RU2716043C1 - Low-noise technical room - Google Patents

Abstract

FIELD: construction.

SUBSTANCE: technical device is presented in the form of low-noise technical room equipped with mounted with air gaps between opposite end faces (γ) and relatively opposite mounting surfaces of wall and ceiling enclosing structures (k) of technical room, separated by integral moulded composite sound-absorbing panels made of porous air-sound absorbing structure of substance lined with sound-transparent layer of material. Inner surface facing sound-insulating shells of separate shaped-piece combined sound-absorbing panels form through bypass diffraction-dissipative channels, communicating face and rear surfaces of bearing outer surface facing sound-transparent shells and external surface protective facing sound-transparent layers of materials, at that diameters of through bypass diffraction-dissipative channels d satisfy relationship: d = (0.5…0.8)t, where t is overall thickness of end faces of separate shaped-piece combined sound-absorbing panels; k is a remote air gap formed between the back surface of the mounted detached unitary composite sound-absorbing panel and the opposite wall or ceiling of the technical room; γ - remote air gap formed between opposite surfaces of end faces of mounted isolated solid-moulded combined sound-absorbing panels.

EFFECT: technical device of low-noise technical room is endowed with broadband frequency composition sound absorption due to use of porous air-permeable sound-absorbing structures of structural materials with integration into their structural composition of through bypass diffraction-dissipative channels.

1 cl, 17 dwg

Description

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

It is known that in order to protect the environment from intense acoustic pollution (high noise levels) produced by various types of noise-generating technical objects, various types of soundproofing (noise-insulating) fencing of noisy technical rooms (screen partitions, casings, panel linings of bearing and / or cabinet are widely used) constructions) equipped with additional layers of viscoelastic vibration-damping and / or porous air mounted on their surfaces oproduvaemyh sound-absorbing and / or dense vozduhoneproduvaemyh soundproofing materials, and / or various combinations of all matching, with optional inclusion of carrier reinforcing, sound transmission, protective, adhesive, decorative material layers or corresponding structural elements. Also, for the same purposes, isolated single or interlocked ones can be used, presented in the form of noise-damping aggregated modular batteries composed of various types of acoustic resonators - quarter-wave (R ^I ), half-wave (R ^II ), Helmholtz (R ^III ). Volumetric expansion chambers contained in technical rooms that are connected to waveguide sound-transmitting channels (openings) of the corresponding type can be used, blocking (weakening) the transmission of acoustic energy due to the sound-reflecting air (gas-filled) “acoustic plugs” formed in them, characterized by sharp changes (sudden changes ) wave acoustic impedances. In the vast majority of cases, various various combination combinations of the above types of noise-attenuating (noise-reducing) techniques are applied in the form of methods and technical devices for their implementation, and their specific choice is predetermined by both technical and safety, environmental and economic factors. The use of such a diverse type of noise-suppressing techniques (methods), technical devices and substances (materials) for their implementation, allows one way or another to provide an acoustically safe noise-comfortable living environment for people and animals. In particular, various types of hybrid noise-reducing structures are widely used, using the combined implementation of the physical processes of sound absorption and sound insulation, when the total noise-reducing effect of the technical device used can be based both on the effects of reflection of sound energy and on the combined combination of sound absorption and sound reflection effects. Sound-damping devices may, in particular, not contain porous air-blown sound-absorbing or air-blown sound-proof structures of materials, and the resulting sound attenuation effects are narrow-band and 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 widespread use of their use in the form of perforated plates of structures located with a given air gap of relatively rigid sound-reflecting surfaces, with the formation of the corresponding cavity resonator devices (Helmholtz acoustic resonators R ^III ). This type of cavity resonant sound-damping devices can be both hollow, and, in some cases, partially filled with a porous sound-absorbing substance.

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

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

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

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

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

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

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

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

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

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

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

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

The expressed useful advantages of using the above frequency-tuned technical devices for damping acoustic energy include the possibility of their use, including under conditions of exposure to aggressive environments, high temperatures and intense dynamic loads, due to the forced exclusion of the use of porous air-blown (gas-blown) in their structural composition fibrous and / or foamed open-cell structures of organic or synthetic origin characterized by I, as a rule, are not sufficiently high thermo-moisture-biostable characteristics. In these cases, they use exclusively dense structures of perforated metal or heat-resistant polymer materials that form cavity resonator elements, with the possible inclusion, in some cases, of heat-resistant porous fibrous (basalt, glass, metal), and / or foamed open-cell metal, and / or ceramic materials. At the same time, the negative technical characteristics of this type of noise-attenuating devices include their narrow working frequency sound range of effective functioning, high sensitivity to frequency detuning and loss of sound-suppressing effect with a corresponding operational change in the physical parameters of the propagation medium of sound waves, with an insufficiently high value for achieving the effect noise attenuation in the necessary, in most cases, a wide sound frequency range, high cost, poor overall performance and increased consumption of materials. At the current level of technological development, these negative factors can limit their widespread distribution in the effective solution of urgent practical problems of suppressing the energy of spurious 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 constructions, the used front (front) wall of the acoustic panel is, as a rule, perforated and has a rather high perforation coefficient, which usually exceeds 0.2. This tells her the properties of acceptable sound transparency and, in essence, ensures unhindered (with an insignificant, not exceeding 10% sound reflection effect) passage of sound waves into the cavity of the acoustic panel filled with porous sound-absorbing material. Through, mainly round holes or narrow slotted grooves with bends are the most common type of perforation of this type of front wall of an acoustic panel. As examples of this type of known noise reduction technical devices, it should be noted:

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

The above-mentioned well-known noise-reducing technical devices, along with satisfactory acoustic characteristics achieved in the medium and high frequencies of the sound range, are nevertheless characterized by a certain loss of potential noise-attenuating properties due to the formation of an abrupt change (drop) in the wave acoustic resistance on a flat separation boundary ( Section) of elastic layered propagation media of sound waves in the considered zone ozdushnoy medium adjacent to the solid ploskolistovoy layered structure, with different values of wave acoustic resistances, consisting of adjacent air environment as a solid-state planar wall perforated front panel or structure ploskolistovoy porous sound-absorbing substance in the acoustical panel cavity. This causes not only the corresponding potential loss of sound-absorbing effect, but also the perforations contained throughout the solid surface of the flat front face wall of the acoustic panel, which also cause a certain loss in the soundproofing (due to the decrease in sound reflecting) properties of the formed multilayer structure of the wall partition as a whole.

To increase the noise-reducing properties of this type of acoustic structures, by providing smoother (rather than sharp abrupt) coordination of wave acoustic impedances along the propagation paths of sound waves in the boundary zones of separation of the elastic air medium of propagation of sound waves, including adjacent boundary contact zones of the external hard shell surface of the front acoustic panels of a technical device with external and internal cavity zones of adjoining air environment, to ntours of the outer shell (wall) of the front acoustic panel is given a “matching” non-planar corrugated geometric shape (wedge-shaped, wave-shaped, rock-shaped), as is, in particular, presented in the following well-known technical devices:

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

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

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

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

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

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

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

The above noise-reducing constructions of technical devices are characterized, first of all, by a significant complication of their technological design and relatively high cost, when the sound insulating ability is not high enough (due to the presence of alternating multiple “sound-insulating dips” in separate sound frequency ranges of the sound-damping characteristic due to formation of excited intrinsic “parasitic” cavity airborne acoustic resonances), and also arising forced concomitant reduction (“crowding out”) of the large-sized noise-reducing constructions used by the useful spatial 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 the need to increase the share of absorbed sound energy, is the implementation of a technical device directly perceiving direct incident sound waves, perforation holes with specified narrow technological tolerances for the execution of geometric shapes and their defined overall dimensions. This type of noise reducing technical devices are known from the following patent documents:

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

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

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

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

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

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

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

The specified noise-reducing technical devices can be characterized by improved operational and decorative (improved external design) properties. However, their noise-reducing properties are, nevertheless, not high enough due to the limited potential used to further improve the efficiency of the structural modification of the technical device, based solely on rationalizing the geometric shapes and overall dimensions of the perforation holes. Also, their production is associated with the need to use more complex and expensive high-tech equipment, ensuring compliance with this type of narrow technological 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 several physical effects of sound energy absorption), borrowed from the above groups of well-known technical devices, allowing in one or another degrees (and, accordingly, in one or another sound frequency range, with one or another achieved positive sound-damping effect ektom) purposefully further improve their acoustic properties. This type of combined hybrid noise reduction technical devices are described in the following patent documents:

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

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

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

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

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

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

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

Also known and used in architectural acoustics of premises, a technique for partially eliminating (partially attenuating) the development of the physical process in them of the expressed pronounced half-wave acoustic resonances of the formed elastic bodies of air volumes represented by the internal three-dimensional air cavities of the rooms, worsening their acoustic qualities, is the direct application of the original structural the execution of the technical room, presented in the form of the corresponding measuring acoustic research instruments made in the form of a measuring reverberation chamber, as described, in particular, in [1, 2, 3]:

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

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

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

The overall dimensions and geometric shapes of this type of measuring reverberation chamber, the ratios of its composite overall dimensions, and the physical characteristics of its wall structures that are being implemented allow us to a certain extent to exclude (partially weaken) the development of the physical process of the formation of in-phase resonant addition of acoustic energy on half-lengths of sound waves (λ / 2) and multiples of sound harmonics excited inside a closed spatial air cavity of the measuring reverberation chamber In this case, the noise-generating sound source under study (or a calibrated sound emitter) placed inside it, thereby preventing the formation of energy amplification of sound on pronounced resonant intrinsic acoustic modes of the air volume of the room of the measuring reverberation chamber. This allows us to partially exclude (weaken) the development of the physical process of the formation of a pronounced uneven spatial density of the sound energy intensity distribution localized in the closed spatial air cavity of the measuring reverberation chamber from the composition of the emerging diffuse (reverberation) acoustic field of the internal spatial air cavity of this type of technical room. This type of measuring reverberation chambers are of limited use and are used mainly in the field of specialized acoustic research and measurement of the sound power of noise-generating technical objects, as well as for assessing the sound-absorbing characteristics of samples of acoustic materials performed in a diffuse sound field. They are also used to study the sound-absorbing characteristics of full-scale structures of parts, components and systems of machines (or their prototypes), performed in a diffuse (reverberation) sound field. The regulatory requirements given in [1, 2, 3] provide guidance on the relevant regulatory principles for the design of measuring reverberation chambers designs, imposing requirements on the volume (overall dimensions) and geometric shape of its spatial air cavity, the physical characteristics of the wall structures used, excluding ( weakening) the negative development of physical processes of the formation of resonantly expressed spatial zones of unequal distribution of sound energy intensity and, as well as eliminating (attenuating) the undesired sound absorption process produced by the enclosing surfaces of the wall structures and the doorway of the measuring reverberation chamber, which worsens the characteristics of the diffuse sound field in the reverberation acoustic chamber. However, the alternative multifunctional use of this type of original design of measuring reverberation chambers, as possible typical variant designs of low-noise technical rooms, with eliminated (attenuated) half-wave acoustic resonances, is insufficient, significantly complicates and increases the cost of designs of typical technical rooms intended for subsequent installation in them noise-generating technical objects (SHGTO) during their design, construction and subsequent general operation. An obvious drawback of this type of technical premises, made in the form of measuring reverberation chambers, is also the unsatisfactory (incomplete and inconvenient to use) use of their useful working space, due to the non-parallel opposite surfaces of the wall fencing, floor and ceiling (ceiling) implemented in them. Moreover, in some cases, to ensure the required diffuseness of the sound field (the realization of a more uniform spatial density of the 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 e energy in the air cavity of the measuring reverberation chamber, which, however, is associated with an undesirable additional clutter of its useful working space.

A technical solution is known according to the RF patent for the invention No. 2670309, published on 10.10.2018, which presents a description of a low-noise technical room containing load-bearing enclosing rigid sound-reflecting elements in the form of walls, a ceiling, a floor, a doorway with a closed entrance door, a supply and exhaust ventilation openings forming a closed internal three-dimensional air cavity, represented by a hollow rectangular parallelepiped with overall dimensions A (L⋅B⋅H). It is characterized by certain physical parameters of the sound and temperature fields in which at least one operated sound-generating technical object (SHGT) is mounted, operating at a given steady-state (constant) high-speed operational mode of operation n _s , accompanied by corresponding physical processes of sound and thermal energy radiation . The spectral sound composition of the radiation of a typical SHGTO contains, as a rule, distinguished discrete values of sound pressure levels (SPL) at individual working dominant functional frequencies f _ms characterized by the corresponding sound wavelengths λ _ms . At least one of the linear dimensional parameters A of the internal three-dimensional air cavity of the technical room, represented by a rectangular parallelepiped with overall dimensions L⋅B⋅H, satisfies the given requirements of the interconnected relationship with the physical parameters of the sound and temperature field of the internal three-dimensional air cavity of the technical room, which allows, in ultimately, to exclude intense resonant frequency-modal interactions of sound radiation SHGTO with emerging idents acoustic modes (natural frequencies of sound vibrations f _mA, characterized by wavelengths λ _mA) inside a three-dimensional technical room air cavity defined by the expression:

рабочей доминирующей функциональной частоты f_ms звукового излучения шумогенерирующего технического объекта, укладывающихся в ограничительных пределах габаритного параметра А, характеризующего габаритные размеры внутренней трехмерной воздушной полости технического помещения (L, В, Н);where n _vs is the integer (natural number) of the half-lengths of sound waves

the working dominant functional frequency f _{ms of the} sound radiation of a noise-generating technical object, falling within the bounds of the dimensional parameter A, characterizing the overall dimensions of the internal three-dimensional air cavity of the technical room (L, B, H);

K ' _t is the temperature coefficient of correction of the speed of sound c and the sound wavelength λ _{ms of the} working dominant functional frequency f _ms emitted by the noise generating technical object at a given steady-state speed operational mode of operation n _s , in the operational range of air temperature Δt ° C in the internal three-dimensional air cavities of a technical room (L, B, N);

Thus, the implementation of the known technical device of a low-noise technical room can prevent the occurrence of intense airborne cavity acoustic resonances in the space of the technical room with a SHGO installed in it, which helps to eliminate (reduce) the resulting resonant amplification of acoustic radiation both directly in the spatial air cavity of the technical room and in adjacent spatial zones (adjacent rooms, open spaces ). This, in turn, contributes to the process of improving the acoustic safety of the environment.

A disadvantage of the known technical solution is the need for accurate coordination of the overall dimensions of the technical room at the design stage, taking into account the predicted (calculated, instrumentally measured) characteristics of the SHGTO acoustic field, which will be installed in it, which leads to the need for an additional (reserve) modernization of the technical room in in case of non-compliance with sufficient conditions for the mismatch of the overall dimensions of the internal three-dimensional air cavity th rooms with specific objective sound and the physical parameters of temperature fields, realized in the airspace technical room. In the presented description of the technical room, there are also no noise-reducing devices in the technical room, as well as structural elements that provide noise reduction of SHGTO in a wide sound frequency range, including as a range of discrete low sound frequencies, with low-frequency sound harmonics that stand out in the spectrum, typical for engineering-technical radiated noise equipment operating at a constant (unchanged) high-speed mode of operation, presented, in particular, pumping, compressor stations, power plants (internal combustion engines, diesel generator sets), ventilation and air conditioning systems, electric machines (electric motors, electric transformers), as well as medium and high frequency sound range (500 ... 8000 Hz). Also, as a drawback, it is necessary to point out the need to perform selective frequency tuning of the technical device, aimed exclusively at the mismatch of the dynamic resonance interaction of the physical parameters of the sound field generated by the SHGTO and the own sound field of the air cavity of the technical room in which the SHGTO is located.

As a PROTOTYPE, the well-known technical solution for the invention patent RU 2677621 “Low noise technical room”, publ. 01/17/2019. According to the description of the indicated technical solution according to the patent RU 2677621, on the supporting enclosing elements (walls, ceiling) of the low-noise technical room, using appropriate fasteners, separate combined sound-absorbing panels (OKZP) are fixed, with the formation of the corresponding air gaps between their rear surfaces and opposite opposite to them the surfaces of the wall and ceiling structures of the technical room. Also, the corresponding air gaps are formed between the opposed opposing surfaces of the faces located relative to each other of separate, adjacent to each other, samples of the OKZP. At the same time, the structural composition of the CSP is represented by separate crushed sound-absorbing elements placed in the cavity of the closed separate containers of the supporting sound-transparent shells, which contain the separate structures of the frequency-tuned quarter-wave acoustic resonators R ^I , the neck parts of which are mounted on the end faces of the CSP. Using the indicated technical solution allows both combined broadband and frequency-tuned absorption of sound energy generated by SHGT on the frequency components f _ms dominating in the spectrum of sound radiation, coinciding in numerical values with the natural resonant frequencies of sound vibrations f ' _{R of the} used quarter-wave acoustic resonators R ¹ _ms . However, of this type, the claimed design of a noise suppressing device (patent RU 2677621), adopted as a prototype, has a significant drawback associated with its exceptional effective functioning only in the field of constant constant frequencies of sound radiation SHGTO f _ms , which, in turn, is associated with with the forced observance of constant (constant) speed modes of its operation only at one given (passport) steady-state speed operational mode of operation n _s . In cases where SHGTO is operated at several different high-speed operating modes, when its parameters n _s and f _ms are different, or when SHGTO is operated on unsteady variables (smooth acceleration and deceleration modes in the range of operating operational modes of operation) operating modes, or the operating temperature regime of the air in the space of the technical room (for example, in winter and summer) changes significantly, then, respectively, for example, at varying frequencies, the sound Radiation f _ms, substantially changed and lengths of sound waves λ _ms, which causes the detuning frequency and, consequently, inefficient operation of the quarter-wave acoustic resonators used R ^l _ms. This type of frequency-mismatch-sensitive, frequency-dependent noise-attenuating acoustic resonators R ^l _ms require severe restrictions on the permissible fluctuations in the speed and temperature conditions of operation of a SHGTO mounted in a technical room. Otherwise, their functioning as noise-suppressing technical devices is ineffective (inefficient).

