Noise reduction compressor

Abstract

The invention discloses a noise reduction compressor. The noise reduction compressor is provided with an exhaust end. A silencing channel is arranged in the exhaust end; a compressed working medium generated by the noise reduction compressor flows through the noise reduction channel; a plurality of silencing modules are sequentially arranged on the side wall of the silencing channel in the moving direction of the compressed working medium; the exhaust end is provided with an adjusting device; and the adjusting device is used for changing the position of the compressed working medium entering the silencing channel so as to change the number of the compressed working medium passing through the silencing module. According to the noise reduction compressor, the noise reduction compressor can adapt to different working conditions, and the noise reduction effect and the operation efficiency are both considered.

Description

Technical Field

[0001] This invention relates to the field of compressors, and more particularly to a noise-reducing compressor. Background Technology

[0002] When a screw compressor operates, the male and female rotors mesh continuously, pushing the compressed working fluid from the intake end to the exhaust end. When a pair of inter-tooth volumes connects to the exhaust port, the compressed working fluid within is suddenly released, and then the volume closes, causing a sharp drop in pressure. The next pair of inter-tooth volumes immediately connects to the exhaust port, and the pressure suddenly rises again. This periodic pressure release and reconstruction generates strong periodic airflow pulsations at the exhaust port, constituting the low-frequency portion of the most concentrated energy in broadband noise. High-pressure compressed working fluid is injected at high speed from the narrow inter-tooth volumes through gaps at the exhaust port edge into the relatively low-pressure exhaust chamber or pipeline. This high-speed jet generates injection noise and turbulence noise. These two types of noise superimpose and are amplified through possible structural resonance, ultimately forming complex noise at the screw compressor exhaust port. This noise travels far and penetrates deeply, deteriorating the working environment and potentially causing hearing damage and fatigue. Therefore, noise reduction is crucial.

[0003] To reduce noise, existing screw compressors have silencer modules installed at their exhaust ends. However, since the displacement of screw compressors changes according to actual needs, the existing silencer modules cannot adapt to the different displacements of screw compressors, resulting in poor noise reduction. Summary of the Invention

[0004] In order to overcome the shortcomings of the prior art, the present invention provides a noise-reducing compressor with the advantages of strong noise reduction adaptability and good effect.

[0005] To achieve the above objectives, the present invention adopts the following technical solution: A noise-reducing compressor has an exhaust end; the exhaust end has a silencing channel; the compressed working fluid generated by the noise-reducing compressor flows through the silencing channel; a plurality of silencing modules are sequentially arranged on the side wall of the silencing channel along the moving direction of the compressed working fluid; an adjustment device is installed on the exhaust end; the adjustment device is used to change the position of the compressed working fluid entering the silencing channel, thereby changing the number of silencing modules through which the compressed working fluid passes.

[0006] By adopting the above technical solution, when the compressor discharges, the compressed working fluid enters the silencer channel, where silencer modules distributed along its flow path attenuate the noise generated by airflow pulsation and high-speed jets in stages. The adjustment device can flexibly adjust the specific position of the compressed working fluid entering the silencer channel according to actual operating conditions, such as the compressor's discharge volume or the required noise reduction effect. When a stronger noise reduction effect is needed, the adjustment device can be used to allow the compressed working fluid to enter from a higher position in the silencer channel, thus passing through more silencer modules, allowing the noise to be sufficiently weakened through a longer propagation path and the action of more silencer modules. In scenarios where noise reduction requirements are not high but exhaust efficiency must be guaranteed, the entry position of the compressed working fluid can be adjusted to reduce the number of silencer modules it passes through, reducing exhaust resistance while meeting basic noise reduction needs, achieving a dynamic balance between noise reduction effect and exhaust performance. This design allows the noise-reducing compressor to adapt to different operating conditions, balancing noise reduction effect and operating efficiency, thereby making central air conditioning or refrigeration equipment using this noise-reducing compressor more energy-efficient.

[0007] Optionally, the silencing channel has a silencing flow path; the silencing flow path is used for the flow of compressed working fluid; the silencing module is disposed on the side wall of the silencing flow path; the plane in which the silencing flow path is located is perpendicular to the axial direction of the noise reduction compressor.

