Silencer and vehicle

Abstract

The utility model provides a silencer and a vehicle, and belongs to the technical field of automobile silencing devices. Whether a certain branch pipe is conducted or not is controlled through the control valve, whether the corresponding main body silencing cavity is used for restraining noise of a certain frequency band or not is selected, the inherent contradiction of a traditional silencer among frequency spectrum adaptability, back pressure control and space limit is solved, and the noise restraining reliability of the silencer is effectively improved. The branch pipes are closed or opened through the rotating action of the valve element, the control valve is simple in overall structure, the control mode is convenient and fast, and switching of the opening and closing states of all the branch pipes is easier to complete. And by arranging the flow dividing slopes, airflow can reach the corresponding branch pipes more stably, strong turbulent flow caused by airflow steering is avoided, and the exhaust smoothness is improved. The shell is designed to be of a flat structure, so that circulation of exhaust airflow in all the main body silencing cavities is more stable, and the noise reduction effect is enhanced.

Description

Mufflers and vehicles Technical Field

[0001] This application belongs to the field of automotive muffler technology, and more specifically, relates to a muffler and a vehicle. Background Technology

[0002] Automotive mufflers primarily reduce engine exhaust noise through physical principles such as sound wave interference, reflection, and energy dissipation using sound-absorbing materials. Their core function is to attenuate sound wave energy through internal structural design. Mufflers are essential automotive components that meet environmental standards.

[0003] Existing automotive mufflers have inherent contradictions in terms of spectrum adaptability, back pressure control, and spatial limitations. Their acoustic characteristics are difficult to adapt to the requirements of wide spectrum operating conditions, making it difficult to further improve the performance of the mufflers. Summary of the Invention

[0004] The purpose of this application is to provide a muffler and vehicle that aims to solve the problem that the acoustic characteristics of existing mufflers are difficult to adapt to the requirements of wide spectrum operating conditions, and that there is an inherent contradiction between spectrum adaptability, back pressure control and space constraints.

[0005] To achieve the above objectives, the technical solution adopted in this application is as follows:

[0006] In a first aspect, embodiments of this application provide a muffler, including:

[0007] The outer shell has multiple isolated main sound-absorbing cavities inside, which are sequentially distributed along a first path, and each main sound-absorbing cavity has a different sound-absorbing method.

[0008] An input pipe passes through the main anechoic cavity located at one end of the first path. The input end of the input pipe extends outside the outer shell, and the output end of the input pipe is located inside the main anechoic cavity. The output end of the input pipe is provided with multiple branch pipes, and each main anechoic cavity is connected to the output end of at least one of the branch pipes.

[0009] The output tube is connected to the main anechoic cavity located at the other end of the first path;

[0010] A control valve is movably disposed within the input pipe. The control valve can control the opening and closing of each of the branch pipes, so that the exhaust gas flow introduced from the input pipe can flow along the first path through at least one of the main silencer chambers and finally be discharged from the output pipe.

[0011] Existing mufflers mostly employ a fixed structure, using Helmholtz resonant cavities or expansion chamber designs to reduce noise by optimizing the transmission loss of sound waves in specific frequency bands. With a fixed structure design, low-frequency exhaust pulsation is significant at low speeds, requiring a larger structural volume or low-frequency resonant cavity, but this exacerbates noise regenerated by high-speed airflow. At high speeds, high-frequency turbulent noise intensifies, necessitating additional sound-absorbing layers or porous structures; however, such designs significantly increase exhaust back pressure, leading to engine power loss. Passively increasing the volume of the muffler's internal cavity wastes assembly space, and adding more sound-absorbing material further worsens the back pressure. Therefore, existing fixed-structure mufflers inherently contradict each other in terms of spectrum adaptability, back pressure control, and space constraints, making it difficult to meet the demands of wide-spectrum operating conditions. Achieving better adaptability to wide-spectrum operating conditions has become a key technical bottleneck restricting the balance of muffler performance.

[0012] Compared with the prior art, the solution shown in this application embodiment allows multiple main silencing cavities within the housing to be designed with different silencing methods according to actual usage requirements. The exhaust airflow received by the input pipe flows along the input pipe to the control valve. Although the exhaust airflow can flow along the first path within the housing, under the control of the control valve on / off of each branch pipe, the branch pipe in the conducting state and its corresponding main silencing cavity can play a corresponding noise suppression role. Therefore, by controlling whether a certain branch pipe is conducting through the control valve, it is possible to select whether to use the corresponding main silencing cavity to suppress noise in a certain frequency band. Ultimately, the noise suppression function of each main silencing cavity can be selectively activated according to the actual characteristics of the noise, giving the muffler a more flexible silencing processing mode. The muffler of this application does not require increasing the housing volume or adding additional sound-absorbing materials inside the main silencing cavity, and also has good wide-spectrum adaptability. It solves the inherent contradiction between spectrum adaptability, back pressure control, and space limitations in traditional mufflers, effectively improving the reliability of the muffler in noise suppression.

[0013] In conjunction with the first aspect, in one possible implementation, the control valve includes a control shaft and a valve core, the valve core being rotatably connected to the input pipe via the control shaft, the input ends of each of the branch pipes being distributed around the control shaft, and the valve core being capable of blocking the input port of at least one of the branch pipes during rotation.

[0014] In the above technical solution, the branch pipe is closed or opened by rotating the valve core. The overall structure and control method of the control valve are relatively simple, and it is easier to switch the open and closed states of each branch pipe.

[0015] In some embodiments, the output end of the input tube forms a control chamber, the control chamber has an arc-shaped circumferential sidewall, the valve core has an arc-shaped sealing surface adapted to the inner wall of the control chamber, and the input ends of the plurality of branch tubes are respectively connected to the circumferential sidewall.

[0016] In the above technical solution, a control chamber is set up to facilitate the installation of the control valve and to accommodate the movement of the control valve. At the same time, the arc-shaped circumferential sidewall and the arc-shaped sealing surface can always be in contact when the valve core rotates. After rotating to the input end of the branch pipe, automatic sealing is achieved. There is no need to design more degrees of freedom for the valve core. The sealing control method of the control valve is relatively simple and the sealing reliability is high.

