the dynamic length ( l ^I _R), taking into account the value of the dynamic increment, which is formed given hydraulic diameter of the flow cross section of the tubular portion 28 - d _etc., considering the influence on the magnitude of its possible use protective footer damping layer in materials 33 mounted on the neck portion 30 (covering the orifice throat portion 30 at its open end section). The technical design of the tubular part 28 made of an air-blown material structure, with the bottom part 29 hermetically attached to it, in the form of a rigid sound-reflecting bottom made also of an air-blown material structure, allows forming (localizing) in the formed deadlock cavity of an elastic-mass air column excited impinging on the neck portion 30 of the sound wave with the frequency f _ms and the wavelength λ _ms and excited therein cavitary resonant oscillation of the elastic air Art forehead with frequency f _Rms, which quarter-wavelength

provides compensatory equalization of pressure fields of incident smooth and reflected P _OTR sound waves in the area of the throat part 30 of the quarter-wave acoustic resonator R ^I (pos. 11). The indicated frequency tuning of the effective functioning of the quarter-wave acoustic resonator R ^I (pos. 11) is carried out taking into account specified known (determined by calculation or experimentally, or known according to the passport characteristics of the operating SHGTO 9, or known according to the technical design specifications or production specifications for the SHGTO 9) spectral acoustic characteristics of SHGTO 9 mounted in technical room 1, known overall geometric parameters of it Cored oil dimensional air chamber 8, the known values of the operational air temperature in the technical room 1 (already exploited or projected).

The functioning of quarter-wave acoustic resonators R ^I (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 own (resonant) vibration frequencies f ^I _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 the intrinsic (resonant) oscillation frequency f ^I _R ) of the indicated used quarter-wave acoustic resonators R ^I (pos. 11). The Q factor is equal to the ratio of the value of the intrinsic (resonant) frequency of oscillations f ^I _{R of the} quarter-wave acoustic resonator R ^I (pos. 11) to the width of the adjacent frequency band Δf _R , at the boundaries of which the acoustic energy during stimulated resonant oscillations is half (3 dB) less acoustic energy at a resonant frequency f ^I _R. The Q factor of the quarter-wave acoustic resonator R ^I (pos. 11) is determined (formed) by the internal dissipative losses realized in it, which arise both directly in the composite structures (elements) of the quarter-wave acoustic resonator R ^I (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 quarter-wave acoustic resonator R ^I (pos. 11). Operation with frequency tuning to own (resonant) frequency of oscillation f ^I _R quarter-wave acoustic resonators R ^I (pos. 11), based on the respective wave (wavelength λ, the wave phase φ) the dynamic interaction of the amplitudes of the incident P _pad sound waves on a reflecting obstacle , represented by its bottom (rigid reflective bottom) - pos. 29, and reflected from it P _{OTR of} sound waves, with the resulting effect of interference (phase-amplitude) compensation suppression of the energy of sound waves propagating in an elastic (air) medium of a given frequency range that coincides (close in value) with natural (resonant) frequencies f ^I _R quarter-wave acoustic resonators R ^I (key 11), see FIG. 20. As you know, in general, the frequency f and the wavelength λ of sound vibrations are related to the speed with their propagation in an elastic (air) medium by the following known [4] relation (2)

where λ is the sound wavelength, m;

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

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

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

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

t ° C - air temperature in ° C

помещающейся в габаритах тупиковой пустотелой полости трубчатой части 28 четвертьволнового акустического резонатора R^I _ms (поз. 11) -

и отсчитываемой от поверхности жесткого донышка донной части 29, включающая его горловую часть 30 с вязкоприсоединенным к ней динамическим удлинением на величину (0,1…0,3)d_пр (здесь d_пр - приведенный гидравлический диаметр, в м, произвольной геометрической формы проходного сечения трубчатой части 28 (для круглого проходного сечения d_пр=d_кp, где d_кp - диаметр крута) четвертьволнового акустического резонатора R^I _ms, поз. 11), характеризуемого физическим параметром динамическая длина l^I _Rms четвертьволнового акустического резонатора R^I _ms (поз. 11), удлиняющим его геометрическую длину l^I _rms на величину (0,1…0,3)d_пp, может быть представлена в виде соотношения (4):Thus (see Fig. 20), taking into account the known expressions (2) and (3), a quarter of the length of the emitted SHGTO (pos. 9) of the sound wave

placed in the dimensions of the dead-end hollow cavity of the tubular part 28 of the quarter-wave acoustic resonator R ^I _ms (pos. 11) -

and measured from the surface of the hard bottom of the bottom part 29, including its throat part 30 with a dynamic extension viscous attached to it by the amount of (0.1 ... 0.3) d _pr (here d _pr is the reduced hydraulic diameter, in m, of an arbitrary geometric shape of the passage the cross section of the tubular part 28 (for a circular _bore d _pr = d _cr , where d _cr is the steep diameter) of the quarter-wave acoustic resonator R ^I _ms , pos. 11), characterized by the physical parameter dynamic length l ^I _{Rms of the} quarter-wave acoustic resonator R ^I _ms (pos . 11) taking its geometric length l ^I _rms by the amount of (0.1 ... 0.3) d _pp , can be represented in the form of the relation (4):

or

Given the expressions (6) and (7):

Where

π = 3.14;

