RU2647781C2 - Crankshaft pulley for driving auxiliary units of piston machine - Google Patents

Abstract

FIELD: machine engineering.

SUBSTANCE: crankshaft pulley contains a hub portion, a rim, a disc portion, and a device for reducing its sound radiation. The device for reducing sound radiation is represented in the form of ports and perforation holes made in the pulley disc portion. On the both sides of its surface, the pulley disc portion is lined with a porous air-blown sound-absorbing material. Said material is coated with a protective sound-transparent film or foil or non-woven fabric layers with layers of materials.

EFFECT: noise emission suppression.

14 cl, 13 dwg

Description

The invention relates to mechanical engineering, in particular to transport and power engineering, mainly to reciprocating machines (PM) such as reciprocating internal combustion engines (MPE), reciprocating pumping units (PNU) and reciprocating compressor units (PKU) containing a crank mechanism (KShM ) equipped with a crankshaft, on the end section of which (the toe of the crankshaft) a pulley is mounted, designed for mechanical belt drive of various auxiliary units and systems contained in Stand PM (PDVS, PNU, PKU) type of generator, air conditioner, water, oil or fuel pumps.

Due to the rigid mounting of the hub part of the crankshaft pulley for driving auxiliary PDVS units (PKU, PNU) on the end vibroactive zone (on the toe) of the crankshaft (crankshaft), which directly perceives intense alternating loads arising in the crankshaft from gas forces, unbalanced forces and moments inertia, during the workflow in the PM (MPE, PKU, PNU), as a result of which it performs interconnected bending, torsional and axial vibrations and, accordingly, directly reports (p makes it possible) to a crankshaft pulley rigidly mounted on it (at its end section), designed to drive auxiliary units, the latter (crankshaft pulley), in turn, also performs the corresponding spatial bending, torsional and axial vibrations with vibrations of its components, transforming , ultimately, into sound (noise) radiation, characterized by structural noise produced by the PM crankshaft pulley into the surrounding space, in fact, the oscillating disk part of the PM crankshaft pulley (MPE, PC , PND) represented oscillating diaphragm plate radiator of sound energy type cone speaker, while its oscillating the hub portion fixedly mounted on an oscillating crank sock HDR, represented exciting electromagnetic system (voice coil). The most intense sound (noise) radiation of the PM crankshaft pulley (PDVS, PKU, PNU) is recorded both in the modes of resonant (bending, torsional, axial) vibrations of the crankshaft, and directly on the natural resonance vibrations of its disk part. Noise radiation generated in the spatial air zone near the crankshaft pulley can be significantly amplified by vibroacoustic excitation and sound radiation of flexurally vibrating walls of PM housing parts (PDVS, PKU, PNU) - the front cover of the cylinder block and the end wall of the oil pan - connected to the bearing support of the crankshaft. Thus, the spatial air zone of the localized location of the PM crankshaft pulley (MPE, PKU, PNU) is characterized by a high concentration (high intensity) of sound energy radiation (spurious noise radiation) and, therefore, needs to be effectively suppressed by this spurious noise radiation.

On the other hand, the rotating PM crankshaft pulley also performs the accompanying aerodynamic noise excitation and radiation produced by it into the environment (aerodynamically excites the adjacent air column). In particular, this applies to devices when the spoke design of the PM crankshaft pulley with large windows is formed, or the PM crankshaft pulley design with through small holes made in its disk part, as well as other possible characteristic structural inhomogeneities contained in its disk part or rim (for example, radial stiffeners located in the disk part of the pulley, sharp edges, balancing elements), capable of rotating the pulley during their rapid angular movement in an elastic air environment (dynamic mixing of the air environment) generate the corresponding aerodynamic noise radiation of the blade (scapular) type, which manifests itself mainly at discrete frequencies (and at harmonics multiple to them) with respect to the angular velocity (frequency) of rotation of the pulley equal and / or multiple, for example, the number of holes, the number of spokes (number of windows). Also, a broadband medium- and high-frequency noise radiation of a turbulent vortex-forming nature is also generated. Thus, there is the problem of eliminating (maximally suppressing) this type of spurious noise emissions that pollute the environment and worsen the consumer properties (acoustic comfort) of the operated technical facility, as well as making it difficult to comply with regulatory standards that regulate the maximum permissible noise emissions of technical objects, for example , motor vehicles (ATS), or stationary PM (PDVS, PKU, PNU).

A pulley is known, intended primarily for MPE, according to the USSR author's certificate No. 819461 (publication date 04/07/1981), in which to reduce the levels of structural noise it produces, its design is made of spoke with large windows in the disk part, which provides a dynamic process of quick compensation alignment of the pressure fields formed on both (front and back) sides of its disk part, due to the implementation of large-sized windows and the corresponding small-sized components leblyuschihsya plate members pulley (spoke and rim). The implementation of the dynamic process of rapid compensation alignment of pressure fields on both sides of this type of small-sized lamellar pulley elements (spokes, rims), in essence, eliminates the disk part of the pulley as a significant dominant source of structural noise radiation of the diaphragm pulley, due to the implementation of large-sized holes in it ( windows), with the formation of the corresponding structural elements - small dimensions of the spokes, which also reduces the surface of the pulley radiating structural noise surface . In this way, weaker dynamic excitation of pressure elastic waves by the oscillating disk part of the pulley (its spoke structure), propagating in the adjacent air in the form of sound waves and perceived by humans (recorded by instrumental means of measuring sound pressure levels) in the form of structural noise radiation of one or another intensity, is ensured. (those or other values of sound levels estimated in dBA). However, at the same time, the known spoke design of the crankshaft pulley is obviously characterized by an increased level of aerodynamic noise generated by the rotating spokes and other distinguished structural heterogeneities of the pulley design.

There is also known a technical solution for the USSR author's certificate No. 1237846 (publication 06/15/1986) for further improvement of the above invention according to the USSR author's certificate No. 819461, presented in the form of designs of spokes for the pulley of the crankshaft of variable speed engine with variable bending moments in proportion to their distances from the hub to the pulley rim, which contributes to the improvement of acoustic (additional reduction of structural noise) properties, while ensuring acceptable strength characteristics and shenie metal design. However, this known pulley design is also characterized by unsatisfactory aerodynamic characteristics of noise generation.

A known design of a spoke pulley according to USSR author's certificate No. 934096 (publication 07.06.1982), in which perforation holes are made in the construction of its rim to further reduce the radiation of structural noise produced by the oscillating rim of the pulley due to the implementation of physical processes of corresponding effective compensations of the dynamic pressure fields, formed by the vibrating rim of the pulley (its opposite surfaces), which entails an additional reduction in the structural noise emitted by it. At the same time, the rotating spoke design of the pulley continues to be an undesirable source (generator) of the aerodynamic component of the noise emission of the pulley.

