Silencer for refrigerant and air conditioning system

Abstract

The utility model relates to air conditioning system, specifically provide a refrigerant's silencer and air conditioning system, to solve the refrigerant of existing in air conditioning system operation easy to produce high frequency noise and difficult to effectively restrain, and the existing noise reduction scheme still has the problem of significant deficiency in high frequency noise control, safety, system performance and compactness of structure etc. For this purpose, a refrigerant's silencer of the utility model includes tubular shell, and the refrigerant can flow inside the tubular shell, and the tubular shell includes first stage cavity, second stage cavity and third stage cavity connected in turn, the diameter of first stage cavity is greater than the diameter of second stage cavity, and the diameter of second stage cavity is greater than the diameter of third stage cavity. By setting the diameter of three tubular structures from big to small in turn decreases, can effectively change the refrigerant flow state under the premise of not significantly increasing system resistance, realizes the graded attenuation and disturbance suppression of different frequency band noise especially high frequency noise.

Description

Technical Field

[0001] This utility model relates to air conditioning systems, specifically providing a refrigerant muffler and an air conditioning system. Background Technology

[0002] In air conditioning systems using R290 refrigerant, its low density, high flow velocity, and flammability easily generate high-frequency mechanical noise, turbulent noise, and gas-liquid two-phase flow noise during operation, significantly impacting the overall quietness and user experience. To address this issue, the market currently offers three main technical solutions: compressor optimization, system design optimization, and external noise reduction measures. Compressor optimization involves improving key components such as valves and bearings to reduce mechanical vibration and friction, employing low-oil-volume technology to reduce flammability risks and oil noise, and introducing variable frequency control to dynamically adjust speed while balancing energy efficiency and noise control. System design involves adjusting capillary tube length and inner diameter to reduce airflow pulsation, optimizing heat exchanger structure to reduce flow noise, and controlling R290 charge to avoid abnormal noise sources. External noise reduction measures include using sound-absorbing cotton to cover the casing and compressor, and attaching sound-absorbing sponges to noise-generating areas such as air ducts or motors to achieve physical blocking and absorption.

[0003] While the aforementioned technologies have improved the noise problem of R290 systems to some extent, significant shortcomings remain. On the one hand, traditional silencing structures have limited effectiveness in suppressing high-frequency noise above 2000Hz and can cause significant pressure drops in high-flow-rate R290 environments, affecting system performance. On the other hand, due to flame-retardant safety considerations, the types and thicknesses of porous sound-absorbing materials are strictly limited, thus restricting their sound absorption capacity. Furthermore, the high-frequency vibration transmission path of the compressor has not been effectively isolated, leading to further exacerbation of secondary radiated noise. More importantly, existing optimization solutions often involve increased equipment size, higher costs, more complex debugging, and long-term performance degradation. Therefore, there is an urgent need to propose a novel noise reduction solution that is compact, adaptable to the properties of R290, and possesses high acoustic performance and good safety to overcome the limitations of existing technologies.

[0004] Therefore, there is an urgent need in the field for a refrigerant silencer and air conditioning system to solve the above problems. Utility Model Content

[0005] The present invention aims to solve the above-mentioned technical problems, namely, to solve the problem that existing refrigerants easily generate high-frequency noise during the operation of air conditioning systems and are difficult to suppress effectively, and that existing noise reduction solutions still have significant shortcomings in terms of high-frequency noise control, safety, system performance and structural compactness.

[0006] In a first aspect, the present invention provides a refrigerant silencer, the silencer comprising a tubular outer shell, wherein the refrigerant is capable of flowing inside the tubular outer shell, the tubular outer shell comprising a first-stage cavity, a second-stage cavity, and a third-stage cavity connected in sequence, wherein the diameter of the first-stage cavity is larger than the diameter of the second-stage cavity, and the diameter of the second-stage cavity is larger than the diameter of the third-stage cavity.

[0007] In the specific implementation of the above-mentioned muffler, the volume of the first-stage cavity is greater than the volume of the second-stage cavity, and the volume of the second-stage cavity is greater than the volume of the third-stage cavity.