[0017] In some embodiments, the valve core has two sets of opposing diversion ramps on the side near the input end of the input pipe, and the distance between the two sets of diversion ramps gradually increases in the direction away from the input end of the input pipe.

[0018] In the above technical solution, the junction of the two diversion ramps presents a sharp angle, thereby achieving the diversion of the exhaust airflow. Under the guidance of the diversion ramps, the diverted exhaust airflow can reach the corresponding branch pipe more smoothly, avoiding strong turbulence caused by airflow turning and improving the smoothness of exhaust.

[0019] In some embodiments, the outer peripheral wall of the housing includes two straight walls and two arcuate walls, and the two straight walls and the two arcuate walls are alternately arranged in the circumferential direction of the housing; the axis of the control shaft is arranged perpendicular to the straight walls, and the two ends of the control shaft are respectively connected to the straight walls on the corresponding sides.

[0020] In the above technical solution, the outer shell adopts a flat design, which makes the airflow of exhaust gas more stable in each main silencer cavity and enhances the noise reduction effect.

[0021] In conjunction with the first aspect, in one possible implementation, an auxiliary silencing cavity is further formed inside the outer shell. The auxiliary silencing cavity is disposed adjacent to the main silencing cavity located at one end of the first path and is isolated from the adjacent main silencing cavity.

[0022] The input tube passes through the auxiliary anechoic chamber, and its input end extends outside the auxiliary anechoic chamber;

[0023] The auxiliary silencing cavity is a resonant cavity, and the portion of the input tube located inside the auxiliary silencing cavity has micro-perforations.

[0024] The main anechoic cavity located at the other end of the first path is an expansion cavity.

[0025] In the above technical solution, low-frequency noise is suppressed by setting an auxiliary anechoic cavity. By setting the main anechoic cavity at the other end of the first path as an expansion cavity, not only can mid-to-high frequency noise be effectively suppressed, but the characteristics of the expansion cavity can also be used to easily set an output pipe to discharge airflow. Therefore, the layout of this embodiment can effectively meet the suppression of low-frequency, mid-frequency and high-frequency noise, while the structure is relatively simple and compact with a small number of pipes.

[0026] In some embodiments, the main anechoic cavity includes a second anechoic cavity located at one end of the first path and a third anechoic cavity located at the other end of the first path, wherein the second anechoic cavity is a Helmholtz resonant cavity and the third anechoic cavity is an expansion cavity;

[0027] The branch pipe is provided with at least three, at least two of the branch pipes are connected to the third anechoic chamber at their output ends, at least one of the branch pipes is connected to the second anechoic chamber at its output end, and the output pipe is connected to the third anechoic chamber.

[0028] The above technical solution minimizes the number of silencing chambers by setting up an auxiliary silencing chamber, a second silencing chamber, and a third silencing chamber, while meeting the silencing requirements for low-speed, medium-speed, and high-speed operating conditions. It has a simple structure and good reliability.

[0029] In some embodiments, among the two branch pipes communicating with the third anechoic chamber, one branch pipe is coaxially arranged with the input pipe, and the other branch pipes are arranged at an angle to the input pipe. The branch pipe coaxially arranged with the input pipe is defined as the first branch pipe, and the branch pipe arranged at an angle to the input pipe is defined as the second branch pipe. The inner diameter of the first branch pipe is larger than the inner diameter of the second branch pipe, and the second branch pipe is a normally open pipe.

[0030] In the above technical solution, the coaxial arrangement places one branch pipe on the same straight path as the input pipe, simplifying the pipe distribution structure, reducing the number of airflow turning areas, and improving airflow stability. Simultaneously, it reduces the pipe's size in the perpendicular direction, enhancing structural compactness. Under medium and high speed conditions, the first branch pipe is opened to reduce back pressure, allowing airflow to primarily pass through it. The first and second branch pipes can then flow at appropriate flow rates to the third silencer cavity, preventing improper flow division from failing to fully utilize the expansion cavity's design characteristics. Under low speed conditions, the first branch pipe is blocked, controlling the gas flow to the third silencer cavity, thus preventing airflow turbulence while maintaining low back pressure.

[0031] In some embodiments, the branch pipe communicating with the second anechoic cavity is defined as the third branch pipe, and the inner diameter of the third branch pipe is not less than the inner diameter of the first branch pipe.

[0032] In the above technical solution, under low-speed and medium-speed operating conditions, the third branch pipe with a larger inner diameter can ensure the reliability of resonance silencing and suppress low-frequency noise to the greatest extent.

[0033] Secondly, embodiments of this application also provide a vehicle including the aforementioned muffler.

[0034] Compared with the prior art, the solution shown in this application, by adopting the above-mentioned muffler, solves the inherent contradiction between spectrum adaptability, back pressure control and space limitation of traditional mufflers, and can better adapt to the needs of wide spectrum operating conditions, effectively improve the reliability of the muffler in noise suppression, and thus help improve the overall quality of vehicle use. Attached Figure Description

[0035] To more clearly illustrate the technical solutions in the embodiments of this application, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0036] Figure 1 is a schematic diagram of the internal structure of the muffler provided in Embodiment 1 of this application;

[0037] Figure 2 is a schematic diagram of the internal structure of the muffler provided in Embodiment 2 of this application;

[0038] Figure 3 is a three-dimensional structural diagram of the muffler provided in Embodiment 3 of this application;

[0039] Figure 4 is a schematic diagram of the internal structure of the silencer provided in Embodiment 3 of this application;

[0040] Figure 5 is a schematic diagram of the internal structure of the silencer provided in Embodiment 3 of this application;

[0041] Figure 6 is an enlarged view of the assembly of the input pipe, branch pipe and control valve in Figure 5;

[0042] Figure 7 is a perspective view of the control valve used in Embodiment 3 of this application.