[0008] By adopting the above technical solution, the plane of the silencer channel is perpendicular to the compressor axis, making the flow direction of the compressed working fluid within the silencer channel perpendicular to the compressor axis, forming a radial flow path. This layout ensures that the silencer module can effectively contact and act on the airflow, while also helping to optimize the overall structural space of the compressor exhaust end. When the compressed working fluid is discharged from the compressor axis, it needs to turn and enter the silencer channel in the vertical plane. This turning process itself can also buffer the pulsation of the airflow. At the same time, the design structure of a single silencer channel is relatively simple, facilitating processing, manufacturing, installation, and maintenance. The silencer modules are centrally located on the side wall of this single silencer channel, which also facilitates centralized control and optimization of the silencer effect.

[0009] Optionally, the noise-reducing compressor includes a noise-reducing compressor body and a silencer barrel; the noise-reducing compressor body has a connecting end; the silencer barrel is detachably connected to the connecting end; and the silencer flow channel is formed between the connecting end and the silencer barrel.

[0010] By adopting the above technical solution, the connection between the silencer and the noise-reducing compressor body is detachable, such as by threaded connection, snap-fit ​​connection, or flange connection. This greatly facilitates the cleaning and maintenance of the silencer channel and the replacement of the silencer module. When it is necessary to clean the inside of the silencer channel to remove accumulated dust or impurities to avoid affecting the silencer effect and the flow efficiency of the compressed working fluid, or when the silencer module needs to be replaced due to aging and performance degradation after long-term use, it is only necessary to disassemble the silencer from the connection end. The silencer channel formed between the connection end and the silencer can be operated directly without the need for complex disassembly of the compressor body, significantly reducing maintenance difficulty and cost. At the same time, this detachable structure also makes it possible to replace silencers of different specifications or types (which can form silencer channels with different structures or configurations of different silencer modules) according to different noise reduction requirements, enhancing the flexibility and adaptability of the compressor.

[0011] Optionally, the silencing channel has at least two silencing channels; the silencing channels are used for the flow of compressed working fluid; the silencing module is disposed on the side wall of the silencing channel; the plane in which the silencing channel is located is perpendicular to the axial direction of the noise reduction compressor; a plurality of the silencing channels are distributed sequentially along the axial direction of the noise reduction compressor.

[0012] By adopting the above technical solution, at least two silencer channels are sequentially distributed along the compressor axis, and the plane of each silencer channel is perpendicular to the compressor axis. This allows the compressed working fluid to pass through multiple axially distributed radial silencer channels sequentially during exhaust, forming a multi-stage silencer structure. Compared to a single silencer channel, multiple sequentially distributed silencer channels provide a longer silencer path and more opportunities for the silencer modules to function, thus significantly enhancing the overall noise reduction effect. Each silencer channel has a silencer module on its sidewall. As the compressed working fluid flows out of one silencer channel and into the next, noise is gradually attenuated in each stage of the silencer channel. Especially for specific frequency noises that are difficult to completely eliminate with a single silencer channel, the synergistic effect of multiple silencer channels can more effectively suppress them. Furthermore, the design of multiple silencer channels provides a richer adjustment dimension for subsequently changing the number of silencer modules the compressed working fluid passes through via an adjustment device, making the adjustment of the noise reduction effect more precise and flexible.

[0013] Optionally, the noise-reducing compressor includes a noise-reducing compressor body, at least one silencer seat, and a silencer barrel; the noise-reducing compressor body has a connecting end; the silencer seat is detachably connected between the connecting end and the noise-reducing compressor body; a silencer flow channel is provided between the silencer seat and the connecting end; a silencer flow channel is provided between the silencer seat and the silencer barrel; when the number of silencer seats is greater than or equal to two, a silencer flow channel is provided between adjacent silencer seats.

