Underground construction device

Abstract

The application provides an underground construction device, comprising: a shield machine; a hydraulic pump station comprising: a hydraulic pump group adapted to provide hydraulic power for the shield machine; a first shell adapted to accommodate the hydraulic pump group, the first shell being provided with an air inlet and an air outlet; two sound attenuation mechanisms respectively arranged at the air inlet and the air outlet, the two sound attenuation mechanisms partially extending into the first shell, each sound attenuation mechanism having a first air port and a second air port, an air duct being formed between the first air port and the second air port, and each sound attenuation mechanism comprising: two groups of resonance units symmetrically arranged on two sides of the air duct, the two groups of resonance units being configured to consume sound energy in a first frequency range of sound waves by resonating with the sound waves generated by the hydraulic pump group; and a sound absorption unit configured to absorb sound energy in a second frequency range of the sound waves, the frequency of the second frequency range being greater than the frequency of the first frequency range.

Description

Technical Field

[0001] This application relates to the technical field of noise control for construction machinery, and more specifically, to an underground construction device. Background Technology

[0002] Hydraulic pump stations are the "heart" of underground tunnel construction equipment, especially tunnel boring machines (TBMs), continuously providing power to various hydraulic systems. However, the structural characteristics of hydraulic pump units result in significant vibration and noise. Construction workers, exposed to this high-noise underground environment for extended periods, experience not only hearing loss but also negatively impacting their work morale and psychological stress. Therefore, construction companies are imposing increasingly stringent noise control requirements on underground tunnel construction equipment, and construction workers are becoming more environmentally conscious. The vibration and noise problems caused by hydraulic pump stations urgently need to be addressed. Encasing the hydraulic pump station in a ventilated, soundproof enclosure is an economical and effective measure to reduce noise, but it often fails to achieve both good ventilation and effective noise reduction. Summary of the Invention

[0003] To address at least one of the technical problems in the prior art, embodiments of this application provide an underground construction device that ensures sufficient sound energy consumption while maintaining good ventilation performance.

[0004] An embodiment of this application provides an underground construction device, including: a tunnel boring machine (TBM); a hydraulic pump station including: a hydraulic pump group adapted to provide hydraulic power to the TBM; a first housing adapted to accommodate the hydraulic pump group, the first housing having an air inlet and an air outlet; two silencing mechanisms respectively disposed at the air inlet and the air outlet, and the two silencing mechanisms partially extending into the first housing, each silencing mechanism having a first air outlet and a second air outlet, the first air outlet and the second air outlet forming an air duct, each silencing mechanism including: two sets of resonant units symmetrically arranged on both sides of the air duct, the two sets of resonant units being configured to consume the sound energy of a first frequency band in the sound waves by resonating with the sound waves generated by the hydraulic pump group; and a sound-absorbing unit configured to absorb the sound energy of a second frequency band in the sound waves, the frequency of the second frequency band being greater than the frequency of the first frequency band.

[0005] According to some embodiments of this application, each of the above-mentioned silencing mechanisms further includes: a frame; a second housing, which is covered on the outside of the frame, the bottom of the second housing forms the second air vent, and the side wall of the second housing forms the first air vent; two sets of the above-mentioned resonant units are symmetrically arranged on opposite sides of the frame along the width direction, and the above-mentioned sound-absorbing unit is arranged downstream of the flow direction of the ventilation airflow and close to the first air vent, so that the two sets of the above-mentioned resonant units, the sound-absorbing unit and the above-mentioned second housing together form the bent air duct, so that the ventilation airflow flowing in from the second air vent turns at a right angle and is output to the outside through the first air vent.

[0006] According to some embodiments of this application, each group of the above-mentioned resonant units includes: four resonant modules disposed along the height direction on the frame, each of the above-mentioned resonant modules having a first open end, and the first open end being disposed facing the air duct, the four above-mentioned resonant modules having different sound absorption peak values, so as to consume sound energy of different frequency bands in the first frequency band when resonating with the sound wave.

[0007] According to some embodiments of this application, each of the above-mentioned resonant modules includes: a first substrate disposed at the first opening end, wherein the first substrate has a plurality of first through holes arranged in an array and penetrating the first substrate; a first support housing having a concave cross-section, wherein the first support housing is installed on the side of the first substrate near the second housing and together with the first substrate forms a first resonant cavity, wherein the first resonant cavity is connected to the air duct through the plurality of the first through holes.

[0008] According to some embodiments of this application, the space between the first support housing and the second housing is filled with sound-insulating material to absorb noise generated by the vibration of the first support housing.

[0009] According to some embodiments of this application, the four resonant modules are sequentially designated as a first resonant module, a second resonant module, a third resonant module, and a fourth resonant module along the flow direction of the ventilation airflow. The sound absorption peak value of the first resonant module is 900±2Hz, the sound absorption peak value of the second resonant module is 675±2Hz, the sound absorption peak value of the third resonant module is 225±2Hz, and the sound absorption peak value of the fourth resonant module is 450±2Hz.

[0010] According to some embodiments of this application, the sound-absorbing unit includes: a perforated mesh, installed on the frame and forming a sound-absorbing cavity between it and the second housing, the sound-absorbing cavity being filled with sound-absorbing material to absorb the sound energy of the second frequency band, the frequency of the second frequency band being greater than 1000Hz.

[0011] According to some embodiments of this application, each of the above-mentioned silencing mechanisms further includes: a plurality of blades, which are arranged in parallel between the frame and the first air outlet at intervals, and a flow channel is formed between adjacent blades to allow the ventilation airflow to pass through. Each blade includes: a connecting section connected to the frame, and the extension direction of the connecting section is parallel to the direction in which the ventilation airflow flows out of the first air outlet; and an extension section connected to the connecting section, and the extension section and the connecting section form an angle of 120° to 150° to reflect and interfere with the sound waves.