[0043] In the diagram: 100, outer shell; 1001, straight wall; 1002, curved wall; 110, main shell; 120, front end cover; 130, rear end cover; 140, inner partition; 200, input pipe; 201, control chamber; 202, circumferential side wall; 2021, curved section; 2022, straight section; 210, first inner core tube; 2101, micro-perforation; 220, second inner core tube; 300, output. Pipe; 400, Control valve; 410, Rotary shaft; 420, Valve core; 4201, Diverting slope; 4202, Sealing surface; 500, Main silencer cavity; 520, Second silencer cavity; 530, Third silencer cavity; 600, Branch pipe; 610, First branch pipe; 620, Second branch pipe; 630, Third branch pipe; 700, Auxiliary silencer cavity; 800, Inlet flange; 900, Outlet flange. Detailed Implementation

[0044] To make the technical problems, technical solutions, and beneficial effects to be solved by this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and are not intended to limit the scope of this application.

[0045] It should be noted that the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0046] It should be noted that the terms "front" and "rear" refer to the front-rear direction of the vehicle body, the terms "left" and "right" refer to the left-right direction of the vehicle body, and the terms "up" and "down" refer to the up-down direction of the vehicle body. Other directional terms, unless otherwise explicitly defined, such as "center," "horizontal," "vertical," "top," "bottom," "inner," "outer," "high," and "low," are used to indicate direction or positional relationships based on the directions and positional relationships shown in the accompanying drawings. These are merely for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation. Therefore, they should not be construed as limiting the specific protection scope of the present invention.

[0047] Please refer to Figures 1 to 7 together. The silencer provided in this application will now be described. The silencer includes a housing 100, an input pipe 200, an output pipe 300, and a control valve 400. The housing 100 has multiple isolated main silencing cavities 500, which are sequentially distributed along a first path. Each main silencing cavity 500 has a different silencing method. The input pipe 200 passes through the main silencing cavity 500 located at one end of the first path. The input end of the input pipe 200 extends outside the housing 100, and the output end of the input pipe 200 is located inside the main silencing cavity 500. The output end of pipe 200 is provided with multiple branch pipes 600, and each main silencer cavity 500 is connected to the output end of at least one of the branch pipes 600; the output pipe 300 is connected to the main silencer cavity 500 located at the other end of the first path; the control valve 400 is movably disposed in the input pipe 200, and the control valve 400 can selectively control the opening and closing of each branch pipe 600 so that the exhaust airflow introduced from the input pipe 200 can flow along the first path through at least one main silencer cavity 500 and finally be discharged from the output pipe 300.

[0048] In this embodiment, the input end of the input pipe 200 is connected to the upstream post-processing component to receive the exhaust airflow from the upstream. The main silencing cavity 500 connected to the output pipe 300 is the last main silencing cavity 500 that the exhaust airflow passes through in the exhaust airflow path. After passing through this main silencing cavity 500, the exhaust airflow is discharged along the output pipe 300 and continues to flow to the downstream component. It should be noted that "the exhaust airflow can flow through at least one main silencing cavity 500 along the first path" means that when the exhaust airflow flows along the first path inside the housing 100, under the action of the control valve 400, the exhaust airflow can suppress noise in the corresponding frequency band under the action of the main silencing cavity 500 when it flows through the main silencing cavity 500 in the conducting state of the branch pipe 600.

[0049] In this embodiment, the output end of the input tube 200 may not be directly connected to the input end of the output tube 300, but may be indirectly connected through the corresponding branch tubes 600. The output end of the input tube 200 may be located in the main anechoic cavity 500 located away from the output tube 300 according to actual needs, and may be connected to different main anechoic cavities 500 through various branch tubes 600.

[0050] In this embodiment, the first path can be a straight path or a curved path, and the arrangement is selectively chosen according to the shape of the housing 100 and the actual sound absorption requirements. Figures 1 to 4 show the first path as a straight path parallel to the front-back direction.

[0051] Existing mufflers mostly employ a fixed structure design, using a Helmholtz resonator or expansion chamber design. Noise reduction is achieved by optimizing the transmission loss of sound waves in specific frequency bands, with a fixed exhaust airflow pattern. With a fixed structure design, low-frequency exhaust pulsation is significant at low speeds, requiring a larger structural volume or low-frequency resonator, but this exacerbates noise regenerated by high-speed airflow. At high speeds, high-frequency turbulence noise intensifies, necessitating additional sound-absorbing layers or porous structures; however, such designs significantly increase exhaust back pressure, leading to engine power loss. Passively increasing the volume of the muffler's internal cavity wastes assembly space, and adding more sound-absorbing material further worsens the back pressure. Therefore, existing fixed-structure mufflers inherently contradict each other in terms of spectrum adaptability, back pressure control, and space constraints, making it difficult to meet the needs of wide-spectrum operating conditions and becoming a key technical bottleneck restricting the balance of muffler performance.

[0052] Compared with the prior art, the silencer provided in this application allows multiple main silencing cavities 500 within the housing 100 to be designed with different silencing methods according to actual usage requirements. The exhaust airflow received by the input pipe 200 flows along the input pipe 200 to the control valve 400. Although the exhaust airflow can flow along the first path within the housing, under the control of the control valve 400 on each branch pipe 600, the branch pipe 600 in the conducting state and its corresponding main silencing cavity 500 can play a corresponding noise suppression role. Therefore, by controlling whether a certain branch pipe 600 is conducting through the control valve 400, it is possible to select whether to use the corresponding main silencing cavity 500 to suppress noise in a certain frequency band. Ultimately, the noise suppression function of each main silencing cavity 500 can be selectively activated according to the actual characteristics of the noise, giving the silencer a more flexible silencing processing mode. The silencer of this application does not require expanding the volume of the outer shell by 100, nor does it require adding additional sound-absorbing material inside the main silencer cavity 500. It also has good wide spectrum adaptability, which solves the inherent contradiction between spectrum adaptability, back pressure control and space limitations of traditional silencers. It can better adapt to the needs of wide spectrum operating conditions and effectively improve the reliability of the silencer in noise suppression.

[0053] In addition, due to the use of a branch manifold design, the pipeline path is relatively short, the pipeline layout is simpler, and it is more conducive to smooth exhaust.

