Silencer ring gap control method, supercharger and vehicle

Abstract

The application belongs to the technical field of engines, and discloses a silencer ring gap control method, a supercharger and a vehicle. The silencer ring gap control method comprises the following steps: obtaining a silencer ring gap calibration value based on a current engine working condition; adjusting the silencer ring so that the silencer ring gap is equal to the silencer ring gap calibration value; and the calibration method of the silencer ring gap calibration value comprises the following steps: testing the supercharger noise corresponding to different silencer ring gaps under a to-be-tested engine working condition; obtaining the width value of the silencer ring gap at the time when the noise is the smallest under the to-be-tested engine working condition, calibrating the width value as the silencer ring gap calibration value under the to-be-tested engine working condition, and obtaining the corresponding relationship between the engine working condition and the silencer ring gap. The silencer ring gap control method can realize accurate control of the silencer ring gap, solve the supercharger noise problem caused by the improvement of the engine performance, and realize effective balance between the engine performance and the noise control.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of engines, in particular to a silencer ring gap control method, a supercharger and a vehicle. BACKGROUND

[0002] The turbocharger comprises a coaxial and spaced compressor casing inlet outer pipe and a compressor casing inlet inner pipe, a gas flow channel is formed between the two, and an air inlet is formed inside the compressor casing inlet inner pipe. The air inlet and the air outlet of the gas flow channel are both communicated with the air inlet. The turbocharger will produce a howling sound when the engine is in a high load condition. To solve the problem of turbocharger howling noise, a silencer ring is usually configured in the supercharger. The silencer ring is a circular ring structure arranged inside the compressor casing inlet outer pipe. The silencer ring gap is the axial distance between the silencer ring and the outer end surface of the compressor casing inlet inner pipe. The flow broadening flow channel is a through groove opened on the compressor casing inlet inner pipe and serves as the air inlet of the gas flow channel, and is communicated with the air cavity and the gas flow channel, which can broaden the flow and reduce the low-frequency noise when the gas flow enters the gas flow channel.

[0003] The prior art provides a supercharger system. When the engine is in a low load condition, the air outlet of the gas flow channel is opened to reduce the low-frequency noise at the outlet of the gas flow channel by using the gas flow from the air outlet of the gas flow channel to block the transmission of sound waves. When the engine is in a high load condition, the air outlet of the gas flow channel is closed to prevent the gas flow from the air outlet of the gas flow channel, thereby reducing the high-frequency noise at the outlet of the gas flow channel.

[0004] The above-mentioned supercharger system can only reduce the noise under different conditions of the engine by opening and closing the air outlet of the gas flow channel, but does not provide a related balancing means for the influence of the noise control process on the performance of the supercharger, and cannot accurately reduce the noise under the premise of ensuring the performance to effectively balance the engine performance and noise reduction.

[0005] Therefore, there is an urgent need for a silencer ring gap control method, a supercharger and a vehicle to solve the above problems. SUMMARY

[0006] According to one aspect of the present application, the purpose is to provide a silencer ring gap control method which can accurately control the silencer ring gap, solve the problem of supercharger noise caused by improving the engine performance, and effectively balance the engine performance and noise control.

[0007] To achieve this purpose, the present application adopts the following technical solutions:

[0008] The muffler ring gap control method can adjust the muffler ring gap of a supercharger, the supercharger comprising a compressor shell and a muffler ring, the compressor shell comprising a compressor inlet outer pipe and a compressor inlet inner pipe, the muffler ring being connected to the compressor shell and being arranged in the axial direction of the compressor inlet outer pipe and spaced from the compressor inlet inner pipe to form the muffler ring gap; the muffler ring gap control method comprising:

[0009] obtaining a muffler ring gap calibration value based on the current engine operating condition;

[0010] adjusting the muffler ring so that the muffler ring gap is equal to the muffler ring gap calibration value;

[0011] The calibration method of the muffler ring gap calibration value comprises:

[0012] testing the supercharger noise corresponding to different muffler ring gaps under the to-be-tested engine operating condition; obtaining the width value of the muffler ring gap when the noise is the smallest under the to-be-tested engine operating condition, and calibrating the width value as the muffler ring gap calibration value under the to-be-tested engine operating condition; and obtaining the corresponding relationship between the engine operating condition and the muffler ring gap.

