CN113205791A - Rail transit vehicle, cab and noise control method of cab - Google Patents

Rail transit vehicle, cab and noise control method of cab Download PDF

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Publication number
CN113205791A
CN113205791A CN202110432163.7A CN202110432163A CN113205791A CN 113205791 A CN113205791 A CN 113205791A CN 202110432163 A CN202110432163 A CN 202110432163A CN 113205791 A CN113205791 A CN 113205791A
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cab
sound
frequency
sound absorption
plate
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Inventor
李登科
蒋忠城
张俊
刘晓波
王先锋
郭冰彬
江大发
金淼鑫
李旺
何辉永
何妙
邱昂
李中意
罗志翔
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CRRC Zhuzhou Locomotive Co Ltd
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CRRC Zhuzhou Locomotive Co Ltd
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    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/172—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general using resonance effects
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61D—BODY DETAILS OR KINDS OF RAILWAY VEHICLES
    • B61D17/00—Construction details of vehicle bodies
    • B61D17/04—Construction details of vehicle bodies with bodies of metal; with composite, e.g. metal and wood body structures
    • B61D17/18—Internal lining, e.g. insulating
    • B61D17/185—Internal lining, e.g. insulating for sound insulating

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  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Multimedia (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Wood Science & Technology (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Interior And Exterior Ornaments, Soundproofing, And Insulation (AREA)

Abstract

The invention discloses a rail transit vehicle, a cab and a noise control method of the cab, and relates to the field of noise control inside the rail transit vehicle. The noise control method comprises the specific steps of firstly, acquiring modal frequency distribution of an acoustic cavity in a cab; secondly, setting a noise reduction frequency interval according to the modal frequency distribution of an acoustic cavity in the cab, and further determining the design frequency of the sound absorption plate; and finally, determining the arrangement positions of the sound absorbing plates with different frequencies according to the sound pressure distribution in the cab under each modal frequency and the noise reduction frequency interval of each sound absorbing plate. The invention designs the noise reduction plate with high-efficiency sound absorption by carrying out spectrum analysis on the noise in the cab, and simultaneously realizes high-efficiency control on the unsteady low-frequency noise of the cab by combining the sound pressure distribution under each order of modal frequency in the cab.

Description

Rail transit vehicle, cab and noise control method of cab
Technical Field
The invention relates to the field of noise control in rail transit vehicles, in particular to a rail transit vehicle, a cab and a noise control method of the cab.
Background
When the rail vehicle runs on a road, wheel rail noise, air conditioner fan noise and a vehicle-mounted equipment noise source are directly transmitted into a reverberation space in a cab, so that the noise source is complex and all-around, and the acoustic environment of the rail vehicle is complex and acoustic signals are unstable.
The reflection coefficient of the surface of the cab interior panel structure is defined as
Figure BDA0003031785840000011
Wherein P isrReflecting the amplitude of the sound, P, for the cab interior panellinginFor the amplitude of the sound wave of the panel in the cab, the larger the sound absorption coefficient is, the lower the reflection coefficient is, and the interior panel structures of the cab of the existing vehicle are all strong reflection plates with low sound absorption coefficientAnd the reflection coefficient r of the strong reflection surface is 1, and at the moment, strong reverberation exists in the cab, wherein low-frequency sound waves have a certain standing wave mode, so that low-frequency noise is remarkable. The wall surface of the cab is a strong reflection surface, the cab is integrally sealed, low-frequency noise in the cab easily generates reverberation, and unsteady signals are difficult to control by adopting the traditional noise reduction means.
Disclosure of Invention
The invention aims to solve the technical problems that reverberation is easy to generate and control is difficult to generate in low-frequency noise of a cab of a rail vehicle, and provides a rail transit vehicle, the cab and a noise control method of the cab, so that high-efficiency control over unsteady low-frequency noise of the cab is realized.