The inventive technical device “Low-noise technical room” is aimed at eliminating most of the identified and analyzed disadvantages of analogues and prototype with respect to achieving an acceptable high manufacturability, environmental friendliness, cost and efficiency of operation, while providing the effect of expanding the frequency sound range to reduce the level of sound radiation produced by SHGTO . The objective of the claimed invention is to develop a low-noise technical room, equipped with elemental devices of broadband frequency composition to reduce noise levels, effective both in the medium and high frequency sound range, and in the low frequency range of sound frequencies, not sensitive to changes (fluctuations) in operating speed and temperature parameters SHGTO and air of the technical room.

The technical result of the claimed technical device is to ensure an acceptable high acoustic safety of the environment due to the achieved improvement in sound-absorbing (noise-reducing) characteristics of the used technical device, implemented in a wide frequency range of sound radiation generated by SHGTO, including low, medium and high frequency sound ranges, in all operational speed, load and temperature conditions of operation of SHGTO and changing external ones ambient temperature conditions. The inventive technical device is represented by a low-noise technical room, equipped with technical means for effectively suppressing the acoustic radiation generated by SHGTO, mounted on wall and ceiling fences (floors) of this technical room (Fig. 1 ... 3).

The technical result is achieved through appropriate installation, with the specified air gaps, on the wall and ceiling fences and floors of the technical premises of various types of structural and technological versions of separate integral molded sound-absorbing panels (OTsKZP) made of solid-state porous air-blown sound-absorbing substances characterized by a porous air-soluble / or a crushed sound-absorbing structure, in which additionally containing Xia (integrated) through bypass diffraction-dissipative channels (SPDDK). The achieved effective reduction in the level of sound energy generated by SHGTO is realized in these cases, as confirmed by the results of experimental studies (see Fig. 13), in the extended frequency range of the sound spectrum, covering both low-frequency and medium- and high-frequency sound radiation. Moreover, to ensure the effect of additional absorption of sound energy in the low-frequency sound range, the additional use of frequency-tunable low-frequency resonator elements (R ^I , R ^II , R ^III ), characterized by selective narrow-band noise reduction efficiency only at pronounced discrete frequencies f _R , to which they customized. This is due to the appropriate structural and technological design of the OCCCH, containing end-to-end bypass diffraction-dissipative channels (SPDC), made accordingly in the structure of a porous monolithic or crushed air-blown sound-absorbing substance, from which the OCCAC is formed, which are designed to provide additional suppression of the generated sound of SHGTO in the technical room energy in a wide sound frequency range. The amplification of the broadband dissipative absorption of sound energy used by the porous monolithic or crushed air-blown sound-absorbing substance used in the OTKZP is carried out by means of the physical process of diffraction enveloping by sound waves (incident and reflected from wall and ceiling barriers) when they fall and pass through the hollow cavities of the SPDK, and dissipation of sound energy in a porous sound-absorbing substance located perimetrically zones surrounding SPDDK. In the physical process of absorbing sound energy, free (open) sound-absorbing surface zones formed by the free surfaces of the faces of each of the isolated crushed fragmented elements of the crushed porous sound-absorbing substance are also included. In addition, there is a concomitant occurrence of additional mechanisms of intensification of the physical process of absorption of sound energy caused by realized diffractive dissipative losses that occur in the zones of edge face and edge sections of separate crushed fragmented sound-absorbing elements, when they travel and bend around by sound waves along the formed, randomly distributed, communicating twisting branched air channels formed by contact and / or clearance gaps with adjacent and / or adhesive mating contacting ribs and faces of separate crushed fragmented sound-absorbing elements that occur along with typical physical processes of sound absorption that are realized directly by the monolithic porous structures of sound-absorbing substances of each of the isolated crushed fragmented sound-absorbing elements. In turn, the hollow air cavities of SPDK formed in the porous structures of the OCSCP, bounded (formed) by the walls of the sound-transparent film elastic shells, contribute to the formation of the anisotropic acoustic structure of the OCCP, which additionally enhances (intensifies) the physical processes of dissipative absorption of sound energy. An additional edge diffractive dissipative absorption of sound energy also arises in the process of enveloping by the propagating sound waves of the end (edge) perimetric surface zones of the open front and back parts of the SPDDK, as well as the free end faces of the bccps when they are narrowly gap-gap placed relative to each other (see diagrams in FIG. 9, 11).

The same physical phenomena (the formation of acoustic anisotropy that enhances the dissipative absorption of sound energy) can be facilitated by the deliberate additional introduction of a sound-absorbing substance composed of porous air-blown sound-absorbing materials represented by separate fragmented porous sound-absorbing elements corresponding in structural composition and geometric dimensions of crushed fragments made of dense (non-porous ) airborne polymeric substances (see Fig. 10). In these cases, their specified limited quantitative dosage composition must be observed, with the necessary appropriate volumetric distribution in the resulting mixture of dissimilar (porous and non-porous) crushed fragments. The mounting installation of the OTsKZP relative to each other with the corresponding narrow-gap air gaps between their opposite opposite end parts causes the dissipative diffraction absorption of sound energy to be realized by the free surface edge zones of the porous sound-absorbing structure, when they are freely enveloped by propagated sound waves (see Fig. 11).

As a result of achieving higher resulting sound-absorbing effects with broad frequency composition, in some cases (if necessary), this reduces the amount of expensive porous sound-absorbing substance used, provided that the desired value (achieved by the technical design or development specifications) is achieved sound attenuation effect. For similar reasons, it is possible (permissible) to use cheaper and / or more environmentally friendly starting semi-finished raw materials in the production of sound-absorbing material (hereinafter - ZPM), which forms a bcc, from the corresponding industrial and technological waste, industrial waste containing porous sound-absorbing structures of materials as part of noise insulation packages of various types of technical objects that have completed their life cycle and have to be recycled. Ultimately, all this contributes to the improvement of the safety ecological characteristics of the claimed technical device (leading to a concomitant "improvement" of the environment), which is realized by reducing the amount of unproductively disposed solid sound-absorbing substances, for example, forcedly subjected to burial processes (for example, in the form of dismantled noise-reducing packages included in the composition of utilized parts and nodes of automatic telephone exchanges that have completed their life cycle), which do not allow their immediate energy utilization by burning, due to the release of harmful and dangerous products of combustion and / or destroying the ozone layer (emissions of CO ₂ ). Thus, this even more actualizes the economic and environmental efficiency of the feasibility of using technical devices using recyclable waste as the initial raw material semi-finished product, made in accordance with the claimed technical solution (invention). Also, in these cases, the 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 composition of the initial semi-finished raw materials includes already manufactured parts and assemblies (panels, upholstery, gaskets from porous ZPM) selected from the dismantled soundproofing packages of various technical objects such as noise-active vehicles (automobile, railway, aviation, tractors, combines, mobile municipal and road-building equipment, etc.), and / or other noise generating units and systems of various power plants (stationary ICE, stationary and mobile compressor units, etc.), and / or used in various types of building objects (zvukoteploizolyatsionnye fibrous or open cell foam facing panels for wall lining floors, elevator shafts, ventilation systems). Ultimately, this allows to reduce the resulting cost of the produced technical device and provides a concomitant reduction in environmental pollution by already generated production wastes and accumulated unused products for the disposal of acoustic materials. Thus, this contributes to the implementation of improved environmental characteristics of the device, which are carried out, among other things, by reducing the number of sound-absorbing substances subject to compulsory disposal (for example, noise-reducing packages in the components of automatic telephone exchanges that have expired), which do not allow their direct energy utilization by burning. To manage the simplification of the technological operations of mechanical crushing (cutting / cutting) and their subsequent volumetric distribution to ensure 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 low-noise technical rooms, it can also used produced "new" isolated crushed fragmented sound-absorbing elements. The term "new" means crushed fragmented sound-absorbing elements made from "new" (not recyclable) raw materials, for example, from the corresponding semi-finished flat-sheet type (flat sheets or ZPM rolls). Combined mixtures of sound-absorbing substances can also be used, given in certain proportions of dosed combinations of isolated crushed fragmented sound-absorbing elements obtained from recycled recycling acoustic materials of parts and assemblies, to which a certain amount of produced “new” isolated crushed fragmented sound-absorbing elements of given geometric shapes and dimensions is added sizes made from the “new” original half briquette raw materials for the production of porous ZPM (sheet, roll). In a number of cases, this makes it possible to more flexibly control the final physical (acoustic) parameters of the formed mixed combined structural mass of sound-absorbing substances (acoustic, weight, density, stiffness, operational) carried out by introducing the “quantitative” new quantitative dosed additives in the required proportions into it. isolated crushed fragmented sound-absorbing elements characterized by narrower scatter fields of controlled acoustic parameters of pores sound absorbing substance. Thereby, technological procedures can be implemented, to one degree or another, to the extent that improve the physical (acoustic) characteristics of the resulting structure of the OTZP as part of the inventive low-noise technical room.

