Silencing structure and compressor

Abstract

The invention discloses a silencing structure and a compressor. The silencing structure comprises a shell with a silencing cavity, a first exhaust channel, a second exhaust channel and an adjusting assembly. The first exhaust channel communicates with the silencing cavity, and the second exhaust channel communicates with the silencing cavity through the sound absorption channel. The adjusting assembly can adjust the opening degree of the first exhaust channel and the second exhaust channel according to temperature changes, so that the opening degree of the first exhaust channel is larger than that of the second exhaust channel at the first temperature, and conversely, the opening degree of the second exhaust channel at the second temperature. The second temperature is greater than the first temperature. The opening degrees of the two channels are automatically adjusted through the adjusting assembly according to the temperature, so that the opening degree of the first exhaust channel is large at low frequency and low temperature, refrigerant is rapidly discharged from a path with small flow resistance to guarantee the performance, the opening degree of the second exhaust channel is large at high frequency and high temperature, and the refrigerant is discharged from a path with large flow resistance and good noise elimination effect to reduce noise; therefore, energy efficiency loss caused by purely increasing the volume or reducing the area of the exhaust port is avoided, and noise control is optimized for different frequencies.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a noise reduction structure and compressor. Background Technology

[0002] During compressor operation, aerodynamic noise is a major problem, especially at high frequencies. Traditionally, aerodynamic noise is reduced by adding an expansion chamber silencer near the exhaust port of the compression chamber. The noise reduction effect is mainly achieved by increasing the volume of the silencer chamber and reducing the exhaust port area of ​​the silencer.

[0003] However, as air conditioner evaporators and condensers become smaller, the operating frequency of compressors continues to increase, and the operating conditions become more severe, leading to increased noise problems during high-frequency operation. Although increasing the volume of the silencer cavity and reducing the exhaust port area can improve the silencer effect, this method will reduce the energy efficiency of the compressor, especially during low-frequency operation. Due to the smaller load, the noise itself is smaller, but the design of the silencer leads to a decrease in energy efficiency and insufficient operating capacity. Summary of the Invention

[0004] The embodiments of the present invention provide a noise reduction structure and compressor that can effectively improve the noise problem of compressors during high-frequency operation without sacrificing low-frequency energy efficiency.

[0005] To address the aforementioned problems, according to one aspect of this application, an embodiment of the present invention provides a noise reduction structure, the noise reduction structure comprising a housing, a first exhaust channel, a second exhaust channel, and an adjustment component, wherein a noise reduction cavity is formed within the housing; the first exhaust channel communicates with the noise reduction cavity, and the second exhaust channel includes a sound-absorbing channel, the inlet of which communicates with the noise reduction cavity; the adjustment component is capable of adjusting the opening degree of the first exhaust channel and the second exhaust channel according to temperature changes, such that at a first temperature, the opening degree of the first exhaust channel is greater than the opening degree of the second exhaust channel, and at a second temperature, the opening degree of the second exhaust channel is greater than the opening degree of the first exhaust channel; wherein the second temperature is greater than the first temperature.

[0006] In some embodiments, the adjustment component includes a first adjustment unit and a second adjustment unit. The first adjustment unit is disposed at the first exhaust passage and is capable of continuously adjusting the opening of the first exhaust passage according to the temperature. The second adjustment unit is disposed at the inlet of the second exhaust passage and is capable of continuously adjusting the opening of the second exhaust passage according to the temperature.

[0007] In some embodiments, the first adjustment unit includes a first actuator and a first temperature-sensing drive, the first temperature-sensing drive being connected to the first actuator and the housing, and its deformation driving the first actuator to move to change the opening of the first exhaust passage; the second adjustment unit includes a second actuator and a second temperature-sensing drive, the second temperature-sensing drive being connected to the second actuator and the housing, and its deformation driving the second actuator to move to change the opening of the second exhaust passage.

[0008] In some embodiments, the first temperature-sensing actuator and the second temperature-sensing actuator are shape memory alloy elements, and the first temperature-sensing actuator is configured to elongate when the temperature rises, and the second temperature-sensing actuator is configured to contract when the temperature rises.

[0009] In some embodiments, the shape memory alloy element is a shape memory alloy spring.

[0010] In some embodiments, the sound-absorbing channel is provided with multiple sound-absorbing cavities of different depths, and the depth of each sound-absorbing cavity is set based on a quadratic remainder sequence Sn, where Sn=n 2 mod p, where n is a natural number and p is an odd prime number.

[0011] In some embodiments, the depth dn of the sound-absorbing cavity is determined by the formula dn=Sn*c / (2*f*p), where c is the sound velocity of the refrigerant and f is the target center frequency.

[0012] In some embodiments, the housing includes a flange, a partition, and a muffler cover, the muffler cover, the flange, and the partition together forming the muffler cavity; the first exhaust passage is disposed on the muffler cover, and the sound absorption passage is formed between the flange and the partition.

[0013] According to another aspect of this application, embodiments of the present invention provide a compressor that includes the noise reduction structure described above.