[0008] In a specific embodiment of the above-described muffler, the tubular outer shell further includes an inlet, which is located at the end of the first-stage cavity away from the second-stage cavity, and the diameter of the inlet is smaller than the diameter of the first-stage cavity; and / or

[0009] The tubular outer shell also includes an outlet, which is located at the end of the third-stage cavity away from the second-stage cavity, and the diameter of the third-stage cavity is larger than the diameter of the outlet.

[0010] In a specific embodiment of the above-described muffler, the tubular outer shell further includes a first transition section, which is disposed between the inlet and the first-stage cavity, and the first transition section is a conical shell; and / or

[0011] The tubular outer shell further includes a second transition section, which is disposed between the first-stage cavity and the second-stage cavity, and the second transition section is in the shape of a conical shell; and / or

[0012] The tubular outer shell further includes a third transition section, which is disposed between the second-stage cavity and the third-stage cavity, and the third transition section is in the shape of a conical shell; and / or

[0013] The tubular outer shell also includes a fourth transition section, which is disposed between the third-stage cavity and the outlet, and the fourth transition section is a conical shell.

[0014] In a specific embodiment of the above-mentioned muffler, the muffler further includes a first muffler component, which is cylindrical in shape and has multiple through holes. The first-stage cavity of the tubular outer shell is sleeved on the outside of the first muffler component, and the inner wall of the first-stage cavity is spaced apart from the first muffler component.

[0015] In a specific embodiment of the above-mentioned muffler, the muffler further includes a first silencing layer, which is laid on the inner wall of the first-stage cavity.

[0016] In a specific embodiment of the above-mentioned muffler, the inner wall of the second-stage cavity is provided with threads, and the refrigerant in the second-stage cavity can flow along the threads.

[0017] In a specific embodiment of the above-mentioned muffler, the muffler further includes a second silencing layer, which is laid on the inner wall of the third-stage cavity. The second silencing layer is provided with a plurality of stepped holes, the large-diameter end of which is close to the inner wall of the third-stage cavity, and the small-diameter end of which is far away from the inner wall of the third-stage cavity.

[0018] In a specific embodiment of the above-mentioned muffler, the muffler further includes a second muffler component and a third muffler layer. The second muffler component is cylindrical in shape and has multiple through holes. The third-stage cavity of the tubular outer shell is fitted over the second muffler component. The third muffler layer is laid on the inner wall of the third-stage cavity. The third muffler layer is spaced apart from the second muffler component.

[0019] In a second aspect, the present invention provides an air conditioning system that includes the aforementioned muffler.

[0020] By adopting the above technical solution, this utility model, through the setting of a tubular structure with a first-stage cavity, a second-stage cavity, and a third-stage cavity whose diameters decrease sequentially from large to small, can effectively change the refrigerant flow state without significantly increasing the system resistance, thereby achieving graded attenuation and disturbance suppression of noise in different frequency bands, especially high-frequency noise. At the same time, this structure has good fluid guidance and structural compactness, which is conducive to improving the overall noise reduction performance and reducing pressure drop loss, while also taking into account the high flow rate characteristics and safety requirements of R290 refrigerant, and has excellent comprehensive noise reduction effect and engineering application value.

[0021] Furthermore, by setting the volume of the first-stage cavity to the third-stage cavity in a sequentially decreasing manner, the silencer can achieve gradual energy dissipation and smooth transition of pressure gradient during the refrigerant flow process, effectively reducing turbulence and pulsating noise caused by sudden changes in flow velocity or gas-liquid two-phase interaction. Especially when dealing with complex sound sources under high-frequency and high-flow-velocity conditions, this graded volume design can improve the adaptability and suppression efficiency of noise in different frequency bands, while reducing flow resistance and pressure drop, which helps to improve the overall acoustic performance and maintain the stability and energy efficiency of system operation.