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

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

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

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

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

смешанные пути передачи воздушного и структурного звука дверным проемом 5 и входной дверью 6 технического помещения (строительного здания) 1

mixed transmission paths of air and structural sound by the doorway 5 and the front door 6 of the technical room (building) 1

прямое звуковое излучение шумогенерирующего технического объекта 9, передаваемое воздушными путями передачи

direct sound radiation of a noise generating technical object 9 transmitted by air transmission

вторичный структурный звук «твердых» ограждающих элементов технического помещения 1, возбужденный шумогенерирующим техническим объектом 9;

the secondary structural sound of the "solid" enclosing elements of the technical room 1, excited by the noise-generating technical object 9;

- in FIG. 2 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 installed on the wall (pos. 2) and ceiling 3 (not shown in Fig.), With air gaps between the opposite opposite end faces ОЦКЗП 10, made in a porous sound-absorbing structure ОЦКЗП 10 СПДДК (pos. 11), the walls of which are formed by the supporting inner film elastic soundproof shell 18;

- in FIG. 3 shows an illustrative, specific example of a technical room 1 with a ShGTO 9 installed in it, presented in the form of a diesel generator set, with ceiling ceilings (pos. 2) and ceiling 3 (not shown) in Fig. 10, installed in the porous sound-absorbing structure of OTsKZP 10 SPDDK (pos. 11), the walls of which are formed by the supporting inner film elastic soundproof sheath 18;

- in FIG. 4 schematically shows the front fragment of the execution of the wall enclosing ceiling (pos. 2) of the technical room 1 with OTKZP 10 mounted on its surface, installed with narrow-gap air distance gaps γ, formed between their opposite opposite end faces 25;

- in FIG. 5 schematically shows a fragment of the execution of the wall enclosing ceiling (pos. 2) of the technical room 1 with mounted OTsKZP 10 installed with a remote air gap k of their rear surfaces 17 relative to the opposite opposite surface of the wall overlap (pos. 2);

- in FIG. 6 schematically shows the design of the wall enclosure (floor) 2 of the technical room 1 with the installation of OTsKZP 10 installed with a predetermined air distance clearance k of their rear surfaces 17 with respect to the opposite surface of the wall enclosure (overlap), pos. 2, while OTsKZP 10 from the side of their front surfaces is additionally blocked by a sound-transparent facing protective and decorative perforated panel 24;

- in FIG. 7a presents an example of the technological design of the technical means of securing the OTsKZP 10 in a horizontal position through the use of appropriate suspension units mounted on the horizontal surface of the ceiling 3 of the technical room 1, made in the form of the corresponding type of remote mechanical fasteners 12;

- in FIG. 7b presents an example of the technological design of the technical means of securing the OTsKZP 10 in a horizontal position 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 supporting translucent sheath 19;

- in FIG. 7c shows an example of the technological design of technical means of securing the OTsKZP 10 in a horizontal position 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 the corresponding type of suspended cable elements 13 connected to the internal embedded reinforcing sound-transparent element 23 of the OTsKZP 10;

- in FIG. 8a shows an isometric image of the OTKZP 10 with SPDK made in its porous structure (pos. 11);

- in FIG. 8b shows a fragment of an isometric cross-section of a bcc 10;

- in FIG. Figure 9 shows a diagram of the implementation of the physical mechanisms of diffraction enveloping and energy absorption of incident sound waves in the porous sound-absorbing structure of the OTsKZP 10 arising at the peripheral edge zones of the open front and back parts of the SPDK (pos. 11). The arrows in FIG. 9 is indicated:

- in FIG. 10 shows a diagram of the implementation of a physical process (mechanism) of diffraction envelope by sound waves, with concomitant absorption of the energy of sound waves propagating inside a porous air-blown sound-absorbing structure of a substance 27, concentrated in a closed internal cavity of the SCLP 10, containing in this structure of a porous air-blown sound-absorbing substance 27 isolated crushed fragmented sound-absorbing elements 15, including, including sound-reflecting air-blown closed-cell foam and / or dense non-porous structures of polymeric materials. The arrows in FIG. 10 is indicated:

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

Direction of incident sound waves to a separate, all-molded sound-absorbing panel (key 10)

Направление дифракционных огибаний звуковыми волнами плотных воздухонепродуваемых звукоотражающих элементов 21, помещенных в структуру пористого воздухопродуваемого звукопоглощающего вещества 27, представленного в виде обособленных дробленных фрагментированных звукопоглощающих элементов 15;

The direction of the diffraction envelopes by sound waves of dense air-blown sound-reflecting elements 21, placed in the structure of a porous air-blown sound-absorbing substance 27, presented in the form of separate fragmented fragmented sound-absorbing elements 15;

- in FIG. 11 is a diagram of the implementation of the physical process of diffraction envelopes by the propagated sound waves of the edge end faces of the bcc in the formed narrow-gap air gaps 26 between the opposite opposite edge (end, end) zones of the end faces 25, with the subsequent propagation into the porous sound-absorbing air-borne substances arising concomitant irreversible dissipative energy losses (with arising additional absorption of sound a marketing energy). The arrows in FIG. 11 is indicated:

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

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

Направление дифракционных огибаний распространяемыми звуковыми волнами узкощелевых воздушных зазоров (поз. 26) краевых (концевых, торцевых) зонах (торцевых гранях 25) обособленных цельноформованных звукопоглощающих панелей (поз. 10) и перепускных каналов (поз. 11);

The direction of the diffraction envelopes of the narrow-gap air gaps (key 26) by the propagated sound waves (pos. 26) of the edge (end, end) zones (end faces 25) of the separate whole-formed sound-absorbing panels (pos. 10) and bypass channels (pos. 11);

- in FIG. 12 is a diagram of the mounting clearance (γ, k) layouts of the OTsKZP 10 with respect to the opposing opposite sound-reflecting surface of the enclosing wall structure (item 2) of the technical room 1 (gap k) and between the opposite opposing end faces 25 of the OTKZP 10 (clearance γ) with schematic images of a straight line sound wave incidence (solid arrows) and reflected sound wave incidence (dashed arrows). The arrows in FIG. 12 is indicated:

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

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

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

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

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

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

- in FIG. 13 shows the results of comparative measurements of the reverberation sound absorption coefficient α _rev (in conventional units) of the initial state of the studied prototype OTKZP 10 with overall dimensions l ^× b ^× h = 1000 ^× 1000 ^× 50 mm, the porous air-produced sound-absorbing substance (item 27) of which separate crushed fragmented sound-absorbing elements (pos. 15) placed in a sound-transparent capacitive cavity made of an elastic sound-transparent layer of a polyester film, 0.012 mm thick, in versions of it gapless (k = 0) and gap (k = 300 mm) mounting relative to the floor surface of the Cab Alfa small reverberation chamber, as well as in the variants of subsequent execution in the structure of the porous air-blown sound-absorbing substance (pos. 27) of additional SPDK (pos. 11) diameter of 50 mm in an amount of 5 pcs. and 9 pcs. The lines on the graph mean:

1 - a monolithic prototype OTsKZP (pos. 10) with overall dimensions l × b × h = 1000 × 1000 × 50 mm, made of separate crushed fragmented sound-absorbing elements (pos. 15), placed in soundproof capacitive cavities made of a layer of polyester film , thickness 0.012 mm, gaplessly mounted on the floor surface of the small reverberation chamber “Cabin Alpha”; 2 - a monolithic prototype OTsKZP (pos. 10) with overall dimensions l × b × h = 1000 × 1000 × 50 mm, made of separate crushed fragmented sound-absorbing elements (pos. 15), placed in soundproof capacitive cavities made of a layer of polyester film , 0.012 mm thick, mounted on a soundproof mounting platform with an air gap of k = 30 mm relative to the sound-reflecting surface of the floor of the Cab Alfa small reverberation chamber; 3 - a monolithic prototype bccb (pos. 10) with overall dimensions l × b × h = 1000 × 1000 × 50 mm, made of separate crushed fragmented sound-absorbing elements (pos. 15), placed in soundproof capacitive cavities made of a layer of polyester film , thickness 0.012 mm, gaplessly installed on the sound-reflecting surface of the floor of the small reverberation chamber “Cabin Alpha”, with 5 bypassed diffraction-dissipation channels with a diameter of d = 50 mm; 4 - monolithic prototype OTsKZP (pos. 10) with overall dimensions l × b × h = 1000 × 1000 × 50 mm, made of separate crushed fragmented sound-absorbing elements (pos. 15) placed in soundproof capacitive cavities made of a layer of polyester film , with a thickness of 0.012 mm, gaplessly installed on the sound-reflecting surface of the floor of the small reverberation chamber “Cabin Alpha”, with 9 SPDDKs with a diameter of d = 50 mm; 5 - monolithic prototype OTsKZP (pos. 10) with overall dimensions l × b × h = 1000 × 1000 × 50 mm, made of separate crushed fragmented sound-absorbing elements (pos. 15), placed in translucent capacitive cavities made of a layer of polyester film , 0.012 mm thick, mounted on a soundproof mounting platform with an air gap of k = 30 mm relative to the sound-reflecting floor surface of the Cab Alfa small reverberation chamber, with 5 SPDDKs with a diameter of d = 50 mm; 6 - a monolithic prototype bccb (pos. 10) with overall dimensions l × b × h = 1000 × 1000 × 50 mm, made of separate crushed fragmented sound-absorbing elements (pos. 15) placed in soundproof capacitive cavities made of a layer of polyester film , 0.012 mm thick, mounted on a soundproof mounting platform with an air gap of k = 30 mm relative to the sound-reflecting floor surface of the Cab Alfa small reverberation chamber, with completed bypass diffraction-dissipation channels with a diameter of d = 5 0 mm in the amount of 9 pcs.;

