RU2767126C1 - Reciprocating internal combustion engine intake system - Google Patents

Abstract

FIELD: engine building.

SUBSTANCE: invention relates to engine building. The intake system of a reciprocating internal combustion engine contains an air cleaner (6) in the form of a volumetric expansion chamber, to which an inlet pipe and an air intake pipe (7) are connected, including a connecting part (16), an inlet part (15), limited by an inlet section (18), in the cavity of which the noise suppression device (19) is coaxially mounted. Noise suppression device (19) comprises a housing with tubular (22), bottom (24) and neck (23) parts, forming integral combined parts of two acoustic resonators - quarter-wave and half-wave acoustic resonators. A longitudinal plate divider (28) is mounted in the air cavity of the quarter-wave acoustic resonator, forming a corresponding bypass window, forming communicating tubular branches of the tubular part (22) of the half-wave acoustic resonator with its two neck (23) parts located in the plane of the throat part (23) of the quarter-wave resonator jointly forming the throat part (23) of the combined resonator muffler (27).

EFFECT: reduction of sound levels throughout the high-speed operation of the engine.

5 cl, 38 dwg

Description

The invention relates to mechanical engineering, in particular engine building, and in particular to reciprocating internal combustion engines (hereinafter referred to as PDVS) equipped with technical means for reducing the noise generated by its intake system (intake noise) and being one of the dominant sources of their acoustic (noise) radiation. The technical solution according to the invention is intended mainly for PDVS as part of the power units of motor vehicles, which are subject to stringent environmental (toxicity, fuel consumption, noise) power, cost and overall restrictions (mainly due to the problems of their cramped layout in engine compartments). engine bays). At the same time, the invention can find the widest application in stationary power plants equipped with PDVS, as well as in other types of reciprocating machines (compressors, pumps).

To suppress resonant gas pulsations in the PDVS intake system (pulsating working process of air suction into the PDVS cylinders, carried out through the air duct and air cleaning components of the PDVS intake system) and to reduce the sound (noise) radiation accompanied (caused) by them into the environment, produced through open end pipe sections of the air intake pipe of the air cleaner of the intake system (aerodynamic noise), as well as the acoustic radiation produced by the vibrating walls of the body elements of the intake system (structural structure-borne noise) - a wide variety of noise-suppressing technical devices are known and used in practice:

- acoustic quarter-wave resonators Ra ^I ;

- Acoustic Helmholtz resonators Ra ^III ;

- chamber mufflers made in the form of volumetric expansion chambers;

- dissipative sound energy absorbers, made in the form of passive surface energy diffusers, made of porous sound-absorbing structures of materials;

- dissipative local absorbers of sound energy, presented in the form of through compensating perforation holes made in the air duct wall of the tubular element;

- technical devices for active noise suppression (anti-phase anti-sound) generated by an additional source (loudspeaker cone) controlled by an external generator;

- controllable, adaptive tunable to different actual frequencies f _R acoustic energy attenuation settings for individual high-speed and / or load modes of operation of a noise-generating technical object, acoustic resonators (quarter-wave acoustic resonators Ra ^I and Helmholtz acoustic resonators R a ^III ), and / or variable volume expansion chambers that perform the functions of chamber noise silencers;

- various combined combinations of the above technical devices for damping acoustic energy.

So, in particular, the Japanese company "Honda Motor", in the application N 63-219866, F02M 35/10, 09/13/88, proposes to use two separate (autonomous) air ducts connecting the air cleaner and receiver cavities to reduce the noise of the PDVS intake system intake systems equipped with two controllable throttle valves, which ensure the corresponding shutdown of the auxiliary channel at low speeds of the PDVS and the open state of both connecting pipelines - at high speeds of the PDVS crankshaft, thereby providing a two-band adaptive setting of the noise reduction process in a wide speed range of PDVS operation .

The Japanese company "Nippon Rajieta", in the application of Japan N 62-48047, F01N 1/02, 12.10.87, in order to increase the effect of noise damping, proposes instead of using additional large-sized material-intensive designs of silencers in the intake system of PDVS, to use a compact anti-resonant an inlet pipe, including a controlled source of noise or vibrations, an electromagnetic valve, receiving acoustic sensors and a control processor.

The English branch of the Ford Motor company in the UK application N 2203488, F02B 29/00, 10/19/88, to suppress the emerging gas pulsations and noise in the PDVS intake manifold, provides for the installation of technical means for generating additional anti-phase "anti-sound", made using a special loudspeaker or a special tank controlled by an electrovalve.

The Canadian branch of Siemens-Bendix, in the technical solution according to US patent N 4934343, F02M 35/00, 06/19/90, to muffle the noise of the gas flow, carried out without a significant impact on the growth of the hydraulic resistance of the intake tract, provides for the use of two special diffuser sections installed on the bifurcated section of the inlet pipeline, providing a controlled phase shift with compensatory suppression of the amplitudes of pressure and rarefaction pulsation waves with their corresponding addition in the connection zone.

The American branch of Siemens-Bendix, in US patent N 4907547, F02M 35/10, 03/13/90, in a technical device designed to suppress noise and pulsations that occur in the PDVS intake system, suggests using a special wave reflector located across flow section of the inlet pipe on the rotating shaft of one of the cylinders and a pair of cylinders, which, turning accordingly, provides a given selective opening of one of the inlet pipes of the PDVS cylinders.

In the European patent application No. 0278117, F02B 27/00, 08/17/88, it is proposed to use a technical device in the form of resonant pipes mutually agreed on acoustic characteristics and an additional receiver used to improve the filling of the PDVS cylinders with a fresh charge, due to the directional suppression of the amplitudes of resonant acoustic gas pulsations, by their compensatory addition in antiphase.

The Japanese company "Mazda-Motor" in the EPO N 0376299, F02M 35/12, 07/04/90, to suppress gas (air) pulsations and noise propagating in the intake system of the PDVS, provides for the use of a technical device for selective suppression of each of the resulting sound resonant harmonics of the indicated pulsations, which are multiples of the resonant wavelengths of the sonic pulsations.

Known, in particular, the design described in the international patent application PCT(E) No. 91/00958, F02M 35/12, 01/24/91, containing an air cleaner made in the form of a corresponding volumetric expansion chamber, to which an inlet pipe with a device is connected fuel supply to the PDVS cylinders and an air inlet pipe limited by an intake section, including an inlet part in which a noise suppression device is coaxially (coaxially) placed, which is made in the form of an internal insert having a confuser-diffuser shape, with a streamlined intake part and side slotted gaps for entry air inside the insert. The confuser-diffuser section performs the function of an additional dissipative energy-dissipating and sound-reflecting element, which ensures the appropriate damping of the noise of the PDVS intake system.

The Japanese company "Hitachi seisakuse", in the application of Japan N 2-4840, F16L 55/04, 30.01.90, to reduce gas-dynamic pulsations and sound waves propagating in systems of pipeline elements, proposes to use the design of a pipeline branched, at least , into two channels. At the same time, at different distances from the branching point, it is proposed to place volumetric expansion chambers that reflect incident sound waves to the source of generation of gas-dynamic pulsations (to the PDVS cylinders), and the distance between the opposite walls of the volumetric expansion chambers is selected in a certain way.

The Japanese company "Nissan Jidosha", in the Japanese application N 51-23656, F02B 37/00, 05/08/89, to solve the technical problems of reducing the intake noise of the PDVS and increasing its effective power, due to the reduction of the negative effect of the reverse charge air flow, offers use the design of a silencer made in the form of an appropriate volumetric expansion chamber equipped with internal tubes of a certain ratio of diameters and a certain distance of their free sections from each other.

The German company "Volkswagen", in the application of the Federal Republic of Germany N 3742322, F02M 35/10, 07/07/88, provides for the use of technical noise suppression devices that can effectively dampen pulsating oscillations of the intake air flow into the PDVS cylinders due to the inclusion of an additional " soothing" receiver with pliable flexible elastic walls of its body, in which due to the elastic deformations of the receiver walls, due to the pulsating effect on them of the air flow sucked into the PDVS cylinders, the energy of air pulsations will be converted into thermal energy dissipated in the elastically deformable dissipative structure of the material walls with high internal friction of the type of polymer material used (rubber). The obvious disadvantages of using such a noise suppression technique include its relative high cost, instability of operational (in time, under conditions of variable operating temperatures) characteristics, low durability, and the risk of uncleaned air entering the PDVS cylinders if the elastic wall is damaged. A potentially possible increase in the radiation of the body structural sound by an intensely oscillating, dynamically deformed "pulsating" surface of this type of elastic wall is also not ruled out.

The Austrian company "AVL", in the patent application of the Federal Republic of Germany No. 3820607, F01B 25/00, 12/29/88, to expand the operating frequency range of effective noise suppression of the additional resonator used as part of the PDVS intake system, proposes to perform its design in the form of an adaptively "following" (controlled) variable volume, depending on the frequency of rotation of the crankshaft PDVS.

Volumetric expansion chambers, made in the form of Helmholtz resonators Ra ^III , are widely used as well-known noise-reducing technical devices. In particular, the Japanese company "Yamaha Motor", in the application N 61-244824, F02B 27/00, 10/31/86, to reduce the resulting gas-dynamic pulsations and noise sucked into the PDVS air flow cylinders, suggests using this type of two volumetric chamber receivers connected in parallel and in series to the air duct of the PDVS inlet pipeline.

The design of the technical device of the intake system PDVS f. "Mazda Motor Corporation", described in European patent application No. 0379926, F02M 35/12, dated January 15, 1990, contains an air cleaner made in the form of a volumetric expansion chamber, to which an air supply pipe is attached, limited by an open intake cut, also includes a low-frequency quarter-wave acoustic resonator Rа ^I , inlet pipeline, with the first Helmholtz resonator connected to it (Rа ^III ), connecting the volumetric expansion chamber of the air cleaner with the receiver, to the end part of which the second acoustic resonator is connected - acoustic Helmholtz resonator (Rа ^III ), which, in its turn, communicates with the inlet pipes for supplying the air-fuel mixture to the PDVS cylinders.

In the patent RU 2679062, F02M 35/12, 05.02.2019, "Ford Global Technologies, LLK", a technical device for a gas-dynamic flow silencer is claimed, made in the form of successively coaxially (coaxially) arranged expansion chambers, with corresponding dividing partitions covering the inner central a pipe, the open cantilevered end section of which communicates with one of the chambers, while the other chambers communicate with the inner central pipe by corresponding bypass windows of given overall dimensions, which increase in the direction of movement of the sucked air flow into the PDVS cylinders. Due to the communication of this type of design of a multi-chamber muffler of different dimensions of the chambers (volumes of air masses filling them), various dimensions of bypass windows made in the inner central pipe, for each composite expansion chamber of the multi-chamber muffler design, as well as the different wall thicknesses of the inner central pipe and geometric shapes of each of the bypass windows of the claimed design, provides a broadband frequency range of damped sound energy. In fact, the claimed technical device is presented as a set of separate frequency-tuned acoustic Helmholtz resonators (Ra ^III ), and as a typical broadband volumetric expansion chamber for damping gas-dynamic noise (with an open end cut of the inner central tube). The technical device under consideration is intended primarily to muffle the broadband high-frequency noise of the compressor, which forcibly pumps air into its cylinders during suction. The characteristic broadband, predominantly high-frequency, radiation of acoustic energy generated by air pressurization devices of reciprocating machines (compressors) makes it possible to limit the use of small-sized expansion chambers (small-sized chambers of Helmholtz acoustic resonators (Ra ^III )). At the same time, the technical device under consideration cannot be used to effectively dampen its own acoustic resonances present in the low and mid-frequency ranges of the sound emission spectrum of the PDVS intake system. The use of the proposed technique in this case forces the use of very bulky large-sized, complex layout in cramped limited free spaces of the engine compartments of vehicles, technical devices. There are also problems of a forced significant increase in material consumption and the cost of using this type of large-sized devices. Other significant disadvantages of the analyzed technical device include the potential process of generating parasitic vortex noise emissions that stand out in the spectra of their own, arising from the accompanying physical processes of high-speed air flows around the edge perimetric zones of bypass windows during transportation of an injected high-speed air charge in the cavity of the inner central tube of this type multichamber muffler. In turn, this requires the use of various additional technical design and technological methods and elements of their weakening (elimination) associated with additional production costs.

The invention according to the technical solution of the patent RU 2704182, F01N 1/02, October 24, 2019, "Henn GmbH und Co. KG", is also represented by a charge air silencer of a functioning turbocharger, forcibly forcing air into the cylinders of the PDVS, mounted as part of the vehicle. The muffler is made in the form of a two-chamber structure formed by coaxial chambers separated by a partition and interconnected by an internal tubular element located coaxially with respect to the axes of the inlet and outlet openings of the body, made in its end walls. By choosing the size of the passage hole, the location of the partition (forming the volumes of each of their chambers), the overall length and flow section of the internal tubular element, the ratio of the diameter of the internal cavity of the chamber to the diameter of the flow section of the internal tubular element, as well as the mutual ratio between the volumes of the muffler's composite chambers, one or another achievable effect of muffling the noise of the PDVS intake system is provided. A silencer of this type is endowed with a broadband effect of damping sound energy in terms of frequency composition, however, it is concentrated mainly in the high-frequency region of the sound spectrum, which is characteristic of operating PDVS equipped with a turbocharger. Obviously, under the condition of the used small dimensions of the muffler design, in the region of excitation of natural acoustic resonances at low and medium frequencies of the sound spectrum, the efficiency of this type of small-sized chamber mufflers is quite low, while the noise emission spectra of the PDVS intake systems contain pronounced dominant low and mid-frequency components due to resonant amplification of sound radiation at natural frequencies of individual composite air duct elements of the PDVS intake system, for which small-sized chamber structures are unacceptable as effective noise-attenuating technical devices. Another significant drawback of the muffler design under consideration is the need to maintain a high degree of centering of the axis of the inner tubular element with the axes of the inlet and outlet openings of the pipeline elements located in the end walls of the muffler housing. Otherwise, if this condition is not observed, not only increased hydraulic (gas-dynamic) losses occur in the intake tract of the PDVS intake system, but additionally, intensive generation of vortex parasitic sound radiation occurs, which occurs during “turbulent disruptions” of a high-speed air flow at the inlet edges (inlet cut) of the end wall of the inner tubular element, which is an undesirable "parasitic" acoustic defect of the structure as a whole.

A well-known noise suppression technique used in the inlet tract of the PDVS intake system is the use of additional technical devices, presented in the form of quarter-wave resonators Ra ^I , as damping acoustic energy, used both as single stand-alone devices and in combination with noise-attenuating volumetric expansion cameras.

So, in particular, the Japanese company "Honda Motor", in the application N 61-190159, F02M 35/12, 01/14/87, in order to ensure noise suppression in a wide range of audio frequencies, uses a technical device in which it proposes to connect to the inlet pipe, two stand-alone dead-end noise suppression devices - a quarter-wave acoustic resonator (Ra ^I ) and a volumetric resonator chamber.

In modern designs of PDVS, used, in particular, on passenger cars, combined designs of noise dampening devices are widely used, containing two (pair) quarter-wave acoustic resonators (Ra ^I ), differing from each other by two times in the overall length of the tubular parts, represented by dead-end waveguide branch pipes that are appropriately connected to the cavity of the air duct tubular part of the noise-emitting air intake pipe of the air cleaner of the PDVS intake system (cars of Subaru, Fiat, Ford, etc.). The patents of coupled quarter-wave acoustic resonators (Ra ^I ) connected to the cavity of the tubular part of the air intake pipe of the PDVS intake system are known corresponding to these technical solutions (see, in particular, European patent No. 0091038 A1, class F02M 35/12, figure 6, pos. 32 and 34).

In the patent RU 2565487, F01N 1/02, 10/20/2015, "SCANIA SV AB", a technical device for damping the noise of a reciprocating machine, represented by a reciprocating compressor, is considered, mounted as part of the design of the PDVS intake system of a motor vehicle, which is an additional "parasitic" source strong tonal "pulsing" sound. The technical device claimed by the patent is made in the form of a tubular-type quarter-wave acoustic resonator Ra ^I , mounted directly in the muffler housing of the PDVS intake system, represented by a volumetric expansion chamber. Said reciprocating compressor, at the same time, is a direct additional source and generator of "parasitic" sound emitted at the operating frequencies of the pulsations of the injected air into the PDVS cylinders, associated with a given speed mode of the compressor. The piston compressor, at the same time, emits sound waves both in the direction of the combustion chamber (PDVS cylinders), and in the direction of the open cut of the air intake pipe of the air cleaner of the intake system and then directly into the open space. This occurs mainly at the given operating speed modes of operation of the reciprocating compressor itself, without a direct relationship with specific geometric parameters prone to resonant sound amplification (primarily overall lengths) of the composite waveguide pipeline sections of the PDVS inlet system. As noted in the description of patent RU 2565487, the resonant amplification of sound radiation is recorded at the fundamental harmonics of the high-speed operating frequency of air injection by a functioning compressor. At the same time, in the intake system of the PDVS and, in particular, in the air intake pipe of the air cleaner of the intake system, resonant acoustic radiation excited by the working processes of filling the cylinders can occur, which are recorded at natural frequencies of the air mass contained in the cavity of the air intake pipe, not directly related to specific speed mode of operation of the piston compressor used, and depending, first of all, solely on the overall (dynamic, taking into account and connected fluctuating air masses at the open end sections of the pipe) the length of the specified air intake pipe, as a hollow pipe, open from both end sections (in open space and into the air cavity of the air cleaner chamber). At the same time, natural acoustic oscillations are excited in the cavity of the air intake pipe, requiring the use of appropriate technical devices for their suppression in order to exclude the appearance of dominant natural acoustic resonances in the noise emission spectra of the PDVS intake system, as the dominant environmental pollutant by intense motor vehicle noise radiation. The technical solution claimed under patent RU 2565487 is not designed to solve this problem.