[0014] In some embodiments, the compressor is a variable frequency rotary compressor, and the regulating component is capable of adjusting according to the temperature change caused by the change in the compressor's operating frequency.

[0015] Compared with the prior art, the sound-absorbing structure of the present invention has at least the following beneficial effects: The silencing structure provided by the present invention includes a housing, a first exhaust channel, a second exhaust channel, and an adjustment component. A silencing cavity is formed inside the housing. The first exhaust channel is connected to the silencing cavity, and the second exhaust channel is connected to the silencing cavity through a sound-absorbing channel. The adjustment component can adjust the opening of the first exhaust channel and the second exhaust channel according to temperature changes, such that the opening of the first exhaust channel is greater than the opening of the second exhaust channel at a first temperature, and the opening of the second exhaust channel is greater than the opening of the first exhaust channel at a second temperature; wherein the second temperature is greater than the first temperature.

[0016] Background technology indicates that traditional mufflers improve noise reduction by increasing the volume of the muffler cavity and reducing the area of ​​the exhaust port, but this leads to reduced compressor energy efficiency and insufficient low-frequency operation capability. The muffler structure of this invention forms a muffler cavity through a shell and is provided with a first exhaust channel and a second exhaust channel. The opening of the two channels is automatically adjusted according to the temperature using an adjustment component. At low frequency and low temperature, the opening of the first exhaust channel is large, and the refrigerant is quickly discharged through a path with low flow resistance to maintain performance. At high frequency and high temperature, the opening of the second exhaust channel is large, and the refrigerant is discharged through a path with high flow resistance but good noise reduction effect to reduce noise. This avoids the energy efficiency loss caused by simply increasing the volume or reducing the exhaust port area, and optimizes noise control for different frequencies, thereby effectively solving the problem of balancing the low-frequency energy efficiency and high-frequency noise of the compressor.

[0017] The compressor provided by this invention is designed based on the above-mentioned noise reduction structure. Its beneficial effects are the same as those of the above-mentioned noise reduction structure, and will not be repeated here.

[0018] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention and to implement it in accordance with the contents of the specification, the preferred embodiments of the present invention are described in detail below with reference to the accompanying drawings. Attached Figure Description

[0019] To more clearly illustrate the technical solutions in the embodiments of the present invention, 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 the structures shown in these drawings without creative effort.

[0020] Figure 1 A cross-sectional view of a sound-absorbing structure provided in an embodiment of the present invention; Figure 2 This is a schematic diagram of a sound-absorbing structure provided in an embodiment of the present invention; Figure 3 This is a schematic diagram of a sound-absorbing structure from another angle, provided in an embodiment of the present invention. Figure 4 A cross-sectional view of the flange and diaphragm assembly in a sound-absorbing structure provided in an embodiment of the present invention; Figure 5 A schematic diagram of the structure of a noise reduction structure provided in an embodiment of the present invention, showing the first exhaust channel outlet fully open; Figure 6 This is a schematic diagram of a noise reduction structure provided in an embodiment of the present invention, showing the second exhaust channel when it is completely closed. Figure 7 This is a schematic diagram of the structure of a noise reduction structure provided in an embodiment of the present invention, showing the outlet portion of the first exhaust channel when it is open. Figure 8 This is a schematic diagram of a noise reduction structure provided in an embodiment of the present invention, showing the second exhaust channel partially open. Figure 9 This is a schematic diagram of a silencing structure provided in an embodiment of the present invention, showing the first exhaust channel outlet completely closed. Figure 10 This is a schematic diagram of a noise reduction structure provided in an embodiment of the present invention, showing the second exhaust channel when it is fully open. Figure 11 A cross-sectional view of a compressor provided in an embodiment of the present invention; Figure 12 A cross-sectional view of a pump body assembly in a compressor provided in an embodiment of the present invention; Figure label explanation: 10. Housing; 11. Flange; 12. Partition; 13. Silencer Cover; 20. First Exhaust Passage; 30. Second Exhaust Passage; 31. Sound Absorption Chamber; 40. Adjustment Assembly; 41. First Adjustment Unit; 42. Second Adjustment Unit; 411. First Actuating Component; 412. First Temperature Sensing Actuating Component; 421. Second Actuating Component; 422. Second Temperature Sensing Actuating Component; 50. Silencer Chamber; 60. Pump Body Assembly; 61. Crankshaft; 62. Upper Flange; 63. Lower Flange; 64. Sliding Vane; 65. Roller; 66. Cylinder; 70. Housing Assembly; 71. Upper Housing; 72. Housing; 73. Lower Housing; 80. Motor Assembly; 81. Stator; 82. Rotor; 90. Distributor. Detailed Implementation

[0021] To further illustrate the technical means and effects adopted by the present invention to achieve the intended purpose, the specific embodiments, structures, features, and effects according to the present invention will be described in detail below with reference to the accompanying drawings and preferred embodiments. In the following description, different "an embodiment" or "an embodiment" do not necessarily refer to the same embodiment. Furthermore, specific features, structures, or characteristics in one or more embodiments can be combined in any suitable form.

