Exhaust silencing assembly and air compressor assembly
By designing a shrink-expansion-shrink structure and a gradient surface for the exhaust muffler assembly, the problems of pressure pulsation and noise in the compressor pipeline of traditional mufflers are solved, achieving a wide-band, high-efficiency noise reduction effect.
Patent Information
- Application Number
- CN202423236973.3
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-12-25
- Publication Date
- 2025-11-07
- Estimated Expiration
- 2034-12-25
AI Technical Summary
Traditional silencers have significant pressure pulsations and radiated noise in the pipeline between the compressor unit and the silencer, making it difficult to achieve a wide-band, high-amplitude silencer effect.
Design an exhaust muffler assembly, including an intake section, an exhaust section, and an expansion section connecting the two. The airflow channel inside the assembly forms a contraction-expansion-contraction structure. The volume is increased by the expansion section to weaken the sound wave energy. Gradient surfaces are set on the inner surfaces of the intake venturi and exhaust venturi to avoid airflow impact, thereby achieving wideband noise reduction.
Significant noise reduction and silencing effects can be achieved in low, medium and high frequency bands, especially in the 1000Hz to 1200Hz frequency band, where the silencing amount reaches 35 to 40dB, reducing pressure pulsation and noise.
Smart Images
Figure CN223523913U_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The present application relates to the field of noise reduction technology, in particular to an exhaust muffling assembly and an air compressor assembly. BACKGROUND
[0002] In order to meet the needs of various industries, new low-pressure air compressor and blower product series have been continuously introduced in recent years, but the noise problem seriously affects the industrial application experience, therefore, a muffling device is needed to reduce the pressure pulsation and aerodynamic noise downstream of the main machine.
[0003] Traditional muffling devices are mostly installed near the client end, but there is still a large pressure pulsation in the pipeline between the exhaust port of the compressor main machine and the muffling device, which further causes high radiation noise. Some improved muffling devices have limited noise reduction frequency band and amplitude, and it is difficult to achieve good noise reduction effect. Therefore, it is necessary to develop a new type of muffling structure with wider noise reduction frequency band, higher amplitude and lighter weight. SUMMARY
[0004] The present application provides an exhaust muffling assembly and an air compressor assembly, which has a wide noise reduction frequency band and high noise reduction amplitude.
[0005] An exhaust muffling assembly includes an air inlet part, an exhaust part, and an expansion part connecting the air inlet part and the exhaust part, the air inlet part is provided with an air inlet, the exhaust part is provided with an exhaust port, the volume of the expansion part is larger than the volume of the air inlet part and also larger than the volume of the exhaust part, and the area of any flow cross section of the expansion part is larger than the area of each flow cross section of the air inlet part and also larger than the area of each flow cross section of the exhaust part.
[0006] Optionally, the air inlet part includes an air inlet Venturi, the air inlet Venturi includes a first throat with the smallest flow cross section, on the air inlet side of the first throat, the area of the flow cross section of the air inlet Venturi gradually decreases along the airflow direction, and on the exhaust side of the first throat, the area of the flow cross section of the air inlet Venturi gradually increases along the airflow direction; and / or
[0007] The exhaust part includes an exhaust Venturi, the exhaust Venturi includes a second throat with the smallest flow cross section, on the air inlet side of the second throat, the area of the flow cross section of the exhaust Venturi gradually decreases along the airflow direction, and on the exhaust side of the second throat, the area of the flow cross section of the exhaust Venturi gradually increases along the airflow direction.
[0008] Optionally, the air inlet part includes the air inlet Venturi, on the air inlet side of the first throat, the inner surface of the air inlet Venturi gradually shrinks inward along the airflow direction in the form of a tapered arc surface, and on the exhaust side of the first throat, the inner surface of the air inlet Venturi gradually expands outward along the airflow direction in the form of a tapered conical surface.
[0009] Optionally, the air inlet part comprises the air inlet venturi, the air inlet venturi further comprises a first side part arranged at the air inlet side of the first throat part and a second side part arranged at the air exhaust side of the first throat part, the first side part is formed with the air inlet port, the second side part is connected with the expansion part, the distance from the end face of the one end of the first side part away from the expansion part to the first throat part is smaller than the distance from the connecting face of the second side part with the expansion part to the first throat part.