In the patent application US 2019120187A1, F02M 35/12, 04/25/2019, "FORD GLOBAL TECH LLC", a technical device is claimed, presented in the form of a quarter-wave acoustic resonator Ra ^I used as part of the design of the PDVS intake system, made in the form of a dual-band tunable a given (controlled) rarefaction signal (vacuum) of a two-frequency (dual-band) quarter-wave acoustic resonator Ra ^I . Such a tunable discrete frequency tuning (tuning) is achieved by the operation of a controlled damper integrated in the design of the quarter-wave acoustic resonator Ra ^I , which closes the flow area of its tubular part when the preset value of the vacuum control signal is reached. Thus, a stepwise change in the length of the tubular part is achieved (with the possibility of realizing two values of its overall length), which makes it possible to perform a discrete two-frequency resonant tuning of the quarter-wave acoustic resonator Ra ^I for two different values of the natural resonant frequencies of the resonating pipeline element (air intake pipe or, if necessary, another actual resonating section of the pipeline route of the PDVS intake system), which are relevant for a specific solution to the issue of suppressing the resonant acoustic (noise) radiation of the PDVS intake system. With the option of blocking the passage section of the tubular part of the quarter-wave acoustic resonator Ra ^I , the control damper performs the function of a typical sound-reflecting bottom part (bottom) of the quarter-wave acoustic resonator Ra ^I , while realizing its specified discrete frequency tuning to the specific natural resonant frequency that is relevant for a given high-speed mode of operation of the PDVS fluctuations of the air mass concentrated in the pipeline section of the PDVS intake system, to which the throat and tubular parts of the quarter-wave acoustic resonator Ra ^I are connected. As obvious disadvantages of the technical device claimed under US patent 2019120187A1, one should point out the complexity of its constructive and technological implementation, high material consumption and cost, unsatisfactory compactness and low operational reliability caused by the functioning moving elements of the damper control system.

A technique is also known to reduce resonant acoustic radiation at the lowest natural acoustic modes of the excited air volumetric mass contained in the resonating air cavity of the air intake pipe by additionally introducing various structural and technological elements of dissipative energy dissipative losses into its design. They can be implemented, in particular, by introducing into the walls of the air intake pipe additional through discharge perforation holes located in the zones of formation of antinodes (maximum values) of sound pressures of the lowest natural acoustic modes, as stated, in particular, in the patent for invention RU 2737014, F02M 35/00, 11/24/2020, "AVTOVAZ Joint-Stock Company", or the introduction of porous energy-sound-dissipating air-blown sound-absorbing tubular sections (inserts), as described in the patent for invention RU 2602409, G01V 1/40, 11/20/2016, " SCHLUEMBERGER TECHNOLOGY B.V. However, in both of the above variant examples, in their practical implementations, the corresponding branched channels of the divided additional transmission of sound energy are formed by these additionally introduced structural elements, often causing only the redistribution of the transmission of noise radiation by the PDVS intake system into the surrounding space through the formed several divided transmission channels (introduced through holes perforations in the wall of the air intake pipe or porous air-blown sound-transparent structures of the wall of such a pipe), without a significant effect on the change in its total total level. At the same time, the total total reduction in the noise level of the PDVS intake system may remain insignificant, which does not allow achieving acceptable target effects for effectively solving the problem. This is the reason for their limited application in practice. In addition, the implementation of perforation discharge holes in the wall of the air intake pipe (according to RU 2737014) is a well-known technical solution, the description of which is given, in particular, in the author's certificate for the invention SU 1037701, as well as in foreign patents for the invention GB 2127094, GB 2114657, FR 2533265, DE 3240424, SE 8205103-8, CS 245263, IT 1153728. In particular, in the text of the specified copyright certificate for the specified invention SU 1037701, a reference is made to the "Automobile Handbook", author Bussinen, published in the USSR in translation from English in 1959 year, which shows the figures of the air cleaners of the PDVS intake system, in the air intake pipes of which there are through perforation holes made (evenly distributed) along their entire overall length. The indicated discharge perforation holes, at the same time, can be used to slightly improve the power, economic and environmental characteristics of the PDVS, associated, among other things, with improving the filling of the cylinders with a fresh air charge in the suction working process. In the same patent for invention SU 1037701, it is proposed to optimize the location and total area of the flow sections of perforation holes by their localized placement by location in the form of a grouping in the corresponding belts, with hole placement areas limited by the claims. This technical solution makes it possible to ensure, among other things, sufficient efficiency of suppressing the amplitude values of oscillations of a larger number of excited lower resonant acoustic modes of the air mass concentrated in the cavity of the air intake pipe, by compromising the placement of perforation holes in the antinodes (near antinodes) of maximum fluctuations of sound pressures by means of their impact on a larger number of resonant acoustic modes (higher orders). In this case, an energy-dissipative damping effect is provided on a larger number (number) of these resonant acoustic modes (on modes of different orders), and on the other hand, the number, dimensions and total flow area of these perforation relief holes are minimized in order to prevent "excessive" additional transmission through them part of the acoustic energy into the environment. This is important, since when additional perforations are made in the pipe wall, acoustic energy is emitted into the environment by two separated transmission paths to the environment - both by the open end cut of the air intake pipe and by all the pipe perforations made in its wall.

The use of an air-blown sound-absorbing material as an element of dissipative energy-dissipative losses as a structural element of an air intake pipe, as provided for in patent RU 2602409, leads both to an increase in the cost of the design of the device as a whole and to instability (change) in the operational characteristics of the device due to an increase in hydraulic (gas-dynamic) resistance caused by dustiness and contamination by solid amorphous bodies of the porous structure of the pipe wall during long-term operation of a technical object. As a consequence, this leads to a corresponding decrease in the sound-absorbing characteristics of the used porous element and, ultimately, to the loss of its direct functional acoustic purpose. Also, as is known, the sound absorption coefficient of thin-walled porous structures of materials in the low-frequency region of the sound spectrum is quite low. This can cause a corresponding amplification of low-frequency sound radiation transported by such a sound-transparent porous tube structure to the environment.

A close analogue to the claimed technical solution is PDVS according to the technical description of the patent RU 2319856, F02M 35/12, 10.12.2006, "Open Joint Stock Company "AVTOVAZ"". It considers a PDVS equipped with an intake system containing an inlet route that supplies the fuel mixture to the PDVS cylinders, consisting of the corresponding components in the form of intake pipes with a device for supplying fuel to the PDVS cylinders, a receiver that is connected by a main pipe to a volumetric expansion chamber an air cleaner containing an air intake pipe limited by an air intake section, in the inlet part of which, coaxially (coaxially), a noise suppression device is placed, made in the form of a quarter-wave acoustic resonator Ra ^I of a tubular cylindrical body shape, with the formation of a corresponding through annular (slot) air gap in the cavity of the pipe , and the overall length of the specified quarter-wave acoustic resonator Rа ^I is half the overall geometric length of the air intake pipe, the throat of the quarter-wave acoustic resonator Ra ^I is located in the middle (median plane in air cavity) of the air intake pipe, and the bottom (bottom part) of the quarter-wave acoustic resonator Ra ^I is located in the zone of the intake cut plane of the pipe. In the lateral part of the housing wall of the quarter-wave acoustic resonator Ra ^I , several through damping perforations are made, evenly located in the middle zone of the dynamic length of the quarter-wave acoustic resonator Ra ^I. Perforated walls of pipes (nozzles) "streamlined" by high-speed gas (air) flows, as you know, are endowed with such a significant operational disadvantage as the ability to generate, at the same time, parasitic acoustic defects, manifested as "narrow-band whistles" and / or broad-band "hissing" sounds like white noise. This may be a significant drawback or limitation for the wide implementation in practice of the noted technical solution.

As a prototype, the declared according to the patent of the Russian Federation RU 2098652, F02M 35/12, 18.07.95, "JOINT STOCK COMPANY "AVTOVAZ"", PDVS, equipped with an intake system containing an appropriate intake route, providing the supply of a fuel-air mixture to the cylinders PDVS, consisting of inlet pipes with a device for supplying fuel to the cylinders, a receiver connected by a main pipe to an air cleaner made in the form of a volumetric expansion chamber, to which an air inlet pipe is connected, limited by an air intake section, in the inlet inner part of which, a noise suppression device is coaxially placed, made in the form of a quarter-wave acoustic resonator Ra ^I of a tubular cylindrical shape, with the formation of a through slotted annular air gap, and the overall geometric length of the quarter-wave acoustic resonator Ra ^I is half the overall geometric length of the air supply pipe, an open throat tea The quarter-wave acoustic resonator Ra ^I is located in the middle (median plane) of the cavity of the air inlet pipe, and its bottom part is equipped with an aerodynamic fairing of the sucked air flow protruding beyond the plane of the intake section of the air inlet pipe of the air cleaner.

Ensuring the effect of noise suppression in the intake system of the PDVS according to the prototype RU 2098652 is achieved by eliminating unwanted "parasitic" high-frequency amplifications of the radiated intake noise at audio frequencies that are multiples of even numbers of the selected tuning frequency f _Ra ^I of the quarter-wave acoustic resonator Ra ^I , with the damping of sound energy at sound frequencies with wavelengths 0.5 λ, 1 λ, 2 λ, 3 λ, 4 λ.

The absence of through damping perforation holes in the housing wall of the Rа ^I quarter-wave acoustic resonator makes it possible to avoid additional generation of parasitic acoustic defects, in contrast to how it occurs according to the technical solution of patent RU 2319856. However, this does not allow implementing the Rа quarter-wave acoustic resonator ^I is a necessary element of dissipative energy dissipative losses to reduce the sensitivity of the acoustic resonator to the frequency resonant tuning caused by changes in operating conditions, environmental parameters, technical condition of the operating object.

The use of individual autonomous quarter-wave acoustic resonators Ra ^I characterized by their tuning frequency f _Ra ^I , as presented, in particular, in the prototype and close analogues (RU 2098652, EN 2319856), involves the use of typical designs of dead-end tubular quarter-wave acoustic resonators Ra ^I using hard, sound-reflecting bottom (bottom part of a quarter-wave acoustic resonator Ra ^I ). However, practical constructive and technological implementations make it difficult to provide the specified component in the form of an absolutely rigid body (as this implies an idealized design of a quarter-wave acoustic resonator Ra ^I ). Ideally, this would avoid a change (shift) in the phases of the sound wave incident and reflected from the surface of this type of hard sound-reflecting bottom. Some dynamic compliance of the flexible sound-reflecting bottom causes the occurrence of an additional phase change between the incident and reflected sound wave on the sound-reflecting surface of this type of partially compliant bottom (which is not allowed by the idealized absolutely rigid, dynamically unyielding and non-absorbing sound energy design of an ideally rigid sound-reflecting bottom). The resulting dynamic deformation of the bottom wall from the impact of incident sound waves, due to its partial flexibility, and the energy absorption accompanying it (spent on the dynamic deformation caused, with the occurrence of corresponding energy losses), as a result, forms the resulting additional phase shift of the propagated (incident and reflected) sound wave . As a result, the idealized physical process of complete antiphase compensation of the amplitudes of the incident and reflected sound waves is not realized, which causes a limited (incomplete) effect of compensatory suppression of acoustic resonance formed in the air cavity of the air intake pipe on its own resonant acoustic mode. Thus, in practice it is difficult to realize the potentially high efficiency of this type of noise damping device, represented by a typical autonomous quarter-wave acoustic resonator Ra ^I .

From the above analytical review of the considered information sources, it also follows that at this point in time, the use of half-wave acoustic resonators Ra ^II for frequency-tuned damping of the noise generated by the PDVS intake system is not known. Accordingly, it is also not known to use a combined hybrid version of a noise dampening device as part of a compact structural integrated combination in one modular design of both quarter-wave Rа ^I and half-wave acoustic resonators Rа ^II (with subsequent final formation of a combined resonator noise damper Rа ^I -Rа ^II ), based on the combined quarter-wave and half-wave antiphase compensation suppression of the formed sound pressure fields formed by the dead-end, closed bottom part and open throat part, as part of the tubular cavity of the indicated acoustic resonators Rа ^I and Rа ^II , providing reliable and effective resulting suppression of resonant acoustic radiation produced by the air intake branch pipe of the air cleaner of the PDVS intake system. The resulting positive effect implies both a greater magnitude of the achieved damping effect and less sensitivity to possible resonant frequency detuning of the functioning of the noise dampening device caused by various variable design, technological and operational factors.

The classical type half-wave acoustic resonator R _r ^II , made in the form of a hollow rectilinear tubular element of given overall dimensions with open neck parts, is a resonant amplifier (and not a silencer) of sound radiation generated at its own resonant frequency f _Rr ^II (and a multiple of its higher harmonics , when half the length of the resonating sound wave 0.5λ _Rr ^II and the subsequent half lengths multiple of it fit into the air cavity of the tubular part of the resonator Rr ^II ). Half-wave acoustic resonators R _r ^II of this type are widely used in musical and architectural acoustics, as well as various technical devices and technologies for using ultrasound in medicine, industrial production of materials, etc. At the same time, a typical representative of the tubular half-wave acoustic resonator R _r ^II , when such sound amplification is already “parasitic” and undesirable, since it causes an increase in the radiated noise of the PDVS intake system, is a typical type of air intake pipe of the PDVS intake air cleaner. Structurally, it is presented in the form of a hollow pipe of certain overall dimensions, open at both ends (on the side of the open end section, it is open to the free space of the environment, and on the reverse side, to the closed cavity of the volumetric expansion chamber of the air cleaner). In rectilinear hollow tubular half-wave acoustic resonators R _r ^II , with open end parts separated by a certain distance (over the overall length of the hollow tubular part) from each other, when they are dynamically excited by a sucked pulsating air flow, corresponding resonant responses arise in the form of acoustic radiation on generated acoustic eigenmodes, with corresponding natural resonant frequencies f _ms and corresponding sound wave lengths λ _ms , which in various noise-generating technical objects can create safety and environmental problems in the field of protecting the environment from its high acoustic pollution. A straight-line hollow tubular element with spaced open end sections, made in the form of a classic half-wave acoustic resonator Rr ^II , which can be represented by a typical air cleaner inlet pipe, is a resonant amplifier for the emission of sound energy during dynamic excitation of an elastic air mass concentrated in its tubular part (dynamically excited by the sucked-in pulsating air flow, brought to its end part from the side of the air cavity of the air cleaner chamber, as well as by the formed sound field from the dynamic excitation of the vibrating solid structure of the oscillating wall of the tubular part, and / or excited by their simultaneous dynamic combinations). At the same time, for certain ranges of sound frequencies, acoustic fields (sound energy propagating in the medium), formed separately (separately) by each open end section, in this type of rectilinear tubular element, located at a certain distance from each other, are weakly interacting with each other separate isolated sound emitters. This follows from the mutual comparison of the spaced apart spatial arrangement (spatial distance from each other) of these end sound emitters, in relation to the quarter and half values of the lengths (1/4λ _R; 1/2λ _R ) of the sound waves emitted by them at their own resonant frequencies f _R . The condition of relative independence (insignificant influence on each other) in these cases will be observed in the mid- and high-frequency region of the sound spectrum, characterized by lower (smaller) values of the sound wave lengths in relation to the overall lengths of the rectilinear half-wave acoustic resonator Rr ^II in the process of radiation of this type tubular rectilinear emitters of resonant sound at a frequency f _Rr (λ _Rr ). Any pronounced mutual resonant directional absorption of sound wave energy in this type of dimensional rectilinear tubular element Rr ^II with spatially spaced (remote from each other) open end parts does not occur due to the lack of an appropriate compensatory antiphase and / or dissipative mechanism of their directional mutual influence and mutual suppression.

The objective of the claimed invention is to ensure high efficiency of noise suppression and operational reliability of the operation of the noise suppression device as part of the PDVS intake system, with the implementation of simplicity and compactness of the design and technological design, reducing material consumption and cost.

