Air conditioner outdoor unit

Abstract

This application relates to an outdoor unit of an air conditioner, belonging to the field of air conditioning technology. The outdoor unit includes a compressor and a muffler. The muffler includes: a shell, which includes an inlet pipe and an outlet pipe; an inner pipe, with a cavity formed between the outer wall of the inner pipe and the inner wall of the shell; the inner pipe includes a fixed section and an open section, with a plurality of first through holes arranged at intervals on the open section; a first elastic diaphragm, which is disposed at the end of the inner pipe away from the inlet pipe, and a resonant block is disposed at the center of the first elastic diaphragm; and a plurality of second elastic diaphragms, arranged at intervals along the axial direction of the inner pipe, with a plurality of second through holes disposed on the second elastic diaphragms, and a resonant block is disposed at the center of the second elastic diaphragm. This application effectively solves the noise reduction "trough" problem of traditional expansion mufflers by using a triple synergistic noise reduction structure of perforation weakening, expansion weakening, and precise resonance cancellation, significantly enhancing the overall noise reduction capability of the refrigerant noise of the outdoor unit of the air conditioner.

Description

Technical Field

[0001] This application relates to the field of air conditioning technology, and more particularly to an outdoor unit for an air conditioner. Background Technology

[0002] The outdoor unit of an air conditioner is the core device in an air conditioning system that enables heat exchange and refrigerant circulation. It integrates several key components, including a compressor, condenser, cooling fan, refrigerant piping, gas-liquid separator, and four-way valve. The compressor, as the power source for the refrigerant circulation, is responsible for compressing the low-pressure, low-temperature refrigerant into a high-pressure, high-temperature state. The condenser cools and condenses the high-pressure gaseous refrigerant through heat exchange with the outdoor air. The cooling fan enhances the condenser's heat exchange efficiency by forcing airflow. The refrigerant piping serves as the channel connecting these components, forming a closed refrigerant circulation system that collectively achieves the air conditioner's cooling or heating functions.

[0003] As people's requirements for living environments become increasingly demanding, the noise problem of air conditioner outdoor units is receiving more and more attention. The noise of the outdoor unit originates from multiple sources, among which the refrigerant noise caused by the periodic intake and exhaust behavior of the compressor is a significant component. During operation, the compressor's intake and exhaust actions are significantly periodic, causing periodic fluctuations in the pressure within the refrigerant lines, i.e., pressure pulsations. When these pressure pulsations propagate through the refrigerant, they induce pipe vibrations and radiate noise to the outside. Because the compressor speed varies with the air conditioner's operating conditions (such as indoor and outdoor temperature differences, set temperature, etc.), the refrigerant pressure pulsations differ significantly at different speeds, thus causing the frequency of the refrigerant noise to change accordingly.

[0004] Installing silencers on refrigerant pipelines is a common method for reducing refrigerant noise, with expansion silencers being widely used. Their silencing principle involves causing a sudden change in acoustic impedance through the expansion (e.g., a thinner pipe connecting to a thicker pipe) or contraction (e.g., a thicker pipe connecting to a thinner pipe) of the pipe's cross-section. This causes a portion of the sound waves propagating along the pipe to be reflected towards the sound source, thereby reducing the energy of the transmitted sound waves and achieving silencing. However, existing expansion silencers have significant limitations: once the structural dimensions are determined, their corresponding silencing frequency band and noise reduction performance remain fixed. This inevitably leads to differences in reflection efficiency for different frequencies of sound waves, and even the inability to effectively reflect sound waves within a specific frequency range. Therefore, there are bound to be "trough" frequency bands with poor noise reduction (i.e., weak noise reduction intervals). More importantly, when the air conditioning compressor adjusts its speed due to changes in operating conditions, the frequency of refrigerant pressure pulsations changes accordingly. If the frequency of these pressure pulsations happens to fall within the "trough" frequency band of the silencer, it will severely weaken the overall noise reduction effect, making it difficult to meet the air conditioning system's requirement for wide-band and stable noise reduction. Utility Model Content

[0005] This application provides an outdoor unit for an air conditioner, the purpose of which is to reduce pressure pulsation at a specific frequency by designing a "mass-film" system with different resonant frequencies, and to superimpose the impedance change noise reduction characteristics of the original expansion silencer, thereby achieving a better noise reduction effect under multiple effects, thus avoiding the problem of obvious noise reduction "troughs" in traditional expansion silencers.

[0006] To achieve the above objectives, this application adopts the following technical solution: Firstly, an outdoor unit for an air conditioner is provided, comprising: The compressor is used to supply refrigerant to the heat exchanger; A silencer, the silencer connecting the compressor and the heat exchanger, the silencer comprising: The housing includes an inlet pipe and an outlet pipe, the inlet pipe being connected to the outlet of the compressor and the outlet pipe being connected to the inlet of the heat exchanger; An inner tube is disposed inside the outer shell; one end of the inner tube is connected to the inlet pipe, and a cavity is formed between the outer wall of the inner tube and the inner wall of the outer shell; the inner tube is provided with a plurality of first through holes along its axial direction. A first elastic film is disposed in the inner tube near one end of the outlet tube, and a resonant block is disposed at the center of the first elastic film. A plurality of second elastic films are disposed in the inner tube and spaced apart along the axial direction of the inner tube; a plurality of second through holes are provided on the second elastic films, and a resonant block is provided at the center of the second elastic film; Refrigerant flows into the inner tube from the inlet pipe. Some refrigerant passes through the second through holes on each of the second elastic films in sequence and is blocked by the first elastic film. Then it enters the cavity through the first through hole on the inner tube. Some refrigerant enters the cavity directly or through some of the second through holes on the second elastic films and then through the first through hole on the inner tube. During this process, the refrigerant forms pressure pulsations, causing the first elastic film and / or the second elastic film to resonate.

[0007] Secondly, an outdoor unit for an air conditioner is provided, comprising: The compressor is used to supply refrigerant to the heat exchanger; A silencer, the silencer connecting the compressor and the heat exchanger, the silencer comprising: The housing includes an inlet pipe and an outlet pipe, the inlet pipe being connected to the outlet of the compressor and the outlet pipe being connected to the inlet of the heat exchanger; An inner tube is disposed inside the outer shell; one end of the inner tube is connected to the inlet pipe, and a cavity is formed between the outer wall of the inner tube and the inner wall of the outer shell; the inner tube is provided with a plurality of first through holes along its axial direction. A first elastic film is disposed in the inner tube near one end of the outlet tube, and a resonant block is disposed at the center of the first elastic film. A plurality of second elastic films are disposed in the inner tube and between the first elastic film and the inlet tube; a plurality of second through holes are provided on the second elastic films, and a resonant block is provided at the center of the second elastic films; Refrigerant flows into the inner tube from the inlet pipe. Some refrigerant passes through the second through holes on each of the second elastic films in sequence and is blocked by the first elastic film. Then it enters the cavity through the first through hole on the inner tube. Some refrigerant enters the cavity directly or through some of the second through holes on the second elastic films and then through the first through hole on the inner tube. During this process, the refrigerant forms pressure pulsations, causing the first elastic film and / or the second elastic film to resonate.