S _t - the area of the bore, in m ² , of the tubular part 28 of the quarter-wave acoustic resonator R ^I _ms , pos. eleven,

geometric length l ^I _{rms of a} quarter-wave acoustic resonator R ^I _ms , pos. 11 used at the stage of its construction can be determined from known geometric and physical parameters according to the following expressions:

In final form, after the transformation

Similarly (similar considerations), an expression can be presented to determine the geometric length l ^I _{rmA of the} quarter-wave acoustic resonator R ^I _mA (key 11), designed to suppress resonant sound radiation in the technical room 1, due to the excitation of the eigen acoustic modes of the mass-elastic body its three-dimensional air volume, with sound wavelengths λ _mA (λ _mL , λ _mB , λ _mH ) at discrete values of the natural frequencies of sound waves f _mA (f _mL , f _mB , f _mH ), propagated in the internal three-dimensional air cavity 8 of the technical room 1, in the direction of its overall parameters A (L, B, H):

The choice of the range of variation of the value of the additionally viscoadjoint oscillating. air mass to the oscillating column of air mass, limited by the cavity of its tubular part (pos. 28), form a given value of the dynamic length l ^I _{R of the} quarter-wave acoustic resonator R ^I (pos. 11), which includes its geometric length l ^l _r and attached to the open a cut of the throat part (pos. 30), the dynamic increment (0.1 ... 0.3) d _pp according to the expression (6), which is predetermined as the applied geometrical sectional shape of the tubular part of the quarter-wave acoustic resonator R ^I (pos. 11) - round, elliptical , rectangular, trapezoidal, and possible mounting installation in the area of the throat part (pos. 30) of the quarter-wave acoustic resonator R ^I (pos. 11), by one or another type of external surface sound-transparent coating layer of the material (pos. 21), with the passage section overlapping tubular portion (pos. 28) which may be characterized by a wide range of changes in resistance values of the quantities by blowing an air stream (20 ... 500 n⋅s / m ^3), being presented by different kind vozduhoproduvaemymi fabric materials (technical arlyami, vozduhoproduvaemymi fibrous nonwoven webs, polymeric film or microperforated vozduhoproduvaemymi microperforated metal foil materials differing layer thicknesses - 0.025 ... 0.25 mm and a surface density in a specific surface weight - 20 ... 300 g / m ^2). Non-woven fibrous webs can be considered materials such as maliflis, filts, fiberglass, a cloth based on superthin basalt fiber. Microperforated layers of air-blown polymeric film materials can be represented by polyester aluminized, urethane, polyvinyl chloride, polyethylene terephthalate films. Microperforated metal layers of air-blown materials can be represented by steel, aluminum, copper, and brass.

To weaken the sensitivity (reduce the temperature dependence) of unregulated (non-tunable) structures of quarter-wave acoustic resonators R ^I (pos. 11), which are distinguished by simplicity of manufacture, to ensure sufficiently effective functioning of the ambient air environment in some variable operating temperature Δt, possibly by changing the parametric characteristic accordingly "Q-factor" quarter-wave acoustic resonators R ^I (pos. 11), with some acceptable (acceptable) n tereus efficiency of silencing on the magnitude of suppression of the amplitude of the acoustic energy level (decrease of sound pressure level) for discrete values of natural (resonant) frequency f ^I _R, but ensuring the expansion of the frequency range for its functioning This, in particular, can be achieved by introducing a resonant vibrational (acoustic) system containing quarter-wave acoustic resonators R ^I (pos. 11) of the corresponding structural and technological elements with additional dissipative losses and, additionally scattering sound energy and, thereby, providing a corresponding extension of the frequency range of acceptable efficiency of quarter-wave acoustic resonators R ^I (pos. eleven). In these cases, the expansion of the frequency range of efficiency implies a possible increase in the damped number of sound frequencies located (grouped) near the discrete value of the eigen (resonant) frequency f ^I _R and, corresponding to them, groupings of lengths λ ^I _R (quarter lengths λ ^I _R / 4) sound waves that fit during their propagation in the cavity of the tubular portion 28 and attached thereto dynamic elongation accounted dynamic length l ^I _R, a quarter-wave acoustic resonator R ^I (pos. 11) is achieved with the realization of s suitable for solving the technical problem of suppressing the effects of interference compensation (attenuation) of acoustic energy has reached as extended frequency range, taking into account the operating temperature changes.

If necessary (according to the technical requirements for the design), the possible use of complementary or alternative use of technical devices in the form of a typical automated temperature control system (climate control) of the air of a technical room 1, operating in an internal three-dimensional air cavity 8, equipped with adjustable functioning performance (discrete “On / off”, or continuously adjustable high-speed operation mode) fan-controlled (climatic) installation of a ventilation cooling device (not shown in Fig.), which can provide support for a given operational (thermal) operating mode of SHGTO 9 in a fairly narrow temperature range of the air environment Δt. This, accordingly, can eliminate (weaken) the unacceptable frequency detuning of the effective frequency-tuned noise-canceling operation of the used quarter-wave acoustic resonators R ^I (pos. 11), endowed with discrete (narrow-band) frequency-tuned functioning, with specific consideration of the sound wavelengths λ ^I _R (quarters sound wavelengths λ ^I _R / 4), under given physical conditions and propagation velocities of sound waves c (t) at steady-state air temperatures t ° C _st .