Technical solutions are also known for reducing the aerodynamic component of the noise generated by individual structural components of the pulley. So, in particular, according to the USSR author’s certificate No. 1430649 (publication 10/15/1988), the design of the “assembly pulley” is known, which is made in the form of a combined technical device integrating the design of the drive pulley and fan impeller, which additionally generates pronounced spurious aerodynamic noise, which needs its effective suppression. This technical problem is solved by appropriate formation of an additional resonant-type noise-suppressing element in the pulley design, in the form of an Helmholtz acoustic resonator, tuned to suppress the discrete frequency component dominant in the noise emission spectrum in the form of the impeller blade frequency. However, at unsteady (variable) high-speed modes of operation of the PM, due to a change in the frequency (angular velocity) of rotation of the assembly pulley, the blade frequency of the aerodynamic noise generated by the fan impeller also changes. To adjust the Helmholtz acoustic resonator used to the resulting change in the blade frequency of the impeller, movable shutters are used, to one degree or another overlapping the passage sections of the necks of the Helmholtz acoustic resonator in accordance with the speed mode of rotation of the assembled pulley. The technical solution noted is characterized by a narrow-band damping frequency range characterizing a typical classical Helmholtz acoustic resonator design, as well as by additional parasitic high-frequency aerodynamic noise generated by vortex-forming structural elementary pulley inhomogeneities (movable shutters, necks). Also, the specified design of the assembly pulley is characterized by the complexity and efficiency of the frequency tuning of such an adaptive (tracking) device for damping aerodynamic noise, the complexity of its manufacture and high cost.

According to USSR author's certificate No. 1527442 (publication 07.12.1989), the construction of a combined pulley containing a structural element for suppressing aerodynamic noise generated by a fan impeller, which is part of a combined pulley made in the form of a volumetric resonant sound-absorbing element - Helmholtz acoustic resonator, is known. The Helmholtz acoustic resonator, according to the description of the USSR author's certificate No. 1527442, is mainly configured to suppress sound radiation (aerodynamic noise) of a pronounced discrete frequency component, which appears at the blade frequency of the fan impeller, at a specific speed mode (at a given constant speed of the assembly pulley). When changing the speed of the assembly pulley, as, for example, takes place in the PM (MPE) mounted on the PBX, within a wide range of the speed mode of the MPE (from the minimum values of its idle speed to the maximum power RPM), due to a corresponding change in the frequency the rotation of the crankshaft of the internal combustion engine and, accordingly, the frequency of rotation of the pulley of the crankshaft mounted on its toe, the use of such a narrow-frequency tuned to muffle aerodynamic noise design of the combined pulley becomes, in fact, without useful. To provide some expansion of the frequency range of aerodynamic noise noise suppression, in such a construction of a combined pulley, the neck cavity of Helmholtz acoustic resonators (passage sections of the perforation hole cavities made in the wall of the resonant cavity of the Helmholtz acoustic resonator) can be additionally filled with a porous sound-absorbing substance. However, such a design of a combined pulley containing a small-sized sound-absorbing device of a resonator type is not sufficiently effective, including due to the free intense radiation of sound energy produced by the external peripheral edge zone of the fan impeller remote from the neck of the Helmholtz acoustic resonator. The analyzed design of the combined pulley also does not contain any noise suppressing elements to reduce the structural noise generated by the oscillating walls of the disk and impeller zone of the combined pulley, which is its significant drawback.

Technical solutions set forth in the above patents for inventions SU 819461, SU 934096, SU 1430649, the implementation of the device for reducing the acoustic radiation of the PM crankshaft pulley are provided mainly in the corresponding design of its disk part. It, in particular, contains large-sized windows (hereinafter referred to as windows) formed between appropriately made spokes and a pulley rim. The term oversized windows of the pulley disk part means a structure in which their projection of the total surface area onto a plane perpendicular to the axis of rotation of the pulley (total area of their bore) exceeds at least 50% of the surface area of the construction of the solid disk part of the pulley (made without windows and knitting needles ) In these cases, the effect of reducing the structural noise radiation of the pulley disk part due to structural vibrations of the wall of the pulley disk part is caused both by a decrease in the surface area of the structural noise emitter (surface area of the pulley disk part) with the windows made and by the implementation of the physical process of faster compensation equalization of pressure fields formed by the oscillating wall of the disk part of the pulley (knitting needles, rim) through these windows (by reducing the dipole moment of the sound emitter dipole type) in comparison with the design variant with a solid disk part of the pulley. In the known technical solutions set forth in the patents for inventions SU 1430649 and SU 1527442, the implementation of the technical device for reducing the sound emission of the pulley is based on the use of integrated (integrated into the pulley design) frequency-tuned Helmholtz acoustic resonators containing chamber and throat parts as part of the combined drive structure pulley and fan impeller.

The above-mentioned well-known technical solutions also use small-sized holes (hereinafter referred to as perforation holes) made in the construction of pulleys (in the rim according to the patent SU 934096, in the wall of the cavity chamber of the assembled pulleys according to the patents SU 1430649 and SU 1527442). In these cases, perforation holes are also components of technical devices for reducing the sound emission of pulleys. Moreover, their overall dimensions are comparable, as a rule, with the wall thicknesses of the disk part of the pulley and are mainly in the range of values d _p = (1 ... 3) t _d , where d _p is the diameter of the perforation hole, t _d is the wall thickness of the disk part of the pulley.

Known combined design of the PM crankshaft pulley, presented in the patent for invention US 4543924 (publication 01.10.1985), comprising a dynamic damper of torsional vibrations of the crankshaft (damper) and a soundproof cover. The used structure of the soundproofing cover made of neoprene rubber and mounted on the disk part of the pulley to attenuate its sound radiation does not at the same time provide sound absorption effects of sound energy generated by the back side of the wall of the disk part of the pulley, and also does not reduce the sound emissions produced close to crankshaft pulley, intensively vibrating walls of the front cover and the oil pan PM.

Also known is the design of the PM crankshaft pulley (MPE), made as a combined design of a driven multi-ribbed pulley integrated with a damper (dynamic damper) of torsional vibrations of the crankshaft, according to the application for invention DE 102010015249 A1 (publication October 20, 2011), which is adopted as a prototype of the invention . According to the technical description and the graphic part of the prototype presented, the reduction of sound radiation (structural noise of the flexurally oscillating thin-walled plate structure of the disk part) of the crankshaft pulley of the engine crankshaft is carried out by the additional applied elastically mounted soundproofing sound-reflecting plate-like screen elements. It is obvious that dynamically excited elastically fixed soundproofing soundproof reflective plate screen elements can be sound direct secondary structural emitters of sound energy. In particular, the negative sound emitting effects of this type of pulley design will occur at resonant frequencies of oscillations of the annular seismic mass of the elastically attached rim, used as a dynamic damper for torsional vibrations of the PM crankshaft (PDVS), directly transmitted to plate sound-insulating sound-reflecting screen elements, and will also be implemented on their own resonant vibrations of the plate soundproofing sound-reflecting screen elements themselves, dstavlennyh as tverdoelementnyh uprugozakreplennyh mass and flexural vibrating diaphragms. In addition to these acoustic disadvantages of the pulley design made according to the prototype, the PM crankshaft pulley presented is also characterized by the complexity and high cost of manufacture.