[0014] By adopting the above technical solution, the design allows for the detachable connection of the muffler base between the connection end and the compressor body, as well as between the muffler base and the muffler barrel, and between adjacent muffler bases, forming a muffler flow channel. This achieves modular expansion of the number of muffler flow channels. Users can flexibly choose the number of muffler bases according to their actual noise reduction needs: when a stronger noise reduction effect is required, the number of muffler bases can be increased to increase the number of muffler flow channel stages; if the noise reduction requirements are moderate or a more compact structure is desired, the number of muffler bases can be reduced. This modular assembly method not only facilitates manufacturing—each component can be processed independently and then combined—but also greatly improves the convenience of later maintenance and upgrades. For example, when a muffler module in a certain stage of the muffler flow channel needs maintenance or replacement, only the corresponding muffler base needs to be removed without affecting other parts; if noise reduction performance needs to be upgraded, it can also be easily achieved by adding more muffler bases without large-scale modification of the entire compressor exhaust end structure, effectively reducing maintenance and upgrade costs, and also enhancing the product's adaptability to different application scenarios.

[0015] Optionally, the silencing channel has an inlet chamber, an outlet chamber, and a gas passage connecting the inlet chamber and the outlet chamber; the silencing module is disposed on the side wall of the gas passage; the exhaust end has a first inlet channel; the first inlet channel is parallel to the axial direction of the noise-reducing compressor; the first inlet channel penetrates the side wall of the inlet chamber of all the silencing channels; the adjusting device includes an adjusting block slidably disposed in the first inlet channel and an adjusting drive mechanism for adjusting the position of the adjusting block; the outlet chamber is used for discharging the compressed working fluid.

[0016] By adopting the above technical solution, the internal structure of the silencing channel is divided into an intake chamber, a gas passage, and an exhaust chamber. After the compressed working fluid enters from the intake chamber, it must flow through the gas passage equipped with the silencing module before entering the exhaust chamber and finally being discharged. This ensures that the high-speed airflow and noise can fully contact the silencing module within the gas passage, guaranteeing that the noise attenuation effect of the silencing module is effectively utilized. The first intake channel is arranged parallel to the compressor axis and penetrates the sidewall of the intake chamber of all silencing channels, providing a unified channel for the compressed working fluid to enter each intake chamber. Adjusting the sliding of the plug within the first intake channel allows for precise control of its blocking status at the sidewall openings of different intake chambers. For example, when the adjusting drive mechanism moves the adjusting block to block the inlets of several downstream intake chambers, the compressed working fluid can only enter the corresponding gas passage from the unblocked upstream intake chambers, thus reducing the number of muffler modules the compressed working fluid passes through. Conversely, if the adjusting block moves open the inlets of more intake chambers, the compressed working fluid can enter more intake chambers and flow through more gas passages and muffler modules. This structural design allows for continuous adjustment of the position and quantity of the compressed working fluid entering the muffler passage through a single adjusting block. The control method is simple and efficient, and it can be steplessly adjusted according to actual operating conditions (such as exhaust volume and noise level requirements), further improving the accuracy of the dynamic balance between noise reduction and exhaust efficiency.

[0017] Optionally, the air outlet chambers of all the said silencer channels are interconnected.

[0018] By adopting the above technical solution, the exhaust chambers of all the silencer channels are interconnected, allowing the compressed working fluid processed by each silencer channel to be collected and discharged together. This design simplifies the exhaust structure of the silencer, eliminating the need for a separate exhaust port for each silencer channel. Instead, all exhaust chambers are connected through a common connecting space for unified exhaust. This not only reduces the number of exhaust ports, lowering structural complexity and manufacturing costs, but also avoids airflow interference and additional noise that may be generated by multiple independent exhaust ports. Simultaneously, the interconnected exhaust chambers also act as a buffer, allowing the compressed working fluid flowing from different silencer channels to transition smoothly when merging, reducing turbulent noise caused by differences in airflow velocity or sudden changes in direction, further improving the overall noise reduction effect. Furthermore, the unified exhaust channel facilitates the subsequent installation of auxiliary components such as exhaust shut-off valves at the exhaust end, enabling unified control of the entire compressor's exhaust process.

[0019] Optionally, the noise reduction channel is S-shaped.

