A compressor

Abstract

This invention relates to the field of compressor technology and discloses a compressor, including a cylinder, a bearing assembly, a piston, and an exhaust valve assembly; the bearing assembly has an exhaust port; the piston is disposed inside the cylinder; the volume of the compression chamber is Vst (m³); the exhaust valve assembly includes an exhaust valve plate and a lift limit plate; the diameter of the exhaust port is d (m); the exhaust valve plate includes a fixed part and a movable part, the total length of the exhaust valve plate is L (m), the thickness is t (m), the length of the fixed part is L1 (m), the length of the movable part is L2 (m), and the minimum width of the movable part is L3 (m); the Young's modulus of the exhaust valve plate is E (Pa), the rotational speed is n (rpm); the elastic coefficient of the exhaust valve plate is K; this invention limits 7*10 3 <K*t / Vst<1.1*10 4 This can reduce the sound pressure level of exhaust noise, which helps improve the user's listening experience in the low-frequency range.

Description

Technical Field

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

[0002] In rotary compressors, the discharge valve is a core component controlling refrigerant discharge, and its performance directly affects the compressor's reliability and noise level. Existing discharge valves typically consist of a root section, a waist section, and a head section. The head section covers the discharge port, the root section is fixed, and the waist section is the main deformation area. During compressor operation, the valve opens and closes periodically under gas pressure, repeatedly impacting the lift limit plate and valve seat, which can easily lead to valve breakage.

[0003] To address the valve plate fracture problem and improve compressor performance, various improvement schemes have been proposed in the prior art. For example, patent number CN112177892A discloses an exhaust valve plate and compressor, which adjusts the valve plate stiffness without increasing its thickness by setting the waist section of the valve plate as a variable width structure, where the width b1 at the junction with the root section is greater than the width b0 at the junction with the head section. This reduces the maximum bending stress of the valve plate and thus improves its fatigue strength. This solution improves the reliability of the valve plate to a certain extent.

[0004] However, the inventors of this application discovered in actual research and development that the aforementioned prior art mainly focuses on the strength of the valve plate itself and the timely closing at high speeds, but fails to effectively solve the problem of exhaust noise that occurs when the compressor operates at ultra-low speeds (such as 4-8 rpm). Under ultra-low speed conditions, due to changes in gas pressure pulsation characteristics, if the holding force of the exhaust valve plate is relatively strong, its instantaneous opening during exhaust will generate severe pressure fluctuations and impacts, thus causing a harsh noise that seriously affects the user's auditory experience in the low-frequency range. Therefore, how to optimize the design of the exhaust valve plate for ultra-low speed conditions to reduce exhaust noise at its source has become a pressing technical problem in this field. Summary of the Invention

[0005] With the aim of at least solving one of the technical problems existing in the prior art, the present invention aims to provide a compressor that helps improve the user's auditory experience in the low-frequency range.

[0006] To achieve the above objectives, the present invention provides a compressor, including a cylinder, a bearing assembly, a piston, and an exhaust valve assembly; the bearing assembly has an exhaust port; the piston is eccentrically rotatably disposed within the cylinder; the cylinder, the bearing assembly, and the piston together enclose a compression chamber with a volume of Vst (m³); the exhaust valve assembly is disposed on the bearing assembly and is used to control the opening and closing of the exhaust port; the exhaust valve assembly includes an exhaust valve plate and a lift limit plate; the exhaust valve plate includes a fixed portion and a movable portion connected along the length direction of the exhaust valve plate; the fixed portion is fitted and fixed to the lift limit plate; the total length of the exhaust valve plate is L (m), the thickness is t (m), the length of the fixed portion is L1 (m), the length of the movable portion is L2 (m), L2 = L - L1, the minimum width of the movable portion is L3 (m), and the Young's modulus of the material of the exhaust valve plate is E (Pa).

[0007] The elastic modulus K (N / m) of the exhaust valve plate is given by K = (E * L³ * t). 3 ) / (4 * L2 3 ); The above parameters satisfy: 7*10 3 <K*t / Vst<1.1*10 4 .

[0008] In some embodiments, the volume of the compression chamber is Vst (m³), satisfying: 4*10 -5 ≤Vst≤6.5*10 -5 .

[0009] In some embodiments, the diameter of the vent hole is d (m), which satisfies: 0.01≤d≤0.012.

[0010] In some embodiments, the fixed part includes a root section and a first waist section connected along the length direction of the exhaust valve plate, and the movable part includes a second waist section and a head section connected along the length direction of the exhaust valve plate. The head section is disposed opposite to the exhaust hole. The end of the second waist section away from the head section is connected to the first waist section. The second waist section has a minimum width L3 and is a structure with equal width.

[0011] In some embodiments, the total length of the exhaust valve plate is L (m), the length of the fixed part is L1 (m), and the length of the movable part is L2 (m), where L2 = L - L1, satisfying: 0.033 ≤ L2 ≤ 0.038.

[0012] Preferably, 0.04875≤L≤0.059, 0.0155≤L1≤0.021.

[0013] In some embodiments, the minimum width of the movable part is L3 (m), which satisfies: 0.008≤L3≤0.0103.

[0014] In some embodiments, the thickness of the exhaust valve plate is t (m), satisfying: 4.06*10 -4 ≤t≤5.08*10 -4 .

[0015] In some embodiments, the Young's modulus of the material of the exhaust valve plate is E (Pa), satisfying: 2.0 * 10⁻⁶. 11 ≤E≤2.2*10 11 .