[0022] In the description of this invention, it should be clearly stated that the terms "first," "second," etc., in the specification, claims, and accompanying drawings are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence; the terms "vertical," "lateral," "longitudinal," "front," "rear," "left," "right," "up," "down," "horizontal," etc., indicate orientation or positional relationships based on the orientation or positional relationships shown in the accompanying drawings, and are merely for the convenience of describing this invention, and do not mean that the device or element referred to must have a specific orientation or position, and therefore should not be construed as a limitation of this invention.

[0023] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" 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 mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0024] To better understand the above technical solutions, the following will provide a detailed explanation of the technical solutions in conjunction with the accompanying drawings and specific implementation methods.

[0025] Example 1 This embodiment provides a noise reduction structure, such as Figures 1-10 As shown, the silencing structure includes a housing 10, a first exhaust channel 20, a second exhaust channel 30, and an adjustment component 40. A silencing cavity 50 is formed within the housing 10. The first exhaust channel 20 communicates with the silencing cavity 50, and the second exhaust channel 30 includes a sound-absorbing channel 31, the inlet of which communicates with the silencing cavity 50. The adjustment component 40 can adjust the opening of the first exhaust channel 20 and the second exhaust channel 30 according to temperature changes, such that at a first temperature, the opening of the first exhaust channel 20 is greater than the opening of the second exhaust channel 30, and at a second temperature, the opening of the second exhaust channel 30 is greater than the opening of the first exhaust channel 20; wherein, the second temperature is greater than the first temperature.

[0026] In the automatic adjustment silencing structure, a silencing cavity 50 is formed inside the housing 10. The first exhaust channel 20 is directly connected to the housing 10 and communicates with the silencing cavity 50. The second exhaust channel 30 includes a sound-absorbing channel 31, the inlet of which is connected to the silencing cavity 50. The adjustment component 40 is set on the housing 10 and connected to the first exhaust channel 20 and the second exhaust channel 30 respectively. It can directly adjust the opening size of the two channels according to temperature changes. More specifically, the silencing cavity 50 is located in the central area inside the housing 10. The first exhaust channel 20 and the second exhaust channel 30 extend from the silencing cavity 50 to the outside of the housing 10. The adjustment component 40 controls the opening and closing of the channels through mechanical linkage to ensure that the opening ratio of the two channels is automatically adjusted when the temperature changes. The housing 10 serves as an integral structure to house the silencing cavity 50 and provide a mounting base. The silencing cavity 50 reduces the intensity of aerodynamic noise through its volume expansion. The first exhaust channel 20 serves as a direct exhaust path for quickly discharging refrigerant to maintain compressor performance. The second exhaust channel 30 provides additional silencing effect through a sound-absorbing channel to improve noise performance. The regulating component 40 automatically adjusts the opening of the first exhaust channel 20 and the second exhaust channel 30 according to the temperature changes caused by compressor operation, achieving optimized balance under different operating conditions. More specifically, the regulating component 40 drives the valve or sliding cover to change the channel opening through a temperature sensing element, ensuring performance priority at low frequencies and noise control at high frequencies.

[0027] During compressor operation, the refrigerant first enters the silencer 50 for initial noise reduction. When the compressor operates at low frequencies, the temperature is low, and the regulating component 40 makes the opening of the first exhaust passage 20 larger and the opening of the second exhaust passage 30 smaller. Since the flow resistance of the first exhaust passage 20 is less than that of the second exhaust passage 30, the refrigerant is mainly discharged directly from the first exhaust passage 20 with lower flow resistance, reducing energy loss and ensuring high efficiency. When the compressor operates at high frequencies, the temperature rises, and the regulating component 40 makes the opening of the first exhaust passage 20 smaller and the opening of the second exhaust passage 30 larger. The refrigerant then flows out from the second exhaust passage 30, which has higher flow resistance but better noise reduction, further reducing noise through the sound absorption channel. More specifically, this dynamic adjustment allows the compressor to prioritize energy efficiency at low frequencies and noise reduction at high frequencies, achieving automatic optimization.

[0028] Background technology indicates that traditional mufflers improve noise reduction by increasing the volume of the muffler cavity and reducing the area of ​​the exhaust port, but this leads to reduced compressor efficiency and insufficient low-frequency operation capability. The muffler structure of this embodiment forms a muffler cavity 50 through the housing 10 and is provided with a first exhaust channel 20 and a second exhaust channel 30. The opening of the two channels is automatically adjusted according to the temperature by the adjustment component 40. At low frequency and low temperature, the opening of the first exhaust channel 20 is large, and the refrigerant is quickly discharged from the path with low flow resistance to maintain performance. At high frequency and high temperature, the opening of the second exhaust channel 30 is large, and the refrigerant is discharged from the path with high flow resistance but good noise reduction effect to reduce noise. This avoids the energy loss caused by simply increasing the volume or reducing the exhaust port area, and optimizes noise control for different frequencies, thereby effectively solving the problem of balancing the low-frequency energy efficiency and high-frequency noise of the compressor.