[0008] In the above embodiments, this application effectively solves the noise reduction "trough" problem of traditional expansion silencers by using a triple synergistic noise reduction structure of perforation attenuation, expansion attenuation, and precise resonance cancellation, significantly enhancing the overall noise reduction capability of refrigerant noise in the outdoor unit of the air conditioner. Specifically, on the one hand, the inner tube of the silencer is provided with several first through holes, and the second elastic membrane is provided with second through holes. After the refrigerant flows into the inner tube from the inlet pipe, it must first pass through these first and second through holes. The contraction and expansion of the refrigerant at the through holes will initially consume the pressure pulsation energy, laying the foundation for subsequent noise reduction. On the other hand, the first elastic membrane blocks the side of the inner tube facing the outlet pipe, forcing the refrigerant to enter the cavity. The cavity formed between the inner tube and the outer shell is a typical expansion space. After the refrigerant, which has been initially attenuated by the first through holes, enters the cavity, the sudden expansion of the space will cause part of the sound wave propagating along the pipe to reflect towards the sound source, weakening the transmitted sound wave energy. The design achieves secondary attenuation of pressure pulsations, enhancing overall noise reduction capabilities. Most importantly, the inner tube incorporates several resonant systems composed of a first / second elastic diaphragm and a resonant block. This is the core innovation for solving the "valley" problem. When refrigerant pressure pulsations act on the elastic diaphragms, the resonant system resonates at its natural frequency, converting the refrigerant's kinetic energy into mechanical vibration. This precisely cancels out pressure pulsations at specific frequencies. Furthermore, by designing different thicknesses, elastic coefficients, and the mass of the resonant blocks, the natural frequency of each resonant system can be adjusted to cover the "valley" frequency band that traditional mufflers cannot effectively reduce. Simultaneously, the design connecting the muffler inlet pipe to the compressor outlet and the outlet pipe to the heat exchanger inlet ensures a perfect fit between the refrigerant flow path and the air conditioning system. This allows the triple noise reduction structure to participate in the refrigerant circulation throughout the process, ensuring all refrigerant passes through the perforation-expansion-resonance action sequentially. Ultimately, this achieves a stable noise reduction effect with wide frequency coverage and no obvious "valleys," significantly superior to traditional expansion-type mufflers.

[0009] In some embodiments of this application, the muffler further includes a plurality of limiting rings, the total number of which is equal to the total number of the first elastic film and the second elastic film; the first elastic film and each of the second elastic films are clamped and fixed to the inner wall of the inner tube by their respective limiting rings.

[0010] In the above embodiments, the first / second elastic films of this application are the core components of the resonance system, and their position and fixing strength directly determine the stability of the resonance frequency. If the films shift or loosen, the resonance frequency will deviate from the design value, making it impossible to specifically counteract pressure pulsations at a particular frequency, thus losing its function of resolving "troughs". The limiting ring of this application is fixed to the inner wall of the inner tube and prevents the films from shifting under the impact of refrigerant pressure pulsations through clamping force, ensuring that the films are always coaxial with the inner tube, which meets the structural design requirements of the resonance system. Stable fixing can ensure that the natural frequency of the resonance system composed of the films and the resonance block remains unchanged, continuously reducing noise from the target frequency pressure pulsations.

[0011] In some embodiments of this application, the number of the second elastic film is 1 to 3 layers.

[0012] In the above embodiments, the number of the second elastic film layers in this application directly affects the noise reduction effect and system flow efficiency. If there are too many layers (e.g., more than 3 layers), the refrigerant needs to pass through the film through-holes multiple times, which will significantly increase the flow resistance, affect the circulation efficiency of the air conditioning system, and the resonant frequencies of multiple films are prone to mutual interference, weakening the noise reduction effect at specific frequencies. Without the second elastic film, the first elastic film alone cannot cover multiple specific frequencies, making it difficult to fully compensate for the "valleys" of traditional mufflers. This application specifies that the number of the second elastic film layers is 1 to 3. One layer can achieve basic noise reduction at specific frequencies, while three layers can be designed with different resonant frequencies (for the refrigerant frequency at different compressor speeds) to cover more "valley" frequency bands, avoiding excessive flow resistance or resonance interference, and accurately matching the noise reduction requirements. At the same time, the specific layer limit makes the claims more targeted.

[0013] In some embodiments of this application, the diameter of the second through hole is 1 mm to 3 mm, and the ratio of the total area of ​​each second through hole to the surface area of ​​the second elastic film is 30% to 80%.

[0014] In the above embodiments, the second through-hole on the second elastic film of this application needs to simultaneously meet the dual requirements of refrigerant flow and auxiliary noise reduction. If the diameter is <1mm, the through-hole will significantly increase the refrigerant flow resistance, leading to pressure accumulation in the inner tube. If the diameter is >3mm, the through-hole will be too large and will not be able to effectively weaken pressure pulsation through refrigerant contraction and expansion, thus losing its auxiliary noise reduction effect. A diameter range of 1~3mm can find a balance between low flow resistance and pulsation reduction. At the same time, this application also limits the opening ratio. If the opening ratio is <30%, the total area of ​​the through-hole is too small, and the refrigerant flow is not smooth. If the opening ratio is >80%, the strength of the film structure decreases, and the ability to weaken pressure pulsation deteriorates. An opening ratio range of 30%~80% can ensure smooth refrigerant flow while using the through-hole to help weaken broadband pressure pulsation.

[0015] In some embodiments of this application, the inner tube includes a fixed section and an open section connected to the fixed section, wherein the first through hole is formed on the open section.

[0016] In the above embodiments, the fixed section can serve as a stable connection area between the inner tube and the inlet tube. Its holeless design can ensure the structural strength and sealing of the connection part and avoid the decrease in connection reliability caused by the opening. The perforated section focuses on realizing the function of refrigerant flow and pressure pulsation reduction, so that the inner tube can meet the core noise reduction requirements while ensuring the stability of the overall structure.

[0017] In some embodiments of this application, the diameter of the first through hole is 1 mm to 3 mm, and the ratio of the total area of ​​each first through hole to the surface area of ​​the opening segment is 30% to 80%.

[0018] In the above embodiments, the first through hole of the inner tube opening section of this application is the key channel for refrigerant to enter the cavity and the core structure for initially reducing pressure pulsation. If the diameter is <1mm, the resistance of refrigerant entering the cavity from the inner tube is too large, which may lead to excessive pressure in the inner tube and affect the compressor's exhaust efficiency. If the diameter is >3mm, the pressure pulsation is not weakened enough when passing through the through hole, and cannot provide a good foundation for subsequent noise reduction in the cavity. A diameter range of 1~3mm can ensure that the refrigerant enters the cavity smoothly and initially reduces pressure pulsation. In addition, an opening ratio range of 30%~80% can achieve a balance between flow efficiency and initial noise reduction. This parameter design is a targeted optimization for balancing efficiency and noise reduction. If the opening ratio is <30%, the flow rate of refrigerant entering the cavity is insufficient, which may lead to pressure accumulation in the inner tube. If the opening ratio is >80%, the structural strength of the inner tube opening section decreases, and the effect of reducing pressure pulsation deteriorates.