Used in the construction of the prototype, as well as in the analogue, which is described in the patent for invention US 4543924, the device for reducing sound radiation contains elements for attenuating the radiation of sound produced directly by the pulley in the form of mounted screen elements such as soundproof covers (plates) of its disk part, as well as indirect (intermediate) elements of attenuation of sound radiation produced by a pulley, in the form of built-in dynamic dampers of torsional vibrations integrated into a combined the design of the crankshaft pulley, represented by the annular mass of the rim in the form of an oscillating seismic mass, fixed by means of an elastic viscoelastic rubber element to the peripheral zone of the disk part of the pulley. The type of dynamic crankshaft torsional vibration dampers used in this way provide a frequency-tuned suppression of resonant torsional torsional vibrations of the crankshaft arising at only one natural (resonant) crankshaft torsional vibration frequency (to which the dynamic torsional vibration damper is tuned). At the same time, the amplitude-frequency characteristic of the PM crankshaft is characterized by several natural resonant frequencies of torsional vibrations (such as a distributed elastic-mass vibrational system), the suppression of which this type of device is not configured. As a result, the resonant vibrational excitations at these resonant frequencies of the torsional vibrations of the crankshaft are transmitted directly to the crankshaft pulley and, ultimately, are re-emitted by its disk part in the form of intense structural noise of the pulley. For a similar type of reason, the indicated types of dynamic damper for torsional vibrations of the PM crankshaft are not effective for concomitant suppression of resonant bending and axial vibrations of the PM crankshaft, due to their solid transformation to the hub part of the PM crankshaft pulley and subsequent radiation of the corresponding structural noise to its disk portion.

Thus, the PM crankshaft pulley designs considered as well-known analogues and prototypes that would integrate integrated technical solutions aimed at the simultaneous effective suppression of both the structural and aerodynamic components of the noise radiation produced by the PM crankshaft pulley, as well as the associated attenuation noise radiation in the spatial zone of the layout of the crankshaft pulley at the PM cannot be considered as an effective technical solution. It is to solve this complex problem that the claimed technical solution is directed. The inventive design of the PM crankshaft pulley not only excludes the generation of its own structural and aerodynamic noise components of the radiation produced by the pulley, but also reduces the noise radiation produced by other noise-active (noise generating) zones and PM systems located close to the pulley. As such zones should be considered, for example, the total noise radiation distributed in the form of a diffuse sound field in a closed (partially closed) space of the ATS engine compartment. So, in particular, the sound radiation carried out by the end surfaces of flexurally oscillating noise generating walls of the engine block and the oil pan of the engine located in close proximity to the surface of the sound-absorbing structure of the rotating disk part of the crankshaft pulley of the engine will be effectively absorbed by the indicated sound-absorbing pulley structure due to its location ( premises) in a zone of high concentration of sound energy, localized in the immediate vicinity of sound radiation structures of the indicated noise-active walls of the body parts of the internal combustion engine (in the zone of the near hydrodynamic field of flexurally oscillating walls).

The essence of the invention lies in the fact that in the known design of the PM crankshaft pulley containing the hub part, the rim, the disk part and the device for reducing its sound radiation - the device for reducing sound radiation is presented in the form of windows and perforation holes of the disk part overlapping (filled) with porous air-absorbing sound-absorbing substance. pulleys made in the form of their double-sided lining with a porous air-borne sound-absorbing substance lined with an external protective sound-transparent film or a foil or non-woven fabric layer of material.

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

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

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

The invention is illustrated in the drawings.

In FIG. 1 shows a longitudinal section of the MPE, with an auxiliary unit drive pulley mounted on the crankshaft nose.

On Fig, 2 shows the automatic telephone exchange, in the engine compartment of which there is an MPE installed, containing a pulley of the crankshaft of the drive of auxiliary units.

In FIG. 3 is a front view of a pulley of a crankshaft pulley of a drive of auxiliary units PM, lined with a porous air-produced sound-absorbing substance, containing windows in the disk part and perforation holes in the spokes and disk part.

In FIG. 4 shows a cross-section of the crankshaft pulley of the drive of auxiliary PM units lined on both sides of the disk part with a porous air-blown sound-absorbing substance filling the cavity of the windows in the disk part and the perforation holes in the spokes and the disk part.

In FIG. 5 shows a front view of a pulley of a crankshaft pulley of a drive of auxiliary units PM, lined with a porous air-produced sound-absorbing substance, containing windows and perforated holes in its disk part.

In FIG. Figure 6 shows a cross-section of the crankshaft pulley of the drive of auxiliary PM units lined on both sides of the disk part by a porous air-generated sound-absorbing substance filling the cavities of windows and perforation holes made in its disk part.

In FIG. 7 shows a cross-section of a crankshaft pulley equipped with a damper (dynamic damper) of torsional vibrations of the crankshaft drive of auxiliary PM units, in the disk part of which there are windows and perforation holes filled with a porous air-absorbing sound-absorbing substance, with two-sided lining of the disk part of the crankshaft pulley with a porous air-absorbing.

In FIG. Figure 8 shows a diagram of the incidence of sound waves on the surface of a porous air-blown sound-absorbing substance lining the disk part of the crankshaft pulley of the drive of auxiliary PM units; solid arrows show the incident and reflected sound waves, dashed arrows indicate the paths of diffraction enveloping by sound waves of the outer peripheral zones of the rim of the crankshaft pulley of the drive of auxiliary PM units.

In FIG. 9 is a diagram of the incidence and reflection of sound waves on the surface of a porous air-blown sound-absorbing substance from the sound-reflecting panels of the ATS and the walls of the airborne exhaust system, filling the cavities of the windows and perforations made in the disk part of the pulley and lining the disk part of the PM crankshaft pulley on both sides, and the propagation of sound waves in a porous air-blown sound-absorbing structure and during their diffractive dissipative envelope of the outer peripheral zones of the rim and the outer peripheral zones of windows and holes perforation holes made in the disk part of the PM crankshaft pulley.

In FIG. 10 shows the structural and technological design of the lining of the disk part of the crankshaft pulley of the drive of auxiliary units PM with the full filling of the cavities of the windows and perforation holes made in the disk part.

In FIG. 11 shows the structural and technological design of the lining of the disk part of the crankshaft pulley of the drive of auxiliary units PM with the lining of the surfaces of the disk part with hollow window cavities and perforation holes made in the disk part.

In FIG. 12 shows the structural and technological design of the lining of the disk part of the crankshaft pulley of the drive of auxiliary units PM with the partial filling of the cavities of the windows and perforation holes made in the disk part.

In FIG. 13 shows the structural and technological design of the lining of the disk part of the crankshaft pulley of the drive of auxiliary units PM with full filling of the window cavities and unfilled perforation holes made in the disk part.