[0012] According to some embodiments of this application, the first housing has a receiving cavity, and the hydraulic pump station further includes: a temperature sensor disposed in the receiving cavity, suitable for detecting the actual temperature in the receiving cavity; a fan installed in the second air outlet of any one of the two silencing mechanisms; and a controller electrically connected to the temperature sensor and the fan, suitable for adjusting the speed of the fan based on the actual temperature and a preset temperature.

[0013] According to some embodiments of this application, the hydraulic pump station further includes: a second support housing having a concave cross-section, the second support housing being installed on the inner wall of the first housing, the second support housing having a second open end facing the hydraulic pump assembly; a second base plate being disposed at the second open end and forming a second resonant cavity with the second support housing, the second base plate having a plurality of second through holes arranged in an array and penetrating the second base plate, the second resonant cavity communicating with the receiving cavity through the plurality of second through holes to reduce the radiated noise of the hydraulic pump assembly.

[0014] According to the underground construction device of this application embodiment, the sound waves generated by the hydraulic pump unit during operation diffuse outward in a spherical form, with a portion of the sound waves entering the air duct and being transmitted to the outside through the first air inlet. After entering the air duct through the second air inlet, the sound waves flow sequentially through the area where the resonant unit is located and the area where the sound-absorbing unit is located. The two sets of resonant units are configured to consume the sound energy of the first frequency band of the sound waves when resonating with them. After the ventilation airflow passes through the two sets of resonant units through the air duct, the sound-absorbing unit absorbs the sound energy of the second frequency band of the sound waves, the frequency of which is higher than that of the first frequency band. Through the resonance consumption of the two sets of resonant units and the synergistic effect of the sound-absorbing unit, the silencing mechanism silences the low-frequency, mid-frequency, and high-frequency noise leaking through the air duct. Attached Figure Description

[0015] Figure 1 This is a noise sound pressure level spectrum diagram of a hydraulic pump station in the prior art;

[0016] Figure 2 This is a cross-sectional view of a hydraulic pump station according to an illustrative embodiment of this application;

[0017] Figure 3 This is a perspective view of a noise reduction mechanism according to an illustrative embodiment of this application;

[0018] Figure 4 This is a perspective sectional view of a noise reduction mechanism according to an illustrative embodiment of this application;

[0019] Figure 5 This is a side view of a noise reduction mechanism according to an illustrative embodiment of this application;

[0020] Figure 6 yes Figure 5 Cross-sectional view in the AA direction;

[0021] Figure 7 yes Figure 6 Cross-sectional view in the BB direction;

[0022] Figure 8 yes Figure 5 Cross-sectional view in the CC direction;

[0023] Figure 9 This is a transmission loss curve of a noise reduction mechanism according to an illustrative embodiment of this application.

[0024] The meanings of the reference numerals in the attached figure are as follows:

[0025] 1. Hydraulic pump set;

[0026] 2. First shell;

[0027] 3. Silencing mechanism;

[0028] 31. The first opportunity;

[0029] 32. The second wind gap;

[0030] 33. Air duct;

[0031] 34. Frame;

[0032] 35. Second shell;

[0033] 36. First Resonance Module;

[0034] 360°, Third substrate;

[0035] 361. Third supporting shell;

[0036] 37. Second Resonance Module;

[0037] 370. Fourth substrate;

[0038] 371. Fourth supporting shell;

[0039] 38. Third Resonance Module;

[0040] 380. Fifth substrate;

[0041] 381. Fifth supporting shell;

[0042] 39. Fourth Resonance Module;

[0043] 390. The sixth substrate;

[0044] 391. The sixth supporting shell;

[0045] 40. Perforated metal sheet;

[0046] 41. Sound-absorbing cavity;

[0047] 4. Temperature sensor;

[0048] 5. Fan;

[0049] 6. Second substrate;

[0050] 7. Leaves;

[0051] 71. Connecting section;

[0052] 72. Extension section. Detailed Implementation

[0053] The embodiments of this application will now be described with reference to the accompanying drawings. However, it should be understood that these descriptions are exemplary only and are not intended to limit the scope of this application. In the following detailed description, numerous specific details are set forth to provide a thorough understanding of the embodiments of this application for ease of explanation. However, it will be apparent that one or more embodiments may be implemented without these specific details. Furthermore, descriptions of well-known structures and technologies are omitted in the following description to avoid unnecessarily obscuring the concepts of this application.

[0054] The terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the scope of this application. The terms “comprising,” “including,” etc., as used herein indicate the presence of the stated features, steps, operations, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, or components.

[0055] All terms used herein (including technical and scientific terms) have the meanings commonly understood by those skilled in the art, unless otherwise defined. It should be noted that the terms used herein are to be interpreted in a manner consistent with the context of this specification, and not in an idealized or overly rigid way.

[0056] When using expressions such as "at least one of A, B, and C," the expression should generally be interpreted in accordance with the meaning commonly understood by a person skilled in the art (e.g., "a system having at least one of A, B, and C" should include, but is not limited to, systems having A alone, having B alone, having C alone, having A and B, having A and C, having B and C, and / or having A, B, and C, etc.). When using expressions such as "at least one of A, B, or C," the expression should generally be interpreted in accordance with the meaning commonly understood by a person skilled in the art (e.g., "a system having at least one of A, B, or C" should include, but is not limited to, systems having A alone, having B alone, having C alone, having A and B, having A and C, having B and C, and / or having A, B, and C, etc.).