[0013] Through the above arrangement, the muffler ring gap calibration value corresponding to the smallest supercharger noise under the to-be-tested engine operating condition can be obtained, the muffler ring gap calibration value can provide a reference standard for the adjustment of the gap width of the muffler ring gap under the same engine operating condition, and the engine performance and the supercharger noise control can be effectively balanced.

[0014] As a preferred scheme of the muffler ring gap control method provided by the application, the step of "adjusting the muffler ring gap to be equal to the muffler ring gap calibration value" comprises:

[0015] performing closed-loop control on the muffler ring so that the actual width value of the muffler ring gap is equal to the set width value.

[0016] Through the above arrangement, accurate control of the muffler ring gap can be achieved.

[0017] As a preferred scheme of the muffler ring gap control method provided by the application, the engine is confirmed to be in a stable running stage before the step of "obtaining the muffler ring gap calibration value".

[0018] Through the above arrangement, the accuracy of obtaining the muffler ring gap calibration value can be improved.

[0019] According to another aspect of the present application, a supercharger is provided, which comprises a compressor casing and a sound attenuation ring, the compressor casing comprises a compressor inlet outer pipe, a compressor inlet inner pipe and an outlet volute, the compressor inlet outer pipe and the outlet volute are coaxially and fixedly connected, the compressor inlet inner pipe is coaxially arranged in the compressor inlet outer pipe to form an airflow passage, an inlet passage is formed in the compressor inlet inner pipe, a flow widening channel is formed in the compressor inlet inner pipe, the flow widening channel is communicated with the inlet passage and the airflow passage, the sound attenuation ring is connected to the compressor casing and is arranged in the axial direction of the compressor inlet outer pipe and is spaced apart from the compressor inlet inner pipe to form a sound attenuation ring gap, the flow widening channel is the inlet of the airflow passage, and the sound attenuation ring gap is the outlet of the airflow passage.

[0020] The outlet volute is communicated with the inner cavity of the engine and the inlet passage, and can expand the airflow from the inlet passage and guide it into the inner cavity of the engine.

[0021] The supercharger adjusts the sound attenuation ring gap based on the sound attenuation ring gap control method according to any of the above-mentioned aspects, and further comprises an actuator arranged on the compressor casing, the sound attenuation ring is connected to the actuator, and the actuator can drive the sound attenuation ring to move to adjust the sound attenuation ring gap.

[0022] Through the above arrangement, the reliable adjustment of the sound attenuation ring gap can be realized by the actuator.

[0023] As a preferred scheme of the supercharger provided by the present application, the actuator comprises a cylinder, a piston and an elastic element, the cylinder is arranged on the compressor casing, the sound attenuation ring is connected to the piston, and the elastic element is arranged in the axial direction of the compressor inlet outer pipe and is connected between the piston and a fixed part on the compressor casing.

[0024] The sound attenuation ring can move away from the compressor inlet inner pipe under the action of the piston moving in the axial direction of the compressor inlet outer pipe.

[0025] The sound attenuation ring can also move close to the compressor inlet inner pipe under the elastic recovery action of the elastic element.

[0026] Through the above arrangement, the reliable adjustment of the position of the sound attenuation ring can be realized by the cooperation of the cylinder, the piston and the elastic element.

[0027] As a preferred scheme of the supercharger provided by the present application, the actuator further comprises a control valve, the control valve is arranged between a rodless cavity of the cylinder and a gas source, and the control valve can control the amount of gas entering the rodless cavity from the gas source.

[0028] Through the above arrangement, the position of the silencer ring can be adjusted by controlling the opening of the control valve, and the displacement of the silencer ring can be converted into the air intake volume of the rodless chamber of the cylinder for control.

[0029] As a preferred solution of the supercharger provided by the present invention, the supercharger further includes a control mechanism, which is communicatively connected to the control valve and can control the opening of the control valve.