[0019] In some embodiments of this application, the muffler further includes several partitions, which are spaced together on the opening sections of the inner tube along the axial direction of the inner tube; the outer edge of the partition is connected to the inner wall of the outer shell, and the partition is coaxial with the inner tube; several third through holes are provided on the partition.

[0020] In the above embodiment, after the refrigerant enters the cavity through the first through hole of the inner tube, it passes through each baffle in sequence. When the refrigerant passes through the third through hole, the wideband pressure pulsation is weakened again due to the sudden change in the aperture and the contraction and expansion of the airflow, which further improves the overall noise reduction capability. In addition, the coaxial design of the baffle and the inner tube can guide the refrigerant to flow uniformly along the axial direction in the cavity, avoid the generation of local eddies, solve the problem of noise reduction effect fluctuation caused by the turbulence of the flow field in the cavity, and make the overall noise reduction effect more stable.

[0021] In some embodiments of this application, the minimum distance between any two adjacent partitions along the axial direction of the inner tube is greater than or equal to 10 mm.

[0022] In the above embodiments, the core function of the baffle in this application is to reduce pressure pulsation, but the spacing design must take into account flow resistance. If the minimum spacing between adjacent baffles is <10mm, the refrigerant will have just passed through the third through-hole of the previous baffle and will need to enter the next baffle before it has stabilized. This will cause mutual interference between the refrigerants, significantly increasing flow resistance. Excessive flow resistance will affect the refrigerant circulation speed, reduce the heat exchange efficiency of the outdoor unit of the air conditioner, and may even trigger system protection due to excessive pressure. This application specifies that the minimum spacing between adjacent baffles is ≥10mm, which can provide sufficient flow buffer space for the refrigerant, allowing the airflow to fully diffuse and stabilize after passing through one baffle before entering the next baffle, effectively reducing flow resistance and ensuring the normal operation of the air conditioning system. At the same time, this spacing will not affect the noise reduction effect of the baffle, and the baffle can still reduce pressure pulsation through the third through-hole, thus retaining the function of the newly added noise reduction structure and avoiding negative impact on the efficiency of the air conditioning system.

[0023] In some embodiments of this application, the diameter of the third through hole is greater than or equal to the diameter of the first through hole; The ratio of the total area of ​​each of the third through holes to the surface area of ​​the partition is greater than or equal to the ratio of the total area of ​​each of the first through holes to the surface area of ​​the opening segment.

[0024] In the above embodiments, the refrigerant flow path is the first through-hole of the inner tube → cavity → third through-hole of the baffle. The parameters of the two must be matched to avoid flow resistance problems. If the diameter of the third through-hole is less than that of the first through-hole, or the opening ratio of the third through-hole is less than that of the first through-hole, the refrigerant will not be able to pass smoothly after flowing out of the first through-hole because the third through-hole is too narrow / too small, forming a flow bottleneck and increasing flow resistance. This application limits the diameter of the third through-hole to be greater than or equal to that of the first through-hole and the opening ratio to be greater than or equal to that of the first through-hole. This ensures that the refrigerant can pass smoothly through the third through-hole after flowing out of the first through-hole, ensuring that the flow resistance remains unchanged or decreases along the refrigerant flow path, avoiding the bottleneck effect and ensuring the refrigerant circulation efficiency.

[0025] It should be understood that the above general description and the following detailed description are exemplary and explanatory only, and do not limit this application. Attached Figure Description

[0026] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0027] Figure 1 This is a schematic diagram of the overall structure of the muffler provided in the embodiments of this application; Figure 2This is a three-dimensional cross-sectional schematic diagram of the overall structure of the muffler provided in the embodiments of this application; Figure 3 This is a front view schematic diagram of the muffler provided in the embodiment of this application; Figure 4 yes Figure 3 Schematic diagram of the AA section; Figure 5 This is a front view schematic diagram of the partition provided in an embodiment of this application; Figure 6 This is a schematic diagram of the structure of the outer casing provided in an embodiment of this application; Figure 7 This is a schematic diagram of the inner tube provided in an embodiment of this application; Figure 8 This is a cross-sectional schematic diagram of the inner tube provided in an embodiment of this application; Figure 9 yes Figure 8 Enlarged view of part B in the middle; Figure 10 This is a schematic diagram of the limiting ring, the first elastic film, and the resonant block structure provided in the embodiments of this application.

[0028] Figure 11 This is a schematic diagram of the limiting ring, the second elastic film, and the resonant block structure provided in the embodiments of this application.

[0029] Figure 12 This is a schematic diagram of the refrigerant flow path provided in the embodiments of this application; in the figure, the thick solid line represents the refrigerant flow path, the direction of the arrow on the thick solid line represents the direction of refrigerant flow, and F1 and F2 represent different refrigerant flow paths.

[0030] In the above figures: 100, outer shell; 110, inlet pipe; 120, outlet pipe; 130, barrel body; 131, cavity; 200, inner pipe; 210, fixed section; 220, opening section; 221, first through hole; 230, annular boss; 300, partition plate; 310, third through hole; 400, limiting ring; 500, first elastic membrane; 600, second elastic membrane; 610, second through hole; 700, resonant block. Detailed Implementation

[0031] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application. In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between components; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication between two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0032] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0033] In this application, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0034] Additionally, if the meaning of "and / or" in the text is that it includes three parallel options, taking "A and / or B" as an example, it includes option A, option B, or an option that satisfies both A and B.

[0035] The present application will now be described in detail through exemplary embodiments. However, it should be understood that, without further description, elements, structures, and features in one embodiment may be advantageously incorporated into other embodiments.

[0036] The outdoor unit of an air conditioner is the core of the air conditioning system for heat exchange and refrigerant circulation, integrating key components such as the compressor, condenser, cooling fan, and refrigerant piping. The compressor, as the power source, compresses the low-pressure, low-temperature refrigerant into a high-pressure, high-temperature state. The condenser cools the high-pressure gaseous refrigerant through heat exchange with the outdoor air. The cooling fan enhances heat exchange efficiency, and the refrigerant piping connects all components to form a closed loop, collectively achieving the cooling or heating function. As people's requirements for living environments increase, the noise problem of air conditioner outdoor units is receiving more and more attention, with refrigerant noise caused by the periodic intake and exhaust of the compressor being particularly prominent. The periodic intake and exhaust of the compressor causes periodic fluctuations in the pressure within the refrigerant piping (i.e., pressure pulsation). When this pressure pulsation propagates, it causes piping vibration and radiates noise. Furthermore, changes in compressor speed with operating conditions cause synchronous changes in refrigerant pressure pulsation and noise frequency.