In order to solve the technical problems, the technical scheme adopted by the invention is as follows: a noise control method of a cab is characterized by comprising the following steps:
A. obtaining modal frequency distribution of an acoustic cavity in a cab and sound pressure distribution under various orders of modal frequencies in the cab;
B. setting a noise reduction frequency interval by taking the 1 st order modal frequency as the lower limit of the noise frequency of the cab and combining the frequency of the wheel rail noise of the cab;
C. dividing the noise reduction frequency interval into m non-repetitive frequency intervals, and designing m sound absorption plates corresponding to each frequency interval;
D. and C, analyzing the sound pressure distribution of each position in the cab under different orders of modal frequency based on the sound pressure distribution of the cab, and determining the arrangement positions of the m sound absorption plates by combining the frequency intervals corresponding to the sound absorption plates in the step C, wherein the sound absorption plate with the lowest sound absorption frequency interval is arranged at the position with the lowest sound pressure in the cab under the low-frequency modal frequency, and the sound absorption plate with the highest sound absorption frequency is arranged at the position with the highest sound pressure in the cab under the high-frequency modal frequency.
According to the scheme, the noise transmitted into the cab is subjected to spectrum analysis, the efficient sound absorption noise reduction plate is designed, and meanwhile, the sound pressure distribution under each order of modal frequency in the cab is combined, so that the efficient control of unsteady low-frequency noise of the cab is realized.
Go toStep, difference L of sound pressure level of any point in driver's cabptNamely the noise reduction amount, the calculation formula is as follows:
Figure BDA0003031785840000021
wherein
Figure BDA0003031785840000022
And
Figure BDA0003031785840000023
the indoor average sound absorption coefficient L of the cab before and after the arrangement of the m sound absorption boardspt1And Lpt2The sound pressure levels before and after the m sound absorbing boards are respectively distributed at any point in the cab.
Further, the indoor average sound absorption coefficient
Figure BDA0003031785840000024
Is calculated by the formula
Figure BDA0003031785840000025
Wherein s isiRespectively the sound absorption area of the ith block, the value range of i is 1 to m, alphaiThe sound absorption coefficient of the ith sound absorption plate,
Figure BDA0003031785840000026
Real(Zall) Is ZallReal part of (c), Imag (Z)all) Is ZallImaginary part of, ZallIn order to be the specific acoustic impedance of the surface,
Figure BDA0003031785840000027
St0total surface area of m sound absorbing panels in the driver's cab, ZP1，ZP2，…，ZPmThe acoustic impedances of the surfaces of the m sound absorbing panels are respectively.
Further, the sound pressure level L of any point in the cabptIs calculated by the formula
Figure BDA0003031785840000028
LwtFrequency multiplication for sound source in driver cabVocal power level.
According to the scheme, the noise reduction quantity before and after the m sound-absorbing boards are installed in the cab can be calculated, and the noise reduction effect after the m sound-absorbing boards are installed in the cab can be intuitively explained.
Based on the same invention idea, the invention provides a driver cab of a rail transit vehicle and the rail transit vehicle adopting the driver cab. The cab comprises a noise reduction plate arranged on a top plate and/or a back plate; the noise reduction plate comprises m types of sound absorption plates, each type of sound absorption plate corresponds to 1 frequency interval, the m frequency intervals are not repeated except for interval end points, and the union of the m frequency intervals is consistent with the noise reduction frequency interval in the cab in size; the sound absorption plates with the lowest sound absorption frequency interval on the noise reduction plate are respectively arranged at the corner positions of the noise reduction plate; the sound absorption plate with the highest sound absorption frequency interval is arranged at the center of the noise reduction plate. The noise reduction plate is arranged on the top plate and/or the back plate of the cab, so that the noise in the cab can be absorbed.
Specifically, the shape and the size of the noise reduction plate arranged on the top plate are matched with those of the top plate; the shape and the size of the noise reduction plate arranged on the back plate are matched with those of the back plate. The low-frequency broadband noise in the cab can be greatly reduced, the medium and low-frequency sound absorption performance in the cab is effectively improved, and the low-frequency noise reflection in the cab is eliminated.