[0022] Furthermore, this invention, by setting a cylindrical first silencing component with multiple through holes inside the first-stage cavity and forming an interval space between it and the inner wall of the first-stage cavity, can achieve multi-path turbulence and sound wave scattering without significantly affecting airflow, thereby enhancing the interference and absorption effect on high-frequency noise during refrigerant flow. The multiple through holes help sound waves enter the internal cavity for repeated reflection and dissipation, improving sound energy attenuation efficiency. Moreover, the structure is compact and easy to install, which not only enhances noise reduction performance but also maintains the structural stability and adaptability of the system.

[0023] Furthermore, by applying a first sound-absorbing layer to the inner wall of the first-stage cavity, this invention can further enhance the absorption capacity for high-frequency and mid-to-high-frequency noise. Especially in environments with high refrigerant flow rates, this sound-absorbing layer can effectively reduce sound wave reflection and enhance sound energy dissipation, thereby significantly reducing airflow disturbance and secondary radiation noise.

[0024] Furthermore, by setting threads on the inner wall of the second-stage cavity, the refrigerant flows along the thread surface, causing the fluid to generate a rotating turbulent effect, enhancing the interaction between the fluid and the inner wall, thereby effectively disrupting the stable structure of the gas-liquid two-phase flow and reducing the generation of turbulent noise and pulsating noise. At the same time, the threaded structure helps to disperse fluid energy, improve the noise attenuation effect, and improve the uniformity of the flow field while maintaining the flow efficiency, thus significantly improving the noise reduction performance of the silencer for complex sound sources and the overall system operation stability.

[0025] Furthermore, this invention lays a second silencing layer with multiple stepped holes on the inner wall of the third-stage cavity. The stepped hole structure enables multiple refractions and reflections of sound waves, effectively enhancing the absorption and attenuation of high-frequency noise. The large-diameter end of the stepped hole is close to the inner wall, which facilitates the smooth entry of sound waves into the silencing layer, while the small-diameter end is far from the inner wall, forming a gradual change in impedance, which helps to gradually dissipate sound energy and significantly improves the suppression effect of the silencer on high-frequency and complex sound waves. At the same time, this design takes into account the fluid flow performance, avoids excessive pressure drop, and enhances the overall quietness and operating efficiency of the system. Attached Figure Description

[0026] The preferred embodiments of this utility model are described below with reference to the accompanying drawings, in which:

[0027] Figure 1 This is a schematic diagram of the external structure of the tubular shell provided by this utility model;

[0028] Figure 2 This is a schematic diagram of the internal structure of the first-stage cavity provided by this utility model;

[0029] Figure 3 This is a schematic diagram of the internal structure of the second-stage cavity provided by this utility model;

[0030] Figure 4 This is a schematic diagram of the internal structure of the third-stage cavity provided by this utility model.

[0031] List of reference numerals in the attached diagram:

[0032] 1. Tubular outer shell; 11. First-stage cavity; 111. First silencing component; 112. First silencing layer; 12. Second-stage cavity; 121. Thread; 13. Third-stage cavity; 131. Second silencing layer; 132. Stepped hole; 1321. Large diameter end; 1322. Small diameter end; 14. Inlet; 15. Outlet; 16. First transition section; 17. Second transition section; 18. Third transition section; 19. Fourth transition section. Detailed Implementation

[0033] Preferred embodiments of the present invention will now be described with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely illustrative of the technical principles of the present invention and are not intended to limit the scope of protection of the present invention.

[0034] It should be noted that in the description of this utility model, the terms "upper," "lower," "left," "right," "inner," and "outer," which indicate directional or positional relationships, are based on the directional or positional relationships shown in the accompanying drawings. These are merely for ease of description and do not indicate or imply that the device or element must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0035] Furthermore, it should be noted that, in the description of this utility model, unless otherwise explicitly specified and limited, the terms "installation," "setting," and "connection" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection, an indirect connection through an intermediate medium, or a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0036] To address the problem that existing refrigerants easily generate high-frequency noise during air conditioning system operation, which is difficult to suppress effectively, and that existing noise reduction solutions still have significant shortcomings in terms of high-frequency noise control, safety, system performance, and structural compactness, this embodiment discloses an air conditioner. The air conditioner includes a silencer located at the compressor outlet. The refrigerant output from the compressor flows into the silencer. In this embodiment, the refrigerant type is R290. In other embodiments, other types of refrigerants may be used.