According to the claimed technical device of the PDVS intake system, it contains an air cleaner made in the form of a volumetric expansion chamber, in the cavity of which a filter element is placed and to which an inlet pipe with a source of fuel supply to the cylinders of an internal combustion engine and an air intake pipe are connected, including a connecting part, an inlet part , limited by the lead-in section, in the cavity of which a noise suppression device is coaxially mounted, made in the form of a quarter-wave acoustic resonator Ra ^I , containing a tubular, bottom and throat parts, the connecting part of the air intake pipe is connected to the volumetric expansion chamber of the air cavity of the air cleaner housing, while the quarter-wave acoustic resonator Ra ^I is located in the inlet part of the air cavity of the air intake pipe, with the formation of a slotted annular gap that forms a coaxial through flow air channel, and the overall geometric i length Lr ^I of the tubular part of the quarter-wave acoustic resonator Ra ^I is half of the overall geometric length of the air intake pipe L _p , and its open neck part is located in the middle of the overall geometric length L _p of the air intake pipe and is deployed in the direction of the air flow sucked into the volume expansion chamber of the air cavity of the air cleaner housing , and the bottom part of the quarter-wave acoustic resonator Rа ^I is deployed in the direction of the inlet section of the air intake pipe of the air cleaner and is equipped with an aerodynamic fairing of the sucked air flow, while the noise suppression device is represented by a combined resonator muffler Rа ^I -Rа ^II , containing a housing with tubular, bottom and throat parts, forming component combined parts of two acoustic resonators - a quarter-wave acoustic resonator Ra ^I and a half-wave acoustic resonator Ra ^II with their tubular, bottom and throat and parts, while in the air cavity of the quarter-wave acoustic resonator Rа ^I , formed by the tubular, bottom and throat parts, a longitudinal plate divider is mounted, forming the corresponding bypass window, forming communicating tubular branches of the tubular part of the half-wave acoustic resonator Rа ^II with its two throat parts located in the plane of location of the throat part of the quarter-wave acoustic resonator Rа ^I jointly forming the throat part of the combined resonator muffler Rа ^I -Rа ^II .

The invention is illustrated by drawings:

Fig. 1, which schematically shows the design of the PDVS (pos. 1) assembly, equipped with an intake system (pos. 36).

Fig. 2, which schematically shows a typical structural diagram of the air cleaner (item 6) of the intake system (item 36) PDVS (item 1), with an air intake pipe (item 7) attached to the body (item 10) of the air cleaner (item 6) , equipped with a noise suppression device, represented by a combined resonator silencer Rа ^I -Rа ^II (pos. 27);

Fig. 3, which schematically shows the air intake pipe (pos. 7) with the applied sound pressure distribution diagram in the air cavity (pos. 9) of the air intake pipe (pos. 7), which is formed on the lowest (first) natural acoustic mode of resonant sound vibrations, with a frequency f _m1 , when along its dynamic length L _pd , (additionally taking into account the attached end oscillating air masses at the end sections of the air intake pipe in zones Δ ₁ and Δ ₂ ) of the air cavity (pos. 9) of the air intake pipe (pos. 7) fits half the sound wave length ( _½λm1 );

Fig. 4, which shows a cross section of the combined resonator muffler Rа ^I -Rа ^II (pos. 27), illustrating two branched longitudinal plate divider (pos. 28) with a thickness j tubular branches (pos. 33), forming a tubular part (pos. 32) of a half-wave acoustic resonator Ra ^II (pos. 30);

Fig. 5, which shows an illustrative image of the course of the physical process, presented in the form of a diagram of the propagation and absorption of sound energy in the air cavity, which is part of the combined resonator muffler Rа ^I - Rа ^II (pos. 27), half-wave acoustic resonator Rа ^II (pos. 30) on a discrete value of the dominant functional frequency f _m1 of acoustic radiation with a sound wave length λ _m1 of a half-wave acoustic resonator Rа ^II (pos. 30), characterized by its dynamic length L _R ^II , (including the geometric length L _r ^II ) of tubular branches (pos. 33) tubular part (pos. 32) of the half-wave acoustic resonator Ra ^II (pos. 30). The arrows show the direction of propagation of the “incident (incoming)” P _fall and “outgoing” P _out sound waves propagating in the tubular branches (pos. 33) of the waveguide air cavity of the tubular part (pos. 32) of the half-wave acoustic resonator Ra ^II (pos. 30) . The rectangle outlined by the dashed line depicts the spatial zone of the oncoming counter-directional mutual penetrating dissipative anti-phase damping of the vibrational energy of the "incident (incoming)" P _fall and "outgoing" P _out sound waves (sound pressures) propagating towards each other. Circles with signs + and - indicate the zones of antiphase compensations of pressure fields of oppositely directed sound waves, incident (incoming) P _down and outgoing P _out of the tubular branches (pos. 33) of the tubular part (pos. 32) of the half-wave acoustic resonator Rа ^II (pos. 30 ).

Fig. 6, which shows an illustrative diagram of the physical process during the formation of an acoustic quadrupole in the form of mutually compensating acoustic dipoles (opposite-phase interacting closely spaced acoustic monopoles) in the spatial zone of the open throat parts (pos. 31) of the half-wave acoustic resonator Ra ^II (pos. 30). Zone A schematically denotes the emerging acoustic quadrupole, composed of the corresponding pairs of acoustic dipoles (paired antiphase acoustic monopoles).

Fig. 7.1, which shows a longitudinal section of the combined resonator muffler Rа ^I -Rа ^II (pos. 27), made along the installation plane of the longitudinal plate divider (pos. 28), containing through damping perforation holes (pos. 34).

Fig. 7.2, which shows a longitudinal section of the combined resonator muffler Rа ^I -Rа ^II (pos. 27), made in a plane perpendicular to the installation plane of the longitudinal plate divider (pos. 28), containing through damping perforation holes (pos. 34).

Fig. 8, which shows a longitudinal section of the combined resonator silencer Rа ^I -Rа ^II (pos. 27), with an aerodynamic fairing (pos. 26) mounted on the outer side of its bottom part (pos. 24).

Fig. 9, which shows the lead-in section (pos. 18) of the inlet part (pos. 15) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) of the PDVS (pos. 1) from the side of the open atmosphere, with made by a developed flange part (pos. 35) of the lead-in cut (pos. 18) with a radius of r ₁ .

Fig. 10.1, which schematically shows the execution of the end (pos. 42) and tubular (pos. 37) parts of the wall of the combined resonator silencer Rа ^I - Rа ^II (pos. 27), mounted in the air cavity (pos. 9) of the air intake pipe (pos. 7 ) air cleaner (pos. 6) intake system (pos. 36) PDVS (pos. 1).

Fig. 10.2, where the end wall (pos. 42) is shown on an enlarged scale in conjunction with the tubular (pos. 37) part of the body (pos. 41) of the combined resonator silencer Rа ^I -Rа ^II (pos. 27), made in the form of a rounded one side of the edgeless wall.

Fig. 10.3, where the end wall (pos. 42) is shown on an enlarged scale in conjunction with the tubular (pos. 37) part of the body (pos. 41) of the combined resonator silencer Rа ^I -Rа ^II (pos. 27), made with a chamfer.

Fig. 10.4, where the end wall (pos. 42) is shown on an enlarged scale in conjunction with the tubular (pos. 37) part of the body (pos. 41) of the combined resonator silencer Rа ^I -Rа ^II (pos. 27), made in the form of a rounded two sides of the edgeless wall.

Fig. 11, which schematically shows the air intake pipe (pos. 7), with a combined resonator silencer Rа ^I -Rа ^II (pos. 27) mounted coaxially (axially) inside its air cavity, fixed by means of spacer flat ribs (pos. 21);

Fig. 12, which shows a cross section of the air intake pipe (pos. 7), with a combined resonator muffler Rа ^I -Rа ^II (pos. 27) mounted coaxially (axially) inside its air cavity, fixed by means of spacer flat ribs (pos. 21);

Fig. 13, which shows a cross-section of the combined resonator muffler Rа ^I -Rа ^II (pos. 27) with a structural and technological installation option inside its tubular part (pos. 37) of a longitudinal plate divider (pos. 28) with the corresponding groove fastening, in the grooves of the wall tubular part (pos. 37) of the combined resonator muffler Rа ^I - Rа ^II (pos. 27).

Fig. 14, which shows illustrative graphical dependences of sound levels in a 1/3 octave frequency band with a center of 160 Hz, experimentally recorded from the side of the open atmosphere in a spatial zone near (0.06 m) a free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) air cleaner (pos. 6) intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a displacement of 1.6 liters, when it is running at high speed with full load in the range changes in the crankshaft speed 1500 ... 6000 min ^-1 , in options for installing the design of the air cleaner (pos. 6) of the intake system (pos. 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (pos. 7), in version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in the idea of a combined resonator muffler Rа ^I -Rа ^II (pos. 27).

Fig. 15, which shows illustrative graphical dependences of sound levels in a 1/3 octave frequency band with a center of 250 Hz, experimentally recorded from the side of the open atmosphere in a spatial zone near (0.06 m) a free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) air cleaner (pos. 6) intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a displacement of 1.6 liters, when it is running at high speed with full load in the range changes in the crankshaft speed 1500 ... 6000 min ^-1 , in options for installing the design of the air cleaner (pos. 6) of the intake system (pos. 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (pos. 7), in version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in the idea of a combined resonator muffler Rа ^I -Rа ^II (pos. 27).

Fig. 16, which shows illustrative graphical dependences of sound levels in a 1/3 octave frequency band with a center of 315 Hz, experimentally recorded from the side of the open atmosphere in a spatial zone near (0.06 m) a free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) air cleaner (pos. 6) intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a displacement of 1.6 liters, when it is running at high speed with full load in the range changes in the crankshaft speed 1500…6000 min ^-1 , in the options for installing the design of the air cleaner (pos. 6) of the intake system (pos. 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (pos. 7), in version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in the idea of a combined resonator muffler Rа ^I -Rа ^II (pos. 27).

Fig. 17, which shows illustrative graphical dependences of sound levels in a 1/3 octave frequency band with a center of 400 Hz, experimentally recorded from the side of the open atmosphere in a spatial zone near (0.06 m) a free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) air cleaner (pos. 6) intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a displacement of 1.6 liters, when it is running at high speed with full load in the range changes in the crankshaft speed 1500 ... 6000 min ^-1 , in options for installing the design of the air cleaner (pos. 6) of the intake system (pos. 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (pos. 7), in version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in the idea of a combined resonator muffler Rа ^I -Rа ^II (pos. 27).

Fig. 18, which shows illustrative graphic dependences of sound levels in a 1/3 octave frequency band with a center of 630 Hz, experimentally recorded from the side of the open atmosphere in a spatial zone near (0.06 m) a free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) air cleaner (pos. 6) intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a displacement of 1.6 liters, when it is running at high speed with full load in the range changes in the crankshaft speed 1500 ... 6000 min ^-1 , in options for installing the design of the air cleaner (pos. 6) of the intake system (pos. 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (pos. 7), in version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in the idea of a combined resonator muffler Rа ^I -Rа ^II (pos. 27).

Fig. 19, which shows illustrative graphical dependences of sound levels in a 1/3 octave frequency band with a center of 800 Hz, experimentally recorded from the side of the open atmosphere in a spatial zone near (0.06 m) a free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) air cleaner (pos. 6) intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a displacement of 1.6 liters, when it is running at high speed with full load in the range changes in the crankshaft speed 1500 ... 6000 min ^-1 , in options for installing the design of the air cleaner (pos. 6) of the intake system (pos. 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (pos. 7), in version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in the idea of a combined resonator muffler Rа ^I -Rа ^II (pos. 27).

Fig. 20, which shows illustrative graphical dependences of sound levels in a 1/3 octave frequency band with a center of 1250 Hz, experimentally recorded from the side of the open atmosphere in a spatial zone near (0.06 m) a free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) air cleaner (pos. 6) intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a displacement of 1.6 liters, when it is running at high speed with full load in the range changes in the crankshaft speed 1500 ... 6000 min ^-1 , in options for installing the design of the air cleaner (pos. 6) of the intake system (pos. 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (pos. 7), in version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in in the form of a combined resonator muffler Rа ^I -Rа ^II (pos. 27).

Fig. 21, which shows illustrative graphical dependences of 1/3 octave spectra of sound levels, experimentally recorded from the side of the open atmosphere in the spatial zone near (0.06 m) free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a working volume of 1.6 liters, when it is running at full load at a high-speed crankshaft speed of 2060 min ^-1 , in the options for installing the design of the air cleaner (pos. 6) of the intake system (pos. 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (pos. 7), in the version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the claimed technical noise suppression device in the form of a combined resonator silencer Ra ^I -Ra ^II (pos. 27).

Fig. 22, which shows illustrative graphical dependences of 1/3 octave spectra of sound levels, experimentally recorded from the side of the open atmosphere in the spatial zone near (0.06 m) free (open) inlet cut (pos. 18) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a working volume of 1.6 liters, when it is running at full load at high-speed crankshaft speed 2620 min ^-1 with full load, in options for installing the design of the air cleaner (item 6) of the intake system (item 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (item 7), in the version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in the form of a combined resonator g muffler Rа ^I -Rа ^II (pos. 27).

Fig. 23, which shows illustrative graphical dependences of 1/3 octave spectra of sound levels, experimentally recorded from the side of the open atmosphere in the spatial zone near (0.06 m) free (open) inlet cut (pos. 18) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a working volume of 1.6 liters, when it is running at full load at a high-speed crankshaft speed of 2700 min ^-1 with full load, in options for installing the design of the air cleaner (item 6) of the intake system (item 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (item 7), in the version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in the form of a combined resonator g muffler Rа ^I -Rа ^II (pos. 27).

Fig. 24, which shows illustrative graphical dependences of 1/3 octave spectra of sound levels, experimentally recorded from the side of the open atmosphere in the spatial zone near (0.06 m) free (open) inlet cut (pos. 18) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a working volume of 1.6 liters, when it is running at full load at high speed crankshaft speed 3100 min ^-1 with full load, in options for installing the design of the air cleaner (item 6) of the intake system (item 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (item 7), in the version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in the form of a combined resonator g muffler Rа ^I -Rа ^II (pos. 27).

Fig. 25, which shows illustrative graphical dependences of 1/3 octave spectra of sound levels, experimentally recorded from the side of the open atmosphere in the spatial zone near (0.06 m) free (open) inlet cut (pos. 18) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a working volume of 1.6 liters, when it is running at full load at high speed crankshaft speed 3260 min ^-1 with full load, in options for installing the design of the air cleaner (item 6) of the intake system (item 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (item 7), in the version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in the form of a combined resonator g muffler Rа ^I -Rа ^II (pos. 27).

Fig. 26, which shows illustrative graphical dependences of 1/3 octave spectra of sound levels, experimentally recorded from the side of the open atmosphere in the spatial zone near (0.06 m) free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a working volume of 1.6 liters, when it is running at full load at high-speed crankshaft speed 4220 min ^-1 with full load, in options for installing the design of the air cleaner (item 6) of the intake system (item 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (item 7), in the version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in the form of a combined resonator g muffler Rа ^I -Rа ^II (pos. 27).

Fig. 27, which shows illustrative graphical dependences of 1/3 octave spectra of sound levels, experimentally recorded from the side of the open atmosphere in the spatial zone near (0.06 m) free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a working volume of 1.6 liters, when it is running at full load at high speed crankshaft speed 4540 min ^-1 with full load, in options for installing the design of the air cleaner (item 6) of the intake system (item 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (item 7), in the version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in the form of a combined resonator g muffler Rа ^I -Rа ^II (pos. 27).

Fig. 28, which shows illustrative graphical dependences of 1/3 octave spectra of sound levels, experimentally recorded from the side of the open atmosphere in the spatial zone near (0.06 m) free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a working volume of 1.6 liters, when it is running at full load at high speed crankshaft speed 4700 min ^-1 with full load, in options for installing the design of the air cleaner (item 6) of the intake system (item 36) on the PDVS without additional installation of the studied technical noise suppression device in the internal cavity of the air intake pipe (item 7), in the version with a mounted quarter-wave acoustic resonator Ra ^I (pos. 19), and with the installation of the proposed technical noise suppression device in the form of a combined resonator g muffler Rа ^I -Rа ^II (pos. 27).

Fig. 29, which shows illustrative graphical dependences of sound levels in a 1/3 octave frequency band with a center of 6300 Hz, experimentally recorded from the side of the open atmosphere in a spatial zone near (0.06 m) a free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) air cleaner (pos. 6) intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a working volume of 1.6 liters, when it is running at full load in high-speed speed mode crankshaft in the crankshaft speed range of 1500 ... 6000 min ^-1 , with the air cleaner structure (pos. 6) of the intake system (pos. 36) installed on the PDVS (pos. 1) with the claimed technical noise suppression device in the form of a combined resonator muffler Ra ^I -Ra ^II (pos. 27), in two design versions of the longitudinal plate divider (pos. 28) - without through damping holes perforation style (pos. 34) and with two through perforation damping holes (pos. 34) with a diameter of 3 mm.

Fig. 30, which shows illustrative graphical dependences of sound levels in a 1/3 octave frequency band with a center of 8000 Hz, experimentally recorded from the side of the open atmosphere in a spatial zone near (0.06 m) a free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) air cleaner (pos. 6) intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a working volume of 1.6 liters, when it is running at full load in high-speed speed mode crankshaft in the crankshaft speed range of 1500 ... 6000 min ^-1 , with the air cleaner structure (pos. 6) of the intake system (pos. 36) installed on the PDVS (pos. 1) with the claimed technical noise suppression device in the form of a combined resonator muffler Ra ^I -Ra ^II (pos. 27), in two design versions of the longitudinal plate divider (pos. 28) - without through damping holes perforation style (pos. 34) and with two through perforation damping holes (pos. 34) with a diameter of 3 mm.