[0029] In a specific embodiment, such as Figures 1-3 As shown, the adjustment component 40 includes a first adjustment unit 41 and a second adjustment unit 42. The first adjustment unit 41 is disposed at the first exhaust channel 20 and can continuously adjust the opening of the first exhaust channel 20 according to the temperature. The second adjustment unit 42 is disposed at the inlet of the second exhaust channel 30 and can continuously adjust the opening of the second exhaust channel 30 according to the temperature.

[0030] The first adjustment unit 41 is directly disposed at the opening of the first exhaust channel 20 and fixedly connected to the housing 10. Its movable part covers the first exhaust channel 20 to adjust the opening. The second adjustment unit 42 is disposed at the inlet of the second exhaust channel 30, i.e., the starting point of the sound-absorbing channel, and is also fixedly connected to the housing 10. Its movable part covers the inlet to control the refrigerant entry. More specifically, the first adjustment unit 41 and the second adjustment unit 42 are mechanically installed at corresponding positions on the housing 10, so that they can operate independently according to temperature changes, thereby changing the opening and closing state of the channels. The main function of the first adjustment unit 41 is to continuously adjust the opening of the first exhaust channel 20 according to the temperature changes caused by the operation of the compressor, thereby controlling the flow rate of refrigerant directly discharged from the silencer 50, ensuring a larger opening at low temperatures to maintain low flow resistance and high performance. The main function of the second adjustment unit 42 is to continuously adjust the inlet opening of the second exhaust channel 30 according to the temperature changes, thereby controlling the flow rate of refrigerant entering the sound-absorbing channel, ensuring a larger opening at high temperatures to utilize the silencing effect of the sound-absorbing channel to reduce noise. More specifically, the first adjustment unit 41 focuses on optimizing energy efficiency, while the second adjustment unit 42 focuses on improving noise performance.

[0031] When the first regulating unit 41 and the second regulating unit 42 work together, when the compressor operates at a low frequency and low temperature, the first regulating unit 41 increases the opening of the first exhaust passage 20, while the second regulating unit 42 decreases the opening of the second exhaust passage 30. The refrigerant is mainly discharged from the first exhaust passage 20, which has low flow resistance, ensuring high performance and energy efficiency. When the compressor operates at a high frequency and the temperature rises, the first regulating unit 41 decreases the opening of the first exhaust passage 20, while the second regulating unit 42 increases the opening of the second exhaust passage 30. The refrigerant is then discharged from the second exhaust passage 30, which has high flow resistance but good noise reduction, reducing noise through the sound-absorbing channel. This coordinated operation achieves automatic adjustment, enabling the compressor to balance energy efficiency and noise under different operating conditions, thereby effectively improving high-frequency noise without affecting low-frequency performance.

[0032] In a specific embodiment, such as Figure 1 and Figure 3 As shown, the first adjustment unit 41 includes a first actuating element 411 and a first temperature-sensing driving element 412. The first temperature-sensing driving element 412 is connected to the first actuating element 411 and the housing 10. Its deformation drives the first actuating element 411 to move to change the opening of the first exhaust passage 20. The second adjustment unit 42 includes a second actuating element 421 and a second temperature-sensing driving element 422. The second temperature-sensing driving element 422 is connected to the second actuating element 421 and the housing 10. Its deformation drives the second actuating element 421 to move to change the opening of the second exhaust passage 30.

[0033] The first actuating element 411 is directly disposed at the opening of the first exhaust passage 20 and can slide on the surface of the housing 10. One end of the first temperature-sensing driving element 412 is fixedly connected to the housing 10, and the other end is connected to the first actuating element 411, forming a driving relationship. The function of the first actuating element 411 is to cover or expose the opening of the first exhaust passage 20 by sliding, thereby directly controlling its opening size. The function of the first temperature-sensing driving element 412 is to sense temperature changes and drive the movement of the first actuating element 411 through its own deformation. When the two work together, when the compressor operates at a low frequency and the temperature is low, the first temperature-sensing driving element 412 is in a contracted state. In the first exhaust channel 20, the first actuator 411 is pulled away from the opening of the first exhaust channel 20, increasing its opening. This allows the refrigerant to be discharged more easily from the first exhaust channel 20, which has low flow resistance, thus ensuring the compressor's energy efficiency and performance. When the compressor's high-frequency operating temperature rises, the first temperature-sensing actuator 412 gradually stretches, pushing the first actuator 411 towards the opening of the first exhaust channel 20, reducing its opening and restricting the refrigerant from being discharged from the first channel. This causes the refrigerant to turn towards the second exhaust channel 30, which helps reduce noise during high-frequency operation. This automatic adjustment ensures that the compressor can dynamically balance performance and noise under different operating conditions, achieving optimized operation.