[0037] Reference Figure 1The muffler includes a tubular housing 1, which includes an inlet 14, a first transition section 16, a first-stage cavity 11, a second transition section 17, a second-stage cavity 12, a third transition section 18, a third-stage cavity 13, a fourth transition section 19, and an outlet 15 connected sequentially along the axial direction.

[0038] Specifically, the diameter of the first-stage cavity 11 is larger than the diameter of the second-stage cavity 12, the diameter of the second-stage cavity 12 is larger than the diameter of the third-stage cavity 13, and the diameter of the third-stage cavity 13 is larger than the diameters of the inlet 14 and the outlet 15. The first transition section 16 is a conical shell connecting the inlet 14 and the first-stage cavity 11, the second transition section 17 is a conical shell connecting the first-stage cavity 11 and the second-stage cavity 12, the third transition section 18 is a conical shell connecting the second-stage cavity 12 and the third-stage cavity 13, and the fourth transition section 19 is a conical shell connecting the third-stage cavity 13 and the outlet 15.

[0039] Furthermore, the volume of the first-stage cavity 11 is larger than that of the second-stage cavity 12, and the volume of the second-stage cavity 12 is larger than that of the third-stage cavity 13. By setting the volumes of the first-stage cavity 11 to the third-stage cavity 13 to decrease sequentially, the silencer can achieve gradual energy dissipation and smooth transition of pressure gradient during the refrigerant flow process, effectively reducing turbulence and pulsating noise caused by sudden changes in flow velocity or gas-liquid two-phase interaction. Especially when dealing with complex sound sources under high-frequency and high-flow-velocity conditions, this graded volume design can improve the adaptability and suppression efficiency of noise in different frequency bands, while reducing flow resistance and pressure drop, which helps to improve the overall acoustic performance and maintain the stability and energy efficiency of system operation.

[0040] Regarding the volume of the tubular outer shell 1, it should be noted that although the volume of the first-stage cavity 11 in this embodiment is greater than the volume of the second-stage cavity 12, and the volume of the second-stage cavity 12 is greater than the volume of the third-stage cavity 13, this arrangement is not a limitation of the present invention. Without departing from the principle of the present invention, those skilled in the art can adopt other arrangements in other embodiments, such as: the volumes of the first-stage cavity 11, the second-stage cavity 12, and the third-stage cavity 13 are the same. This does not depart from the basic principle of the present invention and therefore will fall within the protection scope of the present invention.

[0041] Furthermore, referring to Figure 2The silencer also includes a first silencing component 111 and a first silencing layer 112. The first silencing layer 112 is laid on the inner wall of the first-stage cavity 11, and the material of the first silencing layer 112 is a sound-absorbing material, specifically a porous ceramic felt sound-absorbing material. The first silencing component 111 is specifically a stainless steel micro-perforated plate (MPP). Specifically, the first silencing component 111 is cylindrical in shape and is inserted inside the first-stage cavity 11. The first silencing component 111 and the first silencing layer 112 are spaced apart. The first silencing component 111 has multiple through holes with a diameter ranging from 0.05 mm to 1.0 mm and a density ranging from 1,000 holes / m² to 1,000,000 holes / m². When the refrigerant carrying noise enters the first-stage cavity 11 from inlet 14, the refrigerant flow rate drops sharply due to the large volume of the first-stage cavity 11. The cavity volume expansion effect effectively weakens low-frequency pressure pulsations, thus providing initial absorption of mid-to-low frequency noise. Simultaneously, the first silencing component 111 absorbs mid-frequency noise through the microporous resonance principle; the first silencing layer 112 dissipates high-frequency sound energy, achieving preferential absorption of mid-to-low frequency noise and suppression of airflow impact.