[0010] Optionally, the air exhaust part comprises the air exhaust venturi, the inner surface of the air exhaust venturi gradually shrinks inward along the airflow direction in a tapered arc surface at the air exhaust side of the second throat part, the inner surface of the air exhaust venturi gradually expands outward along the airflow direction in a tapered conical surface at the air exhaust side of the second throat part.
[0011] Optionally, the air exhaust part comprises the air exhaust venturi and the connecting part, the air exhaust venturi further comprises a third side part arranged at the air inlet side of the second throat part and a fourth side part arranged at the air exhaust side of the second throat part, the third side part is connected with the expansion part, the fourth side part is connected with the connecting part, the distance from the connecting face of the third side part with the expansion part to the second throat part is smaller than the distance from the connecting face of the fourth side part with the connecting part to the second throat part.
[0012] Optionally, the expansion part comprises a first cylindrical segment, a tapered segment and a second cylindrical segment connected in sequence along the airflow direction, the inner diameter of the first cylindrical segment is equal everywhere, the inner diameter of the second cylindrical segment is equal everywhere, the inner diameter of the tapered segment gradually decreases along the airflow direction.
[0013] Optionally, the ratio of the equivalent spherical diameter of the inner cavity of the expansion part to the diameter of the air inlet port is 1.5-3.
[0014] Optionally, the air inlet port and the air exhaust port are spaced apart by an angle α, 90°≤α≤180°.
[0015] An air compressor assembly, comprising:
[0016] An air compressor, comprising an air exhaust end;
[0017] The air exhaust silencing assembly according to any one of the preceding items, the air inlet part of the air exhaust silencing assembly is connected with the air exhaust end. BRIEF DESCRIPTION OF DRAWINGS
[0018] Figure 1 is a schematic view of an air exhaust silencing assembly according to an exemplary embodiment of the present application;
[0019] Figure 2 is Figure 1a cross-sectional view of the exhaust muffling assembly shown in FIG. 1;
[0020] Figure 3 is Figure 1 an exploded view of the exhaust muffling assembly shown in FIG. 1;
[0021] Figure 4 is a further cross-sectional view of the exhaust muffling assembly;
[0022] Figure 5 is a sound wave transmission diagram. DETAILED DESCRIPTION
[0023] The technical solutions in the embodiments (or, modes of implementation) of the present application will be described clearly and completely in conjunction with the accompanying drawings. When the following description refers to the drawings, the same numbers in different drawings represent the same or similar elements unless otherwise indicated.
[0024] If the present application embodiments involve directional indications or positional relationships (such as up, down, left, right, front, back, inner, outer, top, bottom, center, vertical, horizontal, longitudinal, transverse, length, width, counterclockwise, clockwise, axial, radial, circumferential, etc.), such terms are only used to explain the relative positional relationships, movement conditions, etc. between components in a certain posture (as shown in the drawings); if the certain posture changes, the directional indications or positional relationships also change accordingly. In addition, the terms "first", "second", etc. in the present application embodiments are only used for convenience of description, and cannot be understood as indicating or implying relative importance.
[0025] Please refer to Figure 1 and Figure 2 , Figure 1 is a schematic view of an exhaust muffling assembly 100 according to an example embodiment of the present application. Figure 2 is Figure 1 is a cross-sectional view of the exhaust muffling assembly 100 shown in FIG. 1.
[0026] The present application provides an exhaust muffling assembly 100 (hereinafter referred to as assembly 100), which can be installed at the exhaust end of an air compressor, for reducing noise at the exhaust end of the compressor.
[0027] The assembly 100 includes an air inlet portion 10, an air outlet portion 20, and an expansion portion 30 connecting the air inlet portion 10 and the air outlet portion 20. The air inlet portion 10 is provided with an air inlet 101, and the air outlet portion 20 is provided with an air outlet 201, and the airflow flows from the air inlet 101 to the air outlet 201. Figure 2 The direction of the arrow in FIG. 1 is the direction of the airflow.