[0020] By adopting the above technical solution, the S-shaped silencing channel design significantly extends the flow path of the compressed working fluid within the silencing channel. As the compressed working fluid flows through the S-shaped gas passage, its flow direction constantly changes. This tortuous path greatly increases the contact time and area between the airflow and the silencing module, allowing the silencing module to more effectively absorb and attenuate airflow pulsations and noise. Simultaneously, the S-shaped structure forces high-speed airflow to generate vortices and collisions during its turning process, consuming the kinetic energy of the airflow and reducing its speed, thereby reducing jet noise and turbulence noise caused by the high-speed jet. Furthermore, the S-shaped channel can utilize the principles of sound wave reflection and interference during propagation, causing some noise to reflect back and forth within the channel and cancel each other out, further enhancing the silencing effect. Compared to a straight channel, the S-shaped channel provides a longer silencing path and a more complex acoustic environment within the same space, effectively improving noise reduction efficiency per unit space, allowing the silencing channel to perform excellent silencing effects while maintaining a compact structure.

[0021] Optionally, the exhaust end has a plurality of second intake channels; the second intake channels are parallel to the axial direction of the noise reduction compressor; the second intake channels penetrate the sidewalls of all the silencer flow channels; the plurality of second intake channels are distributed sequentially along the flow direction of the compressed working fluid; the adjusting device includes a plurality of adjusting mechanisms; the adjusting mechanisms correspond one-to-one with the second intake channels; the adjusting mechanism includes an opening and closing block slidably disposed in the second intake channel and an opening and closing component for adjusting the position of the opening and closing block.

[0022] By adopting the above technical solution, several second air intake channels are sequentially distributed along the flow direction of the compressed working fluid and all penetrate the sidewalls of all silencer channels. Each second air intake channel corresponds to an independent adjustment mechanism, making the adjustment of the position of the compressed working fluid entering the silencer channel more precise and independent. When the opening and closing mechanism of a certain adjustment mechanism drives the opening and closing block to slide within the corresponding second air intake channel, the opening or closing state of that second air intake channel can be controlled independently. This multi-channel independent adjustment method avoids the adjustment range limitations that may occur with a single adjustment block, enabling step-like precise control of the position of the compressed working fluid entering the channel. It meets the precise requirements for the number of specific silencer modules under different operating conditions, further improving the flexibility and reliability of the adjustment.

[0023] Optionally, the noise-reducing compressor has different set displacement levels; different set displacement levels correspond to different numbers of opening second intake channels; the larger the set displacement, the more second intake channels are opened; the plurality of second intake channels are opened sequentially along the direction away from the outlet end of the muffler flow channel; when a second intake channel is opened, the second intake channel adjacent to it and close to the outlet end of the muffler flow channel is in the open state.

[0024] By adopting the above technical solution, the set displacement of the noise-reducing compressor is correlated with the number and sequence of opening the second intake channels, achieving intelligent control that automatically matches the optimal noise reduction scheme according to the actual operating load of the compressor. When the compressor operates at a larger set displacement, its exhaust volume increases accordingly, and the noise energy generated is also higher. At this time, the system automatically opens more of the second intake channels, and the opening sequence follows the order of starting from the outlet end (i.e., further upstream) closest to the silencer channel, ensuring that the adjacent downstream channels of the opened channels are simultaneously open. For example, if the set displacement increases to the point where three second intake channels need to be opened, the system will first open the first upstream channel, then the second, and then the third. When the third channel is opened, the second and first channels remain open, allowing the compressed working fluid to enter the silencer channel from multiple upstream positions, flowing through more silencer modules, ensuring that the strong noise under large displacement is sufficiently attenuated. Conversely, when the set displacement is reduced, the system closes the downstream portion of the second intake passage, reducing the number of silencer modules the compressed working fluid passes through and lowering exhaust resistance to ensure exhaust efficiency. This control logic, linked to the displacement setting, automatically achieves dynamic adaptation between noise reduction and exhaust performance without manual intervention. This greatly improves the compressor's operating economy and applicability under different load conditions, while also simplifying user operation and ensuring the compressor always operates at its optimal state. Attached Figure Description

[0025] Figure 1 This is a structural schematic diagram of Embodiment 1 of the present invention.

[0026] Figure 2 This is the invention Figure 1 A schematic diagram of a partial cross-sectional structure.

[0027] Figure 3 This is the invention Figure 1 A schematic diagram of the cross-sectional structure of AA.