In the drawings, the following notation:

1 - PM;

2 - PM crankshaft (further crankshaft);

3 - end section (sock) of the crankshaft 2 PM 1 (hereinafter, the sock 3 of the crankshaft 2);

4 - a pulley of the crankshaft 2 PM 1;

5 - front cover PM 1;

6 - cylinder block PM 1;

7 - oil pan PM 1;

8 - a drive belt of auxiliary PDVS units (not shown);

9 - fan cooling system MPE (not shown);

10 - panel mudguard body ATS (not shown);

11 - generator (not shown);

12 - hood (not shown);

13 - road surface;

14 - the rim of the pulley 4 of the crankshaft 2 PM1;

15- disk part of the pulley 4 of the crankshaft 2 PM 1;

16 - the hub part of the pulley 4 of the crankshaft 2 PM 1;

17 - a spoke of a pulley 4 of the crankshaft 2 PM 1;

18 - jumpers of the disk part 15 of the pulley 4 of the crankshaft 2 PM 1;

19 - windows of the disk portion 15 of the pulley 4 of the crankshaft 2 PM 1;

20 - hole perforation of the disk part 15 of the pulley 4 of the crankshaft 2 PM 1;

21 - porous breathable sound absorbing substance;

22 - wall zone of the disk part 15 of the pulley 4 of the crankshaft 2, mating with the rim 14 of the pulley 4 of the crankshaft 2 PM 1;

23 - a parietal zone of the disk part 15 of the pulley 4, mating with the hub part 16 of the pulley 4 of the crankshaft 2 PM 1;

24 - film, or foil, or non-woven fabric, a sound-transparent protective layer of a substance lining the disk part 15 of the pulley 4 of the crankshaft 2 PM 1;

25 - dynamic damper (damper) of torsional vibrations of the crankshaft 2 PM 1;

26 - seismic mass of the damper (dynamic damper) of torsional vibrations 25 of the crankshaft 2 PM 1;

27 - elastic vibration-isolating suspension of seismic mass of the damper (dynamic damper) of torsional vibrations 25 of the crankshaft 2 PM 1;

28 - air cleaner intake system;

29 - panel flap front end of the vehicle;

30 - radiator lining of the cooling system PDVS ATS;

31 - lower mudguard of the engine compartment (not shown);

32 - casing of the fan cooling system MPE (not shown);

33 - air cavities of windows 19 and perforation holes 20 of the disk part 15 of the pulley 4 of the crankshaft 2 PM 1;

34 - ventilation opening of the ATC engine compartment (not shown);

35 - adhesive substance (not shown);

d _p - the diameter of the hole perforation of the disk part 15 of the pulley 4 of the crankshaft 2 PM 1;

t _d - wall thickness of the disk part 15 of the pulley 4 of the crankshaft 2 PM 1;

S _about - the total area of the passage sections of the windows 19 of the disk part 15 of the pulley 4 of the crankshaft 2 PM 1;

S _d - surface area (front or back) of the disk part 15 of the pulley 4 of the crankshaft 2 PM 1;

to _lane is the perforation coefficient of the external protective sound-transparent film layer of the material;

σ is the resistance to blowing by the air flow, Н⋅с⋅м ^-3 ;

f _and - frequency range, in Hz, recording the values of the reverberation coefficient of sound absorption α _r ;

α _r - reverberation coefficient of sound absorption (conventional units).

Terms used in the text of the description of the application for invention.

Sound absorption is the physical process of an irreversible dissipative transition of vibrational mechanical (wave) energy propagated in the elastic medium of a sound wave into thermal energy. It is estimated in arbitrary units by the sound absorption coefficient (normal - α _n and reverberation - α _r ).

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

Soundproofing. The term “sound insulation” is used to denote three technical (physical) characteristics and refers directly to the acoustic (noise-reducing) structure itself, to the complex physical process of absorption and reflection of sound waves by the acoustic structure, and to the quantitative assessment of the change (attenuation) in the transmission of acoustic radiation (numerical change of parameters) physical process of energy transfer of acoustic radiation) introduced by the used acoustic structure. It is a measure of sound insulation by a screen partition, wall or panel, expressed in dB.

Perforated hole (perforation holes) - one or more through holes of a given (usually identical) geometric shape and overall dimensions (passage area) located relative to each other and / or relative to another closely spaced structural element of the part (assembly) at a given distance. Perforation - from the Latin perforato - punch, puncture - the technological process of making through holes of given sizes, located accordingly in the wall structure of the manufactured part (assembly).

Perforation coefficient ( _{per per} ) is the ratio of the total area of perforation holes to the total area of the front surface, wall (part structure) that has been subjected to the perforation procedure (until it is perforated).

Sound transparency - a physical property of structures, individual structural elements (plates, shells, films) to transmit a sound wave without significantly attenuating its energy (without significant reflection in the direction opposite to the propagation from the radiation source). Quantitatively, opacity is characterized by the transmission coefficient of sound. A structure is considered to be translucent if the attenuation of the transmission of sound energy introduced by it does not exceed 10%.

Sound diffraction is a physical property characterizing the deviation of the behavior of sound propagation from the laws of geometric acoustics, due to the wave nature of sound propagation, in particular, causing the phenomenon of bending of propagated sound waves into the region of the sound shadow behind an enveloped sound reflecting obstacle that is larger than the length of the propagated sound wave .

An acoustic emitter of a dipole type (acoustic dipole) is a point emitter of sound, consisting of two antiphase spherical emitters of acoustic monopoles (pulsating spheres).

An acoustic monopole is a classic point emitter such as a pulsating sphere.

The dissipation of vibroacoustic energy is the irreversible conversion (dissipation) of mechanical (vibroacoustic) energy into thermal energy.

A dynamic vibration damper (dynamic vibration damper, dynamic vibration damper) of a PM crankshaft is a technical device operating on the principle of detuning the resonant vibrational properties of a system without absorbing vibrational energy (they have not found practical application in PM), or on the principle of absorbing vibrational energy generated by a PM crankshaft, operating on the principle of increasing inelastic dissipative losses (attenuation) in the resonant vibrational (torsional, bending) structure of the PM crankshaft (damping dry friction bodies, liquid friction dampers, hydraulic vibration dampers). Dynamic vibration dampers containing an elastic rubber viscoelastic layer in which the vibrational energy is dissipated with its irreversible conversion into thermal energy due to internal (molecular) friction in the structure of an elastic viscoelastic element (in a rubber layer) are most widely used in PM constructions. A typical example of the implementation of a dynamic vibration damper integrated in the construction of the PM crankshaft pulley is given, in particular, in the patent and patent application US 4,543,924 and DE 102010015249 A1 (prototype).

Acoustic resistance is the ratio of the complex amplitude of sound pressure to vibrational volume velocity. The real part of acoustic resistance characterizes the energy loss due to sound emission and its dissipation in the acoustic system itself. The imaginary part of acoustic resistance is due to the reaction of elastic forces or inertia forces. Unit of measurement Pa⋅s / m.

Input acoustic impedance is the ratio of sound pressure to vibrational velocity at the boundary of a semi-infinite elastic medium from which sound waves fall, with another elastic medium - where these waves penetrate.

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

Anisotropic medium is a medium whose properties are different in different spatial directions.