[0037] Installing silencers on refrigerant pipelines is currently the mainstream technology for reducing refrigerant noise. Among them, expansion silencers are the most widely used in the industry due to their relatively simple structure and controllable cost. Their silencing principle relies on the expansion (e.g., a thin pipe connecting to a thick pipe) or contraction (e.g., a thick pipe connecting to a thin pipe) of the pipe's cross-section. Specifically, when sound waves propagate along the pipe to a point where the cross-section changes abruptly, the acoustic impedance inside the pipe changes drastically. This impedance change causes some sound waves to be reflected towards the sound source, thereby weakening the transmitted sound wave energy that continues to propagate forward, ultimately achieving a silencing effect. However, the root of the technical problem with existing expansion silencers lies in the strong binding characteristic between their silencing performance and structural dimensions. Once the structural dimensions of the silencer (such as the diameter and length of the expansion section, the contraction transition method, etc.) are designed and finalized, they can only effectively reflect sound waves within a specific frequency range. For sound waves deviating from this frequency range, the reflection efficiency will drop significantly, or even completely lose its reflection capability. This inevitably leads to a significant "trough" frequency band (i.e., a weak range in noise reduction capability) in its noise reduction effect. In actual air conditioning operation, the compressor speed will dynamically adjust with the operating conditions, and the frequency of refrigerant pressure pulsation will also change dynamically. There is an inherent contradiction between this dynamic frequency and the fixed noise reduction frequency band of the expansion muffler. When the dynamically changing pressure pulsation frequency happens to fall into the "trough" frequency band of the muffler, the muffler's ability to suppress noise at that frequency will drop significantly, ultimately making it difficult to meet the core requirements of wide-band and stable noise reduction in practical applications. This technical problem caused by the contradiction between structural fixity and frequency dynamism has become a key bottleneck restricting the improvement of refrigerant noise control.

[0038] Based on this, this application proposes an outdoor air conditioning unit that converts kinetic energy into mechanical vibration by inducing diaphragm resonance through refrigerant pressure pulsation, thereby specifically offsetting pressure pulsation at a certain frequency. At the same time, it uses expansion and contraction, perforation and other structures to weaken pressure pulsation, achieving a superposition effect of wide-band pressure pulsation attenuation and precise noise reduction at a specific frequency. This solves the problem that traditional expansion silencers have noise reduction "troughs" due to their fixed structure and cannot adapt to changes in compressor speed, resulting in unstable refrigerant noise control.

[0039] In the following, embodiments of this application will be described in detail with reference to the accompanying drawings.

[0040] As attached Figures 1 to 11 As shown in an illustrative embodiment of this application, the outdoor unit of the air conditioner includes a housing, and a compressor is disposed inside the housing.

[0041] It is worth noting that the refrigerant mentioned in this application (also known as a refrigerant, such as R32, R410A, etc.) is a medium for heat transfer, and the same applies throughout the application, so it will not be repeated here.

[0042] In some embodiments, the compressor is a gas booster device used to compress refrigerant from a low-pressure, low-temperature state to a high-pressure, high-temperature state. The compressor compresses the incoming low-pressure gaseous refrigerant by driving internal moving parts (such as pistons, rotors, scrolls, etc.) to make mechanical movements through a motor, so as to convert it into a high-pressure gaseous refrigerant. The specific process can be divided into four core stages: intake, compression, exhaust, and expansion (in some types).

[0043] In cooling mode, the air conditioner transfers heat from indoors to outdoors. The refrigerant circulation path is: indoor heat exchanger (evaporator) → gas-liquid separator → compressor → outdoor heat exchanger (condenser) → throttling device → indoor heat exchanger (evaporator). Specifically, in the indoor heat exchanger, low-pressure liquid refrigerant absorbs indoor heat and evaporates into low-pressure, low-temperature gaseous refrigerant. This gaseous refrigerant returns to the outdoor unit via a low-pressure pipeline, first passing through a gas-liquid separator to filter out residual liquid components before entering the compressor. The compressor compresses this gaseous refrigerant into high-pressure, high-temperature gaseous refrigerant, which is then discharged into the outdoor heat exchanger via a high-pressure pipeline. There, it releases heat through heat exchange with outdoor air driven by a fan, condensing into high-pressure, medium-temperature liquid refrigerant. Subsequently, the pressure is reduced to a low-pressure gas-liquid mixture by the throttling device before re-entering the indoor heat exchanger, completing the cycle.

[0044] In heating mode, the air conditioner switches the refrigerant flow direction through a four-way valve to transfer outdoor heat to the indoor unit. The circulation path is: outdoor heat exchanger (evaporator) → gas-liquid separator → compressor → indoor heat exchanger (condenser) → throttling device → outdoor heat exchanger (evaporator). Specifically, the four-way valve switches, temporarily turning the outdoor heat exchanger into an evaporator. The low-pressure liquid refrigerant absorbs heat from the outdoor air and evaporates into a low-pressure, low-temperature gaseous refrigerant, which is then filtered by the gas-liquid separator and enters the compressor. The high-pressure, high-temperature gaseous refrigerant compressed by the compressor is sent to the indoor heat exchanger (temporarily acting as a condenser) through a high-pressure pipeline, where it releases heat through heat exchange with the indoor air (heating the indoor air) and condenses into a high-pressure, medium-temperature liquid refrigerant. Subsequently, the pressure is reduced to a low-pressure gas-liquid mixture by the throttling device and returns to the outdoor heat exchanger, completing the cycle.

[0045] It should be noted that the specific structure of the compressor (including core components such as the compressor motor, cylinder, and piston, as well as the connection relationship between the suction valve, discharge valve, and gas-liquid separator) and the operating principle of the compressor (such as the process of achieving the suction-compression-discharge cycle by driving the internal components to rotate / reciprocate through the motor, compressing the low-pressure, low-temperature gaseous refrigerant into a high-pressure, high-temperature gaseous refrigerant, etc.) are all prior art, and their technical details are well known to those skilled in the art. Therefore, they need not be elaborated upon in this application. The improvement of this application mainly lies in optimizing the pressure pulsation attenuation effect of the refrigerant after it flows out of the compressor outlet through the structural design of the silencer, which will not be elaborated upon further below.

[0046] In some embodiments, a condenser is provided inside the casing. The condenser is the outdoor heat exchanger mentioned above. The condenser is used for heat exchange between the refrigerant and the outdoor air. Its main body is composed of multiple sets of parallel copper (or aluminum) heat exchange tubes and dense metal heat dissipation fins (usually aluminum fins). The heat exchange tubes are inserted and fixed in the preset holes of the fins to form a tube-fin integrated heat exchange matrix. At the same time, the entire heat exchanger is fixed inside the outdoor unit casing by a bracket, and an air circulation channel is reserved on the side corresponding to the cooling fan. Some heat exchangers will also be provided with manifolds at the inlet and outlet of the pipes (for collecting / distributing refrigerant) to ensure that the refrigerant can flow evenly through each heat exchange tube, and finally achieve efficient heat exchange between the refrigerant and the outdoor air.