[0057] Figure 1 This is a noise sound pressure level spectrum diagram of a hydraulic pump station in the existing technology.

[0058] Existing underground tunnel construction equipment uses hydraulic pump stations with large installed capacity, consisting of multiple motor-pump units, resulting in concentrated noise sources. Spectral analysis of the hydraulic pump station noise revealed that the peak frequency of the sound pressure level is closely related to the motor speed and the number of hydraulic pump plungers. Under normal conditions, with a rated motor speed of 1500 rpm and 9 hydraulic pump plungers, the noise sound pressure level spectrum is as follows: Figure 1 As shown, the peak frequency is approximately 225±2Hz and its harmonics. Among these, low-to-mid-frequency noise below 1000Hz has strong penetrating power, good diffraction, and long propagation distance, requiring focused sound insulation and noise reduction measures. Mid-to-high-frequency noise above 1000Hz has weak penetrating power and rapid propagation attenuation; ordinary sound insulation and sound absorption measures can achieve good results. Therefore, controlling the sound pressure level at 225±2Hz and its 2nd, 3rd, and 4th harmonics can reduce the overall sound pressure level of the hydraulic pump station.

[0059] Existing hydraulic pump stations use a combination of fans and ventilation louvers for ventilation and heat dissipation, both of which are fixed to a soundproof enclosure. This presents an inherent contradiction between ventilation and sound insulation: if the opening area of ​​the ventilation louvers is large, it will significantly weaken the sound insulation effect of the enclosure; if the opening area of ​​the ventilation louvers is small, the heat emitted by the motor inside the enclosure cannot be dissipated in time, affecting equipment operation. To resolve this contradiction, multi-layered louvers or labyrinthine louver structures are sometimes used for ventilation and noise reduction. While these structures are effective in controlling mid-to-high frequency noise, the internal air duct design leads to a sharp increase in air resistance and a decrease in ventilation efficiency, which in turn affects the normal operation of the motor pump unit.

[0060] Figure 2 This is a cross-sectional view of a hydraulic pump station according to an illustrative embodiment of this application.

[0061] An underground construction device is provided according to an embodiment of this application, such as... Figure 2As shown, the underground construction equipment includes a tunnel boring machine (TBM) and a hydraulic pump station. The hydraulic pump station includes a hydraulic pump unit 1, a first housing 2, and two silencing mechanisms 3. The hydraulic pump unit 1 is used to provide hydraulic power to the TBM. The first housing 2 is used to house the hydraulic pump unit 1, and has an air inlet and an air outlet. The two silencing mechanisms 3 are respectively located at the air inlet and the air outlet, and both silencing mechanisms 3 extend partially into the first housing 2. Each silencing mechanism 3 has a first air outlet 31 and a second air outlet 32, forming an air duct 33 between the first air outlet 31 and the second air outlet 32. Each silencing mechanism 3 includes two sets of resonant units and a sound-absorbing unit. The two sets of resonant units are symmetrically arranged on both sides of the air duct 33, and are configured to consume the sound energy of a first frequency band in the sound waves by resonating with the sound waves generated by the hydraulic pump unit 1. The sound-absorbing units are configured to absorb the sound energy of a second frequency band in the sound waves, the second frequency band having a frequency greater than the first frequency band.

[0062] In some illustrative embodiments, the hydraulic pump station is suitable for providing hydraulic power to the tunnel boring machine (TBM), for example, to provide hydraulic power to the TBM's propulsion system, cutterhead drive system, segment assembly machine, etc.

[0063] In some illustrative embodiments, the hydraulic pump assembly 1 may be, for example, an electric motor pump assembly, which may include a motor and a hydraulic pump. The motor may be a constant-speed motor or a variable-speed motor, and the hydraulic pump may be a piston pump or a gear pump. Preferably, it is an electric motor pump assembly consisting of a 1500 rpm motor and a 9-piston hydraulic pump.

[0064] In some illustrative embodiments, the first housing 2 can be a multi-layered composite sound insulation structure. From the inside out, the first housing 2 consists of a perforated plate, sound-absorbing cotton, a resonant sound-absorbing film, sound-absorbing cotton, a magnesium oxide damping plate, a damping sound insulation felt, and a metal shell. Through this multi-layered composite sound insulation structure, the mechanisms of mass sound insulation, damping sound insulation, and resonant film sound insulation can be comprehensively utilized to effectively block the direct sound across the low, medium, and high frequency bands generated by the hydraulic pump unit 1.

[0065] In some illustrative embodiments, hydraulic pipes, power lines, control lines, and other pipelines in the hydraulic pump station can extend through the air duct 33 of the silencing mechanism 3 to the outside of the first housing 2 to connect to the external actuators and electrical control cabinet.

[0066] In some illustrative embodiments, the pipeline of the motor pump unit can pass through a perforation in the wall of the first housing 2. To ensure vibration isolation and sealing, the gaps in the perforation can be filled with rubber material.

[0067] In this implementation, the sound waves generated by the hydraulic pump unit 1 during operation diffuse outward in a spherical shape. A portion of the sound waves enters the air duct 33 and is transmitted to the outside through the first air outlet 31. After entering the air duct 33 through the second air outlet 32, the sound waves flow sequentially through the areas where the resonant units and the sound-absorbing units are located. The two sets of resonant units are configured to consume the sound energy of the first frequency band of the sound waves when resonating with them. After the ventilation airflow passes through the air duct 33 and the two sets of resonant units, the sound-absorbing units absorb the sound energy of the second frequency band of the sound waves, the frequency of which is higher than that of the first frequency band. Through the resonant consumption of the two sets of resonant units and the synergistic effect of the sound-absorbing units, the silencing mechanism 3 silences the low-frequency, mid-frequency, and high-frequency noise leaking through the air duct 33.