[0028] The air inlet part 10, the air outlet part 20 and the expansion part 30 are all hollow structures, and the hollow parts form air flow channels for gas to pass through. The air inlet part 10 and / or the air outlet part 20 can be straight pipes with equal diameters, but are not limited to this.
[0029] The volume of the expansion part 30 is larger than that of the air inlet part 10 and also larger than that of the air outlet part 20. The area of any flow cross section of the expansion part 30 is larger than that of each flow cross section of the air inlet part 20 and also larger than that of each flow cross section of the air outlet part 20.
[0030] According to the above description, the flow cross sections of the air flow channels in the assembly 100 form a structure of contraction-expansion-contraction from the air inlet part 10 to the expansion part 30 and then to the air outlet part 20. The assembly 100 is provided with the expansion part 30, so that the air flow channels inside the assembly 100 form an expansion area with an increased volume. The expansion area can reduce pressure pulsation and achieve broadband noise reduction, so as to weaken the sound wave energy and achieve the purpose of noise reduction and noise elimination.
[0031] Please refer to Figure 2 and Figure 3 , Figure 3 for the exploded view of the air outlet noise reduction assembly 100.
[0032] In this embodiment, the air inlet part 10 includes an air inlet Venturi 11, which includes a first throat part 110 with the smallest flow cross section. On the air inlet side of the first throat part 110, the area of the flow cross section of the air inlet Venturi 11 gradually decreases along the air flow direction, and on the air outlet side of the first throat part 110, the area of the flow cross section of the air inlet Venturi 11 gradually increases along the air flow direction. In this scheme, the flow cross section of the air flow channel in the air inlet Venturi 11 forms a structure of contraction-expansion by providing the air inlet Venturi 11, so as to limit the high amplitude of the sound wave and further weaken the sound wave energy.
[0033] In the embodiment shown in Figure 2 , on the air inlet side of the first throat part 110, the inner surface 111 of the air inlet side of the air inlet Venturi 11 gradually shrinks inward along the air flow direction in the form of a tapered arc surface, and on the air outlet side of the first throat part 110, the inner surface 112 of the air outlet side of the air inlet Venturi 11 gradually expands outward along the air flow direction in the form of a tapered conical surface. That is, the inner surface 111 of the air inlet side and the inner surface 112 of the air outlet side are not abrupt surfaces, which can avoid a large impact on the air flow passing through this part, and can reduce the pressure loss while reducing noise.
[0034] As shown in Figure 2 and Figure 3As shown, the air inlet venturi 11 further comprises a first side portion 113 provided at the air inlet side of the first throat portion 110 and a second side portion 114 provided at the air outlet side of the first throat portion 110, the inner surface 111 is the inner surface of the first side portion 113, and the inner surface 112 is the inner surface of the second side portion 114, the first side portion 113 is provided with the air inlet port 101, the second side portion 114 is connected with the expansion portion 30, and the distance L1 from the end surface 1130 of the end of the first side portion 113 away from the expansion portion 30 to the first throat portion 110 is less than the distance L2 from the connecting surface 1140 of the second side portion 114 with the expansion portion 30 to the first throat portion 110. In this way, the volume of the air inlet side of the first throat portion 110 is less than the volume of the air outlet side of the first throat portion 110, so that the noise of different frequency bands can be eliminated, and the noise reduction and silencing in a wide frequency band can be achieved.
[0035] In Figure 3 In the embodiment shown, the end of the first side portion 113 away from the expansion portion 30 is formed with a flange, and the end surface 1130 is the end surface of the flange, and the air inlet port 101 is provided at the end surface 1130.
[0036] In one embodiment, the ratio of L2 to L1 is 2-3. For example, the ratio can be 2, 2.1, 2.2, 2.3, 2.4, 2.5, 2.6, 2.7, 2.8, 2.9, 3, but is not limited thereto. In a preferred embodiment, the ratio can be set to 2.5.