[0030] Through the above arrangement, the control mechanism can improve the accuracy of the control valve action and the accuracy of the adjustment of the silencer ring position.

[0031] As a preferred embodiment of the supercharger provided by the present invention, the actuator further includes a pressure sensor, which is arranged at a fixed portion on the compressor casing, connected to the elastic element, and communicatively connected to the control mechanism. The pressure sensor can detect the elastic force of the elastic element, and can calculate the deformation of the elastic element based on the elastic force of the elastic element. The deformation of the elastic element is equal to the adjustment amount of the silencer ring gap.

[0032] With the above arrangement, feedback of the silencer ring gap can be achieved through the pressure sensor, thereby facilitating closed-loop control of the silencer ring gap.

[0033] As a preferred embodiment of the supercharger provided by the present invention, the cylinder is annular in structure, the piston includes a plurality of piston rods, the plurality of piston rods are arranged circumferentially at intervals on the compressor intake outer pipe, and are all connected to the muffler ring;

[0034] There are multiple elastic elements, each of which corresponds to the multiple piston rods. The multiple elastic elements are arranged at intervals along the circumferential direction on the compressor air inlet outer pipe and are all connected to the silencer ring and the corresponding piston rod.

[0035] Through the above arrangement, the stability of the silencer ring when moving relative to the intake end of the compressor intake inner tube can be improved, and multiple output parts operate simultaneously, which can ensure the uniformity of the silencer ring gap adjustment in the circumferential direction of the silencer ring.

[0036] According to another aspect of the present invention, an object is to provide a vehicle, comprising an engine and a supercharger as described in any of the above schemes, wherein an inner cavity of the engine is connected to the exhaust volute.

[0037] Beneficial effects of the present invention:

[0038] The silencer ring gap control method provided by the application comprises: obtaining a silencer ring gap calibration value based on a current engine working condition; and adjusting the silencer ring, so that the silencer ring gap is equal to the silencer ring gap calibration value. The calibration method of the silencer ring gap calibration value comprises: in the step of obtaining the silencer ring gap calibration value, the turbocharger noise corresponding to different silencer ring gaps under the to-be-tested engine working condition is tested; the width value of the silencer ring gap at the time when the noise is the smallest under the to-be-tested engine working condition is extracted, and is calibrated as the silencer ring gap calibration value under the to-be-tested engine working condition; the width value of the silencer ring gap at the time when the noise is the smallest under the to-be-tested engine working condition is extracted, and is calibrated as the silencer ring gap calibration value under the to-be-tested engine working condition, and the corresponding relationship between the engine working condition and the silencer ring gap is obtained. A certain engine working condition corresponds to a certain turbocharger intake air volume, and the degree of the noise emitted by the turbocharger is different when the turbocharger intake air volume is different. Through the above steps, the silencer ring gap calibration value corresponding to the time when the turbocharger noise is the smallest under the to-be-tested engine working condition can be obtained, the silencer ring gap calibration value can provide a reference standard for the adjustment of the gap width of the silencer ring gap under the same engine working condition in the future, and the engine performance and the turbocharger noise control can be effectively balanced. By adjusting the silencer ring, the turbocharger noise can be reduced by adjusting the gap width of the silencer ring gap under the to-be-tested engine working condition, and the closed-loop control of the engine performance and the noise control can be realized.

[0039] The turbocharger provided by the application can adjust the silencer ring gap by using the silencer ring gap control method provided by the application, so that the engine performance and the turbocharger noise control can be effectively balanced.

[0040] The vehicle provided by the application realizes the intake of the engine by using the turbocharger provided by the application. BRIEF DESCRIPTION OF DRAWINGS

[0041] Figure 1 is a sectional view of part of the structure of the turbocharger provided by the first embodiment of the application;

[0042] Figure 2 is a flow chart of the silencer ring gap control method provided by the second embodiment of the application.