Specifically, the difference Δ L of the sound pressure level of any point of the cabptNamely, the noise reduction is calculated by the following formula:
Figure BDA0003031785840000031
wherein
Figure BDA0003031785840000032
And
Figure BDA0003031785840000033
the indoor average sound absorption coefficient L of the cab before and after the arrangement of the m sound absorption boardspt1And Lpt2Respectively the sound pressure level of any point of the cab before and after the m kinds of sound absorption plates are arranged.
In particular, indoor average sound absorption coefficient
Figure BDA0003031785840000034
Is calculated by the formula
Figure BDA0003031785840000035
Wherein s isiRespectively the sound absorption area of the ith block, the value range of i is 1 to m, alphaiThe sound absorption coefficient of the ith sound absorption plate,
Figure BDA0003031785840000036
Real(Zall) Is ZallReal part of (c), Imag (Z)all) Is ZallImaginary part of, ZallIn order to be the specific acoustic impedance of the surface,
Figure BDA0003031785840000037
St0total surface area of m sound absorbing panels in the driver's cab, ZP1，ZP2，…，ZPmThe acoustic impedances of the surfaces of the m sound absorbing panels are respectively.
In particular, the sound pressure level L of any point in the driver's cabinptIs calculated by the formula
Figure BDA0003031785840000038
LwtThe sound power level of each octave frequency band of the sound source in the cab.
Compared with the prior art, the invention has the beneficial effects that: the noise reduction method comprises the steps of carrying out spectrum analysis on noise transmitted into a cab, designing a noise reduction plate consisting of sound absorption plates with different sound absorption frequency intervals, simultaneously arranging the sound absorption plates at corresponding positions of the noise reduction plate by combining sound pressure distribution under each order of modal frequency in the cab, and arranging the noise reduction plate on a top plate and/or a back plate of the cab, thereby realizing efficient control on unsteady low-frequency noise of the cab, and determining actual noise reduction amount according to the noise reduction method in the cab provided by the invention. Compared with the traditional cab and the rail transit vehicle, the cab and the rail transit vehicle adopting the cab provided by the invention can further improve the riding comfort of drivers and passengers, and have better application effect.
Drawings
Fig. 1 is a schematic layout view of a sound absorbing panel in a noise reduction panel according to an embodiment of the present invention.
Fig. 2 is a schematic view of a cab with a noise reduction panel installed in an embodiment of the invention.
Fig. 3 is a schematic coordinate diagram of a back panel of the cab according to an embodiment of the invention.
Fig. 4 is a simulation diagram of the sound pressure level distribution of the back panel of the cab in the 1 st order frequency mode according to an embodiment of the present invention.
Fig. 5 is a simulation diagram of the sound pressure level distribution of the back panel of the cab in the 35 th order frequency mode according to the embodiment of the present invention.
Fig. 6 is a simulation diagram of the sound pressure level distribution of the back panel of the cab in the 450 th order frequency mode according to an embodiment of the present invention.
Wherein, 1 is the roof of having installed the board of making an uproar, 2 is the backplate of having installed the board of making an uproar, 3 is the grid of air-conditioning outlet, 11 is first acoustic baffle, 22 is the second acoustic baffle, 33 is the third acoustic baffle, 44 is the fourth acoustic baffle. The numbers in fig. 4 are the values of the sound pressure level at that location.
Detailed Description
In the embodiment, a subway vehicle cab is taken as an example for explanation, and the peak frequency interval of the noise of the wheel track measured by the sensor is 600Hz-650Hz, and the peak frequency interval of the noise of the air outlet of the air conditioner is 200Hz-280 Hz. With wheel-track noise being the dominant noise.