- in FIG. Figure 14 shows the results of comparative measurements of the reverberation sound absorption coefficient arev (in conventional units) of the initial state of a prototype monolithic sample ОЦКЗП 10, a porous air-blown sound-absorbing substance (pos. 27) of which is represented by a fully formed fibrous porous air-blown sound-absorbing material with overall dimensions l × b × h = 1000 × 1000 × 20 mm in variants of its clearance-free (k = 0) and clearance (k = 300 mm) mounting relative to the floor surface of the Cab Alfa small reverberation chamber, as well as in the variant x its fragmented crushing into 8 samples of identical overall dimensions, followed by a gapless (γ = 0) and gap (γ = 10 mm) opposite arrangement of their opposite end faces of 25 formed fragmented samples of a bcc 10. The lines on the graph mean:

7 - a monolithic prototype OTsKZP (item 10) with overall dimensions l ^× b ^× h = 1000 ^× 1000 ^× 20 mm, made of a plane porous, one-piece fibrous sound-absorbing material, gaplessly mounted on the floor surface of the Cab Alfa small reverberation chamber with open ( non-soundproof) end faces; 8 - monolithic prototype OTsKZP (item 10) with overall dimensions l ^× b ^× h = 1000 ^× 1000 ^× 20 mm, made of a plane porous, one-piece fibrous sound-absorbing material, mounted on a soundproof mounting platform with an air gap of k = 30 mm relative to the sound-reflecting surface the floor of the small reverberation chamber “Cabin Alpha” with open (non-soundproof) end faces; 9 - a monolithic prototype OTsZP (item 10) with overall dimensions l ^× b ^× h = 1000 ^× 1000 ^× 20 mm, made of a plane porous integrally formed fibrous sound-absorbing material, gaplessly mounted on the sound-reflecting surface of the floor of the Cab Alfa small reverberation chamber with soundproof end faces; 10 - a monolithic prototype OTsKZP (item 10) with overall dimensions l × b × h = 1000 × 1000 × 20 mm, made of flat-sheet porous, one-piece fibrous sound-absorbing material, divided into 8 identical square fragments mounted with end-to-end gaps relative to each other at a distance of γ = 10 mm and with air gaps of their rear surfaces relative to the floor of the Cab Alfa small reverberation chamber (end faces of 8 fragments of prototype samples are not soundproofed).

The digital positions in the figures shown indicate:

1 - technical room;

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

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

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

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

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

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

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

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

10 - separate whole-molded combined sound-absorbing panel (hereinafter - OTsKZP 10);

11 - through bypass diffraction-dissipative channels (hereinafter - SPDK);

12 - remote mechanical fasteners;

13 - suspended cable elements;

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

15 - separate fragmented fragmented sound-absorbing elements (hereinafter - ODFZE);

16 - the front wall of the OTsKZP 10;

17 - the back wall of the OTsKZP 10;

18 - carrier inner film elastic soundproof shell SPDDK 11;

19 - supporting external surface cladding translucent sheath OTsKZP 10;

20 - external surface protective cladding sound-transparent layer of the material OTsKZP 10;

21 - air-blown closed-cell foamed and / or dense non-porous structures of polymeric materials ODFZE 15;

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

23 - internal embedded soundproof reinforcing elements of the rod, mesh or plate-perforated types OTsKZP 10, (hereinafter referred to as internal embedded soundproof translucent reinforcing elements 20);

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

25 - end faces OTsKZP 10;

26 - narrow-gap air gaps formed between opposing opposite opposite end faces 25 OTsKZP 10 mounted on the supporting wall elements of the walls 2 and ceiling 3 of the technical room 1;

27 - porous air-generated sound-absorbing substance (ODFZE 15 or monolithic foamed open-cell polyurethane foam, and / or monolithic whole-molded fibrous material).

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

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

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

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

R ^I - quarter-wave acoustic resonator;

R ^II - half-wave acoustic resonator;

R ^III - Helmholtz acoustic resonator;

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

звуковых волн рабочей доминирующей функциональной частоты f_ms звукового излучения ШГТО 9, укладывающихся в ограничительных пределах габаритного параметра А, характеризующего габаритные размеры внутренней трехмерной воздушной полости технического помещения 1 (L, В, Н);n _vs - integer (natural number) of half-lengths

sound waves of the working dominant functional frequency f _{ms of} sound radiation SHGTO 9, falling within the bounds of the overall parameter A, characterizing the overall dimensions of the internal three-dimensional air cavity of the technical room 1 (L, B, H);

K ' _t is the temperature coefficient of correction of the speed of sound c and the sound wavelength λ _{ms of the} working dominant functional frequency f _ms emitted by SHGTO 9 at a given steady-state operating speed mode n _s , in the operational range of air temperature Δt ° C in the internal three-dimensional air cavity technical room 1 (L, B, N);

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

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

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

λ is the sound wavelength, m;

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

k - remote air gap between the surface of the back wall 17 OTsKZP 10 mounted on the enclosing wall 2 and ceiling 3 of the ceiling and the opposite opposite surface of the wall 2 (ceiling 3) enclosing the technical ceiling 1;

γ - remote air gap between the opposite opposite surfaces of the walls of the end faces 25 OTsKZP 10 mounted on the enclosing wall 2 and ceiling 3 floors of the technical room 1;

d - diameter SPDK 11;

t is the overall thickness of the end faces 25 OTsZKP 10

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

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

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

K _perf - perforation coefficient (conventional units);

ρ _f - density in kg / m ³ filling ODFZE 15, represented by a porous air-generated sound-absorbing substance 27 of the internal cavity of the OCCP 10;

Terminological definitions used in the text of the description of the application for invention

Acoustic resonators (R) - frequency-tuned sound-damping devices (Helmholtz acoustic resonators R ^III , quarter-wave R ^I and half-wave R ^II acoustic resonators R), designed for dissipative absorption (scattering, damping, antiphase compensation) of sound (acoustic) energy propagated in the gas-dynamic under consideration the (aerodynamic) system to which they are connected; the most efficient use of acoustic resonators R refers to the absorption of resonant sound vibrations released in the spectra of sound radiation of a gas-dynamic (aerodynamic) system.

Diffraction of sound waves - a physical phenomenon associated with the deviation of sound waves from their straight-line propagation when interacting with an oncoming solid-body obstacle (located on the path of their propagation); the occurrence of the diffraction-dissipative effect of sound absorption is due to the physical process of additional dissipation of the energy of the sound wave propagated on a solid (porous) obstacle, with a finite value of the input acoustic impedance of the surface of a solid obstacle (porous fibrous or foamed open-cell structure); a new scattered sound wave formed by the diffraction process of propagation at the edges (faces) of a solid-state porous element of finite dimensions (forming an edge diffraction effect) causes an additional flow of sound energy directed (propagating) into the porous solid-state structure of this element, which leads to additional dissipation of sound energy and, accordingly, to an increase in the resulting sound-absorbing effect.

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

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

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.

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

Wave interference is the physical process of combining in unlimited space (or in a limited waveguide) two or more two waves having the same oscillation periods T, as a result of which in different zones of unlimited space (or limited space of a volume waveguide) the amplitude value of the resulting wave increases or decreases in depending on the ratio of the phases of the oscillations ϕ of the folding (interacting) waves, thus forming non-uniform spatial distributions of the amplitude p the resulting wave.

Glues, adhesives - compositions based on organic or inorganic substances capable of joining (gluing) various materials; their action is due to the formation of a strong adhesive bond between the adhesive layer and the joined surfaces; the strength of the adhesive joint is also affected by the cohesion of the adhesive layer and mating surfaces; The basis of organic adhesives are mainly synthetic oligomers and polymers (phenol-formaldehyde, epoxy, polyester resins, polyamides, polyurethanes, silicon-organic polymers, rubbers, etc.) that form the adhesive film as a result of hardening upon cooling (thermoplastic adhesives), curing ( thermoactive adhesives) or vulcanization (rubber adhesives); inorganic adhesives include aluminophosphate, ceramic, silicate, metal.

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

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

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

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

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

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

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

Sound-transparent material (film, foil, microperforated, fabric, non-woven fabric) is a structural material, the installation of which on the surface of the porous sound-absorbing layer (by performing, including contact “technological stitching” of their mating surfaces) causes an acceptable drop in the reverberation sound absorption coefficient (α _rev ) no more than 10%; the provided sound transparency properties are substantially characterized by the selected respective values of the parameters of resistance to blowing by the air flow (fabric or microperforated film or microperforated foil layers), and / or the established values of thickness, bending stiffness and specific surface mass, determined by the mass of material per 1 m ^{2 of the} surface (continuous film or foil layers not blown by the air flow); the values of the resistance to blowing through the air stream of sound-transparent air-blown fabrics or air-blown non-woven fabrics (perforated polymer film or perforated foil metal layers) should be within 20 ... 500 ns / m ³ , with the thicknesses of the fibrous layer of fabric material, fibrous non-woven fabric, microperforated film polymer or microperforated foil metal layer constituting 0.025 ... 0.25 mm and their surface density of 20 ... 300 g / m ² ; values of surface density (specific surface mass) of continuous sound-transparent films not blown by the air flow are in the range of 20 ... 70 g / m ² , with a film thickness of 0.01 ... 0.1 mm; sound-transparent material can be made of various structural materials - polyethylene terephthalate, polyester aluminized, urethane, polyvinyl chloride films, or from a similar type of other polymeric materials acceptable for these purposes; the use of microperforated foil metal material involves the use of aluminum, copper, brass as a structural material; a continuous layer of an air-blown fabric (non-woven fabric) can be made of materials such as maliflis, filts, fiberglass, and fabrics based on superthin basalt fibers.