[0054] The specific usage of the muffler in this embodiment is illustrated below:

[0055] 1) Referring to Figure 1, there are two main anechoic chambers 500. The front main anechoic chamber 500 is used to suppress low-frequency noise (e.g., Helmholtz resonator), and the rear main anechoic chamber 500 is used to suppress mid-to-high-frequency noise (e.g., expansion chamber). There are two branch pipes 600, each connected to a different main anechoic chamber 500. In one operating mode, the control valve 400 closes the branch pipe 600 connected to the front main anechoic chamber 500, so the exhaust airflow can only flow from the input pipe 200 to the rear main anechoic chamber 500. After suppressing mid-to-high-frequency noise in the rear main anechoic chamber 500, the exhaust airflow is discharged from the output pipe 300. In another operating mode, the control valve 400 opens both branch pipes 600, and the exhaust airflow flows sequentially along the flow path to the front and rear main anechoic chambers 500, suppressing low-frequency and mid-to-high-frequency noise respectively, before being discharged from the output pipe 300.

[0056] 2) Referring to Figure 2, there are two main silencing chambers 500. The front main silencing chamber 500 is used to suppress low-frequency noise (e.g., Helmholtz resonator), and the rear main silencing chamber 500 is used to suppress high-frequency noise (e.g., expansion chamber). There are three branch pipes 600, two of which are connected to the rear main silencing chamber 500, and the other branch pipe 600 is connected to the front main silencing chamber 500. In one working mode, the control valve 400 controls the middle branch pipe 600 to close, leaving only one branch pipe 600 connected to the rear main silencing chamber 500. The exhaust airflow flows sequentially along the flow path to the front and rear main silencing chambers 500, suppressing low-frequency and high-frequency noise respectively, before being discharged from the output pipe 300. In another working mode, the control valve 400 controls the branch pipe 600 connected to the front main silencing cavity 500 to close, so the exhaust airflow can only flow from the input pipe 200 to the rear main silencing cavity 500. After the main silencing cavity 500 suppresses high-frequency noise, it is discharged from the output pipe 300.

[0057] In some embodiments, referring to Figure 4, the control valve 400 includes a control shaft 410 and a valve core 420. The valve core 420 is rotatably connected to the input pipe 200 via the control shaft 410. The input ends of each branch pipe 600 are distributed around the control shaft 410. The valve core 420 can block the input port of at least one branch pipe 600 during rotation. In this embodiment, the branch pipe 600 is closed or opened by the rotation of the valve core 420. The overall structure and control method of the control valve 400 are relatively simple, making it easier to switch the open and closed states of each branch pipe 600.

[0058] Optionally, the inner diameter of the inlet pipe 200 is not less than the inner diameter of the branch pipe 600, so that the exhaust airflow can flow stably in the inlet pipe 200 and ensure the smoothness of the airflow. At the same time, a larger inner diameter can also make it easier to install the control valve 400.

[0059] Optionally, the input ends of each branch pipe 600 are all located within the same reference plane, and the control shaft 410 is perpendicular to the reference plane. It should be noted that "the input ends of each branch pipe 600 are all located within the same reference plane" means that the central axis of the input ports of each branch pipe 600 is within the same reference plane. When the input pipe 200 delivers exhaust airflow to each branch pipe 600, the airflow height remains constant, preventing turbulence at the input ends of the branch pipes 600 due to height differences, and avoiding abnormal noise caused by violent airflow fluctuations during flow splitting, thus ensuring the silencer's noise reduction performance. Furthermore, having the input ends of each branch pipe 600 located within the same reference plane also standardizes the height of the input ends of each branch pipe 600, facilitating sealing with the valve core 420.

[0060] In some embodiments, the control valve 400 further includes a drive assembly, which is implemented as follows: The drive assembly includes a drive motor and a transmission gear set. The drive motor is fixed to the housing 100 or the vehicle body. The input end of the transmission gear set is connected to the output shaft of the drive motor, and the output end of the transmission gear set is connected to the control shaft 410. The torque of the drive motor is transmitted to the control shaft 410 through the transmission gear set, thereby causing the valve core 420 to oscillate through the rotation of the control shaft 410. In a specific implementation, the transmission gear set includes at least two gears, two of which are respectively connected to the output shaft of the drive motor and the control shaft 410.

[0061] Of course, the transmission gear set can also be replaced by pulley set, sprocket set, worm gear set, etc., which will not be listed here.

[0062] To achieve the drive control of the control valve 400, this embodiment uses engine speed as a reference variable. A higher engine speed indicates a high-speed operating condition, and vice versa. Specifically, the engine has a first speed threshold R1 and a second speed threshold R2, where R1 < R2. The actual engine speed is defined as R. When the actual speed R ≤ the first speed threshold R1, the engine is in a low-speed operating condition; when the first speed threshold R1 < the actual speed R ≤ the second speed threshold R2, the engine is in a medium-speed operating condition; and when the actual speed R ≥ the second speed threshold R2, the engine is in a high-speed operating condition. A speed sensor is installed inside the engine to monitor the actual engine speed R in real time. The speed sensor and the drive motor are respectively connected to the central control module (e.g., the vehicle computer). The central control module controls the start, stop, and forward / reverse rotation of the drive motor based on the actual speed value monitored by the speed sensor, thereby switching between different noise reduction modes.

[0063] In some embodiments, referring to Figures 4 to 6, a control chamber 201 is formed at the output end of the input pipe 200. The width of the control chamber 201 can be flexibly designed; for example, the width of the control chamber 201 is greater than the width of the main body of the input pipe 200, thereby forming a larger installation space at the output end of the input pipe 200, which facilitates the installation of the control valve 400 and also facilitates the movement of the control valve 400. Based on this, referring to Figures 5 and 6, the control chamber 201 has an arc-shaped circumferential sidewall 202, and the valve core 420 has an arc-shaped sealing surface 4202 that is adapted to the inner wall of the control chamber 201. The input ends of multiple branch pipes 600 are respectively connected to the circumferential sidewall 202. In this embodiment, the valve core 420 rotates around the control shaft 410 to block the input ends of each branch pipe 600. The arc-shaped circumferential sidewall 202 and the arc-shaped sealing surface 4202 can always be in contact when the valve core 420 rotates. After rotating to the input end of the branch pipe 600, it automatically blocks the pipe. There is no need to design more degrees of freedom for the valve core 420. The blocking control method of the control valve 400 is relatively simple and the blocking reliability is high.