According to the claimed technical solution, the outer surface of the disk part 15 of the pulley 4, both with its rear and its front sides, is lined with a porous air-produced sound-absorbing substance 21, with full or partial filling of the cavities of the disk part 15 of the pulley 4, both of the window cavities 19 and the hole cavities perforations 20, indicated by the porous air-borne sound-absorbing substance 21. The porous air-borne sound-absorbing substance 21 can be presented in the form of porous open-cell foam and pores grained fibrous synthetic materials, mineral or organic origin. The outer front surface of the porous air-blown sound-absorbing substance 21 is lined with a moisture-oil and petrol-resistant film, or foil, or non-woven fabric with a sound-transparent protective layer 24. The metal structure of the disk part 15 of the pulley 4 with windows 19 and perforation holes 20 made in the wall zones 22 and 23 of the disk part 15 mating with the hub part 16 of the pulley 4 and the rim 14 of the pulley 4, and / or directly in the spokes 17, or in the jumpers 18 of the disk part 15 of the pulley 4 formed between the air cavities 33 of the windows 19, t used in the manufacturing process of the claimed design of the pulley 4 of the crankshaft 2 PM 1 as an internal standard frame embedded reinforcement installed in the matrix cavity of a given geometric shape of the technological mold, into which a porous air-produced sound-absorbing substance 21 and a facing film, or foil, or non-woven fabric are fed a sound-transparent protective layer 24, with the subsequent implementation of the technological process of forming the construction of the pulley 4, with the formation of adhesion ionic "technological cross-linking" of mating heterogeneous structural layers of materials when creating specified technological temperatures, pressures and introducing appropriate adhesive substances 35. Filling (full or partial) with porous air-blown sound-absorbing substance 21 (open-cell foam or fibrous air-blown structure with possible dosed introduction and volume distribution fragmented formations of dense airborne substances) cavities of said perforation holes 20 in the bridging zones 22 and 23 of the disk part 15 of the pulley 4, mating with the hub part 16 of the pulley 4 and the rim 14 of the pulley 4, and / or directly in the spokes 17 or in the jumpers of the disk part 18 formed between the air cavities 33 of the windows 19 of the window 19 of the disk part 15 of the pulley 4 if necessary, it is possible to provide (increase) the strength and adhesion characteristics of the interface between the metal and porous sound-absorbing components of the pulley 4 elements, providing the specified long-term operational requirements for the design of the crankshaft pulley 4 2 PM 1. The porous sound absorbing structure, footer disk portion 15 of the pulley 4 is preferably used as the porous sound-absorbing substances vozduhoproduvaemyh 21, characterized by blowing the resistance value of the air flow is in the range σ = 900 ... 2000 N⋅s⋅m ^-3. Moreover, the values of its reverberation sound absorption coefficient α _{r are} determined by the values of 0.4 ... 0.99 in the sound frequency range f _and = 400 ... 8000 Hz.

To ensure fire safety requirements for the operation of the claimed technical device, flame retardants can be added to the structure of the porous air-blown sound-absorbing substance 21. Thus, individual substances or mixtures of substances that protect materials of organic origin from ignition and self-combustion can be used. At the same time, flame retardants decompose with the formation of non-combustible substances and / or prevent the decomposition of the material with the release of combustible gases. The flame retardants used may be applied in the form of solutions on the surface of the porous air-blown sound-absorbing substance 21 or may impregnate its internal porous structure. As flame retardants, in particular, aluminum hydroxide, boron compounds, antimony, chlorides, organic and inorganic phosphorus compounds can be used.

The film, or foil, or non-woven fabric, the protective sound-transparent layer 24 can have a variety of structural and technological designs, which can be represented by single or multilayer sound-transparent structures with a wall thickness not exceeding 0.3 mm, made of metal or polymer construction materials or from combined structures of heterogeneous structural acoustic materials endowed with high translucent properties. The protective sound-transparent layer 24 can also be made of continuous air-blown structures of structural materials, including air-blown perforated structures with a given range of values of the perforation coefficient Κ _per ≥0.05. The structural materials of the protective sound-transparent layer 24 may be an elastic polymer film, a metal foil, a layer of a porous air-blown fibrous non-woven fabric. The technical parameters of complementary or alternatively used structures of structural materials of the protective sound-transparent protective layer 24 are limited to the following ranges:

- coefficient of perforation of an elastic polymer film or metal foil - K _per ≥0.05;

- the thickness of the layer of elastic polymer film is 0.010 ... 0.1 mm with its specific surface weight of 20 ... 70 g / m ² ;

- the thickness of the layer of metal foil is 0.05 ... 0.3 mm with its specific surface weight not exceeding 0.8 kg / m ² ;

- the thickness of the porous air-blown fibrous non-woven fabric is 0.025 ... 0.25 mm, with its specific surface weight - 20 ... 300 g / m ² and the specific resistance to blowing by air flow - 20 ... 50 N⋅s⋅m ^-3 ;

The structural film materials used for the protective sound-transparent layer 24 can be represented by polyester aluminized, urethane, polyvinyl chloride films, fibrous non-woven fabrics by maliflis, filts, metal foil by aluminum, brass, copper layer.

An adhesive joint made using an adhesive substance 35, a porous air-blown sound-absorbing substance 21 with a protective sound-transparent layer 24 can be achieved by introducing additional sound-transparent (not having a significant negative, not more than 10%, decrease in the value of the reverberation sound absorption coefficient α _{r of} sound energy) a certain type of adhesive adhesive layers used (sticky adhesive or thermoactive hot-melt substances), made in particular according to erhnostno spaced distinct thin solid lines, or surface spaced distinct thin broken lines, or in the form of perforated through holes thin continuous surface layer of adhesive 35 or in the form of a continuous sound transmission tacky adhesive layer with low specific surface weight (less than 100 g / m ²⁾ , or in the form of a continuous sound-transparent thermoactive layer of adhesive substance 35 with a low specific surface weight (not more than 50 g / m ² ).

Preferred options for structural and technological versions of the proposed technical solution are presented in the dependent claims.

The implementation of work processes in the MPE 1 (PKU, PNU), associated with the implementation of dynamic interactions in its KShM, whose constituent elements (pistons, connecting rods, crankshafts) which absorb intense alternating loads from the action of unbalanced forces and moments of inertia and gas forces, causes the corresponding vibroacoustic excitations body parts of the internal combustion engine (PKU, PNU) - in particular, the unit 6 and the cylinder head of the internal combustion engine, its valve and front 5 covers, oil pan 7 and auxiliary drives, units and item. The caused vibroacoustic excitations of the indicated parts and assemblies of the internal combustion engine (PCU, PNU) are transformed into the corresponding spurious sound radiation, classified by noise. One of the most excited structural elements of PDVS 1 (PKU, PNU) is a pulley 4 of the crankshaft 2 PDVS 1 (PKU, PNU), motionlessly mounted on the toe 3 of the crankshaft 2 of the crankshaft, performing both autonomous and joint with the oscillating crankshaft 2 intense bending, axial and torsional vibrations. Accordingly, the pulley 4 of the crankshaft 2 is one of the intense and dominant direct emitters of sound energy PM (PDVS, PKU, PNU), worsening its acoustic quality.