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

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

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

Waste is any substance or object that the owner throws away, or intends to throw away, or it is to be thrown away (as defined by Directive 75/442 of the EEC).

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

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

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

Dissipative energy losses - irreversible dissipation (loss) of energy (in this case, vibrational energy concentrated in the sound frequency range).

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

The essential features of the claimed technical solution are also illustrated by figures 1 ... 14.

Schematically depicted in FIG. 1 technical room 1, contains rigid load-bearing enclosing elements made in the form of walls 2, ceiling 3, floor 4, doorway 5 with a closed front door 6 and ventilation openings 7. An internal three-dimensional air cavity 8 of technical room 1 is formed by a hollow rectangular cylinder, made in the form of a hollow rectangular parallelepiped with overall dimensions A (L, B, H), in which SHGTO 9 is mounted, producing “spurious” acoustic (noise) radiation, presented in the form of distributed sound waves (sound field), qualified by noise, the basic spatial directions of the propagation paths of sound waves are depicted in the indicated figure by the corresponding arrows. Rigid load-bearing enclosing sound-reflecting elements of the technical room 1 (walls 2, ceiling 3) can be represented by prefabricated large-panel (reinforced concrete, frame-metal), large-block monolithic or manual masonry structural and technological versions.

A distinctive feature of the claimed technical device, presented in the form of a low-noise technical room 1, is the corresponding equipment (lining of wall and ceiling structures) of the technical room 1, mounted with air gaps between opposite (opposite) end faces 25 of OTsKZP 10 and relatively opposed (opposite) enclosing surfaces walls 2 and ceiling 3 of the technical room 1, OTsKZP 10 (see Fig. 2, 3, 4, 5, 6, 7a, 7b, 7c), composed of a porous air-blown sound absorber thickening agent 27 (ОДФЗЭ 15, or a monolithic foamed open-cell polyurethane foam, or a monolithic whole-molded fibrous material), made (integrated) in the structure of a porous sound-absorbing substance 27 SPDDK (item 11), the walls of which are formed by supporting internal film elastic elastic translucent shells 18.

The installation installation of ОЦКЗП 10 in the technical room 1 can be carried out in various ways, in particular, by hanging them from the ceiling 3 using the appropriate type of remote mechanical fasteners 12 (see Fig. 7a) or suspended cable elements 13 (see Fig. 7b and 7c), or mounting on walls 2 by means of a mounting profile 14 (not shown in FIG.), with the formation of a predetermined remote air gap k between the rear surface of the OTKZP 10 and the opposite surface of the walls 2 of the technical room 1 (see Fig. 5, 6, 7a, 7b, 7c). Remote air gap γ formed between opposite (opposite) end surfaces of faces 25 of a number of mounted samples of OTKZP 10, is no more than a quarter of their overall thickness (size t) of end faces 25 of OTsZP 10 (γ≤0.25t). Mounted OTsKZP 10 from the side of their front surfaces can be additionally covered by the installed sound-transparent facing protective and decorative perforated panel 24 (K _perf ≥ 0.25), freely (without significant ≤10% reflection of sound energy) transmitting propagated sound waves in the direction of the mounted OTsKZP 10, as this is particularly illustrated in FIG. 6. Sound-transparent facing protective and decorative perforated panel 24 can be mounted both gaplessly to the front surfaces of OTsKZP 10, and with an air gap. The recommended allowable decrease in the reverberation coefficient of sound absorption α _rev from the additional installation of a sound-transparent facing protective and decorative perforated panel 24 in front of the front surfaces of OTsKZP 10 should not exceed 0.1.

The installation of the OTsKZP 10 with a predetermined air gap k of their rear surfaces relative to the soundproofing surfaces of the ceiling 3 or walls 2 of the technical room 1, which are opposite to them, as shown in FIG. 5, 6, 7a, 7b, 7c, 12, allows to a certain degree to deliberately control the change in the sound-absorbing effect in the low-frequency range of the sound spectrum. In this case, a specific limiting range of changes in the values of k is not established, but is determined based on the requirements of the technical specifications for development, technical operating conditions and cost considerations. It should be borne in mind that an increase in the parameter k causes a corresponding decrease in the useful working space of the technical room. With a corresponding increase in the parameter k, this also leads to an additional effect of enhancing the dissipative diffraction absorption of sound energy that occurs at the free perimetric edges (end zones) of the OCCH 10 when they are diffractively enveloped by reflected sound waves (see Figs. 11, 12). An enveloped sound wave during its propagation, with the occurring process of dissipative friction and scattered in a porous air-produced sound-absorbing substance 27 in the zone of free end peripheral edges of each OTKZP 10, due to the realized edge diffraction effect and the accompanying dissipative absorption of its energy, is accompanied by the process of additional oncoming overflow with its front to the back porous surface and in the opposite direction from the back to the front (see Fig. 11). For a sound wave reflected from the surface of a wall or ceiling, a similar diffractive dissipative effect of the flow of sound energy from the back surface of the OCCH 10 to its front surface takes place, followed by propagation (and attenuation) in the depth of the porous air-blown sound-absorbing structure 27 of the OCCC 10 (see FIG. . 9). This, in turn, leads to a corresponding additional positive effect of the resulting increase in the dissipative absorption of sound energy.

Each mounted, with given air gaps (γ, k), OTsKZP 10, can be considered, including as an autonomous volumetric sound-absorbing element, characterized by significantly higher sound-absorbing characteristics (parameters α _rev , A _ekv ) in comparison with the gaplessly mounted flat sound-absorbing panels of the same surface area, masses made of the identical structure and physical characteristics of the sound-absorbing substance.

The internal cavities of the OTsKZP 10, formed by the supporting external surface cladding sound-transparent shells 19 and the bearing internal film elastic sound-proof shells 18, are filled with a monolithic porous air-produced sound-absorbing substance 27 or formed by separate crushed fragmented sound-absorbing elements 15, with their gaps as a result of which numerous additional communicating sinuous intercostal spaces are formed and inter-face air-blown waveguide sound-propagating (sound-transmitting) and, accordingly, dissipative sound-absorbing channels. This type of crushed sound-absorbing material used can mainly include identical or different types, structures and grades 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 shapes and dimensions, produced x from solid recyclable, mainly polymeric waste, presented in the form of parts and assemblies dismantled from utilizable technical objects that are technologically processed by the method of mechanical crushing of sound-absorbing structures, mainly parts of noise-insulating packages of vehicles that have completed their life cycle, and / or from technological waste and rejects production of sound-absorbing materials and parts and assemblies made from them. Separate crushed fragmented sound-absorbing elements 15 can also be manufactured according to typical technologies for their production from “new” semi-finished sheet (roll) acoustic materials subjected to the subsequent technological process of their mechanical crushing into fragments of a given geometric shapes and dimensions, in addition to the already used separate crushed fragmented sound absorbing elements 15 made from recyclable acoustic materials listed by you neck. As possible structural and technological options for the execution of OTsKZP 10, its closed internal cavity 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 structures of polymeric materials 21.

Between the front 16 and rear 17 walls of the OTsKZP 10 in the porous air-blown structure of the sound-absorbing substance 27, SPDK 11 is made, formed by the walls of the bearing inner film elastic soundproof shells 18.

The ensured sound transparency properties of the supporting outer surface cladding soundproof sheath 19 OTsKZP 10 are substantially characterized by the selected corresponding values of the physical parameters of the resistance to blowing through the air flow of the layers of materials (fabric, non-woven fabric, microperforated film, microperforated foil layers, and / or specified thicknesses, bending stiffness and their specific surface mass, determined by the mass per 1 m ² surface (not continuous film or foil layers blown by the air flow.) The values of the resistance to blowing through the air stream of sound-transparent air-blown fabrics or sound-transparent air-blown non-woven fabrics (micro-perforated polymer film or micro-perforated foil metal layers) are in the range of 20 ... 500 ns / m ³ , with thicknesses fibrous layer of fabric material, fibrous non-woven fabric, microperforated polymer film or microperforated foil a metal layer constituting 0.025 ... 0.25 mm with a specific surface weight of 20 ... 300 g / m ² .