[0064] In some specific embodiments where the control chamber 201 is adapted to the control valve 400, referring to Figures 2, 5, and 6, the circumferential sidewall 202 of the control chamber 201 includes an arc-shaped segment 2021 and a straight segment 2022. The arc-shaped segment 2021 and the straight segment 2022 are connected end to end to form a circular circumferential profile. The valve core 420 of the control valve 400 can swing freely within the arc-shaped segment 2021, but cannot swing into the area where the straight segment 2022 is located. A normally open branch pipe 600 can be set in the area where the straight segment 2022 is located. This branch pipe 600 is never closed in any mode. In this way, the rotation angle of the valve core 420 can be reduced, the control parameters of the valve core 420 can be reduced, and the control logic can be further simplified. At the same time, the width of the control chamber 201 can be reduced, and the encroachment on the internal space of the main anechoic chamber 500 can be reduced.

[0065] In some other specific embodiments where the control chamber 201 is adapted to the control valve 400, referring to Figure 1, the circumferential sidewall 202 of the control chamber 201 is in the shape of a continuously distributed circle, which allows the valve core 420 of the control valve 400 to rotate 360°, with a larger range of motion, and the opening and closing of each branch pipe 600 can be controlled, making the control more flexible.

[0066] In some embodiments, referring to Figures 5 to 7, two sets of opposing diversion ramps 4201 are formed on the side of the valve core 420 near the input end of the input pipe 200. The distance between the two sets of diversion ramps 4201 gradually increases in the direction away from the input end of the input pipe 200. The junction of the two sets of diversion ramps 4201 presents a sharp angle, thereby achieving diversion of the exhaust airflow. Under the guidance of the diversion ramps 4201, the diverted exhaust airflow can reach the corresponding branch pipe 600 more smoothly, avoiding strong turbulence caused by airflow deflection and improving the smoothness of exhaust.

[0067] In some embodiments, referring to FIG3, the outer peripheral wall of the housing 100 includes two straight walls 1001 and two arcuate walls 1002, which are alternately arranged in the circumferential direction of the housing 100. Both straight walls 1001 are parallel to the reference plane, and the axis of the control shaft 410 is perpendicular to the straight walls 1001, with both ends of the control shaft 410 connected to the corresponding straight walls 1001. This embodiment adopts a flattened design for the housing 100, reducing the aspect ratio. The uniform flow velocity distribution of the flat channel can suppress local low-velocity areas, thereby reducing vortex generation and reducing the backflow area. Simultaneously, the arcuate walls 1002 achieve a smooth transition, reducing the separation area and limiting the scale of turbulent vortices. Overall, the flattened housing 100 design makes the exhaust airflow more stable within each main silencer cavity 500, enhancing noise reduction and exhaust smoothness.

[0068] In some embodiments, referring to FIG5, an auxiliary anechoic cavity 700 is also formed inside the housing 100. The auxiliary anechoic cavity 700 is disposed adjacent to the main anechoic cavity 500 located at one end of the first path and is isolated from the adjacent main anechoic cavity 500. The input pipe 200 passes through the auxiliary anechoic cavity 700, and its input end extends outside the auxiliary anechoic cavity 700. The auxiliary anechoic cavity 700 is a resonant cavity, and the portion of the input pipe 200 located inside the auxiliary anechoic cavity 700 is provided with micro-perforations 2101. The main anechoic cavity 500 located at the other end of the first path is an expansion cavity.

[0069] The resonant cavity primarily absorbs noise through resonance. When sound waves enter the silencer, air molecules within the cavity resonate with the sound waves, converting sound energy into heat energy, thus achieving noise reduction. Because low-frequency noise has a longer wavelength, it easily forms effective resonance within the cavity, making the resonant cavity more suitable for eliminating low-frequency noise. When sound waves enter the expansion cavity, they first encounter a smaller cross-section (corresponding to the branch pipe 600), then enter a larger cavity (corresponding to the main silencer cavity 500). As the sound waves propagate within the expansion cavity, the sudden increase in cross-section causes reflection. Multiple reflections within the expansion cavity result in mutual interference of sound wave energy, leading to the dissipation of some energy. This also reduces acoustic impedance, causing partial reflection and transmission of sound waves within the expansion cavity. The reflected sound waves propagate back and forth within the cavity, increasing the propagation path of the sound waves in the medium, thereby consuming sound energy. This method is suitable for eliminating mid-to-high frequency noise.

[0070] This embodiment suppresses low-frequency noise by setting an auxiliary anechoic cavity 700. By setting the main anechoic cavity 500 located at the other end of the first path as an expansion cavity, not only can mid-to-high frequency noise be effectively suppressed, but the characteristics of the expansion cavity can also be used to easily set the output pipe 300 to discharge airflow. Therefore, the layout of this embodiment can effectively meet the requirements for suppressing low-frequency, mid-frequency and high-frequency noise, while the structure is relatively simple and compact with a small number of pipes.

[0071] In some more specific embodiments, referring to FIG5, the main anechoic cavity 500 includes a second anechoic cavity 520 located at one end of the first path and a third anechoic cavity 530 located at the other end of the first path. The second anechoic cavity 520 is a Helmholtz resonant cavity, and the third anechoic cavity 530 is an expansion cavity. There are at least three branch pipes 600, with the output ends of at least two branch pipes 600 connected to the third anechoic cavity 530, the output end of at least one branch pipe 600 connected to the second anechoic cavity 520, and the output pipe 300 connected to the third anechoic cavity 530.

[0072] When sound waves enter the Helmholtz resonant cavity at the resonant frequency, the air mass inside the cavity will vibrate periodically, causing periodic changes in the cavity pressure, thereby reducing or eliminating noise. This method is suitable for eliminating low-frequency noise.

[0073] The working principle of this embodiment is as follows:

[0074] Under low-speed conditions, control valve 400 blocks several branch pipes 600 connected to the third silencing chamber 530, but some branch pipes 600 connected to the third silencing chamber 530 remain open. The gas flow path is through the auxiliary silencing chamber 700 for noise reduction, and then into the input pipe 200. At this time, the branch pipe 600 connected to the second silencing chamber 520 is open, and noise reduction is achieved through the Helmholtz resonator. The airflow then enters the third silencing chamber 530 through the branch pipe 600, eliminating mid-to-high frequency noise, and finally exits through the output pipe 300.