Fig. 31, which shows illustrative graphical dependences of sound levels in a 1/3 octave frequency band with a center of 10,000 Hz, experimentally recorded from the side of the open atmosphere in a spatial zone near (0.06 m) a free (open) entry cut (pos. 18) of the air intake pipe (pos. 7) air cleaner (pos. 6) intake system (pos. 36) PDVS (pos. 1), represented by a four-cylinder eight-valve internal combustion engine with a working volume of 1.6 liters, when it is running at full load in high-speed speed mode crankshaft in the crankshaft speed range of 1500 ... 6000 min ^-1 , with the air cleaner structure (pos. 6) of the intake system (pos. 36) installed on the PDVS (pos. 1) with the claimed technical noise suppression device in the form of a combined resonator muffler Ra ^I -Ra ^II (pos. 27), in two design versions of the longitudinal plate divider (pos. 28) - without making through damping holes in it perforation line (pos. 34) and with two through perforation damping holes (pos. 34) with a diameter of 3 mm.

Fig. 32, which shows the external speed characteristics with experimentally measured values of the effective torque Me (N⋅m) of the studied PDVS (pos. 1), represented by a four-cylinder eight-valve engine with a working volume of 1.6 l, in installation options for PDVS (pos. 1) of the design air cleaner (item 6) intake system (item 36) with a mounted quarter-wave acoustic resonator Ra ^I (item 19), implementing the technical solution according to patent RU 2098652 (prototype), and with the installation of the proposed technical noise suppression device in the form of a combined resonator muffler Ra ^I -Rа ^II (pos. 27).

Fig. 33, which shows the external speed characteristics with experimentally measured values of the effective power Ne (kW) of the investigated PDVS (pos. 1), represented by a four-cylinder eight-valve engine with a working volume of 1.6 l, in installation options for PDVS (pos. 1) of the air cleaner design (pos. 6) intake systems (pos. 36) with mounted only a quarter-wave acoustic resonator Ra ^I (pos. 19), which implements the technical solution according to patent RU 2098652 (prototype), and with the installation of the proposed technical noise suppression device in the form of a combined resonator muffler Ra ^I - Ra ^II (pos. 27).

The positions in the figures are:

1 - piston internal combustion engine (PDVS);

2 - inlet pipes of the intake system (pos. 36) PDVS (pos. 1);

3 - inlet valves of the device for distributing the air-fuel mixture (pos. 40) over the PDVS cylinders (pos. 1);

4 - intake system receiver (pos. 36) PDVS (pos. 1);

5 - main connecting pipe of the intake system (pos. 36) PDVS (pos. 1);

6 - air cleaner of the intake system (pos. 36) PDVS (pos. 1);

7 - air intake pipe of the air cleaner (pos. 6);

8 - walls of the air intake pipe (pos. 7);

9 - air cavity of the air intake pipe (pos. 7);

10 - air cleaner housing (pos. 6);

11 - air cavity of the volumetric expansion chamber of the air cleaner housing (pos. 10);

12 - air cleaner filter element (pos. 6);

13 - outlet of the air cleaner housing (pos. 10);

14 - inlet of the air cleaner housing (pos. 10);

15 - inlet part of the air intake pipe (pos. 7);

16 - connecting part of the air intake pipe (pos. 7);

17 - open section of the air intake pipe (pos. 7) from the side of the air cavity (pos. 11) of the air cleaner body (pos. 10);

18 - inlet section of the air intake pipe (pos. 7) from the side of the open atmosphere;

19 - quarter-wave acoustic resonator Ra ^I (performing the function of an acoustic energy silencer);

20 - walls of the housing of the combined resonator muffler Rа ^I - Rа ^II (pos. 27);

21 - spacer flat ribs for fastening the body (pos. 41) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27);

22 - tubular part of a quarter-wave acoustic resonator Rа ^I (pos. 19) as part of a combined resonator silencer Rа ^I -Rа ^II (pos. 27);

23 - throat part of a quarter-wave acoustic resonator Rа ^I (pos. 19) as part of a combined resonator muffler Rа ^I -Rа ^II (pos. 27);

24 - bottom part (bottom) of a quarter-wave acoustic resonator Rа ^I (pos. 19), as part of a combined resonator muffler Rа ^I -Rа ^II (pos. 27);

25 - slotted air gap of the through flow air channel of the air cavity (pos. 9) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) of the PDVS (pos. 1);

26 - aerodynamic fairing of the intake air flow of the body (pos. 41) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27);

27 - combined resonator muffler Rа ^I -Rа ^II ;

28 - longitudinal plate divider of the tubular part (pos. 37) of the combined resonator silencer Rа ^I -Rа ^II (pos. 27), (hereinafter referred to as the longitudinal plate divider), forming a hybrid noise damping device, presented in the form of two simultaneously functioning acoustic resonators - Rа ^I and Ra ^II ;

29 - bypass window of the tubular part (pos. 37) of the combined resonator silencer Rа ^I -Rа ^II (pos. 27);

30 - half-wave acoustic resonator Ra ^II (acting as an acoustic energy silencer);

31 - throat parts of the half-wave acoustic resonator Ra ^II (pos. 30);

32 - tubular part of the half-wave acoustic resonator Ra ^II (pos. 30);

33 - tubular branches of the tubular part (pos. 32) of the half-wave acoustic resonator Ra ^II (pos. 30);

34 - through damping perforation holes of the longitudinal plate divider (pos. 28);

35 - flanged anti-turbulent anti-vortex part of the entry section (pos. 18) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) of the PDVS (pos. 1);

36 - intake system PDVS (pos. 1);

37 - tubular part of the combined resonator muffler Rа ^I - Rа ^II (pos. 27);

38 - throat part of the combined resonator silencer Rа ^I -Rа ^II (pos. 27);

39 - bottom part of the combined resonator muffler Rа ^I - Rа ^II (pos. 27);

40 - device for distributing the air-fuel mixture over the PDVS cylinders (pos. 1);

41 - housing of the combined resonator muffler Rа ^I -Rа ^II (pos. 27);

42 - end wall (pos. 20) of the body (pos. 41) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27).

Letter designations used in the text of the description of the application for the invention:

R - acoustic resonator;

Ra - acoustic resonator, functioning as an absorber of sound energy (a - absorption);

Rr ^II - classical half-wave acoustic resonator functioning as a tone discrete source of sound energy amplification (r - radiation);

Ra ^I - a quarter-wave acoustic resonator, functioning as an absorber of sound energy (a - absorption);

Ra ^II - half-wave acoustic resonator, functioning as an absorber of sound energy (a - absorption);

Ra ^III - acoustic Helmholtz resonator (functioning as an absorber of sound energy);

Ra ^I -Ra ^II - combined resonator muffler (pos. 27), containing a quarter-wave acoustic resonator Ra ^I (pos. 19) and a half-wave acoustic resonator Ra ^II (pos. 30);

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

f _R - frequency of natural (resonant) oscillations of the acoustic resonator R, Hz

(with ^-1 );

f _Rr ^II - frequency of natural (resonant) oscillations of the half-wave acoustic resonator R _r ^II , Hz (s ^-1 );

f _Ra ^I - frequency of natural (resonant) vibrations of a quarter-wave acoustic resonator Ra ^I , Hz (s ^-1 );

f _Ra ^II - the frequency of natural (resonant) oscillations of the half-wave acoustic resonator Ra ^II , Hz (s ^-1 );

f _Ra ^III - frequency of natural (resonant) oscillations of the acoustic Helmholtz resonator Ra ^III , Hz (s ^-1 );

λ - sound wave length, m;

λ _R is the length of the sound wave at the frequency of natural (resonant) oscillations of the acoustic resonator R, m;

λ _Rr - the length of the sound wave at the frequency of natural (resonant) oscillations of the half-wave acoustic resonator R _r ^II , m;

λ _Ra ^I - the length of the sound wave at the frequency of natural (resonant) oscillations of a quarter-wave acoustic resonator Ra ^I , m;

λ _Ra ^II - the length of the sound wave at the frequency of natural (resonant) oscillations of the half-wave acoustic resonator Ra ^II , m;

f _ms - natural frequency of oscillations of the air mass concentrated in the air cavity (pos. 9) of the air intake pipe (pos. 7), Hz (s ^-1 );

f _m1 - natural frequency of oscillations of the air mass concentrated in the air cavity (pos. 9) of the air intake pipe (pos. 7) on its first natural acoustic mode, Hz (s ^-1 );

f _m2 - natural frequency of oscillations of the air mass concentrated in the air cavity (pos. 9) of the air intake pipe (pos. 7) on the second natural acoustic mode, Hz (s ^-1 );

f _m3 - natural frequency of oscillations of the air mass concentrated in the air cavity (pos. 9) of the air intake pipe (pos. 7) on the third natural acoustic mode, Hz (s ^-1 );

λ _ms is the length of the sound wave at the natural oscillation frequency f _ms of the air mass concentrated in the air cavity (pos. 9) of the air intake pipe (pos. 7), m;

λ _m1 - sound wave length at natural oscillation frequency f _m1 of the air mass concentrated in the air cavity (pos. 9) of the air intake pipe (pos. 7) on the first natural acoustic mode, m;

λ _m2 - sound wave length at natural oscillation frequency f _m2 of the air mass concentrated in the air cavity (pos. 9) of the air intake pipe (pos. 7) on the second natural acoustic mode, m;

λ _m3 - sound wave length at natural oscillation frequency f _m3 of the air mass concentrated in the air cavity (pos. 9) of the air intake pipe (pos. 7) on the third natural acoustic mode, m;

c - speed of sound (velocity of propagation of sound waves in the medium), m/s;

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

t°С - air temperature, °С;

p - sound pressure, N/m ² , Pa;

P _pad - amplitude values of the incident (incoming) sound waves into the open sections of the neck parts (pos. 31) of the half-wave acoustic resonator Ra ^II (pos. 30);

P _out - the amplitude values of the sound waves emerging from the tubular part (pos. 32) in the areas of open sections of the throat parts (pos. 31) of the half-wave acoustic resonator Ra ^II (pos. 30);

L _p - geometric (overall) length of the air intake pipe (pos. 7), m;

L _Pd - dynamic length of the air intake pipe (pos. 7), taking into account its dynamic elongation (increment) of the connecting end part of the air medium, m;

L _r ^I - geometric (overall) length of the tubular part (pos. 22) of the quarter-wave acoustic resonator Rа ^I (pos. 19) as part of the tubular part (pos. 36) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27), m ;

L _R ^I - dynamic length of the tubular part (pos. 22) of the quarter-wave acoustic resonator Ra ^I (pos. 19), taking into account its dynamic elongation (increment) of the connecting end part of the air medium, m;

L _r ^II - geometric (overall) length of the tubular branches (pos. 33) of the tubular part (pos. 32) of the half-wave acoustic resonator Ra ^II (pos. 30), m;

L _R ^II - dynamic length of the tubular branches (pos. 33) of the tubular part (pos. 32) of the half-wave acoustic resonator Rа ^II (pos. 30), taking into account their dynamic extensions (increments) of the attached end parts of the air medium, m;

d ₁ - the maximum outer diameter of the wall surface of the tubular part (pos. 37) of the circular cross-section of the combined resonator muffler Rа ^I -Rа ^II (pos. 27), m;

d ₂ - the minimum diameter of the circular cross section of the air cavity (pos. 9) of the inlet (pos. 15) of the circular cross section of the air intake pipe (pos. 7), m;

d ₃ - the minimum diameter of the circular cross section of the air cavity (pos. 9) of the connecting part (pos. 16) of the air intake pipe (pos. 7), m;

d _R is the diameter of the circular flow section at the cut of the throat part (pos. 23) of the quarter-wave acoustic resonator Rа ^I (pos. 19), the tubular part (pos. 37) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27), m;

r ₁ - radius of the flanged anti-turbulent anti-vortex part (pos. 35) of the lead-in section (pos. 18) of the air intake pipe (pos. 7), m;

r ₂ - the radius of one-sided rounding of the end part of the tubular wall of the combined resonator muffler Rа ^I -Rа ^II (pos. 27), m;

r ₃ - the radius of the double-sided rounding of the end part of the tubular wall of the combined resonator muffler Rа ^I -Rа ^II (pos. 27), m;

h _R - the height of the bypass window (pos. 29) of the tubular part (pos. 37) of the combined resonator muffler Rа ^I - Rа ^II (pos. 27), formed between the wall surface of the bottom part (pos. 24) of the quarter-wave acoustic resonator Rа ^I (pos. . 19) and the end part of the longitudinal plate divider (pos. 28), m;

S _R - bypass window area (pos. 29), m ² ;

Δ _Pd - dynamic extensions (increments) of the attached oscillating air masses to the air cavity (pos. 9) of the air intake pipe (pos. 7) of the air cleaner (pos. 6), m;

Δ ₁ - dynamic elongation (increment) of the attached oscillating air mass from the side of the connecting part (pos. 16) of the air intake pipe (pos. 7), m;

Δ ₂ - dynamic elongation (increment) of the attached oscillating air mass from the side of the inlet part (pos. 15) of the air intake pipe (pos. 7), m;

Δ ₃ - dynamic elongation (increment) of the oscillating air mass to the air cavity of the quarter-wave acoustic resonator Ra ^I (pos. 19), m;

Δ ₄ - dynamic extensions (increments) of oscillating air masses to the air cavity of the half-wave acoustic resonator Ra ^II (pos. 30), m;

α - chamfer execution angle of the end wall (pos. 20) of the body (pos. 41) of the combined resonator silencer Rа ^I -Rа ^II (pos. 27), degree;

j - wall thickness of the longitudinal plate divider (pos. 28), m;

F _resp - cross-sectional area of the through damping perforation hole (pos. 34), or the total area of several through damping perforation holes made in a longitudinal plate divider (pos. 28), m ² ;

_ΣF resp - total area of through damping holes (pos. 34), m ² ;

F _d is the area of the cross section of the tubular part (pos. 37) of the combined resonator muffler Rа ^I -Rа ^II ;

M _e - effective torque PDVS, Nm;

N _e - effective power of PDVS, kW;

V _h - working volume of PDVS cylinders, l;

n - frequency of rotation of the crankshaft PDVS, min ^-1 ;

α _N - normal sound absorption coefficient;

α _rev - reverberation coefficient of sound absorption;

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

X - specific acoustic conductivity of the surface, m / Pa ^x s;;

ν - vibrational velocity of particles, m/s;

Z - complex resistance, taken into account during the propagation of vibrations of acoustic systems, equal to the ratio of the complex amplitude of sound pressure to the vibrational volumetric velocity, Pa⋅s/m;

ϕ = phase of the sound wave;

π is the number Pi, equal to approximately 3.1415926535;

k - multiplicity factor (whole numbers of the natural series 1, 2, 3,…);

US - sound level, dBA;

SPL - sound pressure level, dB.

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

Acoustic resonators (R) - frequency-tuned sound-damping (noise-damping) technical devices, made in the form of Helmholtz Rа ^III acoustic resonators, quarter-wave Rа ^I and half-wave Rа ^II acoustic resonators R, designed for dissipative absorption (scattering, damping, antiphase compensation) of sound (acoustic) energy distributed in the considered gas-dynamic (aerodynamic) system to which they are connected; The most efficient use of acoustic resonators Ra refers to the absorption of resonant sound vibrations that stand out in the sound emission spectra of a gas-dynamic (aerodynamic) system. Half-wave acoustic resonators Rr ^ɪɪ are frequency-tuned sound-amplifying technical devices used in musical and architectural acoustics, ultrasonic diagnostic equipment, technologies for the industrial production of materials, etc., for directional resonant amplification (rather than absorption) of acoustic radiation energy at given discrete values of acoustic frequencies vibrations (or in given limited frequency bands of the sound or ultrasonic radiation range).

Acoustic dipole - a classic sound emitter, consisting of two close to each other (paired), anti-phase included, non-directional spherical emitters of a pulsating type (acoustic monopoles).

Dissipation of sound energy is an irreversible transformation (scattering) of a part of the energy propagated in the medium of a sound wave into heat.

Diffraction of a sound wave is a physical phenomenon associated with the process of rounding solid obstacles in the propagation medium of sound waves on the path of their propagation with the occurrence of irreversible dissipative energy-dissipating effects at the edges (faces) of these solid elements.

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

Sound absorption is a physical process of attenuation of part of the energy of sound vibrations propagating in a porous or viscoelastic non-porous structure of a material (design of a technical device, substance, medium), with the resulting irreversible dissipative conversion of sound energy into thermal energy dissipated exclusively by the medium of the porous and / or viscoelastic structure, in which the sound wave propagates; characterized by sound absorption coefficient (normal α _N or reverberation α _rev ) or equivalent sound absorption area A _ekv .

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

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

Acoustic monopole - a classical omnidirectional sound emitter like a pulsating sphere.