The values of surface density (specific surface mass) of continuous sound-transparent films not blown by the air flow are in the range of 20 ... 70 g / m ² , with a film thickness of 0.01 ... 0.1 mm. The outer surface cladding translucent material layer 20 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 layer of material 20 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 diameter of the passage section of perforation holes not exceeding 1 mm) of a foil material that provides for the use of aluminum, copper, and brass as a structural material. The outer surface cladding a translucent material layer 20 of the supporting outer surface cladding a translucent shell 19, can also be made of a continuous layer of air-blown fabric (non-woven fabric) material, can be represented by materials such as "maliflise", "filts", fiberglass, basalt fabric from superthin basalt fiber. The use of these types of structural materials for the manufacture of an external surface cladding a translucent material layer 20 of a supporting external surface cladding a translucent sheath 19 used in the composition of OTsKZP 10, provides for a given packing density (ρ _f = 10 ... 655 kg / m ³ ) closed inner cavity OTsKZP 10 corresponding separate crushed fragmented sound-absorbing elements 15, the elimination of unwanted ingress and accumulation (absorption) in porous open-cell foamed or porous fibrous structures of isolated crushed fragmented sound-absorbing elements 15, various types of process and / or operating fluids (moisture, fuel, cutting fluids), as well as small amorphous particles or insects during operation of the claimed technical object.

For the formation of the corresponding sound-transparent compounds (the implementation of sound-transparent technological “cross-linking”) of the composite element layers into the monolithic multilayer structure of OTsKZP 10, various types of sound-transparent adhesive coatings 22 can be used, realized, for example, by the appropriate temperature heating and melting of the used hot-melt polymer films or fibers placed on the surface structure of the outer surface protective cladding translucent material layer 20 (not pits of the outer surface cladding soundproof sheath 19), or the supporting inner film elastic soundproof sheath 18, or between the contacting ribs and faces of separate fragmented sound-absorbing elements 15 during the implementation of the manufacturing process (assembly) of OTsKZP 10. For possible implementations of various structural and technological options OTsKZP 10, when the polymer material of the external surface protective cladding soundproofing is used of the casing layer of the material 20 (the supporting outer surface cladding soundproof shell 19) or the supporting inner film elastic soundproof shell 18, which does not provide the required adhesive bond by melting it (with appropriate heating of its structure), a satisfactory adhesive joint can be achieved by introducing additional soundproof ( which do not have a significant negative, by no more than 10%, decrease in the value of the sound absorption coefficient of sound energy) a limited type of adhesive adhesive layers (in the form of sticky adhesive or thermosetting hot melt materials) technologically realized by surface separated thin thin continuous lines, or surface separated by thin thin broken lines, or as a thin continuous continuous surface layer perforated through holes in a sound-transparent adhesive substance, or continuous thin sound-translucent sticky adhesive layer with a low specific surface weight (not exceeding 100 g / m ² ), or in the form of a continuous thin sound-transparent thermoactive hot-melt adhesive layer with a low specific surface weight (not more than 50 g / m ² ).

In the closed internal cavity of the OCCHP 10, filled with a porous air-generated sound-absorbing substance 27 formed by separate crushed fragmented sound-absorbing elements 15, the corresponding internal embedded sound-transparent reinforcing elements 23 of the rod, or mesh, or plate-perforated types may additionally be contained.

The supporting outer surface soundproofing cladding shell 19 OTsKZP 10 can additionally overlap with a metal or polymer soundproofing cladding protective and decorative mesh or perforated panel 24 (as shown in Fig. 6), with a perforation coefficient K _perf ≥0.25.

During operation of SHGTO 9, which contains thermally loaded units and systems mounted in the immediate vicinity of the surface zones of the OTsKZP 10 installation and the sound-transparent facing protective and decorative perforated panels 24 of the technical room 1, the indicated structural elements (pos. 10 and 24) can be performed taking into account their heat-resistant fire-safe design and technological execution. In these cases, in particular, flame retardants can be used for their structural impregnation and / or thin-layer surface application. Thus, additional substances or mixtures of substances that protect materials of organic or synthetic origin from ignition and self-combustion can additionally be used. As flame retardants, aluminum hydroxide, boron, antimony, chloride, organic and inorganic phosphorus compounds can be used in particular. The supporting outer surface cladding soundproof shell 19 in these cases can be made of microperforated metal materials. Similar fire safety requirements for the use of flame retardants can, if necessary, apply to sound-transparent adhesive coatings 22 and to separate crushed fragmented sound-absorbing elements 15. In the considered structural and technological designs, the use of this type of fire-resistant elements can mainly relate only to their local areas of application, and not as part of a complete set of sound-absorbing lining of load-bearing enclosing structures (walls 2, ceiling 3) of technical premises 1. The structures of the specified acoustic elements (pos. 10, 24, 19, 22, 15) removed from the thermally loaded zones of SHGTO 9 can be made of other types of materials that do not require additional treatment with flame retardants or do not require metal construction, as shown above in the description of the claimed technical device.

The outer surface layer formed by adhesively bonded contacting faces and ribs of individual samples of separate crushed fragmented sound-absorbing elements 15, as part of OTKZP 10, can form the corresponding monolithic air-produced sound-absorbing briquetted structure, which, in turn, can adhesively mate with the external surface surface cladding translucent shell 19 as part of the OTsKZP 10.

For the effective implementation of the diffraction-dissipative characteristics of the BCCZP 10, the diameter of the cross section d SPDDK 11 must ensure that the following conditions are met:

where t is the overall thickness of the opposite end faces of the OTsKZP 10.

Thereby, physical processes of propagation of the propagated sound waves through the generated SPDDC 11 with the occurring accompanying diffraction-dissipative sound-absorbing effects (see the diagram in Fig. 9) are realized.

Remote air gap k between the rear wall 17 of the OTsKZP 10 and the opposite surface of the walls 2 or ceiling 3 of the technical room 1 is in the range (0.5 ... 10) t. The specified overall range (k≤ (0.5 ... 10) t) allows you to set (adjust) the process of low-frequency absorption of sound energy when the maximum effect of absorption of sound energy at a quarter-wave distance (λ _s / 4) is determined, which is determined from the front surface of OTsKZP 10 to the opposite the sound-reflecting surface of the wall 2 (ceiling 3) placed on it, on which it is mounted.

The use of SPDDK 11 in the structure of the OTsZKP 10, the surface of which is formed by a supporting internal film elastic elastic translucent shell (pos. 18), allows to realize, in this regard, numerous physical principles of suppressing (absorbing) the propagation of sound energy (see diagram in Fig. 9) . This achieves a more effective resulting dissipative absorption of sound energy due to the implementation of physical phenomena noted above in the text of the description of the application, such as:

- the resulting diffraction of the propagated sound waves in the edge zones of the open front and rear end parts of the SPDDK 11, with their deflecting (bending) penetration (passage) in the opposite direction to the direct propagation of sound waves, followed by dissipative thermal dissipation of energy in a porous air-absorbed, sound-absorbing substance 27 from a monolithic sound-absorbing material or isolated crushed fragmented sound-absorbing elements 15 (see Fig. 9);

- an additional increase in the opposite surface area of the incidence and, accordingly, dissipative absorption of sound energy, due to the introduction of 10 hollow molded cavity containers lined with a supporting internal air-blown film elastic translucent sheath 18 into the porous sound-absorbing structure of the SCCCP 18 in the form of SPDDK 11 (see Fig. 9) ;

- the introduction of hollow molded cavity containers represented by SPDDK (pos. 11) into the porous air-produced sound-absorbing structure (pos. 27) of the OTsKZP 10, contributes to a more smooth (less spasmodic) coordination of wave acoustic impedances in the zones of boundary separation of elastic layered media of sound waves propagation ( air and panel type solid-state porous breathable sound-absorbing substance 27, represented, in particular, separate crushed fragmented sound-absorbing elements 15 enclosed in a closed inner cavity formed by a supporting outer surface cladding soundproof sheath 19 and a bearing inner film elastic soundproof sheath 18), in comparison with a typical flat-surface version of a monolithic flat-sheet sound-absorbing panel without SPDK 11 made therein (not containing alternating internal air cavities and inter-cavity jumpers formed by SPDDK 11), which contributes to a quantitative decrease in reflection energy sound waves and an increase in sound-absorbing effect;

- a decrease in dynamic stiffness (increase in dynamic compliance) of the used porous skeleton formed by a crushed sound-absorbing substance (isolated crushed fragmented sound-absorbing elements 15), as well as due to the additional integration of hollow air cavities in the form of SPDK 11 in the structure of the OTKZP 10, which contributes to the process of additional dissipation of the propagated acoustic energy (see Fig. 9);

- the formation of structural-cavity acoustic anisotropy, with the implementation of the enhancement of the physical process of dissipative dissipation of the energy of propagated sound waves, due to the sound-transparent introduction (connection) of 10 hollow molded cavity air containers integrated into the volumetric structure of the OTKZP in the form of SPDK 11;

- the formation of structural acoustic anisotropy with additional dissipative diffraction absorption of sound energy due to the additional introduction into the volumetric structure of the porous air-blown crushed sound-absorbing substance 27 of separate OCCHP 10 of various types of (different) solid-state air-blown closed-cell foamed and / or dense non-porous polymeric structures. 10);

- the implementation of the physical effects of additional absorption of sound energy arising in narrow-gap air gaps formed between opposite opposite end faces of 25 mounted bcc 10, causing the accompanying additional dissipative diffraction absorption of sound energy by the free end edge zones of the porous sound-absorbing structure in the bcc sound waves (see Fig. 11);

- the implementation of the physical effects of amplification of low-frequency quarter-wave absorption of reflected sound energy from solid-state wall (walls - pos. 2) and ceiling (ceiling - pos. 3) panels of the technical room 1 from the introduction of predetermined air gaps k formed between the rear sides of the surfaces of OTsKZP 10 and opposite opposite sound-reflecting front surfaces of the enclosing wall structures (walls 2, ceiling 3), see FIG. 12;

- the use of structural and technological versions of hollow molded cavity containers containing SPDDK 11, using a translucent thin-film element (supporting the inner film elastic elastic translucent shell 18), allows the physical processes of the passage of sound waves from the molded cavity air tank formed by the carrier inner film elastic translucent sheath 18, into the structure of the porous air-blown sound-absorbing substance 27 located in the bent inner cavity OTsKZP 10, represented by a monolithic sound-absorbing substance or separate crushed fragmented sound-absorbing elements 15, which is preferable, with the implementation of the physical process of broadband in frequency composition dissipative absorption of sound energy.