[0028] Figure 4 This is a schematic diagram of the structure of Embodiment 2 of the present invention.

[0029] Figure 5 This is the invention Figure 4 A schematic diagram of a partial cross-sectional structure.

[0030] Figure 6 This is the invention Figure 4 A schematic diagram of the cross-sectional structure of BB.

[0031] Explanation of reference numerals in the attached figures: 10. Exhaust end; 100. Muffler channel; 101. Second intake channel; 102. Intake chamber; 103. Gas passage; 104. Exhaust chamber; 105. First intake channel; 11. Muffler module; 20. Compressor body; 200. Exhaust chamber; 21. Connecting end; 210. First silencer groove; 30. Silencer barrel; 300. Second silencer groove; 40. Adjusting device; 41. Opening and closing assembly; 42. Opening and closing block; 43. Adjusting drive mechanism; 44. Adjusting block; 50. Exhaust shut-off valve; 60. Silencing base; 600. Third silencing groove; 601. Fourth silencing groove. Detailed Implementation

[0032] The following is in conjunction with the appendix Figures 1-6 The present invention will be described in further detail below.

[0033] Example 1: A noise-reducing compressor is disclosed, applicable to energy-saving central air conditioning or energy-saving refrigeration equipment, used for compressing the working fluid, i.e., compressing gaseous refrigerant; Reference Figures 1-3 The system includes a compressor body 20, a silencer 30, an adjusting device 40, and an exhaust shut-off valve 50. The compressor body 20 has a connecting end 21. The axial direction of the compressor body 20 is the axial direction of the noise-reducing compressor. The silencer 30 is connected to the connecting end 21 to form the exhaust end 10 of the noise-reducing compressor. A silencer channel is provided in the exhaust end 10. The compressed working fluid discharged from the compressor body 20 passes through the exhaust chamber 200 of the compressor body 20 and the silencer channel in sequence and is discharged from the exhaust shut-off valve 50 installed on the silencer 30. The exhaust shut-off valve 50 is connected to an external air-using device. In order to achieve noise reduction, a number of silencer modules 11 are arranged in sequence on the side wall of the silencer channel along the movement direction of the compressed working fluid. The silencer modules 11 adopt micro-perforated plate silencers. All the silencer modules 11 are divided into several groups, and each group of silencer modules 11 is designed for noise in different frequency bands. The adjusting device 40 is used to change the position of the compressed working fluid entering the silencer channel, thereby changing the number of silencer modules 11 that the compressed working fluid passes through.

[0034] refer to Figures 1-3A first silencing groove 210 is formed on the end face of the connecting end 21 near the muffler 30, and a second silencing groove 300 that mates with the first silencing groove 210 is formed on the end face of the muffler 30 near the connecting end 21. The first silencing groove 210 and the second silencing groove 300 form a silencing channel 100. For ease of subsequent description, the silencing channel 100 has an air inlet chamber 102, an air outlet chamber 104, and a gas passage 103 connecting the air inlet chamber 102 and the air outlet chamber 104. The air outlet chamber 104 is connected to the air inlet end of the exhaust shut-off valve 50. The silencing channel 100 is the silencing channel. The silencing module 11 is set on the side wall of the first silencing groove 210 away from the muffler 30. Alternatively, the silencing module 11 can be set on the side wall of the second silencing groove 300 away from the connecting end 21. To maximize noise reduction within a limited space, the silencing channel 100 is S-shaped. Compared to a straight channel, the S-shaped channel provides a longer silencing path and a more complex acoustic environment within the same space, effectively improving noise reduction efficiency per unit space. This allows the silencing channel to perform excellent silencing work despite its compact structure. The plane containing the silencing channel 100 is perpendicular to the axis of the noise-reducing compressor.

[0035] After a period of use, the noise reduction capability of the noise reduction module 11 will inevitably decrease. If the noise reduction module 11 cannot be replaced or repaired at this time, the noise reduction function will be greatly affected. Therefore, the noise reduction barrel 30 and the connection end 21 are designed to be detachably connected. The specific connection method can be a snap-fit ​​connection or a flange connection. This makes it easy for the noise reduction barrel 30 to be opened to expose the noise reduction module 11, so as to facilitate the replacement or repair of the noise reduction module 11.