[0042] Furthermore, referring to Figure 3 The second-stage cavity 12 has internal threads 121, allowing refrigerant flowing into it to move along these threads. This threaded flow-guiding structure effectively disrupts the refrigerant boundary layer development process, weakens turbulence intensity, and reduces eddy shedding, thereby lowering mid-to-high frequency noise caused by turbulence. Simultaneously, the tapered structure of the third transition section 18 improves pressure recovery efficiency, further reducing flow resistance and stabilizing the flow field distribution. The spiral flow-guiding structure and the tapered structure form a synergistic coupling design, achieving not only multi-path suppression of turbulent noise but also simultaneously optimizing airflow orderliness and system pressure loss control. Combining the acoustic reflection and interference characteristics of the cavity, this structural design improves noise reduction efficiency while ensuring the operating efficiency and energy efficiency of the air conditioning system.

[0043] Furthermore, referring to Figure 4The silencer also includes a second silencing layer 131, which is laid on the inner wall of the third-stage cavity 13. The second silencing layer 131 is made of aluminum foam. Furthermore, the second silencing layer 131 is provided with multiple stepped holes 132. The large-diameter end 1321 of the stepped hole 132 is located close to the inner wall of the third-stage cavity 13, and the small-diameter end 1322 is located away from the inner wall of the third-stage cavity 13. When the refrigerant carries residual noise into the third-stage cavity 13, this structure can effectively absorb high-frequency noise using the small-diameter end 1322 of the stepped hole 132, while simultaneously suppressing residual mid-frequency noise through the large-diameter end 1321, thereby achieving synergistic attenuation of wide-band noise. Combining the small volume design of the third-stage cavity 13 and the tapered structure of the fourth transition section 19, the second sound-absorbing layer 131 further enhances the system's targeted suppression effect on high-frequency noise, making its overall attenuation performance significantly better than that of traditional homogeneous cavity structure schemes when dealing with high-frequency noise-concentrated refrigerants such as R290.

[0044] Regarding the third-stage cavity 13 of the silencer, it should be noted that although a second sound-absorbing layer 131 is provided on the inner wall of the third-stage cavity 13 in this embodiment, this arrangement is not a limitation of the present invention. Without departing from the principle of the present invention, those skilled in the art can use other arrangements in other embodiments. For example, the silencer may also include a second sound-absorbing component and a third sound-absorbing layer. The third sound-absorbing layer is made of fiber sound-absorbing material, including but not limited to cotton and linen sound-absorbing materials and glass fiber sound-absorbing materials. The third sound-absorbing layer is laid on the inner wall of the third-stage cavity 13. The second sound-absorbing component is specifically a perforated plate, cylindrical in shape, which is inserted into the interior of the third-stage cavity 13. The second sound-absorbing component and the third sound-absorbing layer are spaced apart, and the perforated plate has through holes. This arrangement enables the second sound-absorbing component to absorb high-frequency noise, and the third sound-absorbing layer to absorb mid-frequency noise. This does not depart from the basic principle of the present invention and therefore falls within the protection scope of the present invention.

[0045] Furthermore, both the stainless steel micro-perforated plate and the foamed aluminum material are non-combustible or flame-retardant structural materials, suitable for air conditioning systems using flammable refrigerants such as R290. While meeting fire safety requirements, they construct a multi-frequency synergistic sound absorption system covering the mid-to-high frequency band. Specifically, the stainless steel micro-perforated plate in the first-stage cavity 11 primarily absorbs mid-frequency noise, while the stepped-hole foamed aluminum material lining the inner wall of the third-stage cavity 13 has excellent absorption and attenuation capabilities for high-frequency noise. The synergistic effect of both effectively overcomes the limitations of single sound-absorbing materials in frequency band coverage, achieving targeted control of the full-spectrum characteristics of R290 noise. Compared to traditional structures using fiber-based sound-absorbing materials, this composite sound absorption system not only possesses higher structural stability and material reliability under high temperature and humidity conditions, but also significantly improves the overall acoustic performance of the silencer and the safety and stability of system operation, making it suitable for the long-term operation requirements of air conditioning outdoor units.