[0075] Under medium-speed operating conditions, the valve core 420 of the control valve 400 is located between the branch pipe 600 connected to the second silencer 520 and the branch pipe 600 connected to the third silencer 530, without blocking any branch pipe 600. The gas flow path is as follows: it is silenced by the auxiliary silencer 700 and enters the input pipe 200. The airflow is silenced by the second silencer 520 and then enters the third silencer 530 through multiple branch pipes 600 connected to the third silencer 530. After eliminating mid-to-high frequency noise, it is finally discharged through the output pipe 300.

[0076] Under high-speed operating conditions, the control valve 400 blocks the branch pipe 600 connected to the second silencer 520, while the branch pipe 600 connected to the third silencer 530 is in the open state. The gas flow path is to be silenced by the auxiliary silencer 700 and enter the input pipe 200. At this time, the branch pipe 600 connected to the third silencer 530 is in the open state, and the airflow can directly enter the third silencer 530. After eliminating mid-to-high frequency noise, it is finally discharged through the output pipe 300.

[0077] This embodiment minimizes the number of silencing chambers by setting up an auxiliary silencing chamber 700, a second silencing chamber 520, and a third silencing chamber 530, while still meeting the silencing requirements for low-speed, medium-speed, and high-speed operating conditions. It has a simple structure and good reliability.

[0078] Optionally, the Helmholtz resonant cavity can be filled with sound-absorbing materials (such as glass wool, foam materials, etc.), and the resonant cavity can also be filled with sound-absorbing materials (such as glass wool, foam materials, etc.). These materials can absorb the energy of sound waves and convert it into heat energy, further reducing the intensity of sound waves.

[0079] It should be noted that the internal configurations of the auxiliary silencing cavity 700, the second silencing cavity 520, and the third silencing cavity 530 can refer to existing cavity configuration designs, and will not be listed here. The number of auxiliary silencing cavities 700, the number of second silencing cavities 520, and the number of third silencing cavities 530 are not limited here. Figure 5 shows an embodiment in which one of each of the auxiliary silencing cavity 700, the second silencing cavity 520, and the third silencing cavity 530 is provided. If two auxiliary silencing cavities 700 are provided, the two auxiliary silencing cavities 700 are continuously distributed in the front-to-back direction. The second silencing cavity 520 and the third silencing cavity 530 are also arranged in a similar manner, and will not be listed here.

[0080] In some specific embodiments of the input tube 200, the input tube 200 includes a first inner core tube 210 and a second inner core tube 220 connected sequentially. The first inner core tube 210 passes through the auxiliary silencing cavity 700 and extends beyond the outer shell 100. A micro-perforation 2101 is formed in the portion of the first inner core tube 210 located in the auxiliary silencing cavity 700. The second inner core tube 220 is located within the second silencing cavity 520. At least three branch tubes 600 are provided at the output end of the second inner core tube 220, and a control valve 400 is disposed within the second inner core tube 220. The outlet ends of the branch tubes 600 located within the second silencing cavity 520 are spaced apart from the interior of the auxiliary silencing cavity 700, and the outlet ends of the multiple branch tubes 600 located within the third silencing cavity 530 are all spaced apart from the inner wall of the third silencing cavity 530. Furthermore, the aperture of the micro-perforation 2101 is 0.5mm to 1mm (e.g., 0.6mm, 0.7mm, 0.8mm, 0.9mm).

[0081] This embodiment, by segmenting the input tube 200, allows for different configurations of the inner core tube for different functions, providing greater design flexibility and better meeting the usage requirements of the resonant cavity.

[0082] In some more specific embodiments, referring to Figures 4 to 6, among the at least two branch pipes 600 communicating with the third anechoic chamber 530, one branch pipe 600 is coaxially arranged with the input pipe 200, and the other branch pipes 600 are arranged at an angle to the input pipe 200. The branch pipe 600 coaxially arranged with the input pipe 200 is defined as the first branch pipe 610, and the branch pipe 600 arranged at an angle to the input pipe 200 is defined as the second branch pipe 620. The inner diameter of the first branch pipe 610 is larger than the inner diameter of the second branch pipe 620, and the second branch pipe 620 is a normally open pipe. This embodiment utilizes a coaxial arrangement to place one of the branch pipes 600 and the input pipe 200 on the same straight path, resulting in a simpler pipe distribution structure, reducing the number of airflow turning areas, and improving airflow stability. At the same time, it also compresses the pipe distribution dimensions in the direction perpendicular to the front and rear, improving the compactness of the structure. Furthermore, since the inner diameter of the first branch pipe 610 is larger than that of the second branch pipe 620, under the premise that the first branch pipe 610 and the second branch pipe 620 are fully open, in order to reduce back pressure, the first branch pipe 610 is opened under medium-speed and high-speed operating conditions, and the airflow mainly flows through the first branch pipe 610. The first branch pipe 610 and the second branch pipe 620 can flow to the third silencer cavity 530 at a suitable flow rate, avoiding the inability to fully utilize the design characteristics of the expansion cavity due to improper flow division. Under low-speed operating conditions, the first branch pipe 610 is blocked to control the gas flow to the third silencer cavity 530, and to avoid airflow turbulence while ensuring that the back pressure is not too high.

[0083] Optionally, "the branch pipe 600 and the input pipe 200 are set at an angle" means that the branch pipe 600 is a straight pipe, but the extension path is inclined in the front-back direction, with an angle of 10° to 50° (e.g., 20°, 30°, 45°); or, the branch pipe 600 is an L-shaped bend, with one end of it directly connected to the input pipe 200 set perpendicular to the front-back direction, and the other end set parallel to the front-back direction (as shown in Figures 5 and 6).

[0084] Optionally, the first branch pipe 610 has the same inner diameter as the input pipe 200.