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

Acoustic conductivity is the reciprocal of acoustic resistance (acoustic impedance). The specific acoustic conductivity of a surface is the ratio of the vibrational velocity of particles (ν) on this surface to the sound pressure (p):

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

Acoustic resistance (acoustic impedance), Z - complex resistance, taken into account during the propagation of oscillations of acoustic systems, equal to the ratio of the complex amplitude of sound pressure to the oscillatory volumetric velocity. The real part of the acoustic impedance is related to the energy losses for sound emission and its dissipation in the acoustic system itself. The imaginary part of the acoustic impedance is due to the reaction of elastic (flexibility) or inertial forces. Unit of measure Pa⋅s/m.

White noise - the generation and propagation of sound energy, characterized by a random distribution of phases, a continuous spectrum and a constant spectral density in a certain frequency range.

The invention can be implemented in PDVS (pos. 1) equipped with an intake system (pos. 36), including an appropriate fuel-air supply line, consisting of intake pipes (pos. 2) with a device for distributing the air-fuel mixture (pos. 40) into the cylinders (in the diagram not shown) PDVS (pos. 1), receiver (pos. 4), main connecting pipe (pos. 5), air cleaner (pos. 6) and air intake pipe (pos. 7).

The housing (pos. 10) of the air cleaner (pos. 6) is made in the form of a three-dimensional expansion chamber, in the cavity (pos. 11) of which a filter element (pos. 12) is installed. The body (pos. 10) of the air cleaner (pos. 6) has an outlet (pos. 13) and an inlet (pos. 14). The main connecting pipe (pos. 5) is connected to the outlet (pos. 13) of the air cleaner housing (pos. 10) (pos. 6), and the air intake pipe (pos. 10) is connected to the inlet (pos. 14) of the air cleaner housing (pos. 10). pos. 7). The connecting part (pos. 16) of the air intake pipe (pos. 7) of the air cleaner (pos. 6), containing an open cut (pos. 17), is located inside the air cavity (pos. 11) of the volumetric expansion chamber of the body (pos. 10) of the air cleaner ( item 6). The inlet part (pos. 15) of the air intake pipe (pos. 7) is limited by an inlet section (pos. 18), which communicates with the open atmosphere.

The air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) PDVS (pos. 1) is represented by a pipe (pipe) of finite dimensions with an overall geometric length L _p , open on both sides (end sections) and is a composite a typical "narrow" waveguide tubular sound-transmitting element, with overall dimensions of the transverse flow section of the tubular part many times smaller than the sound wave length propagating in it (d ₂ <<λ, d ₃ <<λ). One end section of this pipe communicates with the air cavity (pos. 11) of the volumetric expansion chamber of the housing (pos. 10) of the air cleaner (pos. 6) (for PDVS installed, in particular, on cars, the volume of the air cavity (pos. 11) volumetric expansion chamber of the body (pos. 10) of the air cleaner (pos. 6) is 6 ... 15 liters), and the other end section - communicates with the free air space of the engine compartment engine compartment or directly with the open space of the environment - with outboard air intake , sucked in by the intake system (pos. 36) into the cylinders (not shown in the figure) of the PDVS (pos. 1).

In the air cavity (pos. 9) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) PDVS (pos. 1), a hybrid combined noise suppression device PDVS (pos. 1) is mounted coaxially (coaxially), presented in the form of a combined resonator silencer Rа ^I -Rа ^II (pos. 27). The combined resonator silencer Rа ^I -Rа ^II (pos. 27) includes a quarter-wave acoustic resonator Rа ^I (pos. 19), as one of the component element units of the combined resonator silencer Rа ^I -Rа ^II (pos. 27), represented by a hollow a dead-end cylindrical branch pipe containing a tubular (pos. 22), bottom (pos. 24) and throat (pos. 23) parts. Another component element of the combined resonator muffler Rа ^I - Rа ^II (pos. 27) is a half-wave acoustic resonator Rа ^II (pos. 30), which is represented by a hollow cylindrical pipe containing a longitudinal plate divider mounted inside it (pos. 28), which forms the corresponding bypass window (pos. 29), which forms tubular branches (pos. 33) of its tubular part (pos. 32) with two neck parts (pos. 31) located in the plane of location of the throat part (pos. 23) of a quarter-wave acoustic resonator Rа ^I (pos. 19), thus forming together the common neck part (pos. 38) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27). The body of the combined resonator silencer Rа ^I -Rа ^II (pos. 27) is coaxially (coaxially) placed in the inlet part (pos. 15) of the air cavity (pos. 9) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system ( pos. 36) PDVS (pos. 1) and fixed to the walls (pos. 8) of the air intake pipe (pos. 7). Fixing, in particular, can be carried out using spacer flat ribs (pos. 21), with the formation of a corresponding slotted annular air gap (pos. 25), which forms a through flowing air channel formed along the outer surfaces of the wall (pos. 20) of the housing (pos. 41) combined resonator silencer Rа ^I -Rа ^II (pos. 27), between its outer wall surface (pos. 20) and the inner wall surface (pos. 8) of the air intake pipe (pos. 7). The minimum flow area of the formed slotted annular gap (pos. 25) with round cross-sections of the walls of the inlet part (pos. 15) of the air intake pipe (pos. 7) and the body of the combined resonator muffler Rа ^I -Rа ^II (pos. 27) is determined from dependencies:

where d ₁ is the maximum outer diameter of the wall surface (pos. 20) of the circular cross-section of the tubular part (pos. 37) of the combined resonator silencer Rа ^I -Rа ^II (pos. 27), m;

d ₂ - the minimum diameter of the circular cross section of the air cavity (pos. 9) of the inlet (pos. 15) of the circular cross section of the air intake pipe (pos. 7), m;

d ₃ - the minimum diameter of the circular cross-section of the air cavity (pos. 9) of the connecting part (pos. 16) of the air intake pipe (pos. 7), m.

The use of non-circular cross-sections of the indicated elements (for example, elliptical, rectangular or irregular geometric shapes) is not excluded, ensuring appropriate compliance with the conditions for the ratio of the areas of the flow sections of the constituent elements of the device, similar to dependence (1).

Diameters d ₂ and d ₃ with round cylindrical sections of the air intake pipe (pos. 7) can be made either equal or with different overall dimensions. For non-circular cylindrical sections of the air inlet (pos. 7), the same type of statement applies to their cross-sectional areas, which may be either identical or different.

The geometric (overall) length (L _r ^I ) of the tubular part (pos. 36) of the quarter-wave acoustic resonator Rа ^I (pos. 19), which is part of the combined resonator muffler Rа ^I -Rа ^II (pos. 27), is 1/2L _р (where L _p is the geometric length of the air intake pipe, item 7). At the same time, the throat part (pos. 38) of the combined resonator silencer Rа ^I - Rа ^II (pos. 27) is located in the middle of the geometric (overall) length L _{p of the} air intake pipe (pos. 7) and is deployed in the direction of the sucked in fresh air charge from the atmosphere to volumetric expansion chamber of the air cleaner (pos. 6) and further - into the cylinders (not shown in the figure) PDVS (pos. 1). Bottom part (bottom), pos. 24, a quarter-wave acoustic resonator Rа ^I (pos. 19), as an integral part of the design of the combined resonator muffler device Rа ^I -Rа ^II (pos. 27), is deployed in the direction of the entry cut (pos. 18) of the air intake pipe (pos. 7) , is located in the zone of the plane of this cut and can be additionally equipped with an aerodynamic fairing of the sucked air flow (pos. 26).

Combined resonator silencer Rа ^I -Rа ^II (pos. 27) as an assembly is formed by coaxial (coaxial) installation in the tubular part (pos. 37) of the combined resonator silencer Rа ^I -Rа ^II (pos. 27) of the longitudinal plate divider (pos. 28) , made in the form of a flat rigid sound-reflecting polymer or metal plate (it is preferable to use a thin plate with a thickness of j=1…3 mm). At the same time, placed inside the tubular part (pos. 37), the end end surface of the longitudinal plate divider (pos. 28) lags (shifted) from the wall surface of the bottom part (pos. 39) of the combined resonator muffler Rа ^I - Rа ^II (pos. 27) at a given distance h _R (see Fig. 2), which ensures the formation of the corresponding through bypass window (pos. 29) with overall height h _R , overall width d _R and area S _R =h _R d _R , with the formation of communicating between is the corresponding tubular branches (pos. 33) of the tubular part (pos. 32) of the half-wave acoustic resonator Rа ^II (pos. 30) of the same areas of passage cross-sections, correlating with the area of the passage section of the through bypass window (pos. 29) in the form of expression (2 ):

The formed throat parts (pos. 31) of the half-wave acoustic resonator Ra^II (pos. 30), which is an integral element of the combined resonator muffler Ra^I-Ra^II (pos. 27) are located in the plane of the throat part (pos. 23) of the quarter-wave acoustic resonator Ra^I (pos. 19). Selecting the value of the parameter h_R predetermines the unhindered propagation of sound waves along the tubular branches (pos. 33) of the tubular part (pos. 32) of the half-wave acoustic resonator Ra that communicate with each other^II (pos. 30), due to the exclusion in the waveguide air cavity formed in this way of the combined resonator muffler Ra^I-Ra^II (pos. 27) differences in passage sections, which is determined from the conditions of the accepted ratios of the area of the passage section of the bypass window (pos. 29) and the areas of the passage cross sections of tubular branches (pos. 33) as part of the tubular part (pos. 37) of the combined resonator muffler Rа^I-Ra^II (pos. 27) according to expression (2). Generated geometric overall length (L_r ^II) half-wave acoustic resonator Ra^II (pos. 30) less by the value of the double path of the sound wave before and after reflection from the surface of the bottom part (pos. 24), characterized by the parameter 2h_R, the values of the double geometric overall length (L_r ^I) quarter-wave acoustic resonator Ra^I (pos. 19). This provides a corresponding definite shift in the value of its own resonant frequency f_Ra ^II towards higher values, as dependence (26) illustrates. Thus, the frequency band of the effective operation of the combined resonator muffler Ra is expanded.^I-Ra^II (pos. 27) due to close, but not coinciding multiple values of natural resonant frequencies f_Ra ^I and f_Ra ^IIand, thus, the sensitivity to the frequency resonant tuning of the combined resonator muffler Ra is reduced.^I-Ra^II (pos. 27). Installation inside the air cavity of the tubular part (pos. 37) of the combined resonator muffler Ra^I-Ra^II (pos. 27) of a longitudinal plate divider (pos. 28), with the formation of a corresponding through bypass window (pos. 29) in the spatial zone of the bottom part (pos. 39) of the combined resonator muffler Ra^I-Ra^II (pos. 27), the area of which is close to the area of the flow section of each of the tubular branches (pos. 33), provides unhindered propagation and passage in the spatial zone of the bottom part (pos. 39) of sound waves propagating both in the direction of the throat part (pos. 23) quarter-wave acoustic resonator Ra^I (pos. 19), and to the neck parts (pos. 31) of the half-wave acoustic resonator Ra^II (pos. 30). As a result, effective functioning as a quarter-wave acoustic resonator Ra is ensured.^I (pos. 19), and half-wave acoustic resonator Ra^II (pos. 30).

In FIG. 2 schematically shows the air cleaner (pos. 6) of the intake system (pos. 36) of the PDVS (pos. 1), containing the air intake pipe (pos. 7) in the form of a hollow pipe, open at both ends, with a dynamic length L _Рd determined according to the expression:

where L _p is the geometric overall length of the pipe (air intake pipe, item 7),

Δ _Pd - dynamic elongation of the pipe (air intake pipe, item 7), arising due to its connecting from both end zones of the corresponding increments (attached end oscillating air masses) - Δ ₁ and Δ _2.

The additionally attached end oscillating together with the air mass enclosed in the pipe cavity, the masses on both open end sections of the pipe, are taken equal to 0.3 diameters of the circular passage section on the pipe sections (end sections of the air intake pipe, item 7) according to expressions (5) and (6):

A quarter-wave acoustic resonator Ra ^I (pos. 19) is mounted coaxially (coaxially) in the air intake pipe (pos. 7) with a dynamic length L _Рd , open at both ends, presented in the form of a spatially deployed hollow dead-end pipe (tubular part, pos. 22) of a smaller diameter, hermetically muffled by a rigid sound-reflecting part (bottom part, pos. 24) from the side of the located open lead-in section (pos. 18) of the air intake pipe (pos. 7), which directly radiates sound energy into the open space of the environment. The dynamic length L _R ^I of the tubular part (pos. 22) of this type of a quarter-wave acoustic resonator Ra ^I (pos. 19) is determined based on expression (7):

where L _r ^I is the overall geometric length of the internal air cavity of the tubular part (pos. 22) of the housing of the quarter-wave acoustic resonator Ra ^I , pos. 19, (tubular part (pos. 37) of the combined resonator muffler Rа ^I - Rа ^II , pos. 27);

Δ ₃ - dynamic elongation of the oscillating column of air enclosed in the cavity (tubular part, pos. 22) of the quarter-wave acoustic resonator Ra ^I (pos. 19), represented by the corresponding additional elastic oscillating air mass attached to it, taken equal to 0.3 of the diameter d _R circular cross-section of the cut of the tubular part (pos. 22) in the area of the open cut of its neck part (pos. 23), determined according to expression (8):

According to the condition for the development of the most intense half-wave (L _Рd =0.5λ _m1 ) oscillatory acoustic resonance of the air cavity (pos. 9) of the air intake pipe (pos. 7) with its own resonant frequency f _m1 , the dynamic length L _R ^I of the quarter-wave acoustic resonator Ra ^I ( pos. 19) placed in this resonant air cavity must correspond to expression (9):

Thus, for the most effective suppression of acoustic resonance that occurs at the first half-wave (0.5λ_m1) own acoustic mode, with a frequency of natural resonant oscillations f_m1 air cavity (pos. 9) air inlet (pos. 7), geometric overall length L_r ^I tubular part (pos. 22) of the used quarter-wave acoustic resonator Ra^I (pos. 19) must comply with condition (10):

In this case, its dynamic length L _R ^I , already taking into account the increment from the attached dynamic elongation Δ ₃ , according to expression (8), will provide the appropriate location of its geometric overall length L _r ^I , taking into account the specified complementary dynamic elongation Δ ₃ , measured from the open throat cut - directly in the zone of localization of the antinode (maximum amplitude values) of the sound pressure, which is formed on the specified dominant lower half-wave natural acoustic mode, which occurs at its own resonant oscillation frequency f _m1 at half-wave acoustic resonance of an oscillating air column concentrated in the air intake pipe (pos. 7) , taking into account the "lengthening" increments Δ ₁ and Δ ₂ attached to it. Thus, this will ensure a fairly efficient flow of the physical process of functioning of the quarter-wave acoustic resonator Ra ^I (pos. 19). Compensating elongating end displacement of the dynamic length L _Pd of the air intake pipe (pos. 7) into the cavity of the volumetric expansion air chamber (pos. 11) of the body (pos. 10) of the air cleaner (pos. 6) in the area of the open cut (pos. 17) of the air intake pipe ( pos. 7), thus making it possible to provide (take into account) the rational matching placement of the open throat part (pos. 23) of the quarter-wave acoustic resonator Ra ^I (pos. 19) in the area of localization of the antinode of the sound pressure of the lowest natural half-wave acoustic mode (f _m1 , λ _m1 ). Statements of a similar type also apply to the choice parameter of the dynamic length L _R ^II of the half-wave acoustic resonator Ra ^II (pos. 30), due to the coincidence (combination) of the spatial zones of the location of its open throat parts (pos. 31) with the location of the open throat part (pos. 23 ) a quarter-wave acoustic resonator Rа ^I (pos. 19) and the resulting joint formation of an open throat part (pos. 38) of a combined resonator muffler Rа ^I -Rа ^II (pos. 27). In this case, the dynamic length of the half-wave acoustic resonator Ra ^II is determined according to the expression:

or, in final form:

where L _R ^I - dynamic length of a quarter-wave acoustic resonator Ra ^I (pos.19);

L _R ^II - dynamic length of the half-wave acoustic resonator Ra ^II (pos.30);

h _R - bypass window height (pos. 29).

The operation, with a given frequency tuning to the natural (resonant) oscillation frequency f _Ra ^II of half-wave acoustic resonators Rа ^II (pos. 30), is based on the corresponding wave (wavelength λ, wave phase ϕ) interaction with the resulting effect of interference compensation suppression of the energy propagated in elastic (air) medium of the air ducts of the intake system (pos. 36) PDVS (pos. 1) of sound waves (λ _ms , f _ms ) coinciding (close in values) with natural (resonant) frequencies f _Ra ^II of half-wave acoustic resonators Ra ^II (pos. 30). As is known, in general terms, the frequency f and wavelength λ of sound vibrations are related to the velocity c of their propagation in an elastic (air) medium by the following well-known [1] relation (13)

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

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

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

[1] - Helmut V. Fuchs. Schallabsorber und Schalldämpfer, Springer-Verlag Berlin Heidelberg, 2007 - 546 rubles

In turn, the speed of propagation of sound waves c in the air medium is connected by a known functional dependence [1] with the temperature state of this medium tºС, according to expression (14)

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

t°С - air temperature in °С.