[0034] The second actuator 421 is directly installed at the inlet of the second exhaust channel 30, i.e., the starting point of the sound absorption channel, and can move vertically. One end of the second temperature-sensing actuator 422 is fixedly connected to the housing 10, and the other end is connected to the second actuator 421, driving it to move up and down. The function of the second actuator 421 is to open or close the inlet of the second exhaust channel 30 by moving up and down, controlling the flow rate of refrigerant into the sound absorption channel. The function of the second temperature-sensing actuator 422 is to contract or expand according to temperature changes, thereby driving the movement of the second actuator 421. When the two work together, when the compressor operates at low frequency and low temperature, the second temperature-sensing actuator 422... In the stretched state, the second actuator 421 is pushed upward to press against the partition, closing the inlet of the second exhaust passage 30. The refrigerant cannot be discharged from the second passage, ensuring that the refrigerant is preferentially discharged from the first exhaust passage 20 to maintain low flow resistance and high performance. When the compressor's high-frequency operating temperature rises, the second temperature-sensing actuator 422 gradually contracts, pulling the second actuator 421 downward to open the inlet of the second exhaust passage 30. The refrigerant can enter the sound-absorbing channel and be discharged from the second passage. The sound-absorbing channel's noise reduction effect is used to reduce high-frequency noise. This coordinated action enables the compressor to effectively improve noise performance at high temperatures and high frequencies without affecting its operating efficiency at low temperatures and low frequencies.

[0035] In a specific embodiment, the first temperature-sensing actuator 412 and the second temperature-sensing actuator 422 are shape memory alloy elements, and the first temperature-sensing actuator 412 is configured to elongate when the temperature rises, and the second temperature-sensing actuator 422 is configured to contract when the temperature rises. Both the first actuating element 411 and the second actuating element 421 are sliding covers.

[0036] Both the first temperature-sensing actuator 412 and the second temperature-sensing actuator 422 are made of an alloy material with shape memory effect. This material can undergo a reversible phase transition at a specific temperature, thereby changing its shape. More specifically, the first temperature-sensing actuator 412 is designed to elongate when it senses a temperature rise caused by an increase in the compressor's operating frequency. This elongation pushes or pulls the connected first actuator 411 to reduce the opening of the first exhaust passage 20. Simultaneously, the second temperature-sensing actuator 422 is designed to contract under the same temperature rise. This contraction pulls or releases the connected second actuator 421, thereby increasing the inlet opening of the second exhaust passage 30. This reverse motion logic enables the two passages to open and close in a coordinated and complementary manner, thus producing the key effect of automatically switching the exhaust path. When the compressor operates at low frequency and the internal temperature of the casing is low, the first temperature-sensing actuator 412 is shorter and the second temperature-sensing actuator 422 is longer, ensuring that the first exhaust passage 20 is unobstructed while the second exhaust passage 30 is almost closed, thus guaranteeing good operating performance. When the compressor operates at high frequency and the temperature rises to the set value, the first temperature-sensing actuator 412 extends to close the performance passage, while the second temperature-sensing actuator 422 contracts to open the noise reduction passage. This achieves a smooth transition from focusing on energy efficiency to focusing on noise control without relying on external control, perfectly balancing the conflicting needs under different operating conditions. Currently, the mainstream material that can achieve this temperature-driven deformation characteristic is nickel-titanium alloy. At the same time, any other shape memory material that can achieve the above-mentioned characteristic of one side extending and the other side contracting when the temperature rises can also be applied to the first temperature-sensing actuator 412 and the second temperature-sensing actuator 422.

[0037] In a specific embodiment, the shape memory alloy element is a shape memory alloy spring.

[0038] The shape memory alloy element is specifically designed as a shape memory alloy spring. This means that both the first temperature-sensing actuator 412 and the second temperature-sensing actuator 422 adopt the physical form of a spring to realize their functions. This spring is made of an alloy material with shape memory properties and can automatically stretch or contract according to temperature changes. More specifically, as a mechanical element, the helical structure of the shape memory alloy spring allows it to generate linear displacement through changes in its internal crystal structure when the temperature rises, thereby directly pulling or pushing the connected actuator. For example, when the first temperature-sensing actuator 412 stretches when the temperature rises, it will drive the first actuator 411 to slide to reduce the opening of the first exhaust channel 20, while when the second temperature-sensing actuator 422 contracts when the temperature rises, it will pull the second actuator 421 to move to increase the opening of the second exhaust channel 30. The effect of this spring form is that it provides a simple and reliable driving mechanism that can directly convert temperature changes into mechanical motion without the need for an external power source, thereby achieving continuous and automatic adjustment. Furthermore, the elastic characteristics of the spring ensure the smoothness and repeatability of the action, avoid sudden switching changes, and enable the compressor to smoothly transition between different exhaust modes when the frequency changes.

[0039] In a specific embodiment, such as Figure 4 , Figure 6 , Figure 8 as well as Figure 10 As shown, the sound-absorbing channel is provided with multiple sound-absorbing cavities 31 of different depths. The depth of each sound-absorbing cavity 31 is set based on the quadratic remainder sequence Sn, where Sn=n 2 mod p, where n is a natural number and p is an odd prime number.