[0043] In the drawings:

[0044] 100, compressor casing; 110, compressor intake outer pipe; 120, compressor intake inner pipe; 121, flow expansion passage; 130, gas outlet volute; 140, airflow passage; 150, intake passage;

[0045] 200, silencer ring;

[0046] 300, actuator; 310, cylinder; 320, piston; 330, elastic element; 340, control valve; 350, pressure sensor; 360, intake pipe; 370, outlet pipe. DETAILED DESCRIPTION

[0047] The technical solutions of the embodiments of the present application will be further described below in conjunction with the accompanying drawings and specific embodiments.

[0048] To make the objects, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be described clearly and completely below in conjunction with the accompanying drawings of the embodiments of the present application. Obviously, the described embodiments are only some of the embodiments of the present application but not all the embodiments. The components of the embodiments of the present application described and shown in the accompanying drawings can be arranged and designed in various different configurations.

[0049] Therefore, the following detailed description of the embodiments of the present application provided in the accompanying drawings is not intended to limit the scope of the claimed present application, but only represents selected embodiments of the present application. All other embodiments obtained by those of ordinary skill in the art based on the embodiments in the present application without creative labor are within the scope of protection of the present application.

[0050] It should be noted that: similar reference numerals and letters represent similar items in the following drawings, therefore, once an item is defined in one drawing, it does not need to be further defined and explained in subsequent drawings.

[0051] In the description of the present application, it should be noted that the orientations or positional relationships indicated by the terms "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. are based on the orientations or positional relationships shown in the drawings, or the orientations or positional relationships in which the product of the present application is usually placed, and are only for the convenience of describing the present application and simplifying the description, and therefore cannot be understood as indicating or implying that the device or element must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application. In addition, the terms "first", "second", "third", etc. are only used for differentiation in description and cannot be understood as indicating or implying relative importance. In the description of the present application, unless otherwise specified, the meaning of "a plurality of" is two or more.

[0052] In the description of the present application, it should also be noted that, unless otherwise specified and limited, the terms "set", "connected" should be understood broadly, for example, can be fixedly connected, can be detachably connected, or integrally connected; can be mechanically connected, or electrically connected. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to the specific circumstances.

[0053] In the present application, unless otherwise explicitly specified and limited, "on" or "under" of a first feature to a second feature can include that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, "on", "above" and "over" of a first feature to a second feature includes that the first feature is directly above and obliquely above the second feature, or only indicates that the first feature is higher in horizontal height than the second feature. "Under", "below" and "underneath" of a first feature to a second feature includes that the first feature is directly below and obliquely below the second feature, or only indicates that the first feature is lower in horizontal height than the second feature.

[0054] Embodiments of the present application are described in detail below with reference to the accompanying drawings, in which the same or similar elements or elements having the same or similar functions are denoted by the same or similar reference numerals throughout. The embodiments described below by reference to the accompanying drawings are exemplary and are only used to explain the present application and cannot be understood as a limitation of the present application.

[0055] Embodiment one

[0056] The present embodiment provides a supercharger and a vehicle. The vehicle includes an engine and the supercharger provided by the present embodiment. The supercharger can provide compressed air for the engine.

[0057] Figure 1 A cross-sectional view showing part of the structure of the supercharger provided by the first embodiment of the present application is shown. Referring to Figure 1 The supercharger provided by the present embodiment includes a compressor housing 100 and a sound attenuation ring 200. The compressor housing 100 includes a compressor inlet outer pipe 110, a compressor inlet inner pipe 120 and an outlet volute 130. The compressor inlet outer pipe 110 and the outlet volute 130 are coaxially and fixedly connected. The compressor inlet inner pipe 120 is coaxially arranged in the compressor inlet outer pipe 110 to form an airflow passage 140, an inlet passage 150 is formed in the compressor inlet inner pipe 120, and the outlet of the airflow passage 140 is communicated with the inlet end of the inlet passage 150. The compressor inlet inner pipe 120 is provided with a flow widening flow channel 121, which communicates the inlet passage 150 and the airflow passage 140. The sound attenuation ring 200 is connected to the compressor housing 100 and is arranged in the axial direction of the compressor inlet outer pipe 110 and spaced apart from the compressor inlet inner pipe 120 to form a sound attenuation ring gap. The flow widening flow channel 121 is the inlet of the airflow passage 140, and the sound attenuation ring gap is the outlet of the airflow passage 140. By providing the sound attenuation ring 200, the flow can be guided, the flow field of the airflow is more smooth and stable, and the partial aerodynamic noise is reduced. By providing the flow widening flow channel 121, the flow range of the low inlet flow rate region can be widened, and in cooperation with the sound attenuation ring 200, the mid-low frequency surge noise can also be weakened to a certain extent.