Thus, taking into account the known expressions (13) and (14), half the length of the sound wave ½λ _ms emitted by the intake system (pos. 36) and placed in the limited dimensions of the hollow cavity of the tubular part (pos. 32) of the half-wave acoustic resonator Ra ^II ( pos. 30) - ½λ _Ra ^II , including its neck parts (pos. 31) with dynamic elongations Δ ₄ viscously attached to it at the end parts of the overall geometric length of the tubular part (pos. 32) - L _r ^II by 0.3d _R , characterized by the physical parameter of the dynamic length L _R ^II of the half-wave acoustic resonator Ra ^II (pos. 30), which lengthens its geometric length L _r ^II by 0.3d _R , can be represented as the relation (15):

or

Taking into account expression (17), the geometric length L _r ^II of the half-wave acoustic resonator Ra ^II (pos. 30) can be determined from the known geometric and considered physical parameters according to the following expressions (18), (19), (20):

The above dependences (14)-(20), indicating the dependence of the sound speed c(t) and wavelength λ(t) on the ambient temperature, actualize the need to provide a reduced sensitivity of the used acoustic resonators Ra to their frequency detuning of their own resonant frequencies f _Ra from the influence of the temperature of their operational functioning.

Mounting installation with provision of fixed fastening of the longitudinal plate divider (pos. 28) in the tubular part (pos. 37) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27), it is possible to produce a variety of constructive and technological methods, for example, slot fastening in the corresponding groove recesses (protrusions) made in the wall of the tubular part (pos. 37) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27, see Fig. 12), or by using a solid monolithic part (see Fig. 13), or using adhesive adhesive or using additional mechanical fasteners, etc. The longitudinal plate divider (pos. 28) may additionally contain through damping perforation holes (pos. 34, see Figs. 7.1 and 7.2), evenly distributed in the middle of the dynamic length air cavity of a quarter-wave acoustic resonator Ra ^I (pos. 19). The specified through damping holes (pos. 34) in these cases perform the function of an additional damping dissipative element for the irreversible dissipation of resonant vibrational energy into thermal energy, while expanding the frequency band of the effective functioning of the acoustic resonators Ra ^I (pos. 19) and Ra ^II (pos. thirty). It is carried out with a concomitant decrease in the quality factor characteristics of acoustic resonators, while reducing their sensitivity to frequency detuning that occurs due to possible changes in the external operating conditions of the PDVS (pos. 1). A similar type of positive function of expanding the frequency band of the effective functioning of the acoustic resonators Rа ^I (pos. 19) and Rа ^II (pos. 30) due to the accompanying decrease in their quality characteristics and a decrease in their sensitivity to frequency resonant detuning is also performed by the surface of the end part of the longitudinal plate divider (pos.28) combined resonator muffler Rа ^I -Rа ^II (pos. 27) with enveloping diffraction dissipative passage of its sound waves propagating in the area of the bypass window (pos. 29) tubular part (pos. 37) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27), with the corresponding effect of irreversible thermal dissipation of sound energy.

Transferring the location of through damping holes from the surface zone of the outer flow around the walls of the quarter-wave acoustic resonator Ra ^I (pos. 19), (as is used, in particular, in the well-known technical solution according to RU 2319856, where these through damping holes are made directly in the wall of the tubular part (pos. 22) of a quarter-wave acoustic resonator Ra ^I , pos. 19), eliminates the negative noise-generating (whistle, hiss) effect of the process of high-speed air flow around the outer surface of the wall of the tubular part (pos. 37) of the combined resonator muffler Ra ^I - Ra ^II (pos. 27). Thus, this allows, if necessary, to eliminate the process of unwanted defective generation of parasitic noise emissions caused by the indicated through perforation holes (pos. 34), as solid turbulent vortex-forming inhomogeneities directly flown around by high-speed air flow. The total area of through damping holes (pos. 34) _ΣF resp is determined according to expression (21):

where F _d is the cross-sectional area of the tubular part (pos. 37) of the combined resonator silencer Rа ^I -Rа ^II (pos. 27).

The free end sections of the tubular part (pos. 37) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27) may also contain additional aerodynamic (anti-turbulent, anti-vortex) designs, made, for example, in the form of a corresponding rounded edgeless wall (see Fig. 10.2, 10.4), with an additional chamfer (see Fig. 10.3), thereby eliminating sharp-edged disruptions of the sucked-in air flow flowing around its tubular part (pos. 37) in the area of open end sections as a quarter-wave Ra ^I (pos. 19), and half-wave Rа ^II (pos. 30) acoustic resonators used as part of the combined resonator muffler Rа ^I -Rа ^II (pos. 27).

To further improve the aerodynamic properties (reduce hydraulic resistance) of the air intake pipe (pos. 7), its lead-in section (pos. 18) may contain a developed flanged anti-turbulent anti-vortex part (pos. 35), made with a radius r ₁ equal to 2..5 mm , as shown in FIG. nine.

Due to the possible diversity of structural and technological implementations, within the claims of the claims, there may be other insignificant differences in the geometric shapes of the air intake pipe implemented in practice (with a cross section of a circle, ellipse, rectangle, trapezoid, irregular geometric shape) with their respective mounting layout in the composition designs of the combined resonator muffler Rа ^I - Rа ^II (pos. 27).

With all the various implementations of the design options for the half-wave acoustic resonator Ra^II (pos. 30), which performs the function of an effective absorber of resonant sound energy at its own resonant frequency f_Ra ^II, coinciding with the first half-wave acoustic mode of natural resonance oscillations with frequency f_m1formed in the air cavity (pos. 9) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the PDVS (pos. 1), when along the length of the oscillating air mass concentrated in the cavity of its tubular part with the air masses with dimensions Δ₄ (see Fig. 3), half the length of the resonating sound wave 1/2λ_Ra ^II, - open end sections of its tubular part are reduced (spatially located near each other) at a minimum (structurally realizable) distance. This is achieved by the appropriate use of isolated separation of the dead-end cavity of the tubular part of the combined resonator muffler Ra^I- Ra^II (pos. 27) with a flat plate dividing soundproof partition containing a corresponding bypass window (pos. 29) between the air cavities formed divided by a longitudinal plate divider (pos. 28) into two parts, communicating with each other in its middle part (in the zone of formation of a dead-end element bottom part (pos. 39) of the combined resonator silencer Ra^I- Ra^II (pos. 27), in the form of interconnected tubular branches (pos. 33) of the tubular part (pos. 33) of the half-wave acoustic resonator Ra^II (pos. 30), see fig. 2, 3, 5, 6. In this case, the phase φ of the sound wave entering the throat parts (pos. 31) of this type of half-wave acoustic resonator Ra^II (pos. 30), as an integral element of the combined resonator muffler Ra^I- Ra^II (pos. 27), propagating through both of its open end sections, will not suffer noticeable changes at the inlet of its both open neck parts (pos. 31), separated by the thickness of a thin (j=1..3 mm) separating partition, made in the form of a longitudinal plate divider (pos. 28). Said thickness range j of the partition wall, measured in mm, is small relative to the lengths of the resonating sound waves λ, measured in meters. As a result, quarter (1/4λ_R) and half (1/2λ_R) the lengths of the resonant half-wave acoustic mode at its first natural resonant frequency f_R1 will already exceed the indicated thickness range j of the longitudinal plate divider (pos. 28) by orders of magnitude. Thus, an acceptable identity of the phase values (common phase) of the propagated sound wave, simultaneously entering both throat parts of the half-wave acoustic resonator Ra, is ensured.^II (pos. 30). With the variant of the rectilinear design of the half-wave acoustic resonator represented by Rr^II and performing the function of a resonant amplifier of acoustic energy, its open end sections are separated from each other by a distance of the overall geometric length of its tubular part. In contrast, the practical use of the half-wave acoustic resonator Ra^II(pos. 30) for the purpose of resonant absorption of sound energy generated by the intake system (pos. 36) PDVS (pos. 1), implies its placement (axial layout) inside the resonating air tubular cavity of the sound-emitting half-wave acoustic resonator Rr^II, in the form of a hollow with open end sections of overall thickness L_p, which directly represents the air intake pipe itself (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) of the PDVS (pos. 1). Corresponding location of both open end sections (throat parts, pos. 31) of the indicated sound-absorbing technical element, represented by a half-wave acoustic resonator Ra^II (pos. 30) is carried out in the spatial zone of formation of the antinode of a standing resonant sound wave (the maximum value of the amplitude of the sound pressure, see Fig. 3). It corresponds to the first natural half-wave resonant acoustic mode with frequency f_m1, formed in the air cavity of the sound-emitting half-wave acoustic resonator Rr^II, in this case representing a typical air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) of the PDVS (pos. 1). At the same time, into the indicated antinode zone of the standing sound wave on the first (half-wave) natural acoustic mode of the air cavity (pos. 9) of the air intake pipe (pos. 7) with a natural resonant frequency f_m1, simultaneously placed (arranged) and an open cut of a functioning quarter-wave acoustic resonator Ra^I (pos. 19). Its open throat part (pos. 23) is divided by the wall of the longitudinal plate divider (pos. 28), which does not close with the surface of the bottom part (pos. 39) of the combined resonator muffler Ra^I-Ra^II (pos. 27), due to the formation of an appropriate bypass window (pos. 29), designed for unimpeded communication between tubular branches (pos. 33) of the tubular part (pos. 32) of the half-wave acoustic resonator Ra^II (pos. 30). Autonomous joint operation of individual acoustic resonators Ra^I (pos. 19) and Ra^II (pos. 30), as part of the design of the combined resonator muffler Ra^I-Ra^II (pos. 27), allows not only to prevent intense resonant sound radiation of the air intake pipe, but also to increase the reliability of the proposed technical device during its operation, to weaken the necessary requirements for observing (maintaining) constancy in narrow tolerance fields of the stiffness characteristics of the bottom part (pos. 24) quarter-wave acoustic resonator Ra^I(pos. 19), reduce the effect of changes in environmental conditions (temperature, humidity, atmospheric air pressure). The stabilized frequency range of the effective functioning of a technical device is due to the different values of the non-multiple frequency settings of the acoustic resonators Ra^I (pos. 19) and Ra^II (pos. 30) caused by differences in non-multiple geometric ratios (L_r ^I, L_r ^II) and dynamic (L_R ^I, L_R ^II) the lengths of their tubular parts, correlated to the surface of the bottom part (pos. 24) - for a quarter-wave acoustic resonator Ra^I(pos. 19), or to the bypass window (pos. 29) - at the half-wave acoustic resonator Ra^II (pos. 30), as follows from. fig. 2 and FIG. five.

When using the proposed noise damping device, made in the form of a combined resonator muffler Ra^I-Ra^II (pos. 27), its composite acoustic resonators Ra^I (pos. 19) and Ra^II (pos. 30) are simultaneously connected by their open throat parts (pos. 23, 31) to the spatial zone of formation of the antinode of the resonating acoustic mode, in the event of a half-wave acoustic resonance of the air cavity (pos. 9) of the air intake pipe (pos. 7). Thus, this contributes to the elimination of shortcomings in the functioning of individual (isolated) quarter-wave acoustic resonators Ra^I(pos. 19) caused by unstable in production (manufacturing) and operation rigid sound-reflecting characteristics of its constituent element - a sound-reflecting bottom (bottom part, pos. 24). They are compensated by the implemented additional physical process of suppressing sound energy propagating in the tubular part (pos. 37) of the combined resonator muffler Ra^I-Ra^II (pos. 27), with the oppositely directed mutually compensating interaction of sound waves occurring in the area of the bypass window (pos. 29) of the tubular part (pos. 37) of the combined resonator muffler Ra^I-Ra^II(pos. 27), which extend into the specified compensation zone along their individual air cavities, represented by tubular branches (pos. 33) of the tubular part (pos. 32) of the half-wave acoustic resonator Ra^II(pos. 30), which is part of the combined resonator muffler Ra^I-Ra^II(pos. 27). In this case, due to the presence in the composition of the combined resonator muffler Ra^I-Ra^II(pos. 27) half-wave acoustic resonator Ra^II (pos. 30), in which there is no structural element bottom part (pos. 39), non-ideal mechanical (dynamic stiffness) characteristics of the bottom part (pos. 24) of a quarter-wave acoustic resonator Ra^I(pos. 19) as part of the combined resonator muffler Ra^I-Ra^II (pos. 27) no longer plays such a significant role on the idealized physical process of effective compensation of sound fields, which is realized in the cavity of the tubular part (pos. 37) of the combined resonator muffler Ra^I-Ra^II (pos. 27) in the area of the specified bypass window (pos. 29). Thus, the autonomous and joint operation of two acoustic resonators - a quarter-wave Ra^I (pos. 19) and half-wave Ra^II (pos. 30), as components of mutually complementary parts of the combined resonator muffler Ra^I-Ra^II(pos. 27), provides a higher, more reliable and stable effect of damping the energy of the excited resonant (natural) acoustic mode generated in the air cavity (pos. 9) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. . 36) PDVS (pos. 1).

Perforated pipes (pipes), widely used in the design of a noise suppressor, "streamlined" by high-speed gas (air) flows, are endowed with such a significant drawback (defect) as the ability to generate their own "parasitic" sound radiation accompanying them, perceived as defective in terms of auditory perception " narrowband whistles" and/or "hissing" sounds, in the form of broadband "white noise". In this regard, the use of "smooth" (non-perforated) walls of pipes (nozzles), in comparison with perforated ones, if the conditions for the effective functioning of the technical device allow this, is preferable. This is achieved, in particular, according to the proposed technical solution according to the claimed invention, by placing inside the cavity of the tubular part (pos. 37) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27) of a longitudinal plate divider (pos. 28) containing through damping holes perforations (pos. 34), which perform the function of an additional dissipative energy-dissipating element, as part of the technical device of the combined resonator silencer Rа ^I -Rа ^II (pos. 27). Thus, through damping holes of the same type and functional purpose are excluded from the design directly from the wall structure of the tubular part (pos. 37) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27). Thus, the physical process of their high-speed air flow around the specified solid inhomogeneities, represented by through damping holes, is also excluded, as is implemented in the proposed design. This avoids the negative physical process of generating an acoustic defect of “spurious” sound radiation by a technical device, while at the same time implementing an effective damping suppression of its own cavity air resonant excitations of high orders, characterized by high-frequency “acoustic responses” of the excited air cavity (pos. 9) of the air intake pipe ( pos. 7) air cleaner (pos. 6) PDVS (pos. 1). The use of the noted design solution in the form of a perforated longitudinal plate divider (pos. 28) in this case also has a positive effect on the quality factor characteristic of the functioning acoustic resonators Ra ^I (pos. 19) and Ra ^II (pos. 30). Accordingly, this technique has a positive effect on the weakening of the sensitivity to frequency detuning of the acoustic resonators Ra ^I (pos. 19) and Ra ^II (pos. 30) due to a possible change in the external environmental conditions and / or the technical condition of the object in the process of its long-term operation. Thus, the elimination of the functional disadvantage of the noise-attenuating technical device associated with the potential process of occurrence during the period of operation of the frequency detuning of the acoustic resonators Ra ^I (pos. 19) and Ra ^II (pos. 30) is implemented. Appropriate execution of through damping perforation holes (pos. 34) in the design of the longitudinal plate divider (pos. 28) provides additional damping of resonant acoustic vibrations with a concomitant expansion of the frequency band for the effective functioning of acoustic resonators Rа ^I (pos. 19) and Rа ^II (pos. 30). ). Transfer of the element of dissipative damping of vibrational energy from the zone of external surface high-velocity flow around the walls of the tubular parts of acoustic resonators sucked into the PDVS (pos. 1), as is the case in the technical solution according to RU 2319856, and / or from the wall (pos. 8) of the air intake branch pipe (pos. 7) air cleaner (pos. 6) PDVS (pos. 1), as is the case in close analogues (RU 2737014, SU 1037701), inside the air cavity of the combined resonator muffler Rа ^I -Rа ^II (pos. 27) , where these flow processes are absent, makes it possible to eliminate the potential generation of the above "parasitic" noise emissions that occur in the zones of these perforation holes when they are flowed around by high-speed air flows.

The second technique for reducing (weakening) the sensitivity to frequency detuning of acoustic resonators, by appropriately expanding the frequency band of their effective functioning, which is implemented in the technical device of the proposed combined resonator muffler Rа ^I -Rа ^II (pos. 27), is the use of individual non-multiple frequency tuning of each from acoustic resonators Ra ^I (pos. 19) and Ra ^II (pos. 30), i.e. by multiple non-coinciding values (k ≠ 2,3,4) of their own resonant frequencies f _Rа ^I and f _Rа ^II .

Taking into account expression (13), in the most general form, the natural resonant frequencies of sound vibrations f _Ra can be defined as

where c is the speed of sound, m/s;

λ _Ra is the length of the resonant sound wave, m;

k - multiplicity factor (k = 1,2,3…).

Accordingly, for a quarter-wave acoustic resonator Ra ^I (pos. 19), its own resonant frequencies f _Ra ^I can be determined by expression (23):

where λ _Ra ^I is the length of the sound wave at the frequency of natural (resonant) oscillations f _Ra ^I of the quarter-wave acoustic resonator Ra ^I (pos. 19), m.

For a half-wave acoustic resonator Ra ^II (pos. 30), its own resonant frequencies f _Ra ^II can be determined according to expression (24):

where λ _Ra ^II is the length of the sound wave at the frequency of natural (resonant) oscillations f _Ra ^II of the half-wave acoustic resonator Ra ^II (pos. 30), m.