[0085] Based on the above embodiments, referring to Figure 6, the branch pipe 600 connected to the second silencing cavity 520 is defined as the third branch pipe 630, and the inner diameter of the third branch pipe 630 is not less than the inner diameter of the first branch pipe 610. Under low-speed and medium-speed operating conditions, the larger inner diameter of the third branch pipe 630 can ensure the reliability of resonance silencing and suppress low-frequency noise to the greatest extent.

[0086] Optionally, the inner diameter of the second branch pipe 620 is smaller than the inner diameter of the output pipe 300, and the inner diameter of the output pipe 300 is not smaller than the inner diameter of the first branch pipe 610, to ensure the effectiveness of the expansion chamber and the smoothness of exhaust.

[0087] In this embodiment, the third branch pipe 630 is perpendicular to the first branch pipe 610, and the rotation angle range of the valve core 420 is 90°. Taking the perspective of Figure 5 as an example, under low-speed conditions, the valve core 420 is in the position of blocking the first branch pipe 610; after switching to medium-speed conditions, the valve core 420 rotates clockwise by a certain angle to switch to the position between the first branch pipe 610 and the third branch pipe 630; after switching to high-speed conditions, the valve core 420 rotates clockwise by a certain angle to switch to the position of blocking the third branch pipe 630; rotating counterclockwise can restore it to the initial position.

[0088] The specific implementation of this embodiment is illustrated below: Under low-speed conditions, the control valve 400 only blocks the first branch pipe 610. The gas is silenced by the auxiliary silencer 700 and enters the second inner core pipe 220 for further silencing via the Helmholtz resonant cavity. The airflow then enters the third silencer 530 via the branch pipe 600, eliminating mid-to-high frequency noise, and finally exits through the output pipe 300. Under medium-speed conditions, the valve core 420 of the control valve 400 is located between the first branch pipe 610 and the third branch pipe 630, without blocking any branch pipes 600. The gas is silenced by the auxiliary silencer 700 and enters the second inner core pipe 220. The airflow is silenced by the second silencer 520 and then enters the third silencer 530 via multiple branch pipes 600 connected to it, eliminating mid-to-high frequency noise, and finally exits through the output pipe 300. Under high-speed conditions, the control valve 400 blocks the third branch pipe 630, while the first branch pipe 610 and the second branch pipe 620 are in the open state. The gas is silenced by the auxiliary silencer 700 and enters the second inner core pipe 220. Then it directly enters the third silencer 530 to eliminate mid-to-high frequency noise, and finally it is discharged through the output pipe 300.

[0089] In some embodiments, referring to Figure 3, the input end of the input pipe 200 is provided with an inlet flange 800, and the output end of the output pipe 300 is provided with an outlet flange 900. The inlet flange 800 can be connected to the upstream post-treatment pipeline. The flange connection has high reliability and good sealing performance, ensuring good airtightness. Similarly, the outlet flange 900 can be connected to the downstream pipeline, also ensuring good airtightness through a flange connection.

[0090] In some embodiments, referring to Figures 3 to 5, the inlet pipe 200 is a straight pipe with a consistent diameter. The exhaust airflow is delivered to each branch pipe 600 along a straight path, avoiding turbulence and swirling phenomena caused by factors such as turning or diameter change during the airflow process. This ensures that the airflow in the inlet pipe 200 remains as stable as possible, thereby providing a basic guarantee for the noise reduction effect and good exhaust smoothness by avoiding abnormal noise generated by the airflow in the inlet pipe 200.

[0091] Similarly, the output pipe 300 is a straight pipe with a consistent diameter. The silenced airflow flows along a straight path within the output pipe 300, avoiding turbulence and swirling phenomena caused by factors such as turning or diameter change during the airflow process. This ensures that the airflow in the output pipe 300 remains as stable as possible, thus providing a basic guarantee for the silencing effect and good exhaust smoothness by avoiding abnormal noise generated by the airflow in the output pipe 300.

[0092] Similarly, the various silencing cavities within the outer casing 100 are distributed along the front-to-back direction, i.e., in a straight path, reducing airflow deflection and simplifying the design of each silencing cavity, thus ensuring smooth exhaust. The embodiment in Figure 5 exemplarily illustrates an embodiment in which an auxiliary silencing cavity 700, a second silencing cavity 520, and a third silencing cavity 530 are arranged sequentially from front to back, and Figures 1 and 2 also show similar arrangements.

[0093] In some embodiments, referring to Figures 3 and 4, the outer casing 100 includes a main casing 110, a front cover 120, a rear cover 130, and a plurality of inner partitions 140. The main casing 110 is cylindrical, and its axis extends in the front-rear direction. The front cover 120 is sealed over the front opening of the main casing 110, and the rear cover 130 is sealed over the rear opening of the main casing 110. The inner partitions 140 are disposed inside the main casing 110 and can divide the inner cavity of the main casing 110 into at least two independent silencing chambers (e.g., an independent auxiliary silencing chamber 700, a second silencing chamber 520, and a third silencing chamber 530), and each silencing chamber is distributed in the front-rear direction. The input pipe 200 passes through the front cover 120, and at least one branch pipe 600 can pass through the inner partition 140. The front cover 120 and the rear cover 130 not only seal the end opening of the main housing 110 to provide a sealed inner cavity, but also support the input pipe 200 and the output pipe 300 to ensure the structural stability of the pipeline; the inner partition 140 not only isolates multiple silencing cavities, but also supports the branch pipe 600 to ensure the structural stability of the branch pipe 600.

[0094] In this embodiment, the input pipe 200, output pipe 300, branch pipe 600, inner partition 140, front cover 120, rear cover 130 and main housing 110 are all made of metal (e.g. stainless steel), which has a certain degree of corrosion resistance and good structural strength, ensuring the sound absorption effect while also having a long service life.

[0095] Optionally, the outer periphery of the inner partition 140 needs to maintain a sealed connection with the interior of the main housing 110 to ensure that each silencing cavity can be isolated from each other. Examples of sealing adaptation methods are as follows: the inner partition 140 and the main housing 110 are sealed by welding, or the inner partition 140 and the main housing 110 are snap-fitted together, and a sealing gasket is provided between them to achieve a seal between them.