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 of intrinsic low-frequency acoustic resonances of their internal three-dimensional air cavities 8 (see expression (1) The generated (excited) intrinsic acoustic resonances of the internal three-dimensional air cavity 8 of the technical room 1, arising on its own acoustic x modes with frequencies of sound vibrations _{f mA (f mL, f mB} , f mH, wherein m = 1, 2, 3 ...), can substantially enhance the resonant transfer of acoustic energy from the closed inner dimensional air cavity 8 technical room 1 adjacent premises of a building (building) or in open space, with a corresponding increase in acoustic pollution of the environment.This further actualizes the solution to the problem of using appropriate technical means of eliminating (suppressing, attenuating) this type of p resonant amplification of acoustic radiation. Along with the physical process of resonant amplification of acoustic radiation, there may be a development of the physical process of beating of interacting acoustic signals (sound waves) with close values of the frequencies of sound vibrations f _ms and f _mA , manifested in the form of a 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 f _ms and f _mA . For the dominant 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 effects that worsen the psycho-physiological state of a person and is a negative factor in ensuring the acoustic safety of the environment.

In addition to quarter-wave acoustic resonators R ^I _ms (pos. 11) tuned to the working dominant functional frequencies f _{ms of} sound spectra of acoustic radiation of SHGTO 9, samples of quarter-wave acoustic resonances R ^I can also be supplemented or alternatively integrated into the structure of a separate integral molded sound-absorbing panel 10 (pos. 11) tuned to suppress acoustic radiation in other (different from the values of the working functional frequencies f _ms ) frequency ranges of sound spec trays, which can also be formed by numerous other various sources of acoustic radiation, which are part of the technical technical room 1. Such, in particular, can be noise-generating devices for ventilation cooling, as well as individual resonant amplifications of sound radiation arising on intrinsic acoustic modes of the air volume of the internal three-dimensional air cavity 8 of the technical room 1 - f _mA (f _mL , f _mB , f _mH ), determined by calculation according to expression (1). They may also include sound emissions generated by dynamically excited own 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 a multicomponent sound field formed as part of the claimed technical object. Suppression of resonant amplifications of sound emissions arising on the natural acoustic modes of the air volume of the internal three-dimensional air cavity 8 of the technical room 1, with their own (resonant) frequencies f _mA (f _mL , f _mB , f _mH ), determined by calculation according to expression (1), can also be carried out using separate tselnoformovannyh combined acoustical panel 10 by appropriately chastotnonastroennyh quarter acoustic resonators R ^I _mA, and the geometry of the physical cal parameters are determined according to the expressions (4) ... (11). In these cases, the calculated value of the geometric length of the quarter-wave acoustic resonator R ^I _mA , designed to suppress sound radiation arising from the eigenmodes of the internal three-dimensional air cavity 8 of the technical room 1, characterized by overall parameters A (L, В, Н), with sound frequencies fluctuations f _mA (f _mL , f _mB , f _mH ), determined according to the expression (1), can be determined according to the expression (11).

), при своем пространственном распространении попадает в горловую часть 30, распространяется по волноводному каналу трубчатой части 28 в направлении расположения жесткого звукоотражающего донышка донной части 29. При этом, энергия звуковых волн проникает через звукопрозрачную структуру несущей внутренней воздухонепродуваемой пленочной эластичной звукопрозрачной оболочки 20, трубчатой части 28, в пористое звукопоглощающее вещество, составленное из обособленных дробленных фрагментированных звукопоглощающих элементов 18, в котором будет эффективно рассеиваться (поглощаться), преобразовываясь в тепловую энергию, указанным пористым звукопоглощающим веществом, представленным обособленными дробленными фрагментированными звукопоглощающими элементами 18. В этом случае, распространяясь в направлении к звукоотражающему донышку донной части 29 и отражаясь от него, амплитуда звукового давления падающей звуковой волны Р_пад будет уже частично ослабляться. Уже частично ослабленная отраженная звуковая волна Р_отр, распространяясь в обратном направлении к открытой горловой части 30 четвертьволнового акустического резонатора R^I _ms, (поз. 11), будет складываться в противофазе с амплитудой звукового давления падающей звуковой волны Р_пад. В результате образующегося интерференционного противофазного сложения амплитуд звуковых давлений падающей Р_пад и отраженной Р_отр звуковых волн, энергия падающей звуковой волны Р_пад будет соответственно уменьшена (скомпенсирована). Вторым действующим механизмом ослабления энергии падающей звуковой волны Р_пад-является процесс поглощения ее энергии пористым звукопоглощающим веществом, образованным обособленными дробленными фрагментированными звукопоглощающими элементами 18, а также вследствие реализующихся сопутствующих энергопреобразующихся диссипационных эффектов рассеивания звуковой энергии, базирующихся на дифракционных механизмах дополнительного поглощения энергии звуковых волн, огибающих встречные твердотелые препятствия типа пористого дробленного звукопоглощающего вещества (обособленных дробленных фрагментированных звукопоглощающих элементов 18 пористой воздухопродуваемой структуры, и/или воздухонепродуваемой закрытоячеистой вспененной, и/или плотной непористой структуры 23 полимерных материалов, жесткого звукоотражающего донышка донной части 29, а также периметрических зон открытой горловой части 30 четвертьволнового акустического резонатора R^I _ms, (поз. 11)), как это, в частности, иллюстрируется схемами, приведенными на фиг. 20, 21, 22, 24. Использование тупикового звукопрозрачного тонкопленочного волноводного трубчатого канала 28, оборудованного на концевом участке жестким звукоотражающим донышком донной части 29, позволяет реализовать, в связи с этим, многочисленные физические принципы подавления распространения звуковой энергии, генерируемой ШГТО (поз. 9). Это позволит реализовать более эффективное результирующее диссипативное поглощение звуковой энергии за счет осуществления физических явлений, отмеченных в тексте описания заявки, таких как:The formation of the technical device of the quarter-wave acoustic resonator R ^I (pos. 11), using the supporting inner air-blown film elastic shell 20, made in the form of a dead-end tubular cavity element, certain overall dimensions of its sound-transparent air-blown tubular part 28, overlapped by a hard sound-reflecting bottom of the bottom part 29, and open throat part 30, determines the development of the dynamic process of resonator excitation of high-amplitude oscillations in its neck portion 30 and associated dissipative absorption of sound is less efficient in comparison to the "classical" type of operation quarterwave acoustic resonator R ^I, when performing its tubular portion 28 to form a reflecting rigid wall. The physical process of propagation, reflection and absorption of the energy of sound waves of this type by a combined sound-absorbing technical device is clearly illustrated by the diagram shown in FIG. 20. The incident on the throat part 28 of the quarter-wave acoustic resonator R ^I _ms , (pos. 11), from the side of the radiating sound SHGTO 9, the sound wave (energy of the sound wave) of a given frequency f _ms and wavelength λ _ms (quarter wavelength