[0058] Specifically, the outlet volute 130 is in communication with the inner cavity of the engine and the inlet passage 150, and is capable of diffusing and guiding the airflow from the inlet passage 150 into the inner cavity of the engine.

[0059] Further specifically, the supercharger further comprises a rotor (not shown). The rotor is located in the compressor casing 100, and is coaxially arranged with the outlet volute 130. An annular gap is formed between the rotor and the outlet volute 130, and the annular gap is in communication with the inner space of the outlet volute 130. The outlet volute 130 is in communication with a compressor outlet passage, and the compressor outlet passage is capable of guiding the compressed air from the outlet volute 130 into the inner cavity of the engine.

[0060] Continuing to refer to Figure 1 The supercharger further comprises an actuator 300, which is arranged on the compressor casing 100, and the sound attenuation ring 200 is connected to the actuator 300. The actuator 300 is capable of driving the sound attenuation ring 200 to move, so as to adjust the sound attenuation ring gap. The actuator 300 can be a cylinder piston mechanism or a hydraulic mechanism. In the embodiment, the actuator 300 is a cylinder piston mechanism.

[0061] Specifically, the actuator 300 comprises a cylinder 310, a piston 320, and an elastic element 330. The cylinder 310 is arranged on the compressor casing 100, the sound attenuation ring 200 is connected to the piston 320, and the elastic element 330 is arranged along the axial direction of the compressor inlet outer pipe 110, and is connected between the piston 320 and a fixed portion on the compressor casing 100. In the embodiment, the fixed portion on the compressor casing 100 can be a boss which is integrated in the inner portion of the compressor casing 100 and is arranged opposite to the cylinder 310. The boss can serve as a reference for the elastic element 330. The sound attenuation ring 200 can be driven by the piston 320 to move away from the compressor inlet inner pipe 120 along the axial direction of the compressor inlet outer pipe 110. The sound attenuation ring 200 can also be driven by the elastic recovery action of the elastic element 330 to move close to the compressor inlet inner pipe 120.

[0062] Further specifically, the actuator 300 further comprises a control valve 340. The inlet port of the rodless cavity of the cylinder 310 is in communication with a gas source through an inlet pipe 360, and the control valve 340 is arranged in the inlet pipe 360. The control valve 340 is capable of controlling the amount of gas entering the rodless cavity from the gas source, so as to change the pressure of the rodless cavity of the cylinder 310. The rodless cavity of the cylinder 310 is further provided with an outlet pipe 370, which is capable of discharging the gas in the rodless cavity of the cylinder 310. The inlet pipe 360 and the outlet pipe 370 are arranged at a distance.

[0063] When the pressure in the rodless cavity of the cylinder 310 is equal to the elastic force of the elastic element 330, the sound attenuation ring 200 is kept stationary relative to the compressor intake inner pipe 120; when the pressure in the rodless cavity of the cylinder 310 is greater than the elastic force of the elastic element 330, the sound attenuation ring 200 can be pushed away from the intake end of the compressor intake inner pipe 120, thereby increasing the sound attenuation ring gap; when the pressure in the rodless cavity of the cylinder 310 is less than the elastic force of the elastic element 330, the elastic element 330 can push the sound attenuation ring 200 towards the intake end of the compressor intake inner pipe 120, thereby reducing the sound attenuation ring gap.

[0064] More specifically, the pressure booster further comprises a control mechanism. The control mechanism is communicatively connected to the control valve 340 and can control the opening degree of the control valve 340, thereby controlling the amount of gas entering the rodless cavity of the cylinder 310 to control the distance of the piston extending out of the cylinder 310. In the embodiment, the control mechanism can be integrated into the vehicle ECU electronic controller.