In this embodiment, the noise control method for the cab includes the following steps:
A. obtaining modal frequency distribution of an acoustic cavity in a cab and sound pressure distribution under various orders of modal frequencies in the cab;
B. setting a noise reduction frequency interval by taking the 1 st order modal frequency as the lower limit of the noise frequency of the cab and combining the frequency of the wheel rail noise of the cab;
C. dividing the noise reduction frequency interval into 4 non-repetitive frequency intervals, and designing 4 sound absorption plates corresponding to each frequency interval;
D. and C, analyzing the sound pressure distribution of each position in the cab under different orders of modal frequency based on the sound pressure distribution of the cab, and determining the arrangement positions of the 4 sound absorption plates by combining the frequency intervals corresponding to the sound absorption plates in the step C, wherein the sound absorption plate with the lowest sound absorption frequency interval is arranged at the position with the lowest sound pressure in the cab under low-frequency modal frequency, and the sound absorption plate with the highest sound absorption frequency is arranged at the position with the highest sound pressure in the cab under high-frequency modal frequency.
Firstly, a three-dimensional model in a cab is established, as shown in fig. 3, in this embodiment, the center of a back plate of the cab is selected as an origin, x, y, and z are three coordinate axes of a rectangular coordinate system, an x-axis square is a train traveling direction, a y-axis direction is a direction perpendicular to a side plate of the cab, a y-axis positive direction is a direction facing the back plate to the right in the cab, a z-axis positive direction is a direction perpendicular to an upward floor of the cab, and a length l of a sound cavity in the cab is selectedx2.5m, width ly2.9m and high lz＝2.27m。
In the rectangular coordinate system, the acoustic wave equation is:
Figure BDA0003031785840000051
wherein c is0Is the speed of sound in air, and T is time.
The total sound pressure P in the cab is formed by superimposing the modes of a series of acoustic cavities, so the solution of the acoustic wave equation is:
Figure BDA0003031785840000052
wherein
Figure BDA0003031785840000053
For the amplitude of the sound pressure of each mode, nx，ny，nzFor the order, ω, of each modenIs the wave number of the sound wave,
Figure BDA0003031785840000054
the modal frequency f is calculated as:
Figure BDA0003031785840000055
the calculated frequencies of the modes of the respective orders are shown in table 1.
TABLE 1 modal frequencies of the respective orders
Figure BDA0003031785840000056
Figure BDA0003031785840000061
As can be seen from table 1, if the frequency of the 1 st order is 60.8Hz, the lower limit of the cab noise frequency in this embodiment is 60.8 Hz. The frequencies of 31 st order and 35 th order correspond to the noise frequency of the air conditioning opening in the cab. The wheel-track noise of the cab is the main noise, and corresponds to the frequency of 450 th order, and is 630 Hz. According to the above analysis, the noise reduction frequency range in the cab of the present embodiment is set to 50 to 700 Hz.
In this embodiment, the sound pressure distribution of the back plate of the cab at the 1 st, 35 th and 450 th frequencies is taken as an example for the next analysis.
In step C, the sound pressure distribution diagrams of the cab back panel at the 1 st, 35 th and 450 th frequencies are as shown in fig. 4 to 6, and the sound pressure values of the corners, the edge centers and the center positions of the cab back panel are extracted to obtain tables 2 to 4, respectively.
TABLE 2 Sound pressure level of cab Back Panel corners
Figure BDA0003031785840000062
TABLE 3 Sound pressure level of the center of the Back Panel of the cab
Figure BDA0003031785840000063
TABLE 4 Sound pressure level in the center of the Back Panel of cab
Figure BDA0003031785840000064
As shown in fig. 4, fig. 5, and tables 2 to 4, in the sound pressure distribution of the low-frequency mode, the value of the sound pressure p is the lowest when x is equal to y and z is equal to 0 at the midpoint of the cab back plate and equation (2) and equation (3) are substituted; and the corner position of the cab takes x as 0,
Figure BDA0003031785840000071
the sound pressure p is highest when the sound pressure p is substituted into the formula (2) and the formula (3). Because the sound wave of low-order modal frequency is longer, 1 standing wave node exists in the driver's cabin, consequently with the corner position of low frequency acoustic baffle cloth in the driver's cabin, can increase the absorption effect of low frequency sound wave effectively. As shown in fig. 6 and tables 2 to 4, in the sound pressure distribution of the high-frequency mode, the distribution of the high-order sound wave mode in the cab shows a periodic distribution of peaks and troughs, and since the wavelength of the high-order mode frequency is short, a plurality of standing wave nodes exist in the cab, the high-frequency noise reduction plate is arranged in the middle of the cab, and the absorption of the high-frequency sound wave can be effectively increased.