), with its spatial propagation, it enters the throat part 30, propagates along the waveguide channel of the tubular part 28 in the direction of the location of the hard sound-reflecting bottom of the bottom part 29. At the same time, the energy of sound waves penetrates through the sound-transparent structure of the carrier inner air-blown film elastic translucent sheath 20, the tubular part 28 into a porous sound-absorbing substance composed of separate crushed fragmented sound-absorbing elements 18, in which there will be effectively dissipate (be absorbed), being converted into thermal energy by the indicated porous sound-absorbing substance, represented by separate crushed fragmented sound-absorbing elements 18. In this case, propagating in the direction to the sound-reflecting bottom of the bottom part 29 and reflecting from it, the sound pressure amplitude of the incident sound wave P _pad will already partially weaken. The partially weakened reflected sound wave P _sp , propagating in the opposite direction to the open neck 30 of the quarter-wave acoustic resonator R ^I _ms (pos. 11), will add up in phase with the sound pressure amplitude of the incident sound wave P _pad . As a result of the resulting interference antiphase addition of the amplitudes of the sound pressures of the incident P _pad and the reflected P _{arr of} sound waves, the energy of the incident sound wave P _pad will be correspondingly reduced (compensated). The second active mechanism for attenuating the energy of an incident sound wave P _pad is the process of its energy absorption by a porous sound-absorbing substance formed by separate fragmented fragmented sound-absorbing elements 18, as well as due to the accompanying accompanying energy-transforming dissipation effects of sound energy dissipation, based on diffraction mechanisms of additional absorption of sound-wave energy, enveloping oncoming solid-state obstacles such as porous crushed sound absorbing substance (isolated crushed fragmented sound absorbing elements 18 of a porous air-blown structure, and / or air-blown closed-cell foam and / or dense non-porous structure 23 of polymeric materials, a hard sound-reflecting bottom of the bottom part 29, and also the perimeter zones of the open neck portion of the resonator 30 quarter-waves ^I _ms , (pos. 11)), as is particularly illustrated by the circuits shown in FIG. 20, 21, 22, 24. The use of a dead-end sound-transparent thin-film waveguide tubular channel 28, equipped at the end portion with a hard sound-reflecting bottom of the bottom part 29, allows to realize, in this regard, numerous physical principles of suppressing the propagation of sound energy generated by SHGTO (item 9 ) This will allow to realize a more effective resulting dissipative absorption of sound energy due to the implementation of physical phenomena noted in the text of the application description, such as:

- the resulting diffraction of the propagated sound waves in the edge zones of the open throat parts 30, with their bending penetration (passage) in the opposite direction to the direct propagation of sound waves, followed by dissipative energy dissipation in the porous sound-absorbing structure of isolated fragmented fragmented sound-absorbing elements 18 (see Fig. 21 , 24);

- an additional increase in the opposite surface area of the incidence and, accordingly, dissipative absorption of sound energy, due to the introduction of dead-end tubular air cavities in the porous sound-absorbing structure, lined with a supporting internal air-borne film elastic soundproof sheath 20, which is formed by the tubular part 28 of the quarter-wave acoustic resonator R ^I (pos. 11 ), see FIG. 20, 21;