[0047] It should be noted that the specific structure of the condenser (including the copper / aluminum heat exchange tubes, metal heat dissipation fins, manifolds, and other components, as well as the connection relationship between the condenser inlet and compressor outlet pipes, and between the condenser outlet and throttling component pipes) and the operating principle of the condenser (such as transferring heat from the high-pressure, high-temperature gaseous refrigerant to the outdoor air through the heat exchange tubes and fins during cooling, causing the refrigerant to condense into a high-pressure liquid state; and switching to evaporator function during heating, absorbing heat from the outdoor air through the heat exchange tubes and fins, causing the refrigerant to evaporate into a low-pressure gaseous state, etc.) are all prior art, and their technical details are well known to those skilled in the art. Therefore, they need not be elaborated upon in this application.

[0048] In some embodiments, a fan is installed inside the housing, which works in conjunction with the condenser. The fan's core function is to drive outdoor air to flow directionally through the condenser (such as the fins and the outer wall of the heat exchange tubes) via its own rotation. This forced airflow quickly removes heat from the condenser's heat exchange surface (in cooling mode) or accelerates the transfer of heat from the outdoor air to the condenser (in heating mode), thereby increasing the heat exchange rate between the refrigerant inside the condenser and the outdoor air, improving the condenser's heat exchange efficiency, and ensuring the stable and efficient operation of the air conditioning system's cooling or heating functions.

[0049] It should be noted that the specific structure of the aforementioned fan (including the fan motor, fan blades, fixed brackets, and other components, as well as the assembly relationship between the fan and the outdoor unit casing, and the relative positional connection relationship with the condenser) and the operating principle of the fan (such as the process of generating airflow by driving the fan blades to rotate through the motor, causing the outdoor air to flow directionally along the surface of the condenser, thereby accelerating the heat exchange rate between the condenser and the air) are all prior art, and their technical details are well known to those skilled in the art. Therefore, there is no need to elaborate on them in this application.

[0050] In some embodiments, a silencer is provided inside the housing, and the silencer connects the compressor and the heat exchanger.

[0051] Furthermore, the number of silencers is at least one.

[0052] In some embodiments, the muffler connects the compressor to the outdoor heat exchanger.

[0053] In some embodiments, the muffler connects the compressor to the indoor unit heat exchanger.

[0054] In some embodiments, there are two silencers: one silencer connects the compressor to the outdoor heat exchanger, and the other silencer connects the compressor to the indoor heat exchanger.

[0055] In some embodiments, such as Figure 2As shown, the muffler includes a housing 100, which includes an inlet pipe 110, an outlet pipe 120, and a barrel 130. The inlet pipe 110, outlet pipe 120, and barrel 130 are coaxial and integrally formed. The inlet pipe 110 and outlet pipe 120 are coaxially located at both ends of the barrel 130 and are connected to the internal space of the barrel 130. The inner diameter of the barrel 130 is larger than that of the inlet pipe 110 and the outlet pipe 120, forming a cavity 131 inside the barrel 130 to attenuate refrigerant pressure pulsations. When the refrigerant enters the cavity 131, the space abruptly transitions from the narrow diameter of the inner pipe 200 to the wide diameter of the barrel 130, thus further weakening the pressure pulsations. In terms of assembly, the inlet pipe 110 of the muffler is connected to the outlet of the compressor through the refrigerant pipeline, and the outlet pipe 120 is connected to the inlet of the heat exchanger through the refrigerant pipeline. This allows the refrigerant discharged from the compressor to flow sequentially through the inlet pipe 110, the tank 130, and the outlet pipe 120 before entering the heat exchanger, thus completing the connection between pressure pulsation attenuation and refrigerant delivery. This ensures that the refrigerant flow path is compatible with the air conditioning system, allowing the expansion noise reduction function of the cavity 131 to participate in the refrigerant circulation throughout the process, providing a stable expansion-type silencing foundation for the overall noise reduction effect.

[0056] Preferably, the inlet pipe 110 and the outlet pipe 120 have the same diameter.

[0057] In some embodiments, the muffler includes an inner tube 200 disposed inside the outer casing 100. The inner tube 200 is coaxial with the outer casing 100, and a cavity 131 is formed between the outer wall of the inner tube 200 and the inner wall of the outer casing 100 (i.e., the inner wall of the barrel 130).

[0058] In some embodiments, such as Figure 7 As shown, the inner tube 200 includes a fixed section 210 and an open section 220, which are coaxial and integrally formed, forming a smoothly transitioning tubular structure. One end of the fixed section 210 is smoothly connected and fixed to the end of the inlet pipe 110 away from the compressor, and they communicate with each other. One end of the open section 220 is connected to the end of the fixed section 210 away from the inlet pipe 110, ensuring that the inner tube 200 is stably assembled coaxially inside the outer casing 100. This ensures that the refrigerant can smoothly flow from the inlet pipe 110 into the fixed section 210 and communicate with the cavity 131 via the open section 220.

[0059] Furthermore, a number of first through holes 221 are arranged at intervals on the opening section 220.

[0060] It is worth noting that, along the axial direction of the inner tube 200, for each first through hole 221 on the side wall of the inner tube 200, a straight line parallel to the axial direction of the inner tube 200 is drawn from its center towards the end of the inner tube 200 facing the inlet pipe 110 (the straight line extends to the end of the inner tube 200 facing the inlet pipe 110). Among these straight lines, there must be a shortest straight line. The first through hole 221 corresponding to this shortest straight line is the first through hole 221 closest to the inlet pipe 110 (hereinafter referred to as the proximal first through hole 221). Take the intersection point of the outer edge of the proximal first through hole 221 and the aforementioned shortest straight line, and draw a plane perpendicular to the axial direction of the inner tube 200 through this intersection point. This plane is the interface between the fixed section 210 and the opening section 220 of the inner tube 200. The side of the plane facing the inlet pipe 110 is the fixed section 210, and the side facing the partition 300 is the opening section 220.

[0061] In some embodiments, the diameter of the first through hole 221 is 1 mm, which can maximize the reduction of pressure pulsation while ensuring that the refrigerant flow resistance is within an acceptable range.

[0062] In some embodiments, the diameter of the first through hole 221 is 3 mm, which can minimize the refrigerant flow resistance while ensuring that the pressure pulsation reduction effect is within an acceptable range.

[0063] In some embodiments, the ratio of the total area of ​​each first through hole 221 to the surface area of ​​the opening section 220 is 30%. The smaller through hole area allows the refrigerant to undergo more sufficient throttling and buffering when passing through the first through hole 221, effectively reducing pressure fluctuations. At the same time, the moderate increase in flow resistance will not have an excessive impact on the overall flow efficiency of the refrigerant, making it suitable for operating conditions with high requirements for noise reduction performance.