[0065] Continuing to refer to Figure 1 The actuator 300 further comprises a pressure sensor 350. The pressure sensor 350 is arranged on a fixed portion of the compressor shell 100, and one end of the elastic element 330 is connected to the pressure sensor 350. The pressure sensor 350 is communicatively connected to the control mechanism. The pressure sensor 350 can detect the elastic force of the elastic element 330, and the control mechanism can receive the elastic force signal and calculate the deformation amount of the elastic element 330 according to the elastic force of the elastic element 330. The deformation amount of the elastic element 330 is equal to the adjustment amount of the sound attenuation ring gap.

[0066] As a preferred, the cylinder 310 has a ring structure, and the piston 320 comprises a plurality of piston rods which are circumferentially spaced apart on the compressor intake outer pipe 110 and are all connected to the sound attenuation ring 200. The intake pipe 360 and the exhaust pipe 370 are arranged at the top and bottom of the ring-shaped cylinder, respectively. The elastic element 330 is a plurality of elastic elements which correspond one-to-one to the plurality of piston rods, and are circumferentially spaced apart on the compressor intake outer pipe 110 and are all connected to the sound attenuation ring 200 and the corresponding piston rods. Through the above arrangement, the stability of the sound attenuation ring 200 relative to the movement of the intake end of the compressor intake inner pipe 120 can be improved, and the plurality of output portions can act simultaneously to ensure the uniformity of the sound attenuation ring gap adjustment in the circumferential direction of the sound attenuation ring 200.

[0067] In another embodiment, the plurality of cylinders 310 are evenly spaced circumferentially on the compressor housing 100, and each cylinder 310 is provided with a piston 320. Each cylinder is provided with an intake pipe 360 and an exhaust pipe 370, and each of the plurality of intake pipes 360 is provided with a control valve 340. The control mechanism can simultaneously control the opening degrees of the plurality of control valves 340.

[0068] Embodiment Two

[0069] Figure 2 A flow chart of the silencer ring gap control method provided by Embodiment Two of the present application is shown. Referring to Figure 2 The present embodiment provides a silencer ring gap control method. The silencer ring gap control method provided by the present embodiment can be used to adjust the silencer ring gap of the supercharger provided by Embodiment One.

[0070] The silencer ring gap control method comprises: obtaining a silencer ring gap calibration value based on the current engine operating condition; and adjusting the silencer ring 200 so that the silencer ring gap is equal to the silencer ring gap calibration value.

[0071] The calibration method of the silencer ring gap calibration value comprises:

[0072] First, it is confirmed that the engine is in a stable running stage.

[0073] Then, the silencer ring gap calibration value is obtained: the supercharger noise corresponding to different silencer ring gaps is tested under the to-be-tested engine operating condition; and the width value of the silencer ring gap is obtained when the noise is the smallest under the to-be-tested engine operating condition, which is calibrated as the silencer ring gap calibration value under the to-be-tested engine operating condition. A certain engine operating condition corresponds to a certain supercharger intake amount, and the degree of noise emitted by the supercharger is different when the supercharger intake amount is different. Through the above steps, the silencer ring gap calibration value corresponding to the smallest supercharger noise under the to-be-tested engine operating condition can be obtained, which can provide a reference standard for the adjustment of the width value of the silencer ring gap under the same engine operating condition, and effectively balance the engine performance and supercharger noise control, so as to achieve the best noise control under a certain engine operating condition.

[0074] Finally, the silencer ring gap is adjusted: the width value of the silencer ring gap is adjusted to be equal to the silencer ring gap calibration value. Through the above steps, the width of the silencer ring gap can be adjusted to reduce the noise of the supercharger under the to-be-tested engine operating condition, and closed-loop control of the engine performance and noise control can be achieved.