[0096] Optionally, the inlet pipe 200 extends in the front-to-back direction, and the outlet pipe 300 also extends in the front-to-back direction, so that the entire muffler extends in the front-to-back direction, avoiding an overly tortuous exhaust path, improving exhaust smoothness, and at the same time reducing the space occupied by the vehicle body in the left-to-right direction, reducing the difficulty of arranging other surrounding components.

[0097] Optionally, the front cover 120 has a front through hole, through which the input pipe 200 passes and is sealed to the front cover 120 by welding; or, the input pipe 200 passes through the front through hole and a sealing ring is provided between the front through hole and the input pipe 200 to achieve a sealed fit. The rear cover 130 has a rear through hole, through which the output pipe 300 passes and is sealed to the rear cover 130 by welding; or, the output pipe 300 passes through the rear through hole and a sealing ring is provided between the rear through hole and the output pipe 300 to achieve a sealed fit.

[0098] The muffler of this application achieves directional suppression of high and low frequency noise under different operating conditions through the active rotation control valve 400 to switch the muffler mode, breaking through the limitations of the traditional fixed structure muffler frequency band. At the same time, by using the precise adjustment of the valve core angle 420, combined with the optimization of the muffler cavity layout, the formation of high back pressure is avoided, thereby avoiding loss of engine power and balancing noise reduction performance under all operating conditions with exhaust smoothness.

[0099] Based on the same inventive concept, this application also provides a vehicle including the above-described muffler.

[0100] Compared with the prior art, the vehicle provided in this application solves the inherent contradiction between spectrum adaptability, back pressure control and space limitation of traditional mufflers by adopting the above-mentioned muffler. It can better adapt to the needs of wide spectrum operating conditions, effectively improve the reliability of the muffler in noise suppression, and thus help improve the overall quality of the vehicle.

[0101] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A silencer, characterized in that, include: The outer shell (100) has multiple isolated main anechoic chambers (500) inside, which are sequentially distributed along a first path. Each main anechoic chamber (500) has a different anechoic method. An input pipe (200) passes through the main anechoic chamber (500) located at one end of the first path. The input end of the input pipe (200) extends outside the outer shell (100), and the output end of the input pipe (200) is located inside the main anechoic chamber (500). The output end of the input pipe (200) is provided with multiple branch pipes (60). 0), each of the main silencer cavities (500) is connected to the output end of at least one of the branch pipes (600); the output pipe (300) is connected to the main silencer cavity (500) located at the other end of the first path; the control valve (400) is movably disposed in the input pipe (200), and the control valve (400) can control the opening and closing of each of the branch pipes (600) so that the exhaust gas flow introduced from the input pipe (200) can flow along the first path through at least one of the main silencer cavities (500) and finally be discharged from the output pipe (300).

2. The silencer as described in claim 1, characterized in that, The control valve (400) includes a control shaft (410) and a valve core (420). The valve core (420) is rotatably connected to the input pipe (200) through the control shaft (410). The input ends of each branch pipe (600) are distributed around the control shaft (410). The valve core (420) can block the input port of at least one of the branch pipes (600) during rotation.

3. The silencer as described in claim 2, characterized in that, The output end of the input pipe (200) forms a control chamber (201), the control chamber (201) has an arc-shaped circumferential sidewall (202), the valve core (420) has an arc-shaped sealing surface (4202) adapted to the inner wall of the control chamber (201), and the input ends of the plurality of branch pipes (600) are respectively connected to the circumferential sidewall (202).

4. The silencer as described in claim 3, characterized in that, The valve core (420) has two sets of opposing diversion ramps (4201) on the side near the input end of the input pipe (200). The distance between the two sets of diversion ramps (4201) gradually increases in the direction away from the input end of the input pipe (200).

5. The silencer as described in claim 2, characterized in that, The outer peripheral wall of the outer casing (100) includes two straight walls (1001) and two arc-shaped walls (1002). The two straight walls (1001) and the two arc-shaped walls (1002) are alternately arranged in the circumferential direction of the outer casing (100). The axis of the control shaft (410) is perpendicular to the straight walls (1001), and the two ends of the control shaft (410) are respectively connected to the straight walls (1001) on the corresponding sides.

6. The silencer as described in any one of claims 1-4, characterized in that, An auxiliary silencing cavity (700) is also formed inside the outer shell (100). The auxiliary silencing cavity (700) is located adjacent to the main silencing cavity (500) located at one end of the first path and is isolated from the adjacent main silencing cavity (500). The input pipe (200) passes through the auxiliary silencing cavity (700) and its input end extends outside the auxiliary silencing cavity (700). The auxiliary silencing cavity (700) is a resonant cavity, and the portion of the input pipe (200) located inside the auxiliary silencing cavity (700) has micro-perforations (2101). The main anechoic cavity (500) located at the other end of the first path is an expansion cavity.

7. The silencer as described in claim 6, characterized in that, The main anechoic chamber (500) includes a second anechoic chamber (520) located at one end of the first path and a third anechoic chamber (530) located at the other end of the first path. The second anechoic chamber (520) is a Helmholtz resonant cavity, and the third anechoic chamber (530) is an expansion cavity. The branch pipe (600) is provided with at least three branches. The output ends of at least two branches (600) are connected to the third anechoic chamber (530), and the output end of at least one branch pipe (600) is connected to the second anechoic chamber (520). The output pipe (300) is connected to the third anechoic chamber (530).

8. The silencer as described in claim 7, characterized in that, In at least two branch pipes (600) communicating with the third anechoic chamber (530), one branch pipe (600) is coaxially arranged with the input pipe (200), and the other branch pipes (600) are arranged at an angle to the input pipe (200); the branch pipe (600) coaxially arranged with the input pipe (200) is defined as the first branch pipe (610), and the branch pipe (600) arranged at an angle to the input pipe (200) is defined as the second branch pipe (620). The inner diameter of the first branch pipe (610) is larger than the inner diameter of the second branch pipe (620), and the second branch pipe (620) is a normally open pipe.

9. The silencer as described in claim 8, characterized in that, The branch pipe (600) connected to the second silencing cavity (520) is defined as the third branch pipe (630), and the inner diameter of the third branch pipe (630) is not less than the inner diameter of the first branch pipe (610).

10. A vehicle, characterized in that, Includes the silencer as described in any one of claims 1-9.

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