[0037] Please refer to Figure 2 and Figure 4 , Figure 4 is a sectional view of the exhaust silencing assembly 100.
[0038] In one embodiment, the ratio of the inner diameter d1 of the air inlet port 101 to the inner diameter d2 of the first throat portion 110 is 1.3-1.8. For example, the ratio can be 1.3, 1.4, 1.5, 1.6, 1.7, 1.8, but is not limited thereto. In a preferred embodiment, the ratio can be set to 1.5.
[0039] In one embodiment, the ratio of the inner diameter d3 of the air inlet end of the expansion portion 30 to the inner diameter d2 of the first throat portion 110 is 1.2-1.6. For example, the ratio can be 1.2, 1.3, 1.4, 1.5, 1.6, but is not limited thereto. In a preferred embodiment, the ratio can be set to 1.3.
[0040] Please refer to Figure 2 and Figure 3In one embodiment, the exhaust part 20 comprises the exhaust venturi 21, the exhaust venturi 21 comprises a second throat 210 with the minimum flow cross section, the inner surface 211 of the exhaust venturi 21 gradually shrinks inward along the airflow direction in a tapered arc surface manner on the exhaust side of the second throat 210, and the inner surface 212 of the exhaust venturi 21 gradually expands outward along the airflow direction in a tapered conical surface manner on the exhaust side of the second throat 210. That is, the inner surface 211 on the intake side and the inner surface 212 on the exhaust side are not abrupt surfaces, which can avoid large impact of airflow passing through this part, reduce noise and pressure loss at the same time.
[0041] In one embodiment, as shown in Figure 2 and Figure 3 , the exhaust part 20 comprises the exhaust venturi 21 and the connecting piece 22, the exhaust venturi 21 further comprises a third side 213 on the intake side of the second throat 210 and a fourth side 214 on the exhaust side of the second throat 210, the third side 213 is connected with the expansion part 30, the fourth side 214 is connected with the connecting piece 22, the distance p from the third side 213 to the first connection surface 2130 of the expansion part 30 to the second throat 210 is less than the distance q from the fourth side 214 to the second connection surface 2140 of the connecting piece 22 to the second throat 210. In this way, the volume on the intake side of the second throat 210 is less than the volume on the exhaust side of the second throat 210, which can eliminate noise of different frequency bands and achieve noise reduction and noise elimination in a wide frequency band.
[0042] The connecting piece 22 can be a double-hole flange, and can also be a multi-hole flange. An O-shaped elastic ring can be arranged in the connecting piece 22 to reduce rigid impact and achieve flexible connection, but is not limited thereto.
[0043] In one embodiment, the ratio of L7 to L8 is 2-3. For example, the ratio can be 2, 2.1, 2.2, 2.3, 2.4, 2.5, 2.6, 2.7, 2.8, 2.9, 3, but is not limited thereto. In a preferred embodiment, the ratio can be set to 2.5.
[0044] Please refer to Figure 2 and Figure 4 , in one embodiment, the ratio of the inner diameter d5 of the exhaust end of the expansion part 30 to the inner diameter d8 of the second throat 210 is 1.3-1.8. For example, the ratio can be 1.3, 1.4, 1.5, 1.6, 1.7, 1.8. In a preferred embodiment, the ratio can be set to 1.5.
[0045] In one embodiment, the ratio of the inner diameter d7 of the air outlet of the fourth side portion 214 to the inner diameter d8 of the second throat is 1.2 to 1.6. For example, this ratio can be 1.2, 1.3, 1.4, 1.5, or 1.6, but is not limited thereto. In a preferred embodiment, this ratio can be set to 1.3.
[0046] In one embodiment, such as Figure 3 As shown, along the airflow direction, the expansion section 30 includes a first cylindrical section 31, a tapering section 32, and a second cylindrical section 33 connected in sequence. The diameter of the first cylindrical section 31 is constant throughout, the diameter of the second cylindrical section 33 is constant throughout, and the diameter of the tapering section 32 gradually decreases along the airflow direction. This arrangement causes the expansion section 30 to contract at the tapering section 32, which helps to reduce the amplitude of the sound wave.