[0040] The sound-absorbing channel is equipped with multiple sound-absorbing cavities 31 of different depths. The depth of these sound-absorbing cavities 31 is not set arbitrarily, but is arranged based on the mathematical rules of the quadratic remainder sequence Sn, where Sn is equal to the remainder obtained by dividing the square of n by the odd prime number p, where n starts from 1 and takes natural numbers, and p can be odd prime numbers such as 3, 5, 7, 11, etc.

[0041] More specifically, when p is selected as 11, the calculated Sn sequence is 1, 4, 9, 5, 3. This indicates that there are a total of 5 sound-absorbing cavities 31 in the sound-absorbing channel, and the depths of these sound-absorbing cavities are in the ratio of 1:4:9:5:3 in sequence. This design can produce a significant broadband sound absorption effect because the sound-absorbing cavities 31 at different depths can reflect and interfere with sound waves of multiple frequencies. When the refrigerant flows through the sound-absorbing channel, the sound waves will have a phase difference in the sound-absorbing cavities 31 at different depths, which will cause the sound wave energy to cancel each other out and weaken. Furthermore, this depth distribution based on the quadratic remainder sequence ensures that the sound absorption effect covers a wide frequency range, so that the compressor can effectively reduce aerodynamic noise when running at high frequencies, while maintaining the compactness of the structure, thereby optimizing noise control performance without increasing the additional volume.

[0042] In a specific embodiment, the depth dn of the sound-absorbing cavity 31 is determined by the formula dn=Sn*c / (2*f*p), where c is the sound velocity of the refrigerant and f is the optimized target center frequency.

[0043] dn equals Sn multiplied by the refrigerant speed of sound c, then divided by twice the product of the target center frequency f and the odd prime number p, where Sn is the value of the quadratic remainder sequence. More specifically, this formula directly relates the depth of the sound-absorbing cavity to the physical characteristics of the sound wave, ensuring that the depth of each sound-absorbing cavity is optimized for a specific sound wave frequency. For example, when p=11, the Sn sequence is 1, 4, 9, 5, 3. Assuming the refrigerant speed of sound c is 150 meters per second and the target center frequency f is 1000 Hz, then the depth d1 of the first sound-absorbing cavity is calculated as 1 multiplied by 150 divided by 2 multiplied by 1000 multiplied by 11, which equals approximately 6.8 mm. Similarly, d2 is 4 multiplied by 150 divided by the same denominator, which equals approximately... The depth values ​​are 27.3 mm, d3 is approximately 61.4 mm after multiplying by 9, d4 is approximately 34.1 mm after multiplying by 5, and d5 is approximately 20.5 mm after multiplying by 3. These depth values ​​are precisely set based on the sequence ratio. This design can produce a highly efficient broadband sound absorption effect because the sound absorption cavities 31 of different depths can resonate and interfere with multiple frequency sound waves centered on the target center frequency f. When the refrigerant flows through the sound absorption channel, the sound waves are reflected and superimposed in each sound absorption cavity 31. Due to the phase change caused by the depth difference, the sound energy cancels each other out and weakens, thereby significantly reducing the aerodynamic noise of the compressor when it is running at high frequency, while maintaining the structural compactness and further improving the noise reduction performance without affecting the overall efficiency.

[0044] In a specific embodiment, the housing 10 includes a flange 11, a partition 12, and a muffler cover 13, wherein the muffler cover 13, the flange 11, and the partition 12 together form the muffler cavity 50; the first exhaust channel 20 is disposed on the muffler cover 13, and the sound absorption channel is formed between the flange 11 and the partition 12.

[0045] Flange 11, partition 12, and muffler cover 13 are connected by a tight mechanical connection to form housing 10. Flange 11 serves as a basic mounting component, with its lower end face connected to the compressor pump body assembly and its upper end face having a channel for sound absorption. Partition 12 directly covers the upper end face of flange 11, and its shape matches and fits tightly to the upper end face of flange 11, thereby sealing off the area above the sound absorption channel. Muffler cover 13 covers partition 12 and is fixedly connected to flange 11 by screws, so that muffler cover 13, flange 11, and partition 12 together form a closed sound-absorbing cavity 50, and the first exhaust channel 20 is directly opened on muffler cover 13. The main function of flange 11 is to serve as the mounting base for the entire silencing structure. It not only provides a connection interface with the compressor pump body, but the sound-absorbing channel inside it also forms a key part of the second exhaust channel 30, used for noise reduction of the refrigerant. The core function of baffle 12 is to separate the space. It completely isolates the lower sound-absorbing channel from the upper silencing cavity 50, forcing the refrigerant to flow along a predetermined path. At the same time, it and flange 11 together form the boundary of the sound-absorbing channel. The main function of silencer cover 13 is to form the top and side walls of the silencing cavity 50. Together with flange 11 and baffle 12, it forms a complete expansion chamber silencer, and it directly provides the outlet of the first exhaust channel 20.