The noise reduction frequency interval in the cab in this embodiment is divided into four frequency intervals of 50Hz-150Hz, 150Hz-250Hz, 250Hz-400Hz and 400-700Hz corresponding to the frequency intervals, the designed noise reduction panels include 4 sound absorption panels, the sound absorption frequency interval of the first sound absorption panel 11 is 50Hz-150Hz, the sound absorption frequency interval of the second sound absorption panel 22 is 150Hz-250Hz, the sound absorption frequency interval of the third sound absorption panel 33 is 250Hz-400Hz, and the sound absorption frequency interval of the fourth sound absorption panel 44 is 400Hz-700 Hz.
The cab of the embodiment is obtained based on the noise reduction method of the cab in the embodiment, the noise reduction plates are arranged on the top plate and the back plate in the cab, the noise reduction plates are provided with 4 sound absorption plates, the size of each sound absorption plate on the same noise reduction plate is consistent, 4 sound absorption plates are arranged on each sound absorption plate, and the size of each sound absorption plate is the same. The sound absorption plate is a resonance sound absorption structure consisting of a perforated plate and a plate rear cavity.
As shown in fig. 1, on the back panel of the cab, 4 first sound absorbing panels 11 are respectively disposed at 4 corner positions of the back panel, 4 fourth sound absorbing panels 44 are disposed at the center position of the back panel, and 4 second sound absorbing panels 22 and 4 third sound absorbing panels 33 are respectively disposed at other positions on the back panel.
As shown in fig. 2, in this embodiment, after the noise reduction plates are designed according to the sizes of the top plate and the back plate of the cab and then are respectively installed on the top plate and the back plate of the cab, as shown in fig. 1, the area and the number of each sound absorption plate are the same, the area ratio of each sound absorption plate is 1/4, the probability that sound waves are absorbed by a single sound absorption plate is 1/4, and the sound absorption plates have a shunt effect, so that acoustic impedances between the sound absorption plates are in a parallel structure, and it is assumed that the surfaces of the 4 sound absorption plates are: zP1，ZP2，ZP3，ZP4According to the theory of equivalent circuit of parallel structure, the parallel surface specific acoustic impedance Z of four resonance acoustic boards is obtainedallComprises the following steps:
Figure BDA0003031785840000081
the sound absorption coefficient of the sound absorption plate is as follows:
Figure BDA0003031785840000082
Real(Zall) Is ZallReal part of (c), Imag (Z)all) Is ZallThe imaginary part of (c).
After the noise reduction plate is installed in the cab, the average sound absorption coefficient in the cab
Figure BDA00030317858400000810
In order to realize the purpose,
Figure BDA0003031785840000083
wherein alpha isiAnd siSound absorption system of ith sound absorption plateThe number and area, i, ranges from 1 to 4. The internal sound field of the cab is a diffused sound field, and the sound field is obtained by superposing direct sound and reverberation according to the principle of the diffused sound field. Therefore, the sound pressure level L of any point in the cab closed space at different distances from the sound source can be obtained according to the formula (7)pt。
Figure BDA0003031785840000084
In the formula LwtThe unit of the sound power level of each octave frequency band of the sound source in the cab is dB (A); rtrIs a constant for the room or room,
Figure BDA0003031785840000085
Figure BDA0003031785840000086
the total surface area occupied by the 4 sound absorbing panels in the driver's cab is m2；rsThe distance from a sound source to a sound receiving point is m, and the sound receiving point is any point in a cab; q is a directivity constant of a sound source in the cab, and Q is 1 in this embodiment.