[0068] Figure 3 This is a perspective view of a noise reduction mechanism according to an illustrative embodiment of this application. Figure 4 This is a perspective sectional view of a noise reduction mechanism according to an illustrative embodiment of this application.

[0069] According to embodiments of this application, such as Figure 3 and Figure 4 As shown, each silencing mechanism 3 also includes a frame 34 and a second housing 35. The second housing 35 covers the outside of the frame 34, with a second air vent 32 formed at the bottom and a first air vent 31 formed on the sidewall of the second housing 35. Two sets of resonant units are symmetrically arranged on opposite sides of the frame 34 along its width, and the sound-absorbing units are arranged in the direction of airflow (e.g., ...). Figure 4 The position is downstream of the Z direction shown and close to the first air outlet 31, so that the two sets of resonant units, sound-absorbing units and the second housing 35 together form a bent air duct 33, so that the ventilation airflow flowing in from the second air outlet 32 ​​turns at a right angle and is output to the outside through the first air outlet 31.

[0070] In some illustrative embodiments, the frame 34 can be a cuboid frame structure, serving as the skeleton of the entire silencing mechanism 3. The frame 34, in such a way... Figure 4 The length in the X direction shown is greater than 500 mm.

[0071] In some illustrative embodiments, such as Figure 4 As shown, two sets of resonant units are symmetrically distributed on the left and right sides of the frame 34, and sound-absorbing units are distributed on the front, rear, top and left sides of the frame 34 facing the first air vent 31.

[0072] In some illustrative embodiments, the cross-section of the air duct 33 may be rectangular. The cavity between the resonant units on both sides constitutes part of the air duct 33. The air duct 33 is rectangular in width direction (e.g., ...). Figure 4The range of the Y direction shown can be 180mm to 300mm, so as to increase the contact area between the ventilation airflow and the first substrate of the resonant unit on both sides (the first substrate will be described in detail below) while maintaining good ventilation capacity, thereby improving the resonance noise reduction effect.

[0073] Referring to the above structure, two sets of resonant units are symmetrically arranged on both sides of the air duct 33. The two sets of resonant units are configured to consume the acoustic energy of the first frequency band of the sound waves when resonating with them. The first frequency band can be, for example, a low-frequency band, specifically, the 225±2Hz frequency band and its harmonics (e.g., 450±2Hz, 675±2Hz, 900±2Hz). The sound-absorbing units are configured to absorb the acoustic energy of the second frequency band of the sound waves after the ventilation airflow passes through the air duct 33 and the two sets of resonant units. The frequency of the second frequency band is higher than the frequency of the first frequency band; for example, the second frequency band can be a mid-to-high frequency band greater than 1000Hz.

[0074] In this embodiment, two sets of resonant units are symmetrically fixed on opposite sides of the frame 34 along its width, and the sound-absorbing unit is positioned downstream of the airflow direction and close to the first air inlet 31. Thus, the two sets of resonant units, the sound-absorbing unit, and the second housing 35 together form a bent air duct 33. Specifically, the air duct 33 can be enclosed into a figure-7 shaped bend that allows only entry and exit through the second air inlet 32 ​​and the first air inlet 31, so that the airflow entering from the second air inlet 32, after a right-angle turn, is output to the outside through the first air inlet 31. During the right-angle turn of the airflow within the air duct 33, the sound waves undergo multiple reflections and interferences, weakening the sound wave energy to a certain extent and thus reducing noise propagation.

[0075] According to embodiments of this application, each group of resonant units includes four resonant modules. The four resonant modules are aligned along the height direction (i.e., the flow direction of the ventilation airflow, such as...). Figure 4 The four resonant modules (shown in the Z direction) are arranged on the frame 34. Each resonant module has a first open end, and the first open end is set facing the air duct 33. The four resonant modules have different sound absorption peak values, so as to consume the sound energy of different frequency bands in the first frequency band when resonating with the sound wave.

[0076] In this implementation, each of the four resonant modules has a different natural frequency. When sound waves flow through the area where the resonant modules are located via the air duct 33, components in the sound waves with frequencies close to the natural frequency of a particular resonant module drive the air column of that module to vibrate strongly. During the vibration of the air column, nearby sound energy is consumed through friction and radiation losses, thereby attenuating the sound energy in that frequency band from the sound waves. The four resonant modules respectively consume sound energy for four different frequency sub-bands in the first frequency band, so that the silencing mechanism 3 has silencing capability over a wide low-frequency range.

[0077] Figure 5 This is a side view of a noise reduction mechanism according to an illustrative embodiment of this application. Figure 6 yes Figure 5 Cross-sectional view in the AA direction.

[0078] According to embodiments of this application, such as Figure 5 and Figure 6 As shown, each resonant module includes a first substrate and a first support housing. The first substrate is disposed at the first open end, and a plurality of first through holes arranged in an array and penetrating the first substrate are formed on the first substrate. The first support housing has a concave cross-section, and the first support housing is installed on the side of the first substrate near the second housing 35, and together with the first substrate, forms a first resonant cavity, which is connected to the air duct 33 through the plurality of first through holes.

[0079] In some illustrative embodiments, the depth of the first resonant cavity, the diameter of the perforation on the first substrate, the thickness of the substrate, and the perforation rate are designed according to a preset peak absorption frequency (i.e., the target noise reduction frequency). For example, they can be calculated and determined according to the following formula (1). When the sound wave frequency in the air duct 33 is close to the natural frequency of the resonant module, the air column at the neck of the first substrate will vibrate strongly, thereby consuming the nearby sound energy and achieving noise reduction for a specific frequency.