- the introduction of dead-end tubular air cavities, represented by the tubular parts of 28 quarter-wave acoustic resonators R ^I (pos. 11), into the porous sound-absorbing structure of a separate integrally formed combined sound-absorbing panel 10, contributes to a more smooth (less spasmodic) coordination of wave acoustic resistances in the zones of boundary separation of elastic layered propagation media of sound waves (air and solid-state porous crushed sound-absorbing substance, represented by crushed fragmented sound-absorbing elements 18 enclosed in a closed inner cavity 31 formed by a supporting outer surface cladding soundproof sheath 19 and a bearing inner air-blown film elastic soundproof sheath 20), in comparison with a typical plane-surface version of a typical plane-sheet design of a sound-absorbing panel (not containing alternating airborne panels cavities and inter-cavity jumpers), which helps to reduce energy property of reflecting sound waves and increase of sound-absorbing effect;

- a decrease in dynamic stiffness (an increase in dynamic compliance) of the porous skeleton used, formed by a crushed sound-absorbing substance, due to the additional integration of hollow air cavities into the structures of an isolated integral molded combined sound-absorbing panel 10 (see Fig. 20, 21, 24);

- the formation of structural-cavity acoustic anisotropy, with the implementation of the physical process of dissipative dissipation of the energy of propagated sound waves, due to the sound-transparent introduction (connection) of 10 hollow tubular cavities 28 quarter-wave acoustic resonators R ^I integrated into the volumetric structure of a separate integral sound-absorbing panel (pos. 11), see FIG. 20, 21, 24, 11a, 11b, 11c, 12a, 12b, 12c, 13a, 13b, 14a, 14b, 15a, 15b, 16a, 16b, 17a, 17b, 18a, 18b, 19a;

- the formation of structural acoustic anisotropy with additional dissipative diffraction absorption of sound energy due to the introduction into the volumetric structure of the porous crushed sound-absorbing substance of a separate whole-molded combined sound-absorbing panel 10 of various types (various) solid-state air-blown closed-cell foam and / or dense non-porous polymeric structures. 20, 21, 22);

- the implementation of the physical effects of absorption of sound energy arising in narrow-gap air gaps between the opposite end parts of mounted separate integral molded combined sound-absorbing panels 10, causing additional dissipative diffraction absorption of sound energy by their free edge zones of the porous sound-absorbing structure when they are enveloped by wave propagation. 23);

- the implementation of the physical effects of enhancing low-frequency absorption of sound energy from the introduction of predetermined air gaps between the rear sides of the surfaces of separate integral molded combined sound-absorbing panels 10 and the opposite front surfaces of the enclosing wall structures (walls 2, ceiling 3), see FIG. 25;

- the implementation of the diffraction absorption of sound energy at the perimeter edge zones of the hard sound-reflecting bottom of the bottom part 29, when it is enveloped by propagated sound waves (see Fig. 21);

) укладывается в габаритных размерах динамической длины l^I _R четвертьволнового акустического резонатора R^I (поз. 11), как это имеет место в конструкции классического четвертьволнового акустического резонатора R^I (поз. 11), оборудованного трубчатой частью 28, представленной трубчатой звукоизолирующей (звуконепрозрачной, звукооотражающей) твердотелой конструкцией, исключающей прохождение звуковых волн из ее полости в полость несущей внешней поверхностной облицовочной звукопрозрачной оболочки 19, заполненной звукопоглощающим веществом.- the use of the technological design of the tubular channel of the tubular part 28 in the form of a translucent thin-film device equipped at the end section with a hard sound-reflecting bottom of the bottom part 29, presented in the form of a quarter-wave acoustic resonator R ^I (item 11), allows physical processes to be performed not only out of phase compensation amplitude-phase interactions of the direct (entering the throat part 30) and reflected (from the hard sound-reflecting bottom of the bottom part 29), but also ensure to detect the passage of sound waves from a soundproof dead end cavity formed by a carrier of an internal air-blown film elastic soundproof shell 20 into the structure of a porous sound-absorbing substance located in a cavity of a load-bearing external surface soundproof sheath 19 of a separate integrally formed combined sound-absorbing panel 10, represented by fragmented fragmented panels 18, represented by fragmented fragmented elements 18 with the implementation of the physical process shines on frequency composition sound radiation dissipative absorption of sound energy, not only sound energy values at discrete frequencies of the sound waves, which is a quarter length (

) fits into the dimensions of the dynamic length l ^I _{R of the} quarter-wave acoustic resonator R ^I (pos. 11), as is the case in the design of the classical quarter-wave acoustic resonator R ^I (pos. 11), equipped with a tubular part 28, which is represented by a tubular soundproof (soundproof, sound-reflecting) solid-state construction, excluding the passage of sound waves from its cavity into the cavity of the supporting external surface cladding sound-transparent shell 19, filled with sound-absorbing substance.