It should be pointed out that excessive perforation of the porous structure of the OCCHP 10 with a large number and large cross-sectional area of SPDDK 11 inevitably entails both a loss in the bulk mass of the porous air-blown sound-absorbing substance 27 and a decrease in the surface zones of diffraction-dissipative absorption localized in the perimeter regions around SPDDK 11 which as a result causes a decrease in the sound-absorbing properties of OTsKZP 10 as a whole. This circumstance requires the solution of a compromise technical and cost problem.

The incident direct sound waves emitted by SHGTO 9, propagated and penetrating into the porous structures of the composite sound-absorbing elements of OTKZP 10, falling onto their front sound-transparent surfaces and penetrating into the porous air-borne sound-absorbing substances 27, of a monolithic type or, more preferably, composed of isolated 15 fragmented fragments , they are effectively dissipatively scattered with the resulting irreversible conversion of sound energy into heat. This applies directly to both the microporous structures of the separate crushed fragmented elements 15, and to the communicating macroporous sinuous air channels and cavities formed between their loosely (gap) placed or contacting faces and ribs. The process of dissipative absorption of sound energy includes, among other things, molded cavity tanks formed by supporting internal film elastic flexible translucent shells 18 SPDDK (pos. 11).

As follows from the description presented as an application for the invention and the results of experimental studies in FIG. 13 and 14, the technical device of the low-noise technical room is endowed with a broadband in frequency composition sound absorption effect. The SHGTO 9 generated by the broadband medium and high frequency sound radiation is suppressed by the porous sound-absorbing dissipative structures of the porous air-blown sound-absorbing substance 27 used in the technical device, composed of both separate fragmented fragmented elements 15 (Fig. 13), and a monolithic mounting foamed or open-cell foam monolithic integral molded fibrous material OTsKZP 10 (Fig. 14). The realized sound-attenuating effects are further enhanced by the emerging edge diffraction-dissipative sound-absorbing effects, as well as the emerging dissipative effect of acoustic anisotropy due to the inclusion in the porous air-produced sound-absorbing substance 27, presented in the form of a monolithic sound-absorbing substance or in the sound-absorbing fractional structure 15 composed of frac formed by air-generated porous sound-absorbing particles of recyclable materials, including due to the introduction of a certain dosage amount and its corresponding volume distribution of crushed fragments made of air-blown closed-cell foam and / or dense non-porous structures of polymeric materials 21 mixed with separate fragmented fragmented sound-absorbing elements 15. Also to enhance the process absorption of sound energy includes physical phenomena of acoustic anisotropy formed by hollow air-shaped and bladder tanks SPDDK (pos. 11) integrated into the volumetric structure of the porous air-blown sound-absorbing substance 27 (monolithic type or composed of separate crushed fragmented elements 15) of the OTKZP 10. In addition, the accompanying diffractive dissipative absorption of sound energy is realized in the edge zones of the open front and back parts of the SPDK (pos. 11), as well as in the end boundary zones of the end faces 25 of the gap-mounted OTsKZP 10. The deliberate implementation of the specified air gaps formed between the rear side They 17 surfaces OTsKZP 10 and opposite opposite sound-reflecting surfaces of the enclosing wall structures (walls 2, ceiling 3), also provides an increase in sound absorption effects in the low-frequency sound range. Also, the suppression of sound radiation in the low-frequency range is enhanced by performing in the structure of the porous sound-absorbing substance 27 OTsKZP 10 SPDDK (item 11) and introducing air gaps k.

The effectiveness of the proposed technical solution is confirmed by the results of experimental studies. The results of experimental studies of the sound-absorbing characteristics of prototype OTsKZP samples (pos. 10) carried out in Fig. 13, containing a porous air-produced sound-absorbing substance (pos. 27), with corresponding SPDKs (pos. 11) made in their structure, the walls of which are formed by a carrier internal elastic film translucent sheath (pos. 18). The experiments were carried out using the “Cab Alpha” small-sized reverberation chamber, the volume of the air cavity of which was 6.45 m ³ , and the working frequency range of measurements covered 1/3 octave frequency bands with centers 400 ... 10000 Hz. As components of prototype bcc samples (pos. 10), we used briquettes of a porous air-blown sound-absorbing substance (pos. 27) made of separate crushed fragmented sound-absorbing elements (pos. 15) placed in soundproof capacitive cavities made of a layer of polyester film with a thickness 0.012 mm. Two variants of prototype bccs (pos. 10) with overall dimensions l ^× b ^× h = 1000 ^× 1000 ^× 50 mm contained 5 SPDDKs embedded in their bulk structures (pos. 11) with a cross-sectional diameter of d = 50 mm in an amount of 5 pcs. and 9 pcs. To evaluate the effects of changing the values of the reverberation sound absorption coefficient α _rev , a third prototype sample made of porous air-blown sound-absorbing material of identical structural and chemical composition and overall dimensions without SPDK integrated in it was used as a reference comparative base (item 11). As follows from the results of experimental studies, the implementation in the structure of a porous sound-absorbing substance (pos. 27) of prototype OTsKZP (pos. 10) SPDDK (pos. 11), allows you to increase by 20 ... 23% the value of the reverberation sound absorption coefficient α _rev in the entire controlled the working frequency range of 1/3 octave bands of the sound spectrum is 400 ... 10000 Hz.

The potential effects achieved by increasing the sound-absorbing properties of the used OTKZP (pos. 10) during their installation of air-gap arrangements with respect to gapless installations with mounting on a hard sound-reflecting surface of the floor of the test chamber are confirmed by those shown in FIG. 14 relevant experimental results. Measurements reverberant sound absorption coefficient α _rev were produced in a small reverberation room "Cab Alpha" using prototypes OTSKZP 10 made of monolithic porous vozduhoproduvaemogo sound absorbing material (pos. 27) made of ploskolistovogo porous tselnoformovannogo fibrous sound absorbing dimensions of the material sample l ^× b ^× h = 1000 ^× 1000 ^× 20 mm. Simulation of backlash-free installation of OTsKZP 10 provided for their direct installation on the hard, sound-reflecting surface of the floor of the Cab Alfa small reverberation chamber. Simulation of the clearance installation ОЦКЗП 10 was carried out using the additional application of a rigid sound-transparent installation platform made in the form of a flat coarse-mesh (cell dimensions - 20 ^× 20 mm) metal mesh, the surface of which was with a given air gap (k = 300 mm) above the hard, sound-reflecting floor surface small reverberation chamber "Cabin Alpha". The experiments were carried out with open and additionally soundproofed end faces (pos. 25) of the initial prototype OCKZP 10, as well as with fragmented fragmentation into 8 identical parts with overall dimensions l ^× b ^× h = 250 ^× 250 ^× 20 mm. The specified air gaps between the opposite opposite end faces of the 25 fragmented parts of the OTKZP 10 were γ = 10 mm. As the results of measurements illustrate, an increase in the effects of absorption of sound energy is achieved both with the gap arrangement of the OTKZP 10 relative to the sound-reflecting surfaces of the building envelope (k), and with the accompanying narrow-gap gap installation (γ) formed between their opposite opposite end faces (key 25) .

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 (5)

A low-noise technical room containing load-bearing enclosing elements in the form of a floor, walls and ceiling, on which separate fast-formed combined sound-absorbing panels are presented, which are provided with shell structural and technological designs in the form of a rectangular cross-section, isolated, with the corresponding fasteners, with the formation of remote air gaps k and γ whole-molded combined sound-absorbing panels composed of appropriate sound-transparent m terials and sound-absorbing substances placed in the cavities of the external and internal surface cladding sound-transparent shells, overlapped by an external surface protective cladding sound-translucent layer of the corresponding material, sound-absorbing substances are represented by monolithic porous sound-absorbing sound-absorbing structures or separate crushed fragmented sound-absorbing elements, which are characterized by shell form t through-pass bypass diffraction-dissipative channels communicating the surfaces of the bearing external surface cladding sound-transparent shells and external surface protective cladding sound-transparent layers of materials of opposite end faces of separate integral molded sound-absorbing panels, while the diameters of the through-pass diffraction-dissipative channels: d = (0.5 ... 0.8) t, where t is the overall thickness of the end faces of the separate integral molded combined sound-absorbing panels; k is the remote air gap formed between the back surface of the mounted separate integral molded combined sound-absorbing panel and the opposed opposite surface of the wall or ceiling of the technical room; γ is the distance air gap formed between the opposing opposite surfaces of the end faces of the mounted separate integral molded combined sound-absorbing panels.

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