Average sound absorption coefficient in driver's cab
Figure BDA0003031785840000087
Small, the space in the tunnel generates enough reverberant sound, so according to equation (7),
Figure BDA0003031785840000088
therefore, the formula (7) can be simplified as follows.
Figure BDA0003031785840000089
According to the formula, the sound pressure level of the reverberation space in the tunnel is independent of the distance from the sound source to the measuring point.
The average indoor sound absorption coefficient of a cab in front of the noise reduction plate is assumed to be
Figure BDA0003031785840000091
The sound pressure level of any point is Lp 1; after the noise reduction plate is installed, the noise reduction plate is
Figure BDA0003031785840000092
And Lp 2. The sound pressure level difference Δ Lp before and after sound absorption processing is Lp1-Lp2, which is the noise reduction amount, and the calculation formula of the noise reduction amount Δ Lp in the driver's cabin before and after the noise reduction plate is installed according to the formula (8) is:
Figure BDA0003031785840000093
before the noise reduction plate is installed, the inner surface of the cab is of a panel structure such as glass fiber reinforced plastic, the surface of the cab has no sound absorption, and the average sound absorption coefficient of the cab is obtained by calculation
Figure BDA0003031785840000094
Is 0.02. As shown in fig. 2, the noise reduction plate is installed on the top plate and the back plate of the cab according to the arrangement mode shown in fig. 1, and the average sound absorption coefficient is calculated
Figure BDA0003031785840000095
0.2, the noise reduction quantity delta L in the cab after the noise reduction plate is installed can be calculated through a formulaptIs 10 dB. That is, the noise reduction board of the embodiment is installed behind the back board and the top board of the cab, so that the noise reduction in the cab can reach 10 dB.
By the noise control method, the noise frequency interval in the cab can be determined to design sound absorbing plates with m different frequency intervals, and the sound pressure of the corresponding position in the cab can be determined, so that the high-efficiency control of unsteady low-frequency noise of the cab is realized. Meanwhile, the noise control method of the invention can obtain the noise reduction plate, and the sound absorption plate with specific frequency is arranged at the corresponding position according to the sound pressure distribution, thereby effectively increasing the absorption effect of sound waves with corresponding frequency and achieving better noise reduction effect. And installing the noise reduction plate on a top plate and a back plate of the cab to obtain the cab of the embodiment. The method for calculating the noise reduction amount in the noise control method can determine the noise reduction amount before and after the noise reduction plate is arranged in the cab, and the result of the embodiment shows that the noise control method has obvious and effective noise reduction effect.
Compared with the traditional cab and rail transit vehicle, the cab and rail transit vehicle provided by the invention can further improve the riding comfort of drivers and passengers, and have better application effect.

Claims (10)

1. A noise control method of a cab is characterized by comprising the following steps:
A. obtaining modal frequency distribution of an acoustic cavity in a cab and sound pressure distribution under various orders of modal frequencies in the cab;
B. setting a noise reduction frequency interval by taking the 1 st order modal frequency as the lower limit of the noise frequency of the cab and combining the frequency of the wheel rail noise of the cab;
C. dividing the noise reduction frequency interval into m non-repetitive frequency intervals, and designing m sound absorption plates corresponding to each frequency interval;
D. and C, analyzing the sound pressure distribution of each position in the cab under different modal frequencies based on the sound pressure distribution of the cab under each order of modal frequency, and determining the arrangement positions of the m sound absorption plates by combining the frequency intervals corresponding to the sound absorption plates in the step C, wherein the sound absorption plate with the lowest sound absorption frequency interval is arranged at the position with the lowest sound pressure in the cab under the low-frequency modal frequency, and the sound absorption plate with the highest sound absorption frequency is arranged at the position with the highest sound pressure in the cab under the high-frequency modal frequency.