[0075] Specifically, in the above step, "adjusting the width value of the silencer ring gap to be equal to the silencer ring gap calibration value" specifically comprises closed-loop control of the silencer ring 200 so that the actual width value of the silencer ring gap is equal to the set width value, which specifically comprises the following steps:

[0076] The actual width value of the silencer ring gap of the supercharger is obtained, the relationship between the actual difference between the actual width value of the silencer ring gap and the silencer ring gap calibration value and the preset difference value is determined, if the actual difference is not greater than the preset difference value, the actual width value of the silencer ring gap is kept, otherwise, the actual width value of the silencer ring gap is adjusted to be equal to the silencer ring gap calibration value. Through the above steps, after the gap width of the silencer ring gap is initially adjusted to the actual width value of the silencer ring gap, the error between the actual width value of the silencer ring gap and the silencer ring gap calibration value is adjusted again, so as to ensure the accuracy of the adjustment of the gap width of the silencer ring gap.

[0077] Further, the "obtaining the silencer ring gap calibration value" further includes: extracting and calibrating the silencer ring gap calibration values under multiple to-be-tested engine operating conditions, and obtaining the corresponding relationship between the engine operating conditions and the silencer ring gap. The corresponding relationship between the engine operating conditions and the silencer ring gap can be a corresponding relationship diagram or a corresponding relationship table, etc. Different to-be-tested engine operating conditions correspond to different silencer ring gap calibration values. By forming the corresponding relationship between the engine operating conditions and the silencer ring gap, a reference can be provided for subsequent adjustment of the silencer ring gap, so as to quickly obtain the silencer ring gap that can minimize the supercharger noise under a certain operating condition.

[0078] In the embodiment, the control mechanism mainly adjusts the silencer ring gap by controlling the actuator 300. In the embodiment, the control mechanism controls the amount of air entering the annular cylinder by controlling the opening degree of the control valve 340, so as to control the extension distance of the output part relative to the driving part, change the compression amount of the elastic element 330, and thus realize the adjustment of the silencer ring gap.

[0079] Therefore, in the "obtaining the silencer ring gap calibration value" step provided in the embodiment, the control mechanism adjusts the control valve 340 to different opening degrees to adjust the silencer ring 200 to different positions under the to-be-tested engine operating condition, and simultaneously tests the supercharger noise, and the opening degree of the control valve 340 corresponding to the silencer ring gap calibration value is calibrated as the target opening degree under the to-be-tested engine operating condition.

[0080] The engine is sequentially operated to different to-be-tested operating conditions, the target opening degree of the control valve 340 under different to-be-tested engine operating conditions is calibrated according to the above method, and the engine operating condition-control valve opening degree reference diagram is formed, which can provide a reference for the selection of the opening degree of the control valve 340 in the subsequent adjustment of the silencer ring gap.

[0081] Obviously, the above embodiments of the present application are merely exemplary but not intended to limit the embodiments of the present application. Various obvious changes, re-adjustments and substitutions can be made by those skilled in the art without departing from the scope of the present application. It is not necessary or possible to enumerate all the embodiments. Any modification, equivalent replacement and improvement made within the spirit and principle of the present application shall be included in the protection scope of the claims of the present application.