As follows from FIG. 2, 3, and 5, the dynamic lengths of the quarter-wave acoustic resonator L _R ^I and the half-wave acoustic resonator L _R ^II differ by a multiple, i.e. not an integer number of times (they are not multiples of each other in their dimensions). This is due to the presence in the design of the combined resonator muffler Rа ^I -Rа ^II (pos. 27) bypass window height h _R . The lengths of the corresponding sound waves formed in the air cavities of their tubular parts, the lowest resonant acoustic modes, will be:

The natural resonant frequency f _Rа ^II of the half-wave acoustic resonator Rа ^II (pos. 30) in this case will be:

The presence of a small-sized bypass window (pos. 29) in the air cavity of the tubular part (pos. 37) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27) with a height h _R will cause the ratio of the dimensions of the lengths of the propagated sound waves λ _Ra ^I and λ _Ra ^II to be non-multiple lower acoustic eigenmodes of acoustic resonators Rа ^I (pos. 19) and Rа ^II (pos. 30), characterized by corresponding different values of frequencies of natural resonant oscillations f _Rа ^I and f _Rа ^II (h _R << λ _Ra ^I , h _R << λ _Ra ^II ), which leads to fairly close multiple values (but multiple values that do not completely coincide) f _Rа ^I and f _Rа ^II . The achievement of this result ensures the above effect of expanding the frequency band of the effective functioning of the proposed technical device - the combined resonator muffler Rа ^I -Rа ^II (pos. 27) with the corresponding concomitant positive effect of expanding the frequency region of its resonant excitation and reducing its sensitivity to potential frequency detuning.

The advantage of the proposed technical solution, in comparison with the analogues under consideration, is not only its structural compactness, achieved through the combined layout integration of the composite acoustic resonators Rа ^I (pos. 19) and Rа ^II (pos. 30) of the combined resonator muffler Rа ^I -Rа ^II (pos. 27) into the inner cavity (pos. 9) of the air intake pipe (pos. 7), but also the potential exclusion, at the same time, of additional vibrational dynamic excitations of the structural sound of the solid structure of the wall of the tubular part (pos. 30) of the combined resonator muffler Ra ^I -Ra ^II (pos. 27) and the corresponding reduction in the radiation of structure-borne structural noise achieved both directly by the walls (pos. 8) of the air intake pipe (pos. 7) and by the walls of the housing (pos. 41) of the proposed technical device due to its axial placement inside the cavity (pos. 9) air intake pipe (pos. 7). The walls (pos. 8) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) in this case already perform the functions of a passive soundproof casing, in the form of a screen, externally covering the structure of the combined resonator muffler Rа ^I -Rа ^II (pos. 27) . Also, a constructive internal power structural closure of the walls of the tubular part (pos. 37) of the combined resonator muffler Rа ^I - Rа ^II (pos. 27), used by the longitudinal plate divider (pos. 28), makes it possible to further increase the bending rigidity of the thin-walled structure of the device housing as a whole (the longitudinal plate divider, pos. 28, performs, in this case, the function of an internal closing stiffener), which is especially important with a thin-walled design of the body of the combined resonator muffler Rа ^I -Rа ^II (pos. 27) made of polymer material.

The functioning of the claimed technical device of the combined resonator muffler Rа ^I -Rа ^II (pos. 27) is based on the use of the physical foundations of applied acoustics, set forth, in particular, in publications [1] - [3]:

[1] - Helmut V. Fuchs. Schallabsorber und Schalldämpfer, Springer-Verlag Berlin Heidelberg, 2007 - 546 rubles

[2] - Isakovich M.A. General acoustics. Tutorial. Publishing house "Nauka", Main edition of physical and mathematical literature, M., 1973, 495 p.

[3] - Yudin E.Ya., Borisov L.A., Gorenshtein I.V. and others; Noise control at work / Handbook, ed. E.Ya. Yudin. - M.: mechanical engineering, 1985. - 399 p.

The functioning of individual types of acoustic resonators, as technical devices for damping sound energy, is based on the implementation of the physical process of unhindered passage of a sound wave into the throat parts of acoustic resonators (Ra ^I , R a ^II , R a ^III ), when the acoustic (wave) conductivity of their throat parts tends to infinity, and the acoustic (wave) resistance to the passage of the wave into these throat parts tends to zero. The specified physical process is carried out with the frequency of oscillations (natural resonant frequency f _Rа ) incident on the throat parts of acoustic resonators (Rа ^I , Rа ^II , Rа ^III ), sound waves coinciding with the frequency of natural resonant oscillations of acoustic resonators (f _Rа ^I , f _Ra ^II , f _Ra ^III ). In this case, they excite their own acoustic resonances of oscillations of the air column, concentrated, in particular, in the throat part of the acoustic Helmholtz resonator Ra ^III , occurring with a high amplitude of oscillations of the air mass, concentrated in its throat part (as well as attached to it from both sides of the throat part at its end zones of some additional air masses, taking into account the specific geometric parameters of the throat part, temperature, humidity and atmospheric pressure of the air environment). Thus, with natural resonant vibrations of the air mass in the throat part of the acoustic Helmholtz resonator Ra ^III , an accompanying physical process of dissipative thermal energy-dissipating friction of the resonantly (with large amplitude) oscillating air mass against the surface of the wall of the throat part in contact with it occurs, which causes an irreversible process losses (absorption) of oscillatory acoustic energy (amplitude) incident (incoming) P _fall into the throat part of the sound wave at the specified frequency of sound vibrations, coinciding with the natural resonant frequency f _Rа ^III of the acoustic resonator Rа ^III and the irreversible transition of this oscillatory energy into dissipated thermal energy. In turn, the acoustic resonators Ra ^I (pos. 19) and Ra ^II (pos. 30), in contrast to the Helmholtz acoustic resonators Ra ^III , carry out the physical process of absorbing the energy of a sound wave, based on the mutual antiphase compensation of the pressure fields formed by the incident on the throat part (pos. 23) and the reflected sound wave from the bottom part (pos. 24) of the acoustic resonator Ra ^I (pos. 19), or in the process of their in-phase (without significant phase shift) counterdirectional passage, when propagating through the communicating cavity air tubular branches (pos. 33) of the tubular part (pos. 32) sections of the acoustic resonator Rа ^II (pos. 30), the in-phase passage of which is ensured by closely spaced (shifted by a minimum distance equal to the wall thickness j of the longitudinal plate divider, pos. 28, equal to 1 ... 3 mm) to each other by the end sections of the neck parts (pos. 31) of the acoustic resonator Ra ^II (pos. 30, see Fig. 5). As a result of these physical processes, an effective anti-phase mutual amplitude compensation of sound waves propagating in opposite directions is carried out, the oscillation frequency of which coincides with the natural resonant oscillation frequency of the acoustic resonators Ra ^I (pos. 19) and Ra ^II (pos. 30) - f _Ra ^I , f _Rа ^II , when the wave acoustic conductivity of the throat part Rа ^I (pos. 23), as well as the throat parts Rа ^II , pos. 31, tends to infinity, and the wave acoustic resistance to the passage of such a wave into the throat parts of the acoustic resonators Ra ^I (pos. 19) and Ra ^II (pos. 30) tends to zero. This ensures their high efficiency to suppress (absorb) the propagated sound energy at discrete frequencies of sound vibrations that coincide with the natural (resonant) frequencies of these acoustic vibrations of the resonators Ra ^I (pos. 19) and Ra ^II (pos. 30) - f _Ra ^I and f _Ra ^II .

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

An analysis of the known technical solutions in this field of technology has shown that the proposed device has features that are absent in the known technical solutions, and using them in the claimed set of features makes it possible to obtain a new technical result, therefore, the proposed technical solution is new in comparison with the prior art. . The proposed technical solution is industrially applicable, since it can be manufactured industrially, workable, feasible and reproducible, therefore, it meets the condition of patentability "industrial applicability".

The claimed technical device in the form of an intake system (pos. 36) PDVS (pos. 1), equipped with a combined resonator muffler Rа ^I -Rа ^II (pos. 27), works as follows. During the process of combustion of the air-fuel mixture in the combustion chamber of the PDVS (pos. 1), the rotation of the crankshaft, the reciprocating movement of the pistons (not shown in the figure) of the PDVS (pos. 1), in the process of implementing the working intake stroke (air suction into the cylinders, not shown in Fig.), creates periodic pulsating rarefaction (pressure) in the inlet line of its intake system (pos. 36), organizing a periodic, time-varying flow of fresh air into the PDVS cylinders (pos. 1) from the surrounding atmosphere through the lead-in section ( pos. 18) inlet part (pos. 15) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36). The sucked air through the lead-in section (pos. 18) passes through the slotted annular gap (pos. 22) formed by the inner surfaces of the walls (pos. 8) of the air intake pipe (pos. 7) and the outer surfaces of the walls (pos. 20) of the housing (pos. 41) of the combined resonator silencer Rа ^I -Rа ^II (pos. 27), which forms a coaxial (axial) through-flow air channel, enters the air cavity (pos. 9) of the air intake pipe (pos. 7), and then through an open cut ( pos. 17) of the connecting part (pos. 16) of the air intake pipe (pos. 7) enters the air cavity (pos. 11) of the volumetric expansion chamber of the body (pos. 10) of the air cleaner (pos. 6), where a certain damping of the amplitudes of the working gas-dynamic pulsations of the sucked air during its volumetric expansion in the cavity of the volumetric expansion chamber, as well as the corresponding cleaning of the sucked air from the solid and amorphous particles contained in it by the filter elements volume (pos. 12) air cleaner (pos. 6). Further, through the outlet (pos. 13) of the body (pos. 10) of the air cleaner (pos. 6), the sucked air enters the main connecting pipe (pos. 5). At the same time, in the future, a certain additional damping of the amplitudes of the pulsations of the intake air flow rate also occurs during its volumetric expansion in the cavity of the receiver (pos. 4), which at the same time also provides a decoupling weakening (“decoupling”) of the wave relationship between the attached and inlet pipes communicating with its cavity (pos. 2). Further, through the inlet pipes (pos. 2), with a device for distributing the air-fuel mixture (pos. 40) through the PDVS cylinders (pos. 1), when the corresponding inlet valves (pos. 3) are opened, in accordance with the high-speed mode of operation (rotational speed crankshaft) PDVS (pos. 1), the cycle of operation of PDVS (pos. 1) and the number of cylinders of PDVS (pos. 1), the sucked in purified air enters the corresponding cylinders (not shown in Fig.) PDVS (pos. 1).

On the other hand, in the opposite direction of air movement, with respect to the direction of the air charge sucked into the cylinders (not shown in Fig.) PDVS (pos. 1), sound waves are propagated generated in the intake system line (pos. 36) as a result of periodic reciprocating movement of the pistons (not shown in the figure) in the cylinders (not shown in the figure) of the PDVS (pos. 1), due to periodically occurring pulsating pressures (rarefactions and compressions) of the sucked air flow at the moments of opening and closing of the intake valves (pos. . 3), with the formation of the corresponding pulsating fluctuations in flow rate and time-varying gas pressure (mixture of air and fuel), which forms the physical process of generating and propagating elastic sound waves at operating frequencies and specific multiple order harmonics of following the intake working processes, in accordance with a specific high-speed mode of operation (frequency of rotation of the crankshaft, tact of the working process ca and the number of PDVS cylinders, pos. one). Due to the occurrence and propagation of elastic vibrations in the sound frequency range, the generated sound is formed at the moments of opening and closing of the intake valves (pos. 3) of the PDVS gas distribution mechanism (pos. 1), which propagates through the intake pipes (pos. 2) with the air fuel distribution device mixture (pos. 40) into the cavity of the receiver (pos. 4). Further, along the main connecting pipe (pos. 5), in the process of their propagation, sound waves enter through the outlet (pos. 13) into the air cavity (pos. 11) of the volumetric expansion chamber of the housing (pos. 10) of the air cleaner (pos. 6) . Then, through the open cut (pos. 17) of the connecting part (pos. 16), sound waves propagate into the air cavity (pos. 9) of the air intake pipe (pos. 7), pass through the slot annular gap (pos. 25), formed between the internal surfaces of the walls (pos. 8) of the air intake pipe (pos. 7) and the outer surfaces of the walls (pos. 20) of the tubular part (pos. 37) of the combined resonator silencer Rа ^I -Rа ^II (pos. 27), and through the lead-in cut (pos. . 18) of the air intake pipe (pos. 7) are radiated into the open space of the environment. The mass flow rate of the incoming fresh air charge into the air cavity (pos. 11) of the housing (pos. 10) of the air cleaner (pos. 6), while continuously periodically changing over time, in the form of a pronounced dominant pulsating frequency component at the frequency of the working process (repetition frequency) input pulses, as well as multiple frequency harmonics. It is these gas-dynamic oscillations and the accompanying elastic sound waves of “rarefaction-compression” of air propagating in the intake manifold that cause direct emission of sound energy (noise) by the open entry section (pos. 18) of the air intake pipe (pos. 7) into the environment, so they produce dynamic excitation and the accompanying additional resonant sound radiation and resonant amplification of the radiation of individual composite waveguide elements of the intake system (pos. 36) of the PDVS (pos. 1). As a result of this process, at the natural frequencies of oscillations of the composite waveguide elements of the intake system (pos. 36) of the PDVS (pos. 1), this leads to the appearance of additional intense acoustic resonances that stand out in the noise emission spectra of the intake system (pos. 36) of the PDVS (pos. . 1) and PDVS (pos. 1) as a whole (in its total aggregate sound field).

As a result of the abrupt expansion and contraction of the waveguide channel in the zone of the formed air cavity (pos. 11) of the volumetric expansion chamber of the body (pos. 10) of the air cleaner (pos. 6) and the formation of the corresponding air waveguide “sound-reflecting plug” in it, a partial reflection of the propagated sound waves back to the source of excitation and its generation - to the inlet valve (pos. 3). It is carried out both from the zone of the open cut of the outlet (pos. 13) of the air cavity (pos. 11) of the volumetric expansion chamber of the body (pos. 10), and the zone of the open cut (pos. 17) of the air intake pipe (pos. 7) from the side air cavity (pos. 11). With the above process of passage of a sound wave propagating in the volumetric expansion air cavity (pos. 11) of the body (pos. 10) of the air cleaner (pos. 6), its energy is also partially dissipatively dissipated by the porous air-blown structure of the filter element (pos. 12). In the area of the open cut (pos. 17) of the connecting part (pos. 16) of the air intake pipe (pos. 7), the sound wave is partially reflected back to the air cavity (pos. 11) of the volumetric expansion chamber of the body (pos. 10) of the air cleaner (pos. 6 ) due to the abrupt process of narrowing (compression) of the passage section of the considered sound transmitting acoustic waveguide (sound transmitting waveguide channel). In this case, the sound wave is transmitted to the air cavity (pos. 9) of the air intake pipe (pos. 7) and propagates in the direction from the open cut (pos. 17) to the connecting part (pos. 16) of the air intake pipe (pos. 7) and to the inlet section (pos. 18) of the air intake pipe (pos. 7), where the process of partial reflection of the sound wave in the opposite direction also occurs (“sudden expansion” of the acoustic waveguide in the free space zone of the environment). At the same time, the remaining part of the unreflected sound energy in the form of a sound wave is freely radiated by an open lead-in section (pos. 18) into the surrounding airspace. Partial reflection of the sound wave in the area of the open lead-in section (pos. 18) of the air intake pipe (pos. 7) is also caused by an abrupt change in the wave acoustic impedance of the sound-transmitting waveguide in the zones of its “sudden” abrupt changes, as in the above examples considered in the zones of its inlet and outlet from the air cavity (pos. 11) of the volumetric expansion chamber of the body (pos. 10) of the air cleaner (pos. 6). When a sound wave propagates in the air cavity (pos. 9) of the air intake pipe (pos. 7), its own resonant acoustic oscillations are excited in it with a frequency f _ms ( f _m1 , f _m2 , f _m3 ) of the air mass of air enclosed in the cavity of this pipe , open from both end sections, similar to the classical half-wave acoustic resonator R ^II r, widely used in various techniques of intentional amplification of acoustic radiation. In the case of continuous in time dynamic excitation of the specified air mass concentrated in the cavity of such a pipe, by periodic pulsed pulsations of the sucked air in the working process of filling the air charge of the PDVS cylinders (pos. 1), at its natural oscillation frequencies f _ms excited in the pipe, a corresponding resonant amplification occurs sound emitted by open sections of the pipe, carried out both in the direction of the volumetric expansion cavity (pos. 11) of the body (pos. 10) of the air cleaner (pos. 6), and directly in the direction of its opposite end section, and further - into the open space of the environment . The strongest (energy-consuming) resonant sound vibrations are recorded at the same time at their lowest natural oscillation frequencies (at the lowest natural acoustic modes), as a rule, at the first and multiple of it higher overtones - the second and third acoustic natural modes, respectively, with frequencies f _m1 , f _m2 and f _m3 .