[0080] (1);

[0081] Where n represents the rotational speed of the motor-pump unit (in r / min), Z represents the number of plungers in the plunger pump or the number of teeth in the gear pump, and i represents the fundamental frequency of the hydraulic pump station noise ( The i-th harmonic of ), where c represents the speed of sound in air. It is expressed as perforation ratio, t'=t+0.8d, t represents the thickness of the first substrate, d represents the perforation diameter of the first substrate, and D represents the depth of the first resonant cavity.

[0082] According to an embodiment of this application, a sound-insulating material is filled between the first support housing and the second housing 35 to absorb noise generated by the vibration of the first support housing.

[0083] In this implementation, the sound insulation material absorbs the noise generated by the vibration of the first support shell while preventing the noise from propagating through the resonant unit to the outside of the silencing mechanism 3.

[0084] According to an embodiment of this application, the four resonant modules are, in sequence, a first resonant module 36, a second resonant module 37, a third resonant module 38, and a fourth resonant module 39 along the flow direction of the ventilation airflow. The sound absorption peak value of the first resonant module is 900±2Hz, the sound absorption peak value of the second resonant module is 675±2Hz, the sound absorption peak value of the third resonant module is 225±2Hz, and the sound absorption peak value of the fourth resonant module is 450±2Hz.

[0085] Specifically, the first resonant module 36 includes a third substrate 360 ​​and a third support housing 361. The third substrate 360 ​​is disposed at the third open end of the third support housing 361, and the third substrate 360 ​​has a plurality of third through holes arranged in an array and penetrating the third substrate 360. The third support housing 361 has a concave cross-section, and the third support housing 361 is installed on the side of the third substrate 360 ​​near the second housing 35, and together with the third substrate 360, forms a third resonant cavity, which is connected to the air duct 33 through the plurality of third through holes.

[0086] Figure 7 yes Figure 6 Cross-sectional view in the BB direction.

[0087] Furthermore, such as Figure 4 , Figure 5 , Figure 6 and Figure 7 As shown, the third resonant cavity is a rectangular hollow cavity with a depth of 60±2mm in the Y direction and a width of 100mm~150mm in the Z direction. The thickness of the third substrate 360 ​​is 2mm, the cross-section of the third through hole is circular, the diameter of the third through hole is 11mm, and it is distributed in a 20mm×20mm square array. The sound absorption peak of the first resonant module 36 is approximately 900±2Hz.

[0088] Specifically, the second resonant module 37 includes a fourth substrate 370 and a fourth support housing 371. The fourth substrate 370 is disposed at the fourth opening end of the fourth support housing 371, and a plurality of fourth through holes arranged in an array and penetrating the fourth substrate 370 are formed on the fourth substrate 370. The fourth support housing 371 has a concave cross-section and is installed on the side of the fourth substrate 370 near the second housing 35, and together with the fourth substrate 370, forms a fourth resonant cavity, which is connected to the air duct 33 through the plurality of fourth through holes.

[0089] Furthermore, such as Figure 4 , Figure 5 , Figure 6 and Figure 7As shown, the fourth resonant cavity is a rectangular hollow cavity with a depth of 60±2mm in the Y direction and a width of 100mm~150mm in the Z direction. The fourth substrate 370 has a thickness of 2mm, and the fourth through hole has a circular cross-section and a diameter of 6mm, arranged in a 20mm×20mm square array. The peak sound absorption of the second resonant module 37 is approximately 675±2Hz.

[0090] Specifically, the third resonant module 38 includes a fifth substrate 380 and a fifth support housing 381. The fifth substrate 380 is disposed at the fifth opening end of the fifth support housing 381, and the fifth substrate 380 has a plurality of fifth through holes arranged in an array and penetrating the fifth substrate 380. The fifth support housing 381 has a concave cross-section, and the fifth support housing 381 is installed on the side of the fifth substrate 380 near the second housing 35, and together with the fifth substrate 380, forms a fifth resonant cavity, which is connected to the air duct 33 through the plurality of fifth through holes.

[0091] Furthermore, such as Figure 4 , Figure 5 , Figure 6 and Figure 7 As shown, the fifth resonant cavity is a rectangular hollow cavity with a depth of 95mm~100mm in the Y direction and a width of 200mm~300mm in the Z direction. The fifth substrate 380 has a thickness of 2mm, and the fifth through hole has a circular cross-section and a diameter of 3mm, arranged in a 30mm×30mm square array. The peak sound absorption of the third resonant module 38 is approximately 225±2Hz.

[0092] Specifically, the fourth resonant module 39 includes a sixth substrate 390 and a sixth support housing 391. The sixth substrate 390 is disposed at the sixth opening end of the sixth support housing 391, and the sixth substrate 390 has a plurality of sixth through holes arranged in an array and penetrating the sixth substrate 390. The sixth support housing 391 has a concave cross-section, and the sixth support housing 391 is installed on the side of the sixth substrate 390 near the second housing 35, and together with the sixth substrate 390, forms a sixth resonant cavity, which is connected to the air duct 33 through the plurality of sixth through holes.

[0093] Furthermore, such as Figure 4 , Figure 5 , Figure 6 and Figure 7As shown, the sixth resonant cavity is a rectangular hollow cavity. Its length in the X direction is approximately the same as the length of the frame 34. The depth of the sixth resonant cavity in the Y direction is 80±2mm, and its width in the Z direction is 120mm~180mm. The sixth substrate 390 has a thickness of 2mm, and the cross-section of the sixth through-hole is circular with a diameter of 4mm, arranged in a 20mm×20mm square array. The peak sound absorption of the fourth resonant module 39 is approximately 450±2Hz.