Sound waves that form, in particular, a diffuse sound field in a closed (partially closed) space of the ATS engine compartment containing MPE 1, emitted, in particular, by the noise-active zone of the front wall of the MPE body located behind the rear side of the disk portion 15 of the pulley 4 of the crankshaft 2, encountering shielding obstacles (in this case, the disk part 15 of the pulley 4 of the crankshaft 2), on the one hand they are absorbed by its porous air-produced sound-absorbing substance 21, and on the other hand, a part of the non-absorbed en WGIG encloses the outer peripheral edge of the rim 14 of the pulley 4 of the crankshaft 2, whereby in the zone in front of the front surface 4 of the crankshaft pulley 2 is formed acoustic penumbra area. This physical process is called the diffraction of sound, which is explained by the Huygens principle, according to which each point of a traveling sound wave is a point source of a new spherical wave. The envelope of these waves forms the next wave front. In accordance with this principle, the points of the sound wave located near the edge of the screening obstacle (in this case, along the periphery of the rim 14 of the pulley 4 of the crankshaft 2) emit sound not only in the direction of wave propagation, but also into the geometric shadow zone behind the source (in this case - in the area in front of the front side of the pulley 4 of the crankshaft 2). Thus, due to the diffraction process of bending the propagated sound waves towards the back side of the shielding obstacle (in this case, the disk portion 15 of the pulley 4 of the crankshaft 2 lined with a porous air-produced sound-absorbing substance 21) and their penetration into the internal porous air-generated sound-absorbing structure of the porous air-borne sound-absorbing substance 21 of the lining of the disk part 15 of the pulley 4 of the crankshaft 2, an additional dissipative absorption of sound energy with its dissipation into heat (reduction of PM noise level). The sound wave incident on the rear side of the disk part 15 of the pulley 4 of the crankshaft 2 emitted from the side of the pulley 4 of the crankshaft 2 of the noise-emitting wall of the PM housing adjacent to the disk part 15 will envelope the peripheral edges of the rim 14 of the pulley 4 of the crankshaft 2, rushing into the region of geometric sound shadow, under which means the area of space in front of the front of the disk part 15 of the pulley 4 of the crankshaft 2 (when viewed from the front to the PM case - ПДВС, ПКУ, ПНУ with the mounted pulley 4 at the end section (toe) 3 of its crankshaft 2). Propagating through the porous air-generated sound-absorbing structure of the lining in the window region 19 of the spoke structure of the disk portion 15 of the pulley 4 of the crankshaft 2, the sound waves will go around the peripheral sections of the spokes 17 and the rim 14 of the pulley 4 of the crankshaft 2 with the implementation of the edge diffractive dissipative absorption of sound energy. In addition, the part of the sound energy reflected from the surface of the disk portion 15 of the crankshaft pulley 4 of the crankshaft 4, as part of the incident sound wave, will also diffract in the shadow sound zone of the specified space for generating and propagating sound waves. Otherwise, if the surface of the disk part 15 of the pulley 4 of the crankshaft 2 is made in the form of a typical continuous rigid airtight structure, for example, in the form of a metal - steel or cast iron, die-welded sheet metal structure, as this, in particular, is presented in the prototype (application for invention DE 102010015249 A1), the process of reflection of sound waves from it will occur without changing the phase. As a result of this, both parts of the considered diffraction sound wave will be in phase and their resulting total amplitude of the sound pressure will exceed the amplitude of the sound pressure of its individual components. Thus, there will be an increase in the emission of sound energy (increase in noise), and not attenuation - as provided by the claimed technical solution.

Along with the physical process of dissipative diffraction absorption of the energy of sound waves deflecting (bending) in the zones of their external free passage over open peripheral sections of the screening obstacle (disk part 15 in the area of the rim 14 of the pulley 4 of the crankshaft 2) located on the propagation path of sound waves, also the physical process of dissipative absorption of the energy of sound waves propagating in an internal porous anisotropic medium containing prominent boundary zones distinguishing all densities, jumps (sudden changes) in acoustic impedances and resistance to blowing through the air stream of individual localized zones of the porous anisotropic structure, including the distributed placement of hollow cavities and dense air-tight sections of the spokes 17 in it in the areas of the windows 19 of the disk part 15 of the pulley 4 of the crankshaft 2. Due to the formation of hollow cavities, an increase in the sound absorption coefficient is achieved, mainly in the low- and mid-frequency ranges of the sound spectrum, in particular, from 100 to 800 q, compared, for example, varying smoothly or ravnoplotnymi sound absorbing structures characterized by respective input acoustic resistance, resistance by blowing the air stream σ. In addition to the presented structural and technological options for the implementation of porous air-blown sound-absorbing structures with hollow cavities included, dosed injections with appropriate volume distributions as part of the porous air-blown sound-absorbing structure of individual localized particles (fragments, formations) made of dense air-blown substances can also be used. In these cases, they can be considered as hybrid structural-technological variant designs, including the basic structure of a homogeneous porous air-blown sound-absorbing substance 21, hollow cavities and dense air-blown localization of inclusions of individual air-blown substances. The physical processes described above take place in the claimed technical device, individual structural and technological versions of which are represented by a preset combination of mating porous air-blown sound-absorbing structures contained in the lining of the disk part 15 of the pulley 4 of the crankshaft 2, the dense air-blown metal structure of the disk part 15 of the pulley 4 of the crankshaft 2 and 2 hollow cavities formed between the opposite layers of the lining in the areas of the windows 19 and the perforation holes 20 of the disk part and 15 pulley 4 crankshaft 2.

When applying a sound-absorbing lining to the surface of the disk portion 15 of the pulley 4 of the crankshaft 2 containing a window 19 made of a porous air-blown sound-absorbing substance 21 (porous foamed open-cell or porous fibrous structure) - sound reflection (the fraction of sound energy that did not penetrate the structure of the porous air-blown sound-absorbing substance) it will occur (depending on the reverberation coefficient of sound absorption α _{r of the} porous sound-absorbing layer of the lining), with the corresponding im changing the phase of the incident sound wave. Therefore, diffracted sound waves falling into the region of the geometric sound shadow (on both sides of the disk part 15 of the pulley 4 of the crankshaft 2) directly from the incident sound wave and as a result of its reflection with a changed phase from the surface of the disk part 15 of the pulley 4 of the crankshaft 2 will be in one or compensate each other to a different degree, thereby weakening the resulting amplitude of the diffracted sound wave, formed due to the mismatched phase interaction during their addition. In the case of using the solid metal construction of the pulley 4 of the crankshaft 2, equipped with a rigid sound-reflecting surface of its disk part 15, as is the case in the prototype (patent application DE 102010015249 A1), without lining its disk part 15 with a porous air-absorbing sound-absorbing substance 21, in the zone the axis of its rotation in the shadow region, the sound pressure of the reflected sound wave will be equal to the sound pressure in the incident wave. This is because the sound waves enveloping the free peripheral edges of the rim 14 of the pulley 4 of the crankshaft 2 are focused in the area of the axis of rotation of the pulley 4 of the crankshaft 2. In the case of using sound-absorbing lining of the surface of the disk part 15 of the pulley 4 of the crankshaft 2 with a porous air-absorbing sound-absorbing substance 21, as this takes place in the claimed design of the pulley 4 of the crankshaft 2 drive auxiliary units PM - the sound pressure in the area of the axis of rotation will be lower. The actual degree of realizable compensation of the energy of diffractive sound waves (when the sound absorption coefficient is less than 1) in the claimed design of the pulley 4 of the crankshaft 2 will be determined by its specific overall dimensions, the design of the hub 16, disk 15 parts and rim 14, as well as the specific thickness of the lining layer used, the structure and physical properties of the porous air-blown sound-absorbing substance 21 (overall dimensions of communicating pores and capillary channels, porosity, resistance air blowing, tortuosity of the pores, stiffness characteristics of the porous skeleton).