Direct sound waves propagating and penetrating into the structures of composite sound-absorbing elements of a separate integrally formed combined sound-absorbing panel 10, falling onto their front sound-transparent surfaces and penetrating into porous air-blown structures made up of separate fragmented fragmented elements 18, are effectively dissipatively dissipated into them into heat. This applies both to microporous structures of isolated crushed fragmented elements 18, and to communicating macroporous sinuous air channels and cavities formed between their contacting faces and ribs. The process of dissipative absorption of sound energy includes, among other things, molded cavity containers formed by supporting internal air-deflecting film elastic soundproof sheaths 20 presented in the form of quarter-wave acoustic resonators R ^I (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 results of experimental studies of sound fields of various types of technical rooms 1 are given. 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 functional working frequency f _ms sound radiation investigated SHGTO 9 forming the sound ol technical room 1. In particular, measurements of the narrowband FFT-sound spectrum emitted ETPZT placed in the basement of the building construction industrial plant test center (see. FIG. 1) indicate evolved in the sound spectrum prevailing discrete functional operating frequency f _ms in the form of three low-frequency harmonic components of the sound pressure spectrum f _1s = 100 Hz, f _2s = 200 Hz, f _3s = 300 Hz, multiple frequency AC f _c = 50 Hz SHGTO 9 represented force elektrotransform torus. At the same time, the SPL at recorded discrete frequencies (f _1s , f _2s , f _3s ) exceeds 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 EEPT. 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 territory adjacent to it (the measuring microphone was located outside of room 1 in the closed doorway area) and the urgent need to suppress them.

Measurements of the 1/3 octave spectrum of sound pressure emitted by a type 3MK 260-1 power transformer manufactured by PLATTHAUS (Germany), located in the technical room 1 of the industrial testing center (see Fig. 2), also recorded the working dominant functional frequencies f _{ms of} sound radiation 9 SHGTO subjectively perceived as pronounced low-frequency "elektrotransformatornogo hum" Electric power radiated from the sound frequencies: f _1s = 100 Hz, f _2s = 200 Hz, f _3s = 300 Hz (part of the width a frequency band centered 315 Hz). The SPL at the recorded discrete frequencies (f _1s , f _2s , f _3s ) exceeds by more than 15 dB (5.6 times - in linear units of measurement) 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 surrounding sound field of the technical room 1 with its negative impact on 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 (blade) frequency of rotation of the impeller f _1s = 50 Hz and its multiple harmonics f _2s = 100 Hz. The SPL at the indicated discrete values of the frequencies (f _1s , f _2s ) is more than 25 dB (17.8 times in linear units of measurement) higher than the SPL of the adjacent mid- and high-frequency range of the studied spectrum of sound radiation SHGTO 9. This allows us to qualify the indicated frequencies f _1s and f _2s as expressed dominant low-frequency sound emitters forming 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 test center of the industrial enterprise, shown in FIG. 4, two pronounced discrete working dominant functional frequencies of sound radiation SHGTO 9 - f _1s = 200 Hz and f _2s = 400 Hz are also identified. The SPL at the recorded discrete values of sound frequencies (f _1s , f _2s ) is more than 10 dB (3.16 times in linear units of measurement) higher than the SPL of the remaining frequency components of the spectrum of sound radiation recorded in the technical room 1 of the compressor-refrigeration station under study .

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

), с собственными частотами звуковых колебаний f_mA (f_mL, f_mB, f_mH). В это же время, для усиления эффективности их подавления, в необходимых случаях, в составе обособленных цельноформованных комбинированных звукопоглощающих панелей 10 могут применяться заданные частотно настроенные устройства эффективного заглушения звукового излучения выраженных дискретных спектральных составляющих (в виде четвертьволнового акустического резонатора R^I _mA (поз. 11)), включающих дискретные значения собственных частот звуковых колебаний f_mA (f_mL, f_mB, f_mH), проявляющиеся на слабозадемпфированных собственных акустических модах массо-упругого тела воздушного объема, характеризуемых длинами звуковых волн λ_mA (λ_mL, λ_mB, λ_mH), формирующихся во внутренней трехмерной воздушной полости 8 технического помещения 1, и распространяющихся в направлении его габаритных параметров A (L, В, Н).Thus, as follows from the performed research results shown in FIG. 1-4, the working dominant functional frequencies of sound radiation f _{ms of} various types identified as discrete values of the investigated SHGTO 9 installed in the corresponding technical rooms 1, differing in overall dimensions L, B, H, are concentrated in the low-frequency region of the sound spectrum (50 ... 400 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, located in the meter measurement ranges and characterized by their own acoustic modes with sound wavelengths λ _mA (half-lengths

), stacked between opposite (opposite) hard sound-reflecting surfaces of the wall 2 (as well as floor 4 and ceiling 3) of the fencing of the technical room 1. Thus, these factors actualize the solution to the problem of suppressing sound radiation produced by SHGTO 9, as in the overwhelming broadband sound range spectrum, and with the primary (exclusive) task of reducing only its dominant low-frequency components of the sound spectrum. In this regard, the tasks can be solved using combined technical devices for damping sound energy, including both frequency-tuned elements of its damping, endowed with increased efficiency, and broadband sound-damping devices that are reasonably effective in the medium and high frequency sound ranges, which are represented by porous sound-absorbing structures acoustic materials and associated sound-absorbing structures. It should be noted that the lining of the enclosing wall and ceiling structures of the technical room 1 with separate integrally formed combined sound-absorbing panels 10 containing porous sound-absorbing substances will further contribute to the elimination of 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 lengths sound waves λ _mA (half-lengths

), with natural frequencies of sound vibrations f _mA (f _mL , f _mB , f _mH ). At the same time, to enhance the efficiency of their suppression, if necessary, as part of separate integral molded combined sound-absorbing panels 10, predetermined frequency-tuned devices for efficiently damping sound radiation of pronounced discrete spectral components (in the form of a quarter-wave acoustic resonator R ^I _mA (pos. 11 )), including the discrete values of the natural frequencies of sound vibrations _{f mA (f mL, f mB} , f mH), manifested in slabozadempfirovannyh own acoustic mo ah weight and an elastic body of the air volume, characterized by the acoustic wavelength _{λ mA (λ mL, λ mB} , λ mH), formed in the internal three-dimensional air cavity 8 technical room 1, and propagating in the direction of its dimension parameters A (L, B, H )