[0094] In other alternative embodiments, the number of resonant modules can be set to 4 pairs, depending on the frequency range of the noise in the applicable context. Figure 4 The number of resonance modules in the system is 4 pairs, 5 pairs, or 6 pairs or more, but the specific number is not limited here.

[0095] When selecting a motor-pump combination of a 1500rpm motor and a 9-piston hydraulic pump, the peak frequency of the noise sound pressure level generated during operation is approximately 225±2Hz and its harmonics (generally the first 4 harmonics). Four pairs of resonant cavities are set up, with at least two resonant cavities in each pair arranged opposite each other on both sides of the air duct 33 and arranged in the height direction of the air duct. The order of arrangement is not limited. The larger the area of ​​the first substrate of the resonant module (e.g., the third substrate 360 ​​of the first resonant module 36, the fourth substrate 370 of the second resonant module 37, the fifth substrate 380 of the third resonant module 38, and the sixth substrate 390 of the fourth resonant module 39), the better the sound absorption effect.

[0096] According to an embodiment of this application, the sound-absorbing unit includes a perforated mesh 40. The perforated mesh 40 is mounted on the frame 34 and forms a sound-absorbing cavity 41 between itself and the second housing 35. The sound-absorbing cavity 41 is filled with sound-absorbing material to absorb sound energy in a second frequency band, the frequency of which is greater than 1000Hz.

[0097] In some illustrative embodiments, the sound-absorbing material may be, for example, sound-absorbing cotton.

[0098] In this implementation, the perforated mesh 40 can have an opening ratio greater than 80%, serving two purposes: firstly, to support and fix the sound-absorbing cotton; and secondly, to form the inner wall of the air duct 33 together with the first substrate of the resonant unit. The sound-absorbing unit is used to absorb sound energy in the second frequency band, such as absorbing noise in the ventilation airflow within the frequency range greater than 1000Hz.

[0099] Figure 8 yes Figure 5 Cross-sectional view in the CC direction.

[0100] According to embodiments of this application, such as Figure 4 and Figure 8As shown, each silencing mechanism 3 also includes multiple blades 7. These blades 7 are spaced apart and arranged parallel to each other between the frame 34 and the first air outlet 31, forming a flow channel between adjacent blades 7 that allows ventilation airflow. Each blade 7 includes a connecting section 71 and an extension section 72. The connecting section 71 is connected to the frame 34, and its extension direction is parallel to the direction in which the ventilation airflow exits the first air outlet 31. The extension section 72 is connected to the connecting section 71, and an angle of 120° to 150° is formed between the extension section 72 and the connecting section 71 to reflect and interfere with sound waves.

[0101] In this embodiment, each blade 7 has a "V" shaped cross-section, and the connection between the connecting section 71 and the extension section 72 (i.e., the "V" shaped corner position) is an arc connection. The end of the connecting section 71 near the air duct 33 is parallel to the direction in which the ventilation airflow exits the first air outlet 31 (e.g., ...). Figure 4 (Y direction shown). As the ventilation airflow passes through multiple blades 7, the sound waves are reflected and interfered with multiple times, increasing the acoustic impedance and thus reducing noise propagation to a certain extent.

[0102] According to embodiments of this application, such as Figure 2 As shown, the first housing 2 has a receiving cavity, and the hydraulic pump station also includes a temperature sensor 4, a fan 5, and a controller. The temperature sensor 4 is located inside the receiving cavity and is used to detect the actual temperature inside the receiving cavity. The fan 5 is installed at the second air outlet 32 ​​of either of the two silencing mechanisms 3. The controller is electrically connected to the temperature sensor 4 and the fan 5, and is used to adjust the speed of the fan 5 based on the actual temperature and a preset temperature.

[0103] Specifically, temperature sensor 4 collects the actual temperature of hydraulic pump unit 1 in real time and converts it into an electrical signal, which is then transmitted to the controller. The controller compares the actual temperature fed back by temperature sensor 4 with the preset temperature and calculates the temperature difference. If the actual temperature is higher than the preset temperature, the controller increases the speed of fan 5 to enhance heat dissipation. If the actual temperature is lower than the preset temperature, the controller decreases the speed of fan 5 to reduce heat dissipation and noise generated by fan 5 itself. When the actual temperature and the preset temperature tend to be consistent, the current speed of fan 5 is maintained to stabilize the temperature.

[0104] In this implementation, automatic closed-loop regulation of the temperature inside the first housing 2 can be achieved, which reduces the energy consumption and noise of the fan 5 while ensuring heat dissipation.

[0105] According to embodiments of this application, such as Figure 2As shown, the hydraulic pump station also includes a second support housing and a second base plate 6. The second support housing has a concave cross-section and is installed on the inner wall of the first housing 2. The second support housing has a second open end facing the hydraulic pump assembly 1. The second base plate 6 is disposed at the second open end and forms a second resonant cavity with the second support housing. The second base plate 6 has a plurality of second through holes arranged in an array and penetrating the second base plate 6. The second resonant cavity communicates with the receiving cavity through the plurality of second through holes to reduce the radiated noise of the hydraulic pump assembly 1.