[0046] The technical solution of this utility model has been described in conjunction with the preferred embodiments shown in the accompanying drawings. However, it will be readily understood by those skilled in the art that the protection scope of this utility model is obviously not limited to these specific embodiments. Without departing from the principle of this utility model, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after these changes or substitutions will all fall within the protection scope of this utility model.

Claims

1. A refrigerant silencer, characterized in that, The device includes a tubular outer shell (1) in which the refrigerant can flow. The tubular outer shell (1) includes a first-stage cavity (11), a second-stage cavity (12), and a third-stage cavity (13) connected in sequence. The diameter of the first-stage cavity (11) is larger than the diameter of the second-stage cavity (12), and the diameter of the second-stage cavity (12) is larger than the diameter of the third-stage cavity (13).

2. The silencer according to claim 1, characterized in that, The volume of the first-stage cavity (11) is greater than the volume of the second-stage cavity (12), and the volume of the second-stage cavity (12) is greater than the volume of the third-stage cavity (13).

3. The silencer according to claim 1, characterized in that, The tubular outer shell (1) further includes an inlet (14), which is located at the end of the first-stage cavity (11) away from the second-stage cavity (12), and the diameter of the inlet (14) is smaller than the diameter of the first-stage cavity (11); and / or The tubular outer shell (1) also includes an outlet (15), which is located at one end of the third-stage cavity (13) away from the second-stage cavity (12), and the diameter of the third-stage cavity (13) is larger than the diameter of the outlet (15).

4. The silencer according to claim 3, characterized in that, The tubular outer shell (1) further includes a first transition section (16), which is disposed between the inlet (14) and the first stage cavity (11). The first transition section (16) is in the shape of a conical shell; and / or The tubular outer shell (1) further includes a second transition section (17), which is disposed between the first-stage cavity (11) and the second-stage cavity (12), and the second transition section (17) is a conical shell; and / or The tubular outer shell (1) further includes a third transition section (18), which is disposed between the second-stage cavity (12) and the third-stage cavity (13), and the third transition section (18) is in the shape of a conical shell; and / or The tubular outer shell (1) further includes a fourth transition section (19), which is disposed between the third-stage cavity (13) and the outlet (15). The fourth transition section (19) is a conical shell.

5. The silencer according to claim 1, characterized in that, The muffler also includes a first muffler (111), which is cylindrical in shape and has multiple through holes. The first stage cavity (11) of the tubular outer shell (1) is sleeved on the outside of the first muffler (111), and the inner wall of the first stage cavity (11) is spaced apart from the first muffler (111).

6. The silencer according to claim 1, characterized in that, The silencer also includes a first silencing layer (112), which is laid on the inner wall of the first-stage cavity (11).

7. The silencer according to claim 1, characterized in that, The inner wall of the second-stage cavity (12) is provided with threads (121), and the refrigerant in the second-stage cavity (12) can flow along the threads (121).

8. The silencer according to claim 1, characterized in that, The silencer also includes a second silencing layer (131), which is laid on the inner wall of the third-stage cavity (13). The second silencing layer (131) is provided with a plurality of stepped holes (132). The large-diameter end (1321) of the stepped hole (132) is close to the inner wall of the third-stage cavity (13), and the small-diameter end (1322) of the stepped hole (132) is far away from the inner wall of the third-stage cavity (13).

9. The silencer according to claim 1, characterized in that, The muffler also includes a second muffler and a third muffler layer. The second muffler is cylindrical in shape and has multiple through holes. The third-stage cavity (13) of the tubular outer shell (1) is fitted over the second muffler. The third muffler layer is laid on the inner wall of the third-stage cavity (13) and is spaced apart from the second muffler.

10. An air conditioning system, characterized in that, Includes the silencer as described in any one of claims 1-9.

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