The physical processes of propagation of direct and reflected sound waves in the zones of abrupt differences in the sections of sound-transmitting acoustic waveguides (composite interconnected communicating pipeline elements of the intake system (pos. 36) of the PDVS (pos. 1)) and their dynamic interactions contribute to the formation of standing sound waves in them on the corresponding own acoustic modes, characterized by a pronounced uneven formation and propagation of sound pressures in the form of antinodes (maximums) and nodes (minimums), ultimately causing intense acoustic resonances (resonant amplification of the emitted sound energy) by the indicated elements of the composite waveguide, represented by the constituent elements of the intake system (pos. 36) PDVS (pos. 1), requiring the use of additional technical devices for their effective suppression (weakening).

The use of a quarter-wave acoustic resonator Ra ^I (pos. 19) with a natural resonant frequency of sound vibrations f _Ra ^I as one of the constituent key elements of the combined resonator silencer Ra ^I -Rа ^II (pos. 27), tuned to suppress the most energy-intensive lower half-wave self-resonant mode of oscillation (own half-wave acoustic mode) of the air volume enclosed in the cavity (pos. 9) of the air intake pipe (pos. 7), with the frequency of natural sound oscillations f _m1 , when half the length of the resonant (standing) sound wave 0.5λ _m1 , which fits within the dimensions of the dynamic length L _Рd of the air intake pipe (pos. 7), when its throat part (pos. 23) is placed in the zone of maximum values of the amplitudes of the sound pressure localized in the air cavity (pos. 9) of the air intake pipe (pos. 7). The minimum value of the sound pressure of its own acoustic resonance with a frequency f _Ra ^I of a quarter-wave acoustic resonator Ra ^I (pos. 19), which is formed in the air cavity of its tubular part (pos. 22), on its free open cut of the throat part (pos. 23), allows ensure the most efficient passage ("punching") of resonant sound waves into the air cavity of its tubular part (pos. 22). Thus, this physical process is characterized by the occurrence of the phenomenon of a “short acoustic circuit” (caused by the high conductivity of its throat part, pos. 23) of sound vibrations from the air cavity (pos. 9) of the air intake pipe (pos. 7) into the air cavity of the tubular part (pos. . 22) quarter-wave acoustic resonator Ra ^I (pos. 19). The sound wave entering the throat part (pos. 23) of the quarter-wave acoustic resonator Ra ^I (pos. 19), characterized by the parameters f _m1 and λ _m1 , propagates along the dead-end waveguide channel of its tubular part (pos. 22) in the direction of the location of the hard sound-reflecting bottom bottom parts (pos. 24). The sound wave reflected from the rigid sound-reflecting bottom part (pos. 24), propagating in the opposite direction to the throat part (pos. 23) of the quarter-wave acoustic resonator Ra ^I (pos. 19), will be added in antiphase (close to antiphase) with an amplitude sound pressure of the sound wave entering the quarter-wave acoustic resonator Ra ^I (pos. 19). As a result of the resulting interference antiphase addition in the cavity of the tubular part (pos. 22) of the quarter-wave acoustic resonator Ra ^I (pos. 19) of the corresponding amplitudes of sound pressures of the sound waves incident into the throat part (pos. 23) and reflected from the bottom part (pos. 24) , the energy of the resulting sound waves will be effectively reduced (compensated) accordingly.

At the same time, the sound waves generated in the intake system (pos. 36) of the PDVS (pos. 1) propagate through the components of the inlet line of the intake system (pos. 36), including the considered air cavity (pos. 9) of the air intake pipe ( pos. 7), similarly fall into the throat parts (pos. 31) of the tubular branches (pos. 33) of the tubular part (pos. 32) of the half-wave acoustic resonator Ra ^II (pos. 30) with its own resonant oscillation frequency f _Ra ^II , located in close proximity to each other, which causes their in-phase (with identical values of the phases of sound waves propagating through them) parallel hit (entry) and subsequent corresponding waveguide propagation and interaction. When propagating along the specified tubular branches (pos. 33) of the tubular part (pos. 32), their further counter mutually penetrating, mutually compensating energy damping occurs, which is realized in the middle zone of the tubular part (pos. 32) - in the area of the bypass window (pos. 29). Further, it is also realized with counterpropagation of wave impulses of in-phase sound pressure towards each other along both composite half-wave sections of tubular branches (pos. 33) of their half-wave tubular part (pos. 32, see Fig. 5). At the same time, in the zone of their open throat parts (pos. 31), an additional anti-phase energy compensation of the pressure fields of the incident (incoming) Р _pad and exiting from the throat parts Р _output sound waves is realized. As a result, in the indicated spatial compensation zone, a self-compensating near hydrodynamic field of closely spaced pulsating pairs of counter-directional acoustic monopoles is realized, which eventually form acoustic dipoles that weakly emit sound, as is clearly illustrated by the diagram in Fig. 6. In turn, the resulting pairs of acoustic dipoles (horizontal and vertical) in the marked spatial zone of open sections of the composite throat parts (pos. 31) of the half-wave acoustic resonator Ra ^II (pos. 30) form acoustic emitters of an even higher order - acoustic quadrupoles, characterized, ceteris paribus, by a significantly weaker emission of acoustic energy in comparison with radiators of not only monopole, but also dipole types. As a result, mutually suppressing effects of effective energy suppression of sound radiation are realized due to the emerging mutual antiphase compensation generated by the throat parts (pos. 31) of the corresponding sound pressure fields (see Fig. 5, 6).

Simultaneously with the operation of the half-wave acoustic resonator Rа ^II (pos. 30) with its own resonant oscillation frequency f _Ra ^II , as part of the combined resonator muffler Rа ^I - Rа ^II (pos. 27), which suppresses resonant acoustic radiation generated by excited acoustic resonances in the air intake branch pipe (pos. 7) with its own resonant oscillation frequency f _m1 , a similar type of suppression of the half-wave acoustic resonance of the air cavity (pos. 9) of the air intake pipe (pos. 7) of the air cleaner (pos. 6) with its own resonant oscillation frequency f _m1 is also implemented, jointly and autonomously functioning quarter-wave acoustic resonator Ra ^I (pos. 19), at its own resonant oscillation frequency f _Ra ^I . Simultaneous operation of two acoustic resonators - a quarter-wave Rа ^I (pos. 19) and a half-wave Rа ^II (pos. 30) as part of a combined compact design of a combined resonator muffler Rа ^I -Rа ^II (pos. 27), allows to increase both efficiency and reliability its operation, provide a higher damping level of "parasitic" noise radiation of the intake system (pos. 36) PDVS (pos. 1), reduce the sensitivity of the frequency detuning of the noise suppression device, caused both by changes in the external environmental conditions in which the object is operated, and possible technological and operational changes in the rigidity sound-reflecting characteristics of the structure of the bottom part (pos. 24) of the quarter-wave acoustic resonator Rа ^I (pos. 19), which is part of the proposed noise suppression device - the combined resonator muffler Rа ^I -Rа ^II (pos. 27). Also, the noted advantage is facilitated by the structural difference in overall dynamic lengths (L ^I _R and L ^II _R ) of the tubular part (pos. 22) of the quarter-wave acoustic resonator Rа ^I (pos. 19) and the tubular part of the half-wave acoustic resonator Ra ^II , formed by the overall composition of the tubular branches (pos. 33) of the tubular part (pos. 32) of the half-wave acoustic resonator Ra ^II (pos. 30).

High acoustic (noise attenuating) efficiency of the claimed technical solution, mounted as part of the intake system (pos. 36) PDVS (pos. 1), additionally equipped with a noise attenuation device, presented in the form of a combined resonator muffler Rа ^I - Rа ^II (pos. 27), in in comparison with the compared options of the intake system (pos. 36) PDVS (pos. 1) without additional installation of the noise suppression device in the air cavity (pos. 9) of the air intake pipe (pos. 7), as well as with the comparable installation option of the noise suppression device according to the known technical solution according to the prototype (RU 2098652), presented in the form of a functioning single quarter-wave resonator silencer Ra ^I (pos. 19), is confirmed by the results of experimental studies (Fig. 14 ... 33). Comparative experimental studies were carried out in a specialized room of a motor test bench of an anechoic acoustic chamber in a free sound field, on a full-scale sample of a four-cylinder four-stroke PDVS (pos. 1), cylinder displacement V _h = 1.6 l, rated effective power N _e = 66 kW , effective torque M _e = 146 Nm, the results of which are presented in Fig. 14…33. From the analysis of the above research results, it follows that the equipment (equipment) of the intake system (pos. 36) of the PDVS (pos. 1) with a technical noise suppression device, represented by a combined resonator muffler Rа ^I - Rа ^II (pos. 27), allows to reduce the generated intake system ( pos. 36) sound levels (US, dBA), in the entire controlled high-speed mode of operation of the PDVS (pos. 1), recorded in the experimentally established characteristic frequency ranges responsible for the resonant emission of noise by the intake system (pos. 36) PDVS (pos. 1 ):

- in a 1/3 octave band with a center of 250 Hz - by 12 dBA (Fig. 15);

- in a 1/3 octave band with a center of 315 Hz - by 15 ... 30 dBA (Fig. 16);

- in a 1/3 octave band with a center of 400 Hz - by 3 ... 13 dBA (Fig. 17).

As shown in FIGS. 18 ... 20, in 1/3 octave frequency bands with centers of 630, 800, 1250 Hz - the compared ultrasonic frequencies are almost identical. Ultrasound in the marked frequency range does not characterize the acoustic radiation of the intake system (pos. 36) PDVS, pos. 1), recorded at the control measuring point of the test motor stand of the room of the anechoic acoustic chamber, related to the resonant sound radiation of the air intake pipe (pos. 7) of the air cleaner (pos. 6) of the intake system (pos. 36) of the PDVS (pos. 1), which was confirmed their comparison with the recorded levels of the acoustic background (noise interference at the recorded point).

Shown in FIG. 21 ... 28 spectra of sound radiation recorded at the control measuring point, during comparative studies of the acoustic characteristics of the intake system (pos. 36) at high-speed modes of operation of the PDVS (pos. 1) at individual frequencies (revs) of rotation of the crankshaft n, characterized by resonant acoustic radiation intake system (pos. 36) PDVS (pos. 1) equal to 2060 1/min, 2620 1/min, 2700 1/min, 3100 1/min, 3260 1/min, 4220 1/min, 4540 1/min and 4700 1 / min - indicate a significant achieved noise reduction effect of the claimed technical device, equal to 12 dBA (Fig. 21), 15 dBA (Fig. 22), 5 ... 13 dBA (Fig. 23), 21 dBA (Fig. 24), 22 dBA (Fig. 25), 19 dBA (Fig. 26), 27 dBA (Fig. 27), 23 dBA (Fig. 28).

In the shown FIGS. 29 ... 31 shows the results of studies that also indicate the potential achievement of an additional increase in the effect of noise suppression of the intake system (pos. 36) of the PDVS (pos. 1), equipped with a technical noise suppression device in the form of a combined resonator muffler Rа ^I - Rа ^II (pos. 27), with the option of introducing additional through damping perforation holes (pos. 34, made in the form of two holes with a diameter of 3 mm), in a longitudinal plate divider (pos. 28), according to the claimed dependent claim 4 of the claims, equal to 1 ... 5 dBA, registered in the characteristic for typical vortex sounds, broadband high-frequency region of the sound spectrum 6300…10000 Hz.

In FIG. 32 and 33 show the results of power tests of the PDVS (pos. 1) equipped with an intake system (pos. 36) containing a technical noise suppression device, presented in the form of a combined resonator muffler Rа ^I - Rа ^II (pos. 27), with a longitudinal plate divider installed (pos. 28) in its tubular part, pos. 37, (with the implementation of simultaneous operation as part of a combined resonator muffler Rа ^I - Rа ^II (pos. 27) of two acoustic resonators - a quarter-wave Rа ^I (pos. 19) and a half-wave Rа ^II , pos. 30), as well as when dismantling from the cavity the tubular part (pos. 37) of the combined resonator muffler Rа ^I - Rа ^II (pos. 27) of the longitudinal plate divider (pos. 28), with the final implementation of the functioning of only one quarter-wave acoustic resonator Rа ^I (pos. 19), as provided for technical solution according to patent RU 2098652. As follows from the presented results of experimental studies, there were no noticeable negative changes in the parameters of the effective torque (M _e ) and effective rated power (N _e ) during the operation of the test sample of PDVS (pos. 1) according to the external speed characteristic (with full load).

Comparison of the acoustic characteristics of the intake system (pos. 36) equipped with a technical noise suppression device, made in the form of a combined resonator muffler Rа ^I - Rа ^II (pos. 27), with both acoustic resonators functioning simultaneously - a quarter-wave Rа ^I (pos. 19) and a half-wave Ra ^II (pos. 30), in comparison with a functioning only one quarter-wave acoustic resonator Ra ^I (pos. 19), implemented when dismantling a longitudinal plate divider (pos. 28) from the proposed technical noise damping device, indicates higher noise damping qualities of a complete combined noise suppression device equipped with both Rа ^I - Rа ^II (pos. 27) acoustic resonators Rа ^I (pos. 19) and Rа ^II (pos. 30) functioning as part of the combined resonator muffler, with the achievement of higher recorded noise damping effects by an average of 3 dBA (see Fig. 14 ... 31), while at certain speed modes pe zone sound radiation of the intake system (pos. 36) PDVS (pos. 1) registered additional noise reduction effect is 4 dBA.

Claims (17)

1. The intake system of a piston internal combustion engine, containing an air cleaner made in the form of a volumetric expansion chamber, in the cavity of which a filter element is placed and to which an inlet pipe with a source of fuel supply to the cylinders of an internal combustion engine and an air intake pipe are connected, including a connecting part, an inlet part , limited by the lead-in section, in the cavity of which a noise suppression device is coaxially mounted, made in the form of a quarter-wave acoustic resonator Ra ^I , containing a tubular, bottom and throat parts, the connecting part of the air intake pipe is connected to the volumetric expansion chamber of the air cavity of the air cleaner housing, while the quarter-wave acoustic resonator Ra ^I is located in the inlet part of the air cavity of the air intake pipe, with the formation of a slotted annular gap forming a coaxial through flow air channel, and the overall geometric length L _r ^I of the tubular part of the quarter-wave acoustic resonator Ra ^I is half of the overall geometric length of the air intake pipe L _p , and its open throat part is located in the middle of the overall geometric length L _p of the air intake pipe and is deployed in the direction of the air flow body sucked into the volumetric expansion chamber of the air cavity, and the bottom part of the quarter-wave acoustic resonator Rа ^I is deployed in the direction of the inlet section of the air intake pipe of the air cleaner and is equipped with an aerodynamic fairing of the sucked air flow, characterized in that the noise suppression device is represented by a combined resonator muffler Rа ^I -Rа ^II , containing a housing with tubular, bottom and throat parts, forming the composite combined parts of two acoustic resonators - a quarter-wave acoustic resonator Rа ^I and a half-wave acoustic resonator Rа ^II with their tubular, bottom and g eagle parts, while in the air cavity of the quarter-wave acoustic resonator Rа ^I , formed by the tubular, bottom and throat parts, a longitudinal plate divider is mounted, forming the corresponding bypass window, forming communicating tubular branches of the tubular part of the half-wave acoustic resonator Rа ^II with its two throat parts located in the plane of location of the throat part of the quarter-wave acoustic resonator Rа ^I jointly forming the throat part of the combined resonator muffler Rа ^I -Rа ^II . 2. The intake system of a reciprocating internal combustion engine according to claim 1, characterized in that the area of the passage section S _R of the bypass window is 0.9 ... 1.1 of the area of the passage section of the tubular branch of the round tubular part of the half-wave acoustic resonator Ra ^II : S _R \u003d h _R d _R \u003d (0.9 ... 1.1) πd _R ² / 8 where h _R is the height of the bypass window; d _R is the overall width of the bypass window, equal to the diameter of the tubular part of the half-wave acoustic resonator Ra ^II . 3. The intake system of a reciprocating internal combustion engine according to claim 1, characterized in that the minimum area of the passage axial circular section of the slotted annular gap is determined from the dependence:

, where d ₁ is the maximum outer radius of the wall surface of the tubular part of the combined resonator muffler Rа ^I -Rа ^II , m; d ₂ - the minimum radius of the circular flow section of the air cavity of the inlet part of the air intake pipe, m; d ₃ - the minimum radius of the circular passage section of the air cavity of the connecting part of the air intake pipe, m. 4. The intake system of a piston internal combustion engine according to claim 1, characterized in that through damping perforation holes are made in the wall of the longitudinal plate divider, located in the middle of the dynamic length L _R ^I of the quarter-wave acoustic resonator Ra ^I , and the total area of the flow sections _ΣF resp is determined according to the expression: _ΣF resp =0.05...0.06 F _d , where F _d is the area of the cross-flow section of the tubular part of the combined resonator muffler Ra ^I -Ra ^II . 5. The intake system of a reciprocating internal combustion engine according to claim 1, characterized in that the dynamic length L _R ^II of the half-wave acoustic resonator Ra ^II is determined according to the expression: L _R ^II = 2(L ^I _R – h _R ), where L _R ^I is the dynamic length of a quarter-wave acoustic resonator Ra ^I ; h _R is the height of the bypass window.

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