[0106] In some illustrative embodiments, the second substrate 6 can serve as a low-frequency sound-absorbing plate within the first housing 2. The depth, perforation diameter, thickness, and perforation rate of the second resonant cavity of the low-frequency sound-absorbing plate can be determined according to the aforementioned formula (1) and configured to match the peak frequency of the low-frequency noise generated by the hydraulic pump assembly 1. On the one hand, the low-frequency sound-absorbing plate can absorb the direct low-frequency noise from the motor pump assembly; on the other hand, it can block the direct noise that originally reached the inner wall of the first housing 2, so that this part of the noise is absorbed, reflected, and attenuated multiple times before propagating to the inner wall of the first housing 2, thereby reducing the total sound pressure level inside the first housing 2 and ultimately reducing the radiated noise outside the first housing 2.

[0107] Figure 9 This is a transmission loss curve of a noise reduction mechanism according to an illustrative embodiment of this application.

[0108] In some illustrative embodiments, such as Figure 2 , Figure 3 and Figure 4 As shown, the silencing mechanism 3 located at the exhaust vent is used as an example for explanation. For a motor-pump combination of a 1500rpm motor and a 9-piston hydraulic pump, the peak frequency of the noise sound pressure level generated during operation is approximately 225±2Hz and its 2nd, 3rd, and 4th harmonics. During operation, the generated noise sound waves diffuse outward in a spherical form. A portion of the sound waves enters the air duct 33 and is transmitted to the outside. The sound waves enter the air duct 33 of the silencing mechanism 3 from inside the first housing 2 through the second air vent 32. Inside the air duct 33, the sound waves first pass through the resonance zone composed of two sets of resonant units. Since the resonant units are designed with corresponding resonant modules for frequency ranges such as 225±2Hz, 450±2Hz, 675±2Hz, and 900±2Hz, when the sound wave frequency is close to the natural frequency of these resonant modules, a strong air column vibration will be generated at the neck of the first substrate of the resonant module, consuming the sound energy of the corresponding frequency range and achieving targeted sound absorption through resonance. Figure 9As shown, the transmission loss peaks at 225Hz, 450Hz, 675Hz, and 900Hz, indicating that the silencing mechanism 3 is highly effective at reducing these low-frequency peak noises. In the mid-to-high frequency range above 1000Hz, the transmission loss is relatively stable and gradually increases, corresponding to the absorption effect of the sound-absorbing unit on mid-to-high frequency noise. The distance design between the two resonant units (e.g., 180mm~300mm) ensures sufficient sound energy dissipation while maintaining good ventilation performance.

[0109] Subsequently, the ventilation airflow carrying sound waves enters the sound-absorbing zone composed of sound-absorbing units. The sound-absorbing material in the zone has a good absorption effect on mid-to-high frequency noise above 1000Hz. Simultaneously, the ventilation airflow undergoes a right-angle turn within the "7"-shaped duct, and as it flows through multiple blades, the sound waves experience multiple reflections and interferences, further dissipating sound wave energy. Finally, the airflow and sound waves, after multiple noise reduction treatments, are output to the external environment through the first vent 31. By combining this resonant targeted sound absorption with mid-to-high frequency sound absorption, and in conjunction with optimized airflow path, efficient reduction of hydraulic pump station noise, especially low-frequency peak frequency noise, is achieved, resolving the conflict between ventilation and sound insulation.

[0110] According to the embodiment of this application, the hydraulic pump station, with its first housing 2 and silencing mechanism 3 working together, provides sound insulation, noise reduction, and heat dissipation for the hydraulic pump unit 1. First, a low-frequency sound-absorbing panel installed inside the first housing 2 absorbs low-frequency noise at its peak frequency within the hydraulic pump station, and blocks and reflects direct full-frequency noise, thereby reducing the overall sound pressure level inside the first housing 2. Then, the hydraulic pump unit 1 is enclosed in a three-dimensional enclosure composed of the first housing 2 and the silencing mechanism 3 for sound insulation and noise reduction. On one hand, the first housing 2 blocks direct noise from the low, medium, and high frequency bands of the hydraulic pump station. On the other hand, the silencing mechanism 3 absorbs emitted noise from the low, medium, and high frequency bands that attempts to leak through the air duct 33. This design enhances the low-frequency sound insulation effect of the first housing 2 while retaining good heat dissipation capacity within it. Simultaneously, combined with automatic temperature control, it achieves synergistic optimization of heat dissipation and noise reduction, and features a compact structure and excellent noise reduction effect, making it particularly suitable for underground construction equipment such as tunnel boring machines where noise control requirements are stringent.

[0111] Those skilled in the art will understand that the features described in the various embodiments and / or claims of this application can be combined or combined in various ways, even if such combinations or combinations are not explicitly described in this application. In particular, the features described in the various embodiments and / or claims of this application can be combined and / or combined in various ways without departing from the spirit and teachings of this application. All such combinations and / or combinations fall within the scope of this application.

[0112] It should also be noted that the directional terms mentioned in the embodiments, such as "up," "down," "front," "back," "left," and "right," are only for reference to the directions in the accompanying drawings and are not intended to limit the scope of protection of this application. Throughout the drawings, the same elements are represented by the same or similar reference numerals. Conventional structures or constructions will be omitted where they may cause confusion in understanding this application, and the shapes and sizes of the components in the drawings do not reflect actual size and proportion, but only illustrate the content of the embodiments of this application.

[0113] Unless otherwise stated, the numerical parameters in this specification and the appended claims are approximate values ​​and can be varied according to desired characteristics derived from the content of this application. Specifically, all figures used in the specification and claims to indicate composition, reaction conditions, etc., should be understood to be modified by the term "about" in all cases. Generally, this means that a specific amount may vary by ±10% in some embodiments, ±5% in some embodiments, ±1% in some embodiments, and ±0.5% in some embodiments.