[0047] exist Figure 3 In the embodiment shown, the axis of the first cylindrical segment 31 is perpendicular to the axis of the second cylindrical segment 33, and the axis of the tapered segment 32 is collinear with the axis of the second cylindrical segment 33.
[0048] Please combine Figure 4 In one embodiment, the ratio of the equivalent spherical diameter of the inner cavity of the expansion portion 30 to the inner diameter d1 of the air inlet 101 is 1.5 to 3. For example, this ratio can be 1.5, 1.8, 2, 2.2, 2.5, 2.8, or 3, but is not limited to these. In a preferred embodiment, this ratio can be set to 2.
[0049] In one embodiment, the ratio of the inner diameter d4 of the first cylindrical segment 31 to the axial dimension L4 of the first cylindrical segment 31 is 0.8 to 1.2. For example, the ratio can be 0.8, 0.9, 1, 1.1, or 1.2, but is not limited to these. In a preferred embodiment, the ratio can be set to 1.
[0050] In one embodiment, the ratio of the inner diameter d4 of the first cylindrical section 31 to the inner diameter d3 of the air inlet end of the expansion portion 30 is 1.5 to 2. For example, this ratio can be 1.5, 1.6, 1.7, 1.8, 1.9, or 2, but is not limited to these. In a preferred embodiment, this ratio can be set to 1.8.
[0051] In one embodiment, the ratio of the inner diameter d4 of the first cylindrical section 31 to the inner diameter d5 of the outlet end of the expansion portion 30 is 1.3 to 1.8. For example, this ratio can be 1.3, 1.4, 1.5, 1.6, 1.7, or 1.8, but is not limited thereto. In a preferred embodiment, this ratio can be set to 1.5.
[0052] In one embodiment, the ratio of the axial dimension L4 of the inner cavity of the first cylindrical segment 31 to the dimension L5 of the inner cavity of the air intake 10 in this direction is 1.6 to 2.4. For example, the ratio can be 1.6, 1.8, 2, 2.2, or 2.4, but is not limited thereto. In a preferred embodiment, the ratio can be set to 2.
[0053] In one embodiment, the ratio of the dimension L5 of the inner cavity of the expansion portion 30 to the dimension L6 of the inner cavity of the exhaust venturi 21 in a direction perpendicular to the axis of the first cylindrical segment 31 is 3.2 to 4.8. For example, this ratio can be 3.2, 3.5, 3.8, 4, 4.2, 4.4, 4.5, or 4.8, but is not limited to these. In a preferred embodiment, this ratio can be set to 4.
[0054] In one embodiment, such as Figure 3 and Figure 4 As shown, the expansion portion 30 is also provided with a vent hole 34. The ratio of the inner diameter d4 of the inner cavity of the first cylindrical section 31 to the diameter d6 of the vent hole 34 is 2.5 to 3, which ensures sufficient venting capacity. For example, this ratio can be 2.5, 2.6, 2.7, or 2.8, but is not limited to these. In a preferred embodiment, this ratio can be set to 2.8. It should be noted that the specific location of the vent hole 34 is not limited.
[0055] In one embodiment, the air inlet 101 and the exhaust outlet 201 are spaced apart by an angle α, where 90° ≤ α ≤ 180°. α can be 90°, 100°, 120°, 160°, or 180°. In this embodiment, the air inlet 101 and the exhaust outlet 201 are spaced apart by 90°.
[0056] Please refer to Figure 5 , Figure 5 This is a diagram of sound wave transmission loss.
[0057] and Figure 5 It is known that the component 100 provided in this application can achieve noise reduction in low, medium and high frequency bands. Among them, in the range of 1000Hz to 1200Hz, the noise reduction reaches 35 to 40dB, and the noise reduction effect is relatively good.
[0058] This application also provides an air compressor assembly (not shown in the figures), which includes an air compressor and the exhaust muffler assembly 100 described above. The air compressor includes an exhaust end, and the intake portion 10 of the assembly 100 is connected to the exhaust end of the air compressor.