[0036] refer to Figures 1-3 The exhaust end 10 has three second intake channels 101, which are parallel to the axial direction of the noise reduction compressor. The second intake channels 101 penetrate the side wall of the silencer flow channel 100. The three second intake channels 101 are distributed sequentially along the flow direction of the compressed working fluid. The regulating device 40 includes three regulating mechanisms. Each regulating mechanism corresponds to one of the second intake channels 101. Each regulating mechanism includes an opening and closing block 42 that is slidably disposed in the second intake channel 100 and an opening and closing assembly 41 for adjusting the position of the opening and closing block 42. The opening and closing assembly 41 is a hydraulic cylinder. For ease of subsequent explanation, the three second air intake channels 101 are defined sequentially as the downstream channel, midstream channel, and upstream channel along the direction away from the exhaust chamber 104 of the muffler duct 100. That is, the downstream channel is closest to the exhaust chamber 104 of the muffler duct 100, the upstream channel is farthest from the exhaust chamber 104 of the muffler duct 100, and the midstream channel is located between the downstream channel and the upstream channel. At the same time, the regulating mechanism that cooperates with the downstream channel is defined as the downstream regulating mechanism, the regulating mechanism that cooperates with the midstream channel is defined as the midstream regulating mechanism, and the regulating mechanism that cooperates with the upstream channel is defined as the upstream regulating mechanism.

[0037] During operation, when the compressor displacement is 50%, the opening and closing component 41 of the downstream regulating mechanism moves the opening and closing block 42 away from the compressor body 20, thereby opening the downstream channel. The compressed working fluid flows through the gas passage 103 between the downstream channel and the outlet chamber 104. When the compressor displacement is 75%, while the downstream channel is open, the opening and closing component 41 of the midstream regulating mechanism moves the opening and closing block 42 away from the compressor body 20, opening the midstream channel. The compressed working fluid flows through the gas passage 103 between the midstream channel and the outlet chamber 104. When the compressor displacement is 100%, while the downstream channel and the midstream regulating mechanism are open, the opening and closing component 41 of the upstream regulating mechanism moves the opening and closing block 42 away from the compressor body 20, opening the upstream channel. The compressed working fluid flows through the gas passage 103 between the upstream channel and the outlet chamber 104. This allows for matching different displacements of the noise-reducing compressor. In order to absorb noise of different frequency bands at each displacement, the working fluid has noise reduction modules 11 for different frequency bands along its path.

[0038] In other embodiments, the number of second air intake channels 101 can also be set to two or more than three, but the number of second air intake channels 101 cannot be one, and the number of adjustment mechanisms also changes accordingly. The larger the number of second air intake channels 101, the greater the corresponding displacement and the more precise the noise reduction control.

[0039] Example 2: The difference between Example 2 and Example 1 is that the silencing channel is set up differently and the adjustment device 40 is different. (Refer to...) Figures 4-6The exhaust end 10 includes a connecting end 21, a muffler 30, and a muffler seat 60. The muffler seat 60 is detachably located between the connecting end 21 and the muffler 30. The connection method between the muffler seat 60 and the connecting end 21 and the muffler 30 can refer to the snap-fit ​​or flange connection in Embodiment 1. A third muffler groove 600 is formed on the end face of the muffler seat 60 near the connecting end 21, and a fourth muffler groove 601 is formed on the end face near the muffler 30. The third muffler groove 600 and the first muffler groove 210 form a muffler flow channel 100. The fourth muffler groove 601 and the second muffler groove 300 form a muffler flow channel 100. Therefore, the exhaust end 10 has two muffler flow channels 100, that is, the two muffler flow channels 100 form a muffler channel. The plane where the muffler flow channel 100 is located is on the vertical plane of the axial direction of the noise reduction compressor. The two muffler flow channels are distributed sequentially along the axial direction of the noise reduction compressor. Furthermore, the intake structure of the muffler channel differs from that in Embodiment 1. The intake structure of the muffler channel is a first intake channel 105, which is parallel to the axial direction of the compressor and penetrates the sidewalls of the intake chambers of the two muffler channels 100. The adjustment device 40 includes an adjustment block 44 slidably disposed within the first intake channel 105 and an adjustment drive mechanism 43. The adjustment drive mechanism 43 is used to change the position of the adjustment block 44 within the first intake channel 105. The adjustment drive mechanism 43 is a hydraulic cylinder. During operation, when the adjustment block 44 is located at the end of the first intake channel 105 near the exhaust chamber 200, exhaust cannot be performed. When the adjustment block 44 is located between the two muffler channels 100, exhaust is performed using the muffler channel 100 near the exhaust chamber 200. When the adjustment block 44 is located at the end of the first intake channel 105 away from the exhaust chamber 200, exhaust is performed simultaneously using both muffler channels 100, thus adapting to different displacements.