[0114] The use of ordinal numbers such as "first," "second," "third," etc., in the specification and claims to modify the corresponding elements does not imply that the element has any ordinal number, nor does it represent the order of one element with another element, or the order of manufacturing methods. The use of these ordinal numbers is only to enable a named element to be clearly distinguished from another element with the same name.

[0115] Furthermore, unless specifically described or required to occur in a specific order, the order of the above steps is not limited to those listed above and can be varied or rearranged according to the desired design. Moreover, the above embodiments can be used in combination with each other or with other embodiments based on design and reliability considerations; that is, technical features from different embodiments can be freely combined to form more embodiments.

[0116] The embodiments of this application have been described above. However, these embodiments are merely illustrative and not intended to limit the scope of this application. Although various embodiments have been described above, this does not mean that the measures in the various embodiments cannot be used advantageously in combination. The scope of this application is defined by the appended claims and their equivalents. Various substitutions and modifications can be made by those skilled in the art without departing from the scope of this application, and all such substitutions and modifications should fall within the scope of this application.

Claims

1. An underground construction device, characterized in that, include: Tunnel boring machine; Hydraulic pump station, including: A hydraulic pump unit, suitable for providing hydraulic power to the tunnel boring machine; A first housing is adapted to accommodate the hydraulic pump assembly, and an air inlet and an air outlet are provided on the first housing. Two silencing mechanisms are respectively disposed at the air inlet and the air outlet, and both silencing mechanisms partially extend into the first housing. Each silencing mechanism has a first air outlet and a second air outlet, and an air duct is formed between the first air outlet and the second air outlet. Each silencing mechanism includes: Two sets of resonant units are symmetrically arranged on both sides of the air duct. The two sets of resonant units are configured to consume the acoustic energy of the first frequency band of the sound waves by resonating with the sound waves generated by the hydraulic pump group. The sound-absorbing unit is configured to absorb the sound energy of a second frequency band in the sound wave, the frequency of which is greater than the frequency of the first frequency band.

2. The underground construction device according to claim 1, characterized in that, Each of the aforementioned silencing mechanisms further includes: Frame; The second housing is installed on the outside of the frame, the bottom of the second housing forms the second air vent, and the side wall of the second housing forms the first air vent; Two sets of resonant units are symmetrically arranged on opposite sides of the frame along the width direction. The sound-absorbing unit is located downstream of the airflow direction and close to the first air outlet, so that the two sets of resonant units, the sound-absorbing unit and the second housing together form a bent air duct, so that the airflow flowing in from the second air outlet turns at a right angle and is output to the outside through the first air outlet.

3. The underground construction device according to claim 2, characterized in that, Each group of resonant units includes: Four resonant modules are arranged along the height direction on the frame. Each resonant module has a first open end, and the first open end faces the air duct. The four resonant modules have different sound absorption peak values, so as to consume the sound energy of different frequency bands in the first frequency band when resonating with the sound wave.

4. The underground construction device according to claim 3, characterized in that, Each of the resonant modules includes: A first substrate is disposed at the first opening end, and a plurality of first through holes arranged in an array and penetrating the first substrate are formed on the first substrate; The first support housing has a concave cross-section. The first support housing is installed on the side of the first substrate near the second housing and forms a first resonant cavity with the first substrate. The first resonant cavity is connected to the air duct through a plurality of first through holes.

5. The underground construction device according to claim 4, characterized in that, The space between the first support housing and the second housing is filled with sound-insulating material to absorb the noise generated by the vibration of the first support housing.

6. The underground construction device according to claim 4, characterized in that, The four resonant modules are, in sequence, a first resonant module, a second resonant module, a third resonant module, and a fourth resonant module along the flow direction of the ventilation airflow. The sound absorption peak value of the first resonant module is 900±2Hz, the sound absorption peak value of the second resonant module is 675±2Hz, the sound absorption peak value of the third resonant module is 225±2Hz, and the sound absorption peak value of the fourth resonant module is 450±2Hz.

7. The underground construction device according to claim 6, characterized in that, The sound-absorbing unit includes: A perforated mesh is installed on the frame and forms a sound-absorbing cavity between it and the second housing. The sound-absorbing cavity is filled with sound-absorbing material to absorb sound energy in the second frequency band, which has a frequency greater than 1000Hz.

8. The underground construction device according to claim 2, characterized in that, Each of the aforementioned silencing mechanisms further includes: Multiple blades are arranged parallel to each other at intervals between the frame and the first air outlet, and adjacent blades form a flow channel that allows the ventilation airflow to pass through. Each blade includes: A connecting section is connected to the frame, and the extending direction of the connecting section is parallel to the direction in which the ventilation airflow exits the first air outlet; An extension section is connected to the connecting section, and the extension section and the connecting section form an angle of 120° to 150° to reflect and interfere with the sound waves.

9. The underground construction device according to claim 1, characterized in that, The first housing has a receiving cavity, and the hydraulic pump station further includes: A temperature sensor is disposed inside the receiving cavity and is suitable for detecting the actual temperature inside the receiving cavity; A fan is installed at the second air outlet of either of the two silencing mechanisms; The controller, electrically connected to the temperature sensor and the fan, is adapted to adjust the fan speed based on the actual temperature and a preset temperature.

10. The underground construction device according to claim 9, characterized in that, The hydraulic pump station also includes: The second support housing has a concave cross-section and is installed on the inner wall of the first housing. The second support housing has a second open end facing the hydraulic pump assembly. The second substrate is disposed at the second opening end and forms a second resonant cavity with the second support housing. The second substrate has a plurality of second through holes arranged in an array and penetrating the second substrate. The second resonant cavity is connected to the receiving cavity through the plurality of second through holes to reduce the radiated noise of the hydraulic pump assembly.

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