Claims

1. A method for controlling the gap of a silencer ring, capable of adjusting the gap of a silencer ring of a supercharger, the supercharger comprising a compressor casing (100) and a silencer ring (200), the compressor casing (100) comprising a compressor inlet outer pipe (110) and a compressor inlet inner pipe (120), the silencer ring (200) being connected to the compressor casing (100) and being arranged along the axial direction of the compressor inlet outer pipe (110) and spaced apart from the compressor inlet inner pipe (120) to form the gap of the silencer ring; the supercharger further comprising an actuator (300) arranged on the compressor casing (100), the silencer ring (200) being connected to the actuator (300), the actuator (300) being capable of moving the silencer ring (200) to adjust the gap of the silencer ring; the actuator (300) comprising a cylinder (310), a piston (320) and an elastic element (330), the cylinder (310) being arranged on the compressor casing (100), the silencer ring (200) being connected to the piston (320), the elastic element (330) being arranged along the axial direction of the compressor inlet outer pipe (110) and being connected between the piston (320) and a fixed part of the compressor casing (100); the silencer ring (200) being capable of moving away from the compressor inlet inner pipe (120) under the action of the piston (320) moving along the axial direction of the compressor inlet outer pipe (110); the silencer ring (200) being capable of moving towards the compressor inlet inner pipe (120) under the elastic recovery action of the elastic element (330); the method comprising: obtaining a silencer ring gap calibration value based on the current engine operating condition; adjusting the silencer ring (200) so that the gap of the silencer ring is equal to the silencer ring gap calibration value; wherein the method for calibrating the silencer ring gap calibration value comprises: testing the supercharger noise corresponding to different silencer ring gaps under the to-be-tested engine operating condition; obtaining the width value of the silencer ring gap when the noise is the smallest under the to-be-tested engine operating condition, and calibrating the width value as the silencer ring gap calibration value under the to-be-tested engine operating condition; and obtaining the corresponding relationship between the engine operating condition and the silencer ring gap; and adjusting the width value of the gap of the silencer ring to be equal to the silencer ring gap calibration value comprises: performing closed-loop control on the silencer ring (200) so that the actual width value of the gap of the silencer ring is equal to the set width value; and confirming that the engine is in a stable running stage before obtaining the silencer ring gap calibration value. ​ ​ ​ characterized in that ​ ​ ​ ​ ​ 2. The tone ring gap control method of claim 1 wherein, ​ ​ 3. The tone ring gap control method of claim 1 wherein, ​ 4. A supercharger, comprising a compressor housing (100) and a sound attenuation ring (200), the compressor housing (100) comprising a compressor inlet outer pipe (110), a compressor inlet inner pipe (120) and an outlet volute (130), the compressor inlet outer pipe (110) and the outlet volute (130) being coaxially fixedly connected, the compressor inlet inner pipe (120) being coaxially arranged in the compressor inlet outer pipe (110) to form an airflow passage (140), an inlet passage (150) being formed in the compressor inlet inner pipe (120), the compressor inlet inner pipe (120) being provided with a flow widening flow channel (121) which is in communication with the inlet passage (150) and the airflow passage (140), the sound attenuation ring (200) being connected to the compressor housing (100) and being arranged in the axial direction of the compressor inlet outer pipe (110) and spaced apart from the compressor inlet inner pipe (120) to form a sound attenuation ring gap, the flow widening flow channel (121) being an inlet of the airflow passage (140), and the sound attenuation ring gap being an outlet of the airflow passage (140); the outlet volute (130) being in communication with an inner cavity of an engine and the inlet passage (150) and capable of expanding and guiding the airflow from the inlet passage (150) into the inner cavity of the engine; characterized in that the supercharger being capable of adjusting the sound attenuation ring gap based on the sound attenuation ring gap control method according to any one of claims 1-3.

5. The supercharger of claim 4, wherein, The actuator (300) further comprises a control valve (340) arranged between a rodless cavity of the cylinder (310) and a gas source, the control valve (340) being capable of controlling the amount of gas from the gas source entering the rodless cavity.

6. The supercharger of claim 5, wherein, The supercharger further comprises a control mechanism communicatively connected to the control valve (340) and capable of controlling the opening degree of the control valve (340).

7. The supercharger of claim 6, wherein, The actuator (300) further comprises a pressure sensor (350) arranged on a fixed portion of the compressor housing (100), connected to the elastic element (330) and communicatively connected to the control mechanism, the pressure sensor (350) being capable of detecting the elastic force of the elastic element (330) and calculating the deformation amount of the elastic element (330) according to the elastic force of the elastic element (330), the deformation amount of the elastic element (330) being equal to the adjustment amount of the sound attenuation ring gap.

8. The supercharger of any of claims 4-7, wherein, The cylinder (310) has a ring structure, and the piston (320) comprises a plurality of piston rods which are circumferentially and spacedly arranged in the compressor inlet outer pipe (110) and connected to the sound attenuation ring (200). The elastic element (330) is in one-to-one correspondence with the piston rod, and a plurality of elastic elements (330) are circumferentially and spacedly arranged in the compressor inlet outer pipe (110) and connected to the sound attenuation ring (200) and the corresponding piston rod.

9. Vehicle, characterized in that The supercharger according to any one of claims 4 to 8, wherein the engine has a combustion chamber which is connected to the outlet scroll passage (130).

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