[0040] Furthermore, the outlet chambers 104 of the two silencer channels 100 are interconnected. This design simplifies the exhaust structure of the silencer barrel 30, eliminating the need for separate exhaust ports for each silencer channel. Instead, all outlet chambers are connected through a common connecting space for unified exhaust. This not only reduces the number of exhaust ports, lowering structural complexity and manufacturing costs, but also avoids airflow interference and additional noise that may result from multiple independent exhaust ports. Simultaneously, the interconnected outlet chambers also act as a buffer, allowing for a smooth transition of the compressed working fluid flowing from different silencer channels when they converge, reducing turbulent noise caused by differences in airflow velocity or sudden changes in direction, and further improving the overall noise reduction effect. In addition, the unified exhaust channel facilitates the subsequent installation of auxiliary components such as exhaust shut-off valves at the exhaust end, enabling unified control of the entire compressor's exhaust process.

[0041] In other embodiments, the number of muffler seats 60 can be set to multiple, thus providing a wider adjustment range. In this case, the third muffler groove 600 and the fourth muffler groove 601 of adjacent muffler seats 60 form a muffler flow channel 100, and multiple muffler flow channels 100 form a muffler channel.

[0042] Example 3: Using multiple silencing channels 100 from Example 2 and adjustment device 40 from Example 1, the working principle of adjustment device 40 is similar to that of Example 1 but also different.

[0043] During operation, the muffler channels 100 are gradually utilized along the direction away from the exhaust chamber 200. As the displacement increases, the number of muffler channels 100 utilized also increases. The working principle of each muffler channel 100 is as follows: The opening and closing component 41 of the downstream regulating mechanism drives the opening and closing block 42 to move away from the compressor body 20, so that the downstream channel is connected to the muffler channel 100 closest to the exhaust chamber 200; then, while maintaining the connection between the downstream channel and the muffler channel 100 closest to the exhaust chamber 200, the opening and closing component 41 of the midstream regulating mechanism drives the opening and closing block 42 to move away from the compressor body 20, so that the midstream channel is connected to the muffler channel 100 closest to the exhaust chamber 200; then, while maintaining the connection between the downstream channel and the midstream channel, the muffler channel 100 is connected to the muffler channel 100 closest to the exhaust chamber 200. While the upstream channels are all connected to the muffler channel 100 closest to the exhaust chamber 200, the opening and closing component 41 of the upstream adjustment mechanism drives the opening and closing block 42 to move away from the compressor body 20, so that the upstream channel is connected to the muffler channel 100 closest to the exhaust chamber 200. Thus, the first muffler channel 100 is fully utilized. If the displacement needs to be increased, the downstream channel, midstream channel and upstream channel are gradually connected to the second muffler channel 100 according to the above principle. Compared with the first embodiment, the applicable displacement range is larger, and the noise reduction control is more accurate.

[0044] The above are all preferred embodiments of the present invention and are not intended to limit the scope of protection of the present invention. Therefore, all equivalent changes made in accordance with the structure, shape and principle of the present invention should be covered within the scope of protection of the present invention.

Claims

1. A noise-reducing compressor, characterized in that: The noise-reducing compressor has an exhaust end (10); the exhaust end (10) has a silencing channel; the compressed working fluid generated by the noise-reducing compressor flows through the silencing channel; a plurality of silencing modules (11) are arranged sequentially on the side wall of the silencing channel along the moving direction of the compressed working fluid; an adjustment device (40) is installed on the exhaust end (10); the adjustment device (40) is used to change the position of the compressed working fluid entering the silencing channel, thereby changing the number of silencing modules (11) through which the compressed working fluid passes.