[0064] In some embodiments, the ratio of the total area of ​​each first through hole 221 to the surface area of ​​the opening section 220 is 80%. A higher opening ratio means a smoother flow path structure, which can significantly reduce the flow resistance of the refrigerant when passing through the first through hole 221, reduce energy loss caused by flow path restriction, and ensure that the refrigerant can still maintain efficient flow under high flow conditions.

[0065] In some embodiments, the diameter of the first through hole 221 is 1 mm to 3 mm, and the ratio of the total area of ​​all first through holes 221 to the surface area of ​​the opening section 220 is 30% to 80%. Specifically, if the diameter is < 1 mm, the resistance of the refrigerant entering the cavity 131 from the inner tube 200 is too great, which may lead to excessive pressure in the inner tube 200 and affect the compressor's exhaust efficiency; if the diameter is > 3 mm, the pressure pulsation is not weakened enough when passing through the through hole, and cannot provide a good foundation for subsequent noise reduction in the cavity 131. Similarly, if the opening ratio is < 30%, the flow rate of the refrigerant entering the cavity 131 is insufficient, which may lead to pressure accumulation in the inner tube 200; if the opening ratio is > 80%, the structural strength of the opening section 220 of the inner tube 200 decreases, and the effect of weakening pressure pulsation deteriorates.

[0066] In some embodiments, the diameter of the inner tube 200 is the same everywhere along the refrigerant flow direction, and the diameter of the inner tube 200 is equal to the diameter of the inlet tube 110.

[0067] In some embodiments, along the refrigerant flow direction, the diameter of the opening section 220 of the inner tube 200 gradually increases, wherein the minimum diameter of the opening section 220 is the same as the diameter of the inlet tube 110, and the maximum diameter of the opening section 220 is less than or equal to twice the diameter of the inlet tube 110. Furthermore, the opening section 220 is composed of several pipe structures with the same diameter. The diameters of two adjacent pipe structures are different, and any two adjacent pipe sections are connected by a smooth transition (such as arc transition, gradual transition, etc., to avoid abrupt diameter changes).

[0068] In some embodiments, the muffler further includes a first elastic diaphragm 500; the first elastic diaphragm 500 is disposed inside the inner tube 200, and specifically located at the end of the inner tube 200 away from the inlet pipe 110 (or can be understood as disposed at the end of the opening section 220 of the inner tube 200 near the outlet pipe 120), while the first elastic diaphragm 500 is coaxially arranged with the inner tube 200, and a resonant block 700 is fixedly disposed at its center.

[0069] In some embodiments, the muffler further includes a plurality of second elastic films 600; these second elastic films 600 are all disposed inside the inner tube 200 and are arranged at intervals along the axial direction of the inner tube 200, specifically between the first elastic film 500 and the inlet pipe 110, and each second elastic film 600 is coaxially disposed with the inner tube 200. In addition, each second elastic film 600 is provided with a plurality of second through holes 610, and a resonant block 700 is fixedly disposed at the center of each second elastic film 600.

[0070] Through the above design, on the one hand, the opening section 220 of the inner tube 200 of the muffler is provided with several first through holes 221, and the second elastic diaphragm 600 is provided with second through holes 610. After the refrigerant flows into the inner tube 200 from the inlet pipe 110, it must first pass through these first through holes 221 and second through holes 610. The contraction and expansion of the refrigerant at the through holes will initially consume the pressure pulsation energy, laying the foundation for subsequent noise reduction. On the other hand, the first elastic diaphragm 500 blocks the side of the inner tube 200 facing the outlet pipe 120, forcing the refrigerant to enter the cavity 131. The cavity 131 formed between the inner tube 200 and the outer shell 100 is a typical expansion space. After the refrigerant, which has been initially weakened by the first through holes 221, enters the cavity 131, the sudden expansion of the space will cause the refrigerant to... The sound waves propagating through the pipe are partially reflected towards the sound source, weakening the transmitted sound wave energy and achieving secondary attenuation of pressure pulsations, thus enhancing the overall noise reduction capability. Most importantly, the inner pipe 200 contains several sets of resonant systems composed of a first elastic diaphragm 500, a second elastic diaphragm 600, and a resonant block 700. This is the core innovation for solving the "valley" problem. When the refrigerant pressure pulsations act on the elastic diaphragms, the resonant system resonates at its natural frequency, converting the refrigerant kinetic energy into the mechanical vibration of the resonant system. This precisely cancels out pressure pulsations at specific frequencies. Furthermore, by designing different thicknesses, elastic coefficients, and the mass of the resonant blocks, the natural frequency of each resonant system can be adjusted to cover the "valley" frequency band that traditional silencers cannot effectively reduce.

[0071] In some embodiments, the second elastic film 600 has 1 to 3 layers. The number of layers of the second elastic film 600 directly affects the noise reduction effect and system flow efficiency. If there are too many layers (e.g., more than 3 layers), the refrigerant needs to pass through the film through-holes multiple times, which will significantly increase the flow resistance, affect the circulation efficiency of the air conditioning system, and the resonant frequencies of multiple films are prone to mutual interference, weakening the noise reduction effect at specific frequencies. Without the second elastic film 600, the first elastic film 500 alone cannot cover multiple specific frequencies, making it difficult to fully compensate for the "valleys" of traditional mufflers. This embodiment specifies that the number of layers of the second elastic film is 1 to 3. One layer can achieve basic noise reduction at specific frequencies, while three layers can be designed with different resonant frequencies (for the refrigerant frequency at different compressor speeds) to cover more "valley" frequency bands, which avoids excessive flow resistance or resonance interference and can accurately match the noise reduction requirements.

[0072] Preferably, the second elastic film 600 has one layer, and this second elastic film 600 is fixed on the side of the inner tube 200 opening section 220 facing the inlet tube 110.

[0073] In some embodiments, when the diameter of the second through hole 610 is set to 1 mm, the pressure pulsation can be minimized while ensuring that the refrigerant flow resistance is within an acceptable range.

[0074] In some embodiments, when the diameter of the second through hole 610 is set to 3 mm, the refrigerant flow resistance can be minimized while ensuring that the pressure pulsation reduction effect is within an acceptable range.

[0075] In some embodiments, the ratio of the total area of ​​each second through hole 610 to the surface area of ​​the opening section 220 is 30%. The smaller through hole area allows the refrigerant to undergo more sufficient throttling and buffering when passing through the second through hole 610, effectively reducing pressure fluctuations. At the same time, the moderate increase in flow resistance will not have an excessive impact on the overall flow efficiency of the refrigerant, making it suitable for operating conditions with high requirements for noise reduction performance.

[0076] In some embodiments, the ratio of the total area of ​​each second through hole 610 to the surface area of ​​the opening section 220 is 80%. A higher opening ratio means a smoother flow path structure, which can significantly reduce the flow resistance of the refrigerant when passing through the second through hole 610, reduce energy loss caused by flow path restriction, and ensure that the refrigerant can still maintain efficient flow under high flow conditions.