2. The noise control method of cab according to claim 1, wherein the difference Δ L of sound pressure level at any point in the cabptNamely the noise reduction amount, the calculation formula is as follows:
Figure FDA0003031785830000011
wherein
Figure FDA0003031785830000012
And
Figure FDA0003031785830000013
the indoor average sound absorption coefficient L of the cab before and after the arrangement of the m sound absorption boardspt1And Lpt2The sound pressure levels before and after the m sound absorbing boards are respectively distributed at any point in the cab.
3. The noise control method of cab according to claim 2, wherein the indoor average sound absorption coefficient
Figure FDA0003031785830000014
Is calculated by the formula
Figure FDA0003031785830000015
Wherein s isiRespectively the sound absorption area of the ith block, the value range of i is 1 to m, alphaiThe sound absorption coefficient of the ith sound absorption plate,
Figure FDA0003031785830000016
Real(Zall) Is ZallReal part of (c), Imag (Z)all) Is ZallImaginary part of, ZallIn order to be the specific acoustic impedance of the surface,
Figure FDA0003031785830000017
St0total surface area of m sound absorbing panels in the driver's cab, ZP1，ZP2，…，ZPmThe acoustic impedances of the surfaces of the m sound absorbing panels are respectively.
4. The noise control method of cab according to claim 3, wherein the sound pressure level L of any point in the cabptIs calculated by the formula
Figure FDA0003031785830000021
LwtThe sound power of each frequency band of the sound source in the cabAnd (4) stages.
5. The rail transit vehicle cab is characterized by comprising a noise reduction plate arranged on a top plate and/or a back plate; the noise reduction plate comprises m types of sound absorption plates, each type of sound absorption plate corresponds to 1 frequency interval, the m frequency intervals are not repeated except for interval end points, and the union of the m frequency intervals is consistent with the noise reduction frequency interval in the cab in size; the sound absorption plates with the lowest sound absorption frequency interval on the noise reduction plate are respectively arranged at the corner positions of the noise reduction plate; the sound absorption plate with the highest sound absorption frequency interval is arranged at the center of the noise reduction plate.
6. The rail transit vehicle cab of claim 5, wherein the shape and size of the noise reduction plate disposed on the top plate match the shape and size of the top plate; the shape and the size of the noise reduction plate arranged on the back plate are matched with those of the back plate.
7. The rail transit vehicle cab of claim 5, wherein the difference Δ L in sound pressure level at any point of the cabptNamely, the noise reduction is calculated by the following formula:
Figure FDA0003031785830000022
wherein
Figure FDA0003031785830000023
And
Figure FDA0003031785830000024
the indoor average sound absorption coefficient L of the cab before and after the arrangement of the m sound absorption boardspt1And Lpt2Respectively the sound pressure level of any point of the cab before and after the m kinds of sound absorption plates are arranged.
8. The rail transit vehicle cab of claim 7, wherein an indoor average sound absorption coefficient
Figure FDA0003031785830000025
Is calculated by the formula
Figure FDA0003031785830000026
Wherein s isiRespectively the sound absorption area of the ith block, the value range of i is 1 to m, alphaiThe sound absorption coefficient of the ith sound absorption plate,
Figure FDA0003031785830000027
Real(Zall) Is ZallReal part of (c), Imag (Z)all) Is ZallImaginary part of, ZallIn order to be the specific acoustic impedance of the surface,
Figure FDA0003031785830000028
St0total surface area occupied by m kinds of sound absorbing panels in the driver's cab, ZP1，ZP2，…，ZPmThe acoustic impedances of the surfaces of the m sound absorbing panels are respectively.
9. The rail transit vehicle cab of claim 8, wherein a sound pressure level L at any point in the cabptIs calculated by the formula
Figure FDA0003031785830000031
Wherein L iswtThe sound power level of each octave frequency band of the sound source in the cab.
10. A rail transit vehicle, characterized in that a cab according to any one of claims 5 to 9 is used.
CN202110432163.7A 2021-04-21 2021-04-21 Rail transit vehicle, cab and noise control method of cab Pending CN113205791A (en)

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