As follows from the description, the technical device of the low-noise technical room presented as an invention is endowed with a broadband frequency composition of the sound absorption effect, with a pronounced, increased efficiency low-frequency effect of suppressing discrete values of the working dominant functional frequencies of sound radiation f _{ms of} various types of SHGTO 9 mounted in the corresponding technical rooms 1. In this case, the medium and high frequency sound radiation is suppressed used in technical a device with porous sound-absorbing dissipative structures composed of isolated crushed fragmented elements 18 of a separate integral molded combined sound-absorbing panel 10. It is enhanced by edge diffractive dissipative sound-absorbing effects, as well as the realized dissipative effect of acoustic anisotropy due to the inclusion of fragmented structured, porous, porous structure into the volumetric porous structure breathable porous sound absorption particles of recyclable materials, including a certain dosage amount, with its corresponding volume distribution of crushed fragments of dense air-blown elements of solid polymer materials in a mixture with crushed fragments of porous air-blown sound-absorbing elements of solid polymer materials. Also, the physical processes of acoustic anisotropy, formed by the hollow air cavities of the tubular parts of 28 quarter-wave acoustic resonators R ^I (pos. 11), integrated into the composition of separate integral molded combined sound-absorbing panels 10, are also included in the process of absorption of sound energy. In addition, diffractive dissipative absorption of sound energy is realized on edge perimetric zones of the hard sound-reflecting bottom of the bottom part 29, as well as in the edge zones of the throat parts 30 and the edge the zones of the end faces 32 of the gap-mounted separate integral molded combined sound-absorbing panels 10. The implementation of air gaps formed between the rear sides of the surface of the separate integral molded combined sound-absorbing panels 10 and the opposite surfaces of the enclosing wall structures (walls 2, ceiling 3) also provides an increase in sound absorption efficiency at low frequencies range. The most effective resonant sound radiation in the low-frequency range is formed on the discrete working dominant functional frequencies f _ms expressed in the sound spectra generated by SHGTO 9, which is suppressed due to the integrated integrally formed combined sound-absorbing panel 10 of frequency-tuned quarter-wave acoustic resonators R ^I _ms integrated within the structure of the porous sound-absorbing material. (item 11).

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 (30)

1. Low-noise technical room, characterized by physical parameters of the sound and temperature fields established in its internal three-dimensional air cavity, represented by discrete values of the working dominant functional frequencies of sound radiation f _ms operated in the technical room of at least one noise-generating technical object, the lengths of sound frequencies of sound radiation operated noise generating technical object λ _ms , sound velocity c and air temperature during an internal three-dimensional air cavity t ° С, containing load-bearing enclosing elements in the form of a floor, walls and ceiling, on which separate fast-absorbing panels composed of separate crushed fragmented sound-absorbing elements placed in closed cavities are fixed with corresponding fasteners, with the formation of corresponding cavity air gaps separate containers of supporting soundproof shells, and separate structures are mounted in the formed cavity air gaps of twelve-wave acoustic resonators R ^I , the operated noise generating technical object operates at a predetermined steady-state constant high-speed operational mode of operation n _s , accompanied by steady-state physical processes of emission of sound and thermal energy, the spectral sound composition of which contains discrete values of the working dominant functional frequencies f _ms characterized by the corresponding sound wavelengths λ _ms , characterized in that the isolated sound absorb The cover panels are represented by shell structural and technological versions in the form of a predominantly rectangular cross-section of separate integrally formed combined sound-absorbing panels containing a carrier air-deflecting or air-producing external surface cladding sound-transparent shell, adhesively mating with a bearing of an internal air-deflecting film-clad transparent elastic soundproof a combined sound-absorbing panel filled with separate crushed fragmented sound-absorbing elements, while the carrier internal air-blown film elastic sheath is made in the form of at least one dead-end tubular cavity sound-transparent element of certain overall dimensions of its tubular part with an open neck part and overlapped by a hard sound-reflecting bottom forming a quarter-wave acoustic resonator R ^I _ms intrinsic resonance whose real frequency f _Rms coincides with at least one of the discrete values of the working dominant functional frequencies of sound radiation of at least one operated 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 internal three-dimensional air cavity of the technical room (s, t ° C). 2. The low-noise technical room according to claim 1, characterized in that the overall dimensions of the tubular part of the quarter-wave acoustic resonator R ^I _ms , characterized by its geometric length l ^I _rms , which determines its frequency setting for suppressing sound radiation of the given discrete values of the working dominant functional frequencies f _ms with the corresponding lengths of sound waves λ _ms is determined from the expression:

where d _CR - the hydraulic diameter of the bore of the tubular part of the used quarter-wave acoustic resonator R ^I _ms , m; f _ms - discrete value of a given dominant functional frequency, Hz (s ^-1 ); t ° C is the air temperature established in the internal three-dimensional air cavity of the technical room, ° С. 3. The low-noise technical room according to claim 1, characterized in that the overall dimensions of the tubular part of the quarter-wave acoustic resonator R ^I _mA , characterized by its geometric length l ^I _rmA , which determines its frequency tuning of the suppression of resonant sound radiation excited by its own acoustic modes of a mass-elastic body of air volume three-dimensional inner air cavity dimensions technical room a (L, B, H), characterized by the acoustic wavelength _{λ mA (λ mL, λ mB} , λ mH) with discrete values E eigenfrequencies sound vibrations _{f mA (f mL, f mB} , f mH), are determined from the expression:

where d _CR - the hydraulic diameter of the bore of the tubular part of the used quarter-wave acoustic resonator R ^I _mA , m; t ° C - air temperature in the internal three-dimensional air cavity of the technical room, ° C; λ _mА (λ _mL , λ _mB , λ _mH ) - the sound wavelengths of low intrinsic acoustic modes represented by intrinsic acoustic vibrations of the mass-elastic body of the air volume of the internal three-dimensional air cavity of the technical room, m; f _mA (f _mL , f _mB , f _mH ) - discrete values of the natural frequencies of sound vibrations in the natural acoustic modes of a mass-elastic body of air volume characterized by sound wavelengths λ _mА (λ _mL , λ _mB , λ _mH ) formed in the internal three-dimensional air cavities of the technical room, Hz (s ^-1 ); A (L, B, N) - overall dimensions of the internal three-dimensional air cavity of the technical room, m 4. The low-noise technical room according to claim 1, characterized in that the throat parts of the quarter-wave acoustic resonators R ^I _{ms are} made on the end faces of the separate integral molded combined sound-absorbing panels. 5. Low-noise technical room according to claim 1, characterized in that the tubular parts of the quarter-wave acoustic resonators R ^I _{ms are} made coaxially with the opposite throat parts and contain common bottom parts. 6. The low-noise technical room according to claim 1, characterized in that the open throat portion of the quarter-wave acoustic resonators R ^I _{ms is} covered by a protective lining damping air-blown layer of material. 7. The low-noise technical room according to claim 1, characterized in that from the front surfaces of the faces of the separate integral molded combined sound-absorbing panels, sound-transparent facing protective and decorative perforated panels are additionally mounted, the wall perforation coefficient of which corresponds to the expression K _perf ≥ 0.25. 8. 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. 9. The low-noise technical room according to claim 1, characterized in that the sound-transparent adhesive coatings of the mating surfaces of the constituent elements of the separate integral molded combined sound-absorbing panel are represented by hot-melt adhesive fibers and / or a hot-melt powder adhesive material and / or a layer of sticky adhesive and adhesive material / or a continuous or perforated layer of a film of thermosetting adhesive substance. 10. The low-noise technical room according to claim 1, characterized in that the supporting external surface cladding is sound-transparent shell made of micro-perforated with a bore diameter of perforation holes not exceeding 1 mm, foil material - aluminum, copper, brass, or a continuous layer of air-blown fabric (non-woven fabric) structural material such as maliflis, filts, fiberglass, basalt fiber fabric. 11. The low-noise technical room according to claim 1, characterized in that the supporting internal air-blown film elastic sheath forming the tubular part of the quarter-wave acoustic resonators R ^I _ms is made of the corresponding polymeric materials - polyethylene terephthalate, polyvinyl chloride, aluminized polyester, urethane, layer thickness 0.025 ... 0.25 mm and a specific surface weight of 20 ... 200 g / m ² . 12. The low-noise technical room according to claim 1, characterized in that the hard sound-reflecting bottom of the bottom of the quarter-wave acoustic resonator R ^I _{ms is} made of the corresponding polymeric material - polyamide, polyvinyl chloride, polyethylene, polypropylene. 13. The low-noise technical room according to claim 1, characterized in that the isolated crushed fragmented elements are made of solid recyclable, mainly polymer waste, presented in the form of sound-absorbing structures of parts and assemblies technologically processed by mechanical crushing, dismantled from recyclable technical objects, mainly parts of noise insulation packages of vehicles that have completed their life cycle, and / or from technological waste and rejects from the production of sound-absorbing materials and parts and assemblies made from them. 14. The low-noise technical room according to claim 1, characterized in that the narrow-gap air gaps γ installed between the opposite end faces of the separate integrally formed combined sound-absorbing panels mounted on the supporting wall and ceiling enclosing elements do not exceed the values indicated in the expression: γ≤0.25h, where h are the overall thicknesses of the opposite end faces of the separate integral molded combined sound-absorbing panels. 15. The low-noise technical room according to claim 7, characterized in that the sound-proof facing protective and decorative perforated panels are made of the corresponding metal or polymer material - steel, aluminum, polypropylene, polyamide. 16. The low-noise technical room according to claim 1, characterized in that the supporting external surface cladding sound-transparent shells of separate integral molded combined sound-absorbing panels are made of a layer of structural material with a thickness of 0.025 ... 0.25 mm and a specific surface weight of 20 ... 200 g / m ² , represented air-blown polymer film, metal foil, or made of an air-blown layer of fabric, non-woven fabric, microperforated polymer film, microperforated metal foil foil, the resistance to blowing by the air flow of which is in the range of 20 ... 500 N⋅s / m ³ .

Images