[0059] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the scope of protection of this application.
Claims
1. An exhaust silencing assembly, characterized by, The air intake part, the air exhaust part and the expansion part, the air intake part is provided with an air inlet, the air exhaust part is provided with an air outlet, the volume of the expansion part is larger than that of the air intake part and the air exhaust part, the area of any flow cross section of the expansion part is larger than that of the air intake part and the air exhaust part.
2. The exhaust silencing assembly of claim 1, wherein, The air intake part includes an air intake venturi, the air intake venturi includes a first throat with the smallest flow cross section, on the air intake side of the first throat, the area of the flow cross section of the air intake venturi gradually decreases along the air flow direction, on the air exhaust side of the first throat, the area of the flow cross section of the air intake venturi gradually increases along the air flow direction; and / or The air exhaust part includes an air exhaust venturi, the air exhaust venturi includes a second throat with the smallest flow cross section, on the air intake side of the second throat, the area of the flow cross section of the air exhaust venturi gradually decreases along the air flow direction, on the air exhaust side of the second throat, the area of the flow cross section of the air exhaust venturi gradually increases along the air flow direction.
3. The exhaust silencing assembly of claim 2, wherein, The air intake part includes the air intake venturi, on the air intake side of the first throat, the inner surface of the air intake venturi gradually shrinks inward along the air flow direction in the form of a tapered arc surface, on the air exhaust side of the first throat, the inner surface of the air intake venturi gradually expands outward along the air flow direction in the form of a tapered conical surface.
4. The exhaust silencing assembly of claim 2, wherein, The air intake part includes the air intake venturi, the air intake venturi further includes a first side part provided on the air intake side of the first throat and a second side part provided on the air exhaust side of the first throat, the first side part is formed with the air inlet, the second side part is connected with the expansion part, the distance from the end surface of the end of the first side part away from the expansion part to the first throat is smaller than the distance from the surface where the second side part is connected with the expansion part to the first throat.
5. The exhaust silencing assembly of claim 2, wherein, The air exhaust part includes the air exhaust venturi, on the air exhaust side of the second throat, the inner surface of the air exhaust venturi gradually shrinks inward along the air flow direction in the form of a tapered arc surface, on the air exhaust side of the second throat, the inner surface of the air exhaust venturi gradually expands outward along the air flow direction in the form of a tapered conical surface.
6. The exhaust silencing assembly of claim 5, wherein, The air exhaust part includes the air exhaust venturi and a connecting part, the air exhaust venturi further includes a third side part provided on the air intake side of the second throat and a fourth side part provided on the air exhaust side of the second throat, the third side part is connected with the expansion part, the fourth side part is connected with the connecting part, the distance from the surface where the third side part is connected with the expansion part to the second throat is smaller than the distance from the surface where the fourth side part is connected with the connecting part to the second throat.
7. The exhaust silencing assembly according to any one of claims 1 to 6, characterized in that, In the air flow direction, the expansion part includes a first cylindrical segment, a tapered segment and a second cylindrical segment connected in sequence, the inner diameter of the first cylindrical segment is equal everywhere, the inner diameter of the second cylindrical segment is equal everywhere, and the inner diameter of the tapered segment gradually decreases along the air flow direction.
8. The exhaust silencing assembly of claim 7, wherein, The ratio of the equivalent spherical diameter of the inner cavity of the expansion part to the diameter of the air inlet is 1.5-3.
9. The exhaust silencing assembly according to any one of claims 1 to 6, characterized in that, The air inlet and the air outlet are spaced apart by an angle α, 90°≤α≤180°.
10. An air compressor assembly characterized by, The air intake part, the air exhaust part and the expansion part, the air intake part is provided with an air inlet, the air exhaust part is provided with an air outlet, the volume of the expansion part is larger than that of the air intake part and the air exhaust part, the area of any flow cross section of the expansion part is larger than that of the air intake part and the air exhaust part. An air compressor comprising an exhaust end; An exhaust silencing assembly as claimed in any one of claims 1 to 9, the intake portion of the exhaust silencing assembly being connected to the exhaust end.