[0077] In some embodiments, the diameter of the second through hole 610 is 1 mm to 3 mm, and the ratio of the total area of ​​the second through holes 610 to the surface area of ​​the second elastic film 600 is 30% to 80%. The second through holes 610 on the second elastic film 600 need to simultaneously meet the dual requirements of refrigerant flow and auxiliary noise reduction. If the diameter of the second through hole 610 is < 1 mm, the through hole will significantly increase the refrigerant flow resistance, resulting in pressure accumulation in the inner tube 200. If the diameter is > 3 mm, the through hole will be too large and will not be able to effectively weaken the pressure pulsation through the contraction and expansion of the refrigerant, thus losing the auxiliary noise reduction effect. At the same time, this application also limits the opening ratio. If the opening ratio is < 30%, the total area of ​​the through holes is too small, and the refrigerant flow is not smooth. If the opening ratio is > 80%, the strength of the film structure decreases, and the ability to weaken pressure pulsation becomes worse.

[0078] In some embodiments, the first elastic film 500 and the second elastic film 600 are made of rubber-like materials or other polymer materials with similar elastic properties. These materials can generate effective deformation and induce resonance under the action of refrigerant pressure pulsation, and at the same time have good resistance to refrigerant corrosion and structural stability, and can adapt to the working environment inside the muffler.

[0079] In some embodiments, the muffler further includes a plurality of limiting rings 400, the total number of which is equal to the total number of the first elastic diaphragm 500 and the second elastic diaphragm 600. Each of the first elastic diaphragm 500 and each of the second elastic diaphragms 600 is clamped and fixed to the inner wall of the inner tube 200 by its corresponding limiting ring 400. The limiting rings are fixed to the inner wall of the inner tube, and the clamping force prevents the diaphragm from shifting under the impact of refrigerant pressure pulsations, ensuring that the diaphragm remains coaxial with the inner tube, meeting the structural design requirements of the resonant system. Stable fixation ensures that the natural frequency of the resonant system composed of the diaphragm and the resonant block remains unchanged, continuously reducing noise from the target frequency pressure pulsations. This prevents diaphragm displacement or loosening, ensuring that the resonant frequency does not deviate from the design value.

[0080] Furthermore, the limiting ring 400 is fixed in the inner tube 200 by an interference fit.

[0081] In some embodiments, an annular boss 230 is provided on the inner wall of the inner tube 200 facing the outlet tube 120. The first elastic film 500 is clamped together by the corresponding limiting ring 400 and the annular boss 230, thereby achieving stable fixation of the first elastic film 500.

[0082] In some embodiments, the muffler further includes a plurality of baffles 300; these baffles 300 are spaced apart along the axial direction of the inner tube 200 and are all fitted onto the opening section 220 of the inner tube 200 in a sleeve manner. Meanwhile, the outer edge of each baffle 300 is connected to the inner wall of the muffler housing 100, and all baffles 300 are coaxially arranged with the inner tube 200. Furthermore, each baffle 300 is provided with a plurality of third through holes 310 for refrigerant flow and pressure pulsation reduction. After the refrigerant enters the cavity 131 through the first through hole 221 of the inner tube, it passes through each of the baffles 300 in sequence. When the refrigerant passes through the third through hole 310, the wideband pressure pulsation is weakened again due to the sudden change in the aperture and the contraction and expansion of the airflow, which further improves the overall noise reduction capability. In addition, the coaxial design of the baffles 300 and the inner tube 200 can guide the refrigerant to flow uniformly along the axial direction in the cavity 131, avoid the generation of local eddies, solve the problem of noise reduction effect fluctuation caused by the turbulence of the flow field in the cavity 131, and make the overall noise reduction effect more stable.

[0083] In some embodiments, the partition 300 is fixed to the outer casing 100 by means of interference fit, welding or other methods.

[0084] In some embodiments, the partition 300 divides the perforated section 220 of the inner tube 200 into several layers along its axial direction. For each layer of perforated section 220, the diameter of the first through-hole 221 it contains, and the ratio of the total area of ​​all the first through-holes 221 in that layer to the surface area of ​​the perforated section 220 in that layer (i.e., the opening ratio), can be the same or different between layers. Furthermore, along the flow direction of the refrigerant, the diameter of the first through-hole 221 of each layer of perforated section 220 remains constant or gradually decreases, and the opening ratio of each layer also remains constant or gradually decreases.

[0085] In some embodiments, along the axial direction of the inner tube 200, the minimum distance between any two adjacent baffles 300 is greater than or equal to 10 mm. If the minimum distance between adjacent baffles 300 is less than 10 mm, the refrigerant will need to enter the next baffle 300 before it has stabilized after passing through the third through-hole 310 of the previous baffle 300, which will cause mutual interference between the refrigerants and significantly increase flow resistance. Excessive flow resistance will affect the refrigerant circulation speed, reduce the heat exchange efficiency of the outdoor unit of the air conditioner, and may even trigger system protection due to excessive pressure. However, if the minimum distance between adjacent baffles 300 is ≥10 mm, it can provide sufficient flow buffer space for the refrigerant, allowing the airflow to fully diffuse and stabilize after passing through one baffle 300 before entering the next baffle 300, effectively reducing flow resistance and ensuring the normal operation of the air conditioning system. At the same time, this distance will not affect the noise reduction effect of the baffles, and the baffles can still weaken pressure pulsation through the third through-hole 310, thus retaining the function of the newly added noise reduction structure and avoiding negative impact on the efficiency of the air conditioning system.

[0086] In some embodiments, the diameter of the third through hole 310 is greater than or equal to the diameter of the first through hole 221; the ratio of the total area of ​​each third through hole 310 to the surface area of ​​the partition 300 is greater than or equal to the ratio of the total area of ​​each first through hole 221 to the surface area of ​​the opening section 220. The flow path of the refrigerant is the inner tube first through hole 221 → cavity 131 → partition 300 third through hole 310. The parameters of the two must be matched to avoid flow resistance problems. If the diameter of the third through hole 310 is less than that of the first through hole 221, or the opening ratio of the third through hole 310 is less than that of the first through hole 221, the refrigerant will not be able to pass smoothly after flowing out of the first through hole 221 because the third through hole 310 is too narrow / too few, forming a flow bottleneck and increasing flow resistance. In this embodiment, the diameter of the third through hole 310 is greater than or equal to that of the first through hole 221, and the opening ratio is greater than or equal to that of the first through hole 331. This ensures that after the refrigerant flows out of the first through hole 221, it can smoothly pass through the third through hole 310. This ensures that the flow resistance remains unchanged or decreases along the refrigerant flow path, avoids the bottleneck effect, and guarantees the refrigerant circulation efficiency.

[0087] In some embodiments, the number of baffles 300 may be zero or more as needed. The through holes of each baffle 300 should be evenly spaced (to avoid uneven flow field leading to additional pressure pulsation), but the hole diameter and number of perforations of each baffle 300 need not be the same.