2. The noise-reducing compressor according to claim 1, characterized in that: The silencing channel has a silencing flow channel (100); the silencing flow channel (100) is used for the flow of compressed working fluid; the silencing module (11) is disposed on the side wall of the silencing flow channel (100); the plane in which the silencing flow channel (100) is located is perpendicular to the axial direction of the noise reduction compressor.

3. A noise-reducing compressor according to claim 2, characterized in that: The noise-reducing compressor includes a noise-reducing compressor body (20) and a silencer barrel (30); the noise-reducing compressor body (20) has a connecting end (21); the silencer barrel (30) is detachably connected to the connecting end (21); the silencer flow channel (100) is formed between the connecting end (21) and the silencer barrel (30).

4. A noise-reducing compressor according to claim 1, characterized in that: The silencing channel has at least two silencing channels (100); the silencing channels (100) are used for the flow of compressed working fluid; the silencing module (11) is disposed on the side wall of the silencing channel (100); the plane in which the silencing channel (100) is located is perpendicular to the axial direction of the noise reduction compressor; a plurality of the silencing channels (100) are distributed sequentially along the axial direction of the noise reduction compressor.

5. A noise-reducing compressor according to claim 4, characterized in that: The noise-reducing compressor includes a noise-reducing compressor body (20), at least one silencer seat (60), and a silencer barrel (30); the noise-reducing compressor body (20) has a connecting end (21); the silencer seat (60) is detachably connected between the connecting end (21) and the noise-reducing compressor body (20); a silencer flow channel (100) is provided between the silencer seat (60) and the connecting end (21); a silencer flow channel (100) is provided between the silencer seat (60) and the silencer barrel (30); when the number of silencer seats (60) is greater than or equal to two, a silencer flow channel (100) is provided between adjacent silencer seats (60).

6. A noise-reducing compressor according to claim 5, characterized in that: The silencing channel (100) has an intake chamber (102), an outlet chamber (104), and a gas passage (103) connecting the intake chamber (102) and the outlet chamber (104); the silencing module (11) is disposed on the side wall of the gas passage (103); the exhaust end (10) has a first intake channel (105); the first intake channel (105) is parallel to the axial direction of the noise reduction compressor; the first intake channel (105) passes through the side wall of the intake chamber (102) of all the silencing channels (100); the adjusting device (40) includes an adjusting block (44) slidably disposed in the first intake channel (105) and an adjusting drive mechanism (43) for adjusting the position of the adjusting block (44); the outlet chamber (104) is used for discharging the compressed working fluid.

7. A noise-reducing compressor according to claim 6, characterized in that: The air outlet chambers (104) of all the said silencer channels (100) are interconnected.

8. A noise-reducing compressor according to claim 2 or 4, characterized in that: The silencing channel (100) is S-shaped.

9. A noise-reducing compressor according to claim 2 or 4, characterized in that: The exhaust end (10) has a plurality of second intake channels (101); the second intake channels (101) are parallel to the axial direction of the noise reduction compressor; the second intake channels (101) penetrate the sidewalls of all the silencer channels (100); the plurality of second intake channels (101) are distributed sequentially along the flow direction of the compressed working fluid; the regulating device (40) includes a plurality of regulating mechanisms; the regulating mechanisms correspond one-to-one with the second intake channels (101); the regulating mechanism includes an opening and closing block (42) that is slidably disposed in the second intake channel (101) and an opening and closing assembly (41) for adjusting the position of the opening and closing block (42).

10. A noise-reducing compressor according to claim 9, characterized in that: The noise-reducing compressor has different set displacement levels; different set displacement levels correspond to different opening numbers of the second air intake passage (101); the larger the set displacement, the more opening numbers of the second air intake passage (101); the plurality of second air intake passages (101) open sequentially along the direction away from the air outlet of the muffler flow channel (100); when the second air intake passage (101) is open, the second air intake passage (101) adjacent to it and close to the air outlet of the muffler flow channel (100) is in the open state.

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