The physical processes of the diffraction propagation and absorption of energy of sound waves of a similar type described above for the case of propagation of sound waves from the side of the noise-active zone of the PM housing wall (PDVS, PKU, PNU) and their falling on the rear sound-absorbing surface of the disk part 15 of the pulley 4 of the crankshaft 2, lined porous breathable sound-absorbing substance 21, are also applicable to the case of propagation of sound waves from the opposite direction (from the front surface of the pulley 15 4 crankshafts 2) when they fall onto the front lined by a porous air-borne sound-absorbing substance 21, the sound-absorbing surface of the disk part 15 of the pulley 4 of the crankshaft 2. The sources of radiation of sound energy in this case can be, in particular, dispersed numerous "extraneous" noise sources located in closed (partially closed) space of the ATS engine compartment equipped with MPE (intake air cleaner 28, cooling fan 9, generator 11), sound waves reflected from the surfaces of the enclosing body panels forming the ATC engine compartment (hood 12, the front panel guard panels 29, the body mudguard panels 10, the lower mudguard of the engine compartment 31, the radiator linings of the cooling system ПДВС 30, the fan cover of the cooling system ПДВС 32), as well as the sound waves reflected from the surface of the road surface 13 in the area under the open ventilation openings of the engine compartment of the ATS 34. Various types of "extraneous" noise sources and various sound-reflecting enclosing screen elements (not related to typical pulley 4 of the crankshaft 2) are also characterized by typical PKU and PNU devices.

Used as a composite structural element of the crankshaft pulley 4 PM 1 lining by a porous air-produced sound-absorbing substance 21, forming the porous sound-absorbing structure of the disk part 15 of the pulley 4 of the crankshaft 2 can also be considered as a volumetric (double-sided) sound energy absorber placed in a diffuse sound field distributed in particular, in the space of the ATC engine compartment, which implements a comprehensive non-directional absorption of sound energy in this closed (partially closed ) space. Taking into account the close air gap of the porous sound-absorbing structure of the disk part 15 of the pulley 4 of the crankshaft 2 with respect to the noise-generating rigid sound-reflecting wall of the PM housing (front end wall of the cylinder block 6 and the oil pan 7 of the engine), the maximum effect of sound absorption is increased and shifted to the region of lower sound frequencies spectrum relative to, for example, a comparable version of the gapless lining of a similar porous structure mounted on a sound-reflecting surface henna. Because of this, along with the effect of increasing the absorption of sound energy, due to the placement of this type of volumetric absorber of sound energy in the zone of its high concentration (due to its close proximity to the sound radiation source, including the zone of its near hydrodynamic field), the claimed technical device implements and more effective suppression of low-frequency sound radiation, which is, as a rule, the most relevant in the fight against transport and industrial (industrial) noise and radiation.

Perforation holes 20 made in the disk part 15 of the pulley 4 of the crankshaft 2 PM, along with the similar function of the windows 19 of the disk part 15 of the pulley 4 of the crankshaft 2, contribute to the implementation of the physical processes of additional communicative transmission paths and additional dissipative dissipation of sound energy through porous air-blown sound-absorbing structures lining layers of a porous air-blown sound-absorbing substance 21, partially or completely filling the air cavities of windows 19 and openings ne perforations of the 20 disk part 15 of the pulley 4 of the crankshaft 2 PM 1. Also, their separate structural and technological versions can reduce the metal consumption and weight of the structure, improve (simplify) the manufacturing process of the layered structure of the pulley 4 of the crankshaft 2 PM, consisting of dissimilar structural materials and provide higher operational characteristics of the structure by increasing the adhesive bonds of the composite layers (to improve the reliability and durability of the structure).

To ensure acceptable performance characteristics, the outer surfaces of the lining layers of the disk part 15 of the pulley 4 of the crankshaft 2 are lined with an external protective sound-transparent film (polyester, aluminized, urethane, polyvinyl chloride) polymer layer, or a foil (aluminum, copper, brass) metal layer or non-woven fabric layer m ( Filts) 24.

The process of final dynamic balancing of the design of the pulley 4 of the crankshaft 2 PM is carried out upon completion of the technological operations of its manufacture, including its lining with a porous air-blown sound-absorbing substance 21. The end regions of the rim 14 of the pulley 4 of the crankshaft 2 PM are accepted as a zone for removing or introducing additional balancing mass.

Thus, the implementation of the technical solution claimed as an invention allows the following noise-reducing effects to be implemented, based on the following physical principles of suppressing sound energy radiation:

- the presence of windows 19 (with air cavities 33), made in the disk part 15 of the pulley 4 of the crankshaft 2, hollow, or partially or completely filled with porous air-blown sound-absorbing substance 21, eliminates the formation of high-amplitude pressure fields formed between the front and back surfaces of the disk part 15 pulley 4 of the crankshaft 2 PM 1 generated by vibrations of the pulley 15 of the pulley 4, as the dominant emitter of structural noise of the pulley 4 of the crankshaft 2 PM, rigidly mounted on its end section (toe) 3, thereby reducing the dipole moment of the sound radiation of the pulley, which is represented by a typical double-sided plate diaphragm radiator of the dipole type, which, accordingly, reduces the emission of sound energy directly produced by the pulley 4 (its disk part 15);

- overlapping or filling the air cavities of windows and perforations 33 made in the disk portion 15 of the pulley 4 of the crankshaft 2 PM 1 with a porous air-produced sound-absorbing substance 21, eliminates the problem of the emission of aerodynamic "fan" noise generated by the rotation of the pulley 4 of the crankshaft 2 PM 1 containing spokes 17 (windows 19) made in its disk portion 15, including suppressing aerodynamic noise from other possible structural inhomogeneities contained in the design of the rotating pulley 4 (stiffeners, rest s edges) of the closed footer surface of the disk portion 15 of the crankshaft pulley 4 1 2 PM vozduhoproduvaemogo structural layers of porous sound-absorbing material 21;

- the location (layout) of the pulley 4 at the end section (toe) 3 of the crankshaft 2 PM 1 near the noise-active zone of the PM housing wall (ПДВС, ПКУ, ПНУ), excited by working dynamic (vibration) processes occurring in the PM, with a small air gap between the surface of this wall and the rear side of the disk part 15 of the pulley 4 of the crankshaft 2 containing a porous air-produced sound-absorbing structure in the spatial zone of localization of a high concentration of sound energy, which allows for more efficient absorption of this the second part of the noise energy of the PM;