[0046] The refrigerant discharged from the compressor first enters the silencing cavity 50, which is formed by the flange 11, the baffle 12, and the muffler cover 13, for initial noise reduction. This is the first stage of noise reduction. Then, the presence of the baffle 12 ensures that the refrigerant cannot escape directly upwards. Instead, it must be selected according to the state of the regulating component 40: either it is discharged directly through the first exhaust channel 20 on the muffler cover 13 to maintain low flow resistance, or it enters the sound-absorbing channel formed by the flange 11 and the baffle 12 for deeper broadband sound absorption treatment before being discharged through the second exhaust channel 30. This synergistic cooperation produces a staged and selectable noise reduction effect, which provides basic resistance noise reduction through the silencing cavity 50 and efficient broadband sound absorption through the sound-absorbing channel. This allows the structure to automatically optimize according to the compressor's operating frequency, ensuring flow resistance and performance at low frequencies and significantly improving noise suppression capabilities at high frequencies.

[0047] During compressor operation, the refrigerant first exits from the compression chamber and enters the silencer cavity 50, which is formed by the flange 11, the partition 12, and the silencer cover 13, for initial expansion and noise reduction. When the compressor is in low-frequency operation, due to the low temperature, the first temperature-sensing actuator 412, acting as a shape memory alloy spring, is in a contracted state, thereby pulling the first actuating element 411 away from the opening of the first exhaust passage 20, increasing its opening. At the same time, the second temperature-sensing actuator 422, acting as another shape memory alloy spring, is in an extended state, thereby pushing the second actuating element 421 upward to close the inlet of the second exhaust passage 30. Figure 5 and Figure 6 As shown, at this time, the refrigerant is mainly discharged directly from the first exhaust channel 20 with low flow resistance, ensuring that the compressor maintains high efficiency performance. As the compressor's operating frequency increases, causing the temperature to rise, the first temperature-sensing actuator 412 gradually extends, pushing the first actuating element 411 towards the first exhaust passage 20 to reduce its opening. Simultaneously, the second temperature-sensing actuator 422 gradually retracts, pulling the second actuating element 421 downwards to open the inlet of the second exhaust passage 30. Figure 7 and Figure 8 As shown, the refrigerant initially flows to the second exhaust channel 30 and passes through the sound absorption channel; more specifically, the sound absorption channel is provided with multiple sound absorption cavities 31 of different depths, which are set based on the quadratic remainder sequence Sn, so that the sound absorption cavities 31 of different depths can reflect and interfere with broadband sound waves, thereby effectively absorbing noise. When the compressor enters high-frequency operation, the temperature rises further. The first temperature-sensing actuator 412 fully extends, causing the first actuating element 411 to close the first exhaust passage 20. Simultaneously, the second temperature-sensing actuator 422 fully retracts, causing the second actuating element 421 to fully open the inlet of the second exhaust passage 30. Figure 9 and Figure 10 As shown, all the refrigerant is discharged from the second exhaust channel 30, and the sound wave energy is greatly weakened when it flows through the sound absorption channel. This automatic adjustment process ensures that the compressor prioritizes energy efficiency at low frequencies and significantly improves noise at high frequencies, thus achieving an overall balance between performance and noise optimization.

[0048] Example 2 This embodiment provides a compressor, such as Figure 11 and Figure 12 As shown, the compressor includes a noise reduction structure as described in Example 1.

[0049] This compressor incorporates the noise-reducing structure described in Example 1. Its core feature is its ability to automatically adjust the opening of the two exhaust channels based on temperature changes caused by variations in its operating frequency. When the compressor operates at low frequencies, the refrigerant is primarily discharged through the first exhaust channel, which has low flow resistance and is conducive to performance, ensuring energy efficiency. When operating at high frequencies, it switches to the second exhaust channel, which has higher flow resistance but better noise reduction, significantly lowering noise. This allows the compressor to effectively solve the problem of prominent aerodynamic noise at high frequencies without sacrificing its low-frequency operating capabilities.

[0050] In addition, such as Figure 11 and Figure 12 As shown, the compressor also includes a pump body assembly 60, a housing assembly 70, a motor assembly 80, and a distributor 90. The pump body assembly 60 includes a crankshaft 61, an upper flange 62, a lower flange 63, vanes 64, rollers 65, and a cylinder 66. The housing assembly 70 includes an upper housing 71, a housing 72, and a lower housing 73. The motor assembly 80 includes a stator 81 and a rotor 82. The pump body assembly 60 is the core compression part of the compressor. It contains the cylinder 66, which houses the rollers 65 and vanes 64 and is driven by the crankshaft 61, which passes through the upper flange 62 and the lower flange 63. The motor assembly 80 provides power; its rotor 82 is directly mounted on the crankshaft 61, while the stator 81 is fixed inside the housing assembly 70. The housing assembly 70, serving as an integral support and sealing structure, is assembled from the upper housing 71, the main housing 72, and the lower housing 73, enclosing the pump body assembly 60 and the motor assembly 80. The distributor 90 is installed outside the compressor to handle the refrigerant entering the compressor. More importantly, the automatic adjustment silencing structure of the present invention is directly set on the upper flange 62 of the pump body assembly 60 and the end face of the flange 11, specifically in the space between the upper flange 62 and the upper housing 71. This allows the high-pressure refrigerant discharged from the exhaust port of the cylinder 66 to first enter the silencing structure for processing, thereby achieving efficient noise reduction and automatic performance adjustment.