[0088] Refrigerant flows into inner tube 200 from inlet pipe 110. Some refrigerant passes through the second through holes 610 on each of the second elastic films 600 and is blocked by the first elastic film 500. Then it enters cavity 131 through the first through hole 221 on inner tube 200. Some refrigerant enters cavity 131 directly or through the second through holes 610 on some of the second elastic films 600 and then through the first through hole 221 on inner tube 200. During this process, the refrigerant forms pressure pulsations, causing the first elastic film 500 and / or the second elastic film 600 to resonate.

[0089] In some embodiments, there are two partitions 300; there is one second elastic film 600, which is disposed at the boundary between the opening section 220 and the fixing section 210. Figure 12 As shown, when the refrigerant enters the muffler, it first flows through the first layer of the "mass-film" resonance system, which consists of the resonant block 700 and the second elastic film 600. The resonance system resonates at its natural frequency, converting the kinetic energy of the refrigerant into mechanical vibration of the resonance system, thereby reducing the pressure pulsation at the resonant frequency. After passing through the "mass-film" resonance system, the refrigerant flows through different flow paths F1 and F2, passing through different regions of the opening section 220 and different combinations of baffles 300, further reducing the pressure pulsation, and finally flows out of the muffler from the outlet pipe 120. At the same time, the refrigerant also acts on the second layer of the "mass-film" resonance system, which consists of the resonant block 700 and the first elastic film 500, causing it to resonate at its natural frequency, converting the kinetic energy of the refrigerant into mechanical vibration of the resonance system, thereby further reducing the pressure pulsation at the resonant frequency.

[0090] To meet noise reduction requirements, the natural frequency of the resonant system is adjusted by designing parameters such as the mass size of the resonant block (700), the thickness of the elastic film, the elastic coefficient, and the area. The "mass-film" resonant system can be designed with multiple layers, and the resonant frequencies of each layer can be designed to be the same or different as needed to target specific frequencies or multiple frequencies for noise reduction. It is required that each elastic film, except for the last layer, has openings (or uses a mesh elastic material) as a refrigerant passage. The size and number of these openings are designed according to the system resistance and noise reduction requirements (the more and larger the openings, the lower the resistance and the weaker the ability to attenuate pressure pulsations). Additionally, the through-holes on the film also have the function of attenuating broadband pressure pulsations.

[0091] For ease of explanation, the above description has been provided in conjunction with specific embodiments. However, the above exemplary discussion is not intended to be exhaustive or to limit the embodiments to the specific forms disclosed above. Various modifications and variations can be obtained based on the above teachings. The selection and description of the above embodiments are for the purpose of better explaining the principles and practical applications, thereby enabling those skilled in the art to better utilize the above embodiments and various different variations of embodiments suitable for specific application considerations.

Claims

1. An air conditioner outdoor unit characterized by comprising: include: The compressor is used to supply refrigerant to the heat exchanger; A silencer, the silencer connecting the compressor and the heat exchanger, the silencer comprising: The housing includes an inlet pipe and an outlet pipe, the inlet pipe being connected to the outlet of the compressor and the outlet pipe being connected to the inlet of the heat exchanger; An inner tube is disposed inside the outer shell; one end of the inner tube is connected to the inlet pipe, and a cavity is formed between the outer wall of the inner tube and the inner wall of the outer shell; the inner tube is provided with a plurality of first through holes along its axial direction. A first elastic film is disposed in the inner tube near one end of the outlet tube, and a resonant block is disposed at the center of the first elastic film. A plurality of second elastic films are disposed in the inner tube and spaced apart along the axial direction of the inner tube; a plurality of second through holes are provided on the second elastic films, and a resonant block is provided at the center of the second elastic films; Refrigerant flows into the inner tube from the inlet pipe. Some refrigerant passes through the second through holes on each of the second elastic films in sequence and is blocked by the first elastic film. Then it enters the cavity through the first through hole on the inner tube. Some refrigerant enters the cavity directly or through some of the second through holes on the second elastic films and then through the first through hole on the inner tube. During this process, the refrigerant forms pressure pulsations, causing the first elastic film and / or the second elastic film to resonate.

2. The outdoor unit of claim 1, wherein The muffler also includes several limiting rings, the total number of which is equal to the total number of the first elastic film and the second elastic film; the first elastic film and each of the second elastic films are clamped and fixed to the inner wall of the inner tube by their respective limiting rings.

3. The outdoor unit of claim 2, wherein The number of the second elastic film is 1 to 3 layers.

4. The outdoor unit of claim 3, wherein The diameter of the second through hole is 1 mm to 3 mm, and the ratio of the total area of ​​the second through hole to the surface area of ​​the second elastic film is 30% to 80%.

5. An outdoor unit for an air conditioner according to any one of claims 1 to 4, characterized in that, The inner tube includes a fixed section and an open section connected to the fixed section, and the first through hole is formed on the open section.

6. The outdoor unit of claim 5, wherein The diameter of the first through hole is 1 mm to 3 mm, and the ratio of the total area of ​​the first through holes to the surface area of ​​the opening segment is 30% to 80%.

7. The outdoor unit of claim 6, wherein The silencer also includes several partitions, which are spaced together on the opening section of the inner tube along the axial direction of the inner tube; the outer edge of the partition is connected to the inner wall of the outer shell; and several third through holes are provided on the partition.

8. The outdoor unit of claim 7, wherein Along the axial direction of the inner tube, the minimum distance between any two adjacent partitions is greater than or equal to 10 mm.

9. The outdoor unit of claim 7 or 8, wherein The diameter of the third through hole is greater than or equal to the diameter of the first through hole; The ratio of the total area of ​​each of the third through holes to the surface area of ​​the partition is greater than or equal to the ratio of the total area of ​​each of the first through holes to the surface area of ​​the opening segment.

10. An air conditioner outdoor unit characterized by comprising: include: The compressor is used to supply refrigerant to the heat exchanger; A silencer, the silencer connecting the compressor and the heat exchanger, the silencer comprising: The housing includes an inlet pipe and an outlet pipe, the inlet pipe being connected to the outlet of the compressor and the outlet pipe being connected to the inlet of the heat exchanger; An inner tube is disposed inside the outer shell; one end of the inner tube is connected to the inlet pipe, and a cavity is formed between the outer wall of the inner tube and the inner wall of the outer shell; the inner tube is provided with a plurality of first through holes along its axial direction. A first elastic film is disposed in the inner tube near one end of the outlet tube, and a resonant block is disposed at the center of the first elastic film. A plurality of second elastic films are disposed in the inner tube and between the first elastic film and the inlet tube; a plurality of second through holes are provided on the second elastic films, and a resonant block is provided at the center of the second elastic films; Refrigerant flows into the inner tube from the inlet pipe. Some refrigerant passes through the second through holes on each of the second elastic films in sequence and is blocked by the first elastic film. Then it enters the cavity through the first through hole on the inner tube. Some refrigerant enters the cavity directly or through some of the second through holes on the second elastic films and then through the first through hole on the inner tube. During this process, the refrigerant forms pressure pulsations, causing the first elastic film and / or the second elastic film to resonate.

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