- the location (layout) of the pulley 4 at the end section (toe) 3 of the crankshaft 2PM 1 mounted in closed (partially closed) spaces of the ATS engine compartment, which is intensely noisy, limited by the air space enclosing the screen body elements, in which a diffuse sound field from numerous "Extraneous" sources of noise (not related to a direct change in noise by the pulley 4 of the crankshaft 2 PM 1), with the design of its disk part 15 containing a porous air blow a sound-absorbing structure, allows for a more effective comprehensive omnidirectional (both from the front and from the rear surface of the disk part 15 of the pulley 4 of the crankshaft 2) energy absorption of the diffuse sound generated in the engine compartment of the ATS, which is formed as the primary numerous "extraneous" noise sources dispersed in the engine compartment, as well as secondary noise sources formed by the processes of reflection of sound waves from the surfaces of the enclosing screen body elements entov engine compartment and road surface;

- free enveloping by sound waves of the outer free peripheral disk part 15 and rim 14 of the pulley 4 of the crankshaft 2 PM 1, enveloping by the distributed sound waves of the peripheral peripheral zones of the spokes 17 (windows 19) inside the porous air-blown sound-absorbing structure of the porous air-blown sound-absorbing substance 21 radiated from the side, the nearby noise-active zone of the PM 1 housing wall (falling on the back side of the surface of the disk part 15 of the pulley 4 of the crankshaft 2), and also from the side of the noise emitters, located married in other spatial areas of the engine compartment, as well as sound waves reflected from the surfaces of the enclosing screen body elements of the engine compartment and the sound-reflecting zone of the surface of the road surface 13 located above the lower open ventilation opening of the engine compartment 34 (falling on the front side of the disk part 15 of the crankshaft pulley 4 2), which causes the physical process of diffraction of sound waves with the corresponding implementation of the mechanism of dissipative dissipation of sound energy, determine the effect of effective suppression of the level of sound energy in the space of the engine compartment and provide a reduction in the emission of spurious noise energy into the environment (reduce its acoustic pollution).

Of course, the claimed invention is not limited to the specific structural examples of its implementation described in the text and shown in the accompanying figures. Some minor changes in the various structural elements or materials from which these structural elements are made, or their replacement with technically equivalent ones that do not go beyond the scope of the claims indicated by the claims, remain possible.

Claims (14)

1. A pulley of the crankshaft of a piston machine, comprising a hub part, a rim, a disk part and a device for reducing its sound radiation, characterized in that the device for reducing sound radiation is presented in the form of windows and perforation holes made in the disk part of the pulley, which is on both sides of it the surface is lined with a porous air-borne sound-absorbing substance lined with protective sound-transparent film, or foil, or non-woven fabric layers of materials. 2. The pulley of the crankshaft of a piston machine according to claim 1, characterized in that the porous air-produced sound-absorbing substance is a fibrous and / or foamed open-cell sound-absorbing material of synthetic, and / or mineral, and / or organic origin. 3. The pulley of the crankshaft of the piston machine according to claim 2, characterized in that the porous air-produced sound-absorbing substance is characterized by physical parameters of resistance to blowing by the air flow σ = 350 ... 2000 N⋅cm ^-3 and the reverberation coefficient of sound absorption α _r = 0.4 ... 0.99 in the sound frequency range f _and = 400 ... 8000 Hz. 4. The pulley of the crankshaft of the piston machine according to claim 1, characterized in that the ratio of the total area of the passage sections of the windows S _o with respect to the surface area of the disk part of the pulley S _d is at least 0.5 (S _o / S _d ≥0.5 ), and the diameters of the holes of the perforation of the disk part of the pulley d _p are in the range of values of d _p = t _d ... 3t _d , where t _d is the wall thickness of the disk part of the pulley in the area of the perforation hole. 5. The pulley of the crankshaft of the piston machine according to claim 1, characterized in that the external protective sound-transparent film layers of the materials are represented by layers of polyester aluminized, urethane, polyvinyl chloride polymer films. 6. The pulley of the crankshaft of the piston machine according to claim 1, characterized in that the external protective sound-transparent foil layers of materials are represented by metal layers of aluminum, copper, brass. 7. The pulley of the crankshaft of the piston machine according to claim 1, characterized in that the external protective sound-transparent layers of non-woven material are represented by layers of an air-blown non-woven fabric of the type "malifliz" or "filts". 8. The pulley of the crankshaft of a piston machine according to claim 1, characterized in that the surfaces of the constituent elements of the disk part of the pulley are adhesively bonded to the opposing surfaces of the layers of the porous air-blown sound-absorbing substance with sticky adhesive layers and / or thermosetting adhesives of film, fiber or powder type adhesive substances. 9. The pulley of the crankshaft of the piston machine according to claim 1, characterized in that the surfaces of the layers of the external protective sound-transparent film, or foil, or non-woven fabric materials, mating with the surfaces of the layers of the porous air-blown sound-absorbing substance, are fastened with adhesive sound-transparent adhesive adhesive compounds, and / or thermosetting adhesives of film, fibrous or powder type adhesive substances. 10. The pulley of the crankshaft of the piston machine according to claim 1, characterized in that the porous air-produced sound-absorbing substance does not fill the air cavities of windows and perforation holes of its disk part. 11. The pulley of the crankshaft of the piston machine according to claim 1, characterized in that the porous air-generated sound-absorbing substance at least partially fills the air cavities of the windows and / or perforations of its disk portion. 12. The pulley of the crankshaft of the piston machine according to claim 1, characterized in that the structural composition of the porous air-blown sound-absorbing substance contains fragmented formations of dense air-blown substances. 13. The crankshaft pulley of the piston machine according to claim 1, characterized in that the protective sound-transparent film layer is represented by a continuous non-perforated or perforated structural design, characterized by a perforation coefficient K _per ≥0.05, an elastic polymer film layer thickness of 0.01 ... 0.1 mm with its specific surface weight of 20 ... 70 g / m ² , or a metal foil layer thickness of 0.05 ... 0.3 mm with its specific surface weight not exceeding 0.8 kg / m ² , or a non-woven fabric layer thickness of 0.025 ... 0 , 25 mm with a specific surface weight of 20 ... 300 g / m ² and specific resistance to blowing by an air stream 20 ... 50 N⋅s⋅m ^-3 . 14. The pulley of the crankshaft of the piston machine according to claim 1, characterized in that the adhesive joints of the surface layers of the porous air-blown sound-absorbing substance and the protective sound-transparent layers of a film, or foil, or non-woven fabric of materials are represented by sound-transparent adhesive joints of sticky adhesive or thermosetting hot melt materials, made spaced apart thin thin solid lines, or surface spaced apart thin thin dashed lines, whether solid or perforated thin surface layers of adhesive substances, the specific surface weight of less than 100 g / m ² - for sticky or glutinous adhesive substance 50 g / m ² - for thermosetting hot melt adhesive substances.

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