[0051] In a specific embodiment, the compressor is a variable frequency rotary compressor, and the adjustment component 40 can adjust according to the temperature change caused by the change in the compressor's operating frequency.

[0052] The compressor is a variable frequency rotary compressor, and its regulating component 40 can self-regulate based on the temperature changes directly caused by variations in the compressor's operating frequency. More specifically, when the operating frequency of the variable frequency rotary compressor increases, its internal load increases, leading to a corresponding rise in the temperature inside the casing. The regulating component 40 can sense this frequency-driven temperature change and automatically adjust the opening of the first exhaust passage 20 and the second exhaust passage 30. The effect is that when the compressor operates at low frequency and light load, the temperature is lower, and the regulating component 40 directs the refrigerant primarily through the first exhaust passage 20, which is beneficial for performance, ensuring energy efficiency and operational capacity. Conversely, when the compressor operates at high frequency and heavy load, the temperature rises, and the regulating component 40 activates, gradually diverting the refrigerant to the second exhaust passage 30, which offers better noise reduction, thereby significantly improving the particularly prominent aerodynamic noise at this time. This cleverly utilizes the correlation between the variable frequency compressor's operating frequency and temperature to achieve automatic and precise switching of the noise reduction mode, ultimately effectively solving the high-frequency noise problem without affecting low-frequency performance.

[0053] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any person skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope disclosed in the present invention, and these modifications or substitutions should all be covered within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A sound absorbing structure, characterized by, The muffling structure comprises a shell, a first exhaust passage, a second exhaust passage and an adjusting assembly, the shell has a muffling cavity formed therein; the first exhaust passage is in communication with the muffling cavity, the second exhaust passage comprises a sound absorption passage, an inlet of the sound absorption passage is in communication with the muffling cavity; the adjusting assembly is capable of adjusting the opening degree of the first exhaust passage and the second exhaust passage according to temperature change, so that the opening degree of the first exhaust passage is greater than that of the second exhaust passage at a first temperature, and the opening degree of the second exhaust passage is greater than that of the first exhaust passage at a second temperature; wherein the second temperature is greater than the first temperature.

2. The sound attenuation structure of claim 1, wherein The adjusting assembly comprises a first adjusting unit and a second adjusting unit, the first adjusting unit is arranged at the first exhaust passage and is capable of continuously adjusting the opening degree of the first exhaust passage according to temperature, the second adjusting unit is arranged at the inlet of the second exhaust passage and is capable of continuously adjusting the opening degree of the second exhaust passage according to temperature.

3. The sound attenuating structure of claim 2, wherein, The first adjusting unit comprises a first action member and a first temperature-sensing driving member, the first temperature-sensing driving member connects the first action member and the shell, and is capable of driving the first action member to move by deformation to change the opening degree of the first exhaust passage; The second adjusting unit comprises a second action member and a second temperature-sensing driving member, the second temperature-sensing driving member connects the second action member and the shell, and is capable of driving the second action member to move by deformation to change the opening degree of the second exhaust passage.

4. The sound attenuating structure of claim 3, wherein, The first temperature-sensing driving member and the second temperature-sensing driving member are shape memory alloy elements, and the first temperature-sensing driving member is configured to elongate when temperature rises, and the second temperature-sensing driving member is configured to contract when temperature rises.

5. The sound attenuating structure of claim 4, wherein, The shape memory alloy element is a shape memory alloy spring.

6. The sound attenuation structure of claim 1, wherein The sound absorption channel is provided with a plurality of sound absorption cavities with different depths, and the depth of each sound absorption cavity is set based on a quadratic residue sequence Sn, wherein Sn=n 2 modp, n is a natural number, and p is an odd prime number.

7. The sound attenuating structure of claim 6, wherein, The depth dn of the sound absorption cavity is determined by the formula dn=Sn*c / (2*f*p), wherein c is the sound speed of refrigerant, and f is the center frequency of optimization target.

8. The sound attenuation structure of claim 1, wherein, The shell comprises a flange, a partition plate and a muffler cover, the muffler cover, the flange and the partition plate jointly define the muffling cavity; the first exhaust passage is arranged on the muffler cover, and the sound absorption passage is formed between the flange and the partition plate.

9. A compressor characterized by, The compressor comprises the muffling structure according to any one of claims 1 to 8.

10. The compressor of claim 9, wherein, The compressor is a variable frequency rotary compressor, and the adjusting assembly is capable of adjusting according to temperature change caused by compressor operating frequency change.

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