[0016] In some embodiments, the refrigerant of the compressor is one of R290, R32 or R410A.

[0017] Compared with the prior art, the compressor of this invention has the following advantages: by limiting 7*10 3 <K*t / Vst<1.1*10 4 This can balance the "holding force of the exhaust valve plate itself hindering opening" and the "driving force of gas pushing the exhaust valve plate to open"; when K*t / Vst is less than 7*10 3 When the exhaust valve plate opens too easily, it can lead to delayed closure or chattering; when K*t / Vst is higher than 1.1*10 4 When the exhaust valve plate holds too much force, it will generate violent pressure fluctuations and impacts during the exhaust at ultra-low speeds. This is the root cause of the abnormal noise. By limiting K*t / Vst to between 7000 and 11000, the pressure fluctuations and impacts of the exhaust valve plate at ultra-low speeds (e.g., 4-8 rpm) can be reduced, the sound pressure level of the exhaust noise can be lowered, and the user's listening experience in the low-frequency range can be improved. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the structure of a compressor provided in an embodiment of the present invention; Figure 2 This is a front view of a compressor provided in an embodiment of the present invention; Figure 3 This is a cross-sectional view of a compressor provided in an embodiment of the present invention; Figure 4 yes Figure 3 Enlarged view of point A; Figure 5 This is a front view of the exhaust valve assembly provided in an embodiment of the present invention; Figure 6 This is a top view of the exhaust valve plate provided in an embodiment of the present invention; Figure 7 This invention provides a 1 / 3 OCT comparison curve at a rotational speed of 4 rpm; Figure 8 This invention provides a 1 / 3 OCT comparison curve at a rotational speed of 8 rpm.

[0019] In the diagram, 1 represents the cylinder; 2. Bearing assembly; 21. Vent hole; 3. Piston; 30. Compression chamber; 4. Exhaust valve assembly; 41. Exhaust valve plate; 42. Lift limit plate; 411. Fixed part; 412. Movable part; 4111. Root section; 4112. First waist section; 4121. Second waist section; 4122. Head section; X: length direction; Y: width direction; Z: thickness direction. Detailed Implementation

[0020] The specific embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and examples. The following examples are for illustrative purposes only and are not intended to limit the scope of the invention.

[0021] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention 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. Therefore, they should not be construed as limitations on this invention.

[0022] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature.

[0023] In this invention, unless otherwise explicitly 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 or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0024] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0025] Unless otherwise defined, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used in the description of this application is for the purpose of describing particular embodiments only and is not intended to limit the application; the terms "comprising" and "having" and any variations thereof in the description, claims and foregoing drawings of this application are intended to cover non-exclusive inclusion.

[0026] In this application, the reference to "embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places in the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment that is mutually exclusive with other embodiments.

[0027] like Figures 1 to 6 As shown, an embodiment of the present invention provides a compressor including a cylinder 1, a bearing assembly 2, a piston 3, and an exhaust valve assembly 4.

[0028] The bearing assembly 2 is provided with an exhaust port 21; the piston 3 is eccentrically rotatably disposed in the cylinder 1; the cylinder 1, the bearing assembly 2 and the piston 3 together form a compression chamber 30, the volume of the compression chamber 30 is Vst (m³); the exhaust valve assembly 4 is disposed on the bearing assembly 2 and is used to control the opening and closing of the exhaust port 21. The exhaust valve assembly 4 includes an exhaust valve plate 41 and a lift limit plate 42. The diameter of the vent 21 is d (m).

[0029] The exhaust valve plate 41 includes a fixed part 411 and a movable part 412 connected along the length direction X of the exhaust valve plate 41. The fixed part 411 is attached and fixed to the lift limit plate 42.

[0030] The total length of the exhaust valve plate 41 is L (m), the thickness is t (m), the length of the fixed part 411 is L1 (m), the length of the movable part 412 is L2 (m), L2=L-L1, and the minimum width of the movable part 412 is L3 (m); the Young's modulus of the material of the exhaust valve plate 41 is E (pa), and the speed of the compressor is n (rps).

[0031] The elastic modulus K (N / m) of the exhaust valve plate 41: K=(E * L3* t³) / (4 * L2³).

[0032] The compressor's exhaust velocity U (m / s) at a rotational speed n (rps): U=(4 * n * Vst ) / (π* d² ).

[0033] The above parameters satisfy: 7*10 3 <K*t / Vst<1.1*10 4 .

[0034] Based on this technical solution, by limiting 7*10 3 <K*t / Vst<1.1*10 4 This can balance the "holding force of the exhaust valve plate 41 itself hindering opening" and the "driving force of gas pushing the exhaust valve plate 41 to open"; when K*t / Vst is less than 7*10 3 When the exhaust valve plate 41 opens too easily, it may cause delayed closure or chattering; when K*t / Vst is higher than 1.1*10 4 When the exhaust valve plate 41 is held too tightly, it will generate a violent pressure fluctuation and impact during the exhaust at ultra-low speed. This is the root cause of the abnormal noise. By limiting K*t / Vst to between 7000 and 11000, the pressure fluctuation and impact of the exhaust valve plate 41 at ultra-low speed (e.g., 4 to 8 rps) can be reduced, the sound pressure level of the exhaust noise can be reduced, and the user's listening experience in the low frequency range can be improved.

[0035] The exhaust valve plate 41 has a length direction X, a width direction Y, and a thickness direction that are perpendicular to each other.

[0036] It should be noted that in the above formulas; Vst is the compressor's volume, measured in m³. It can be obtained by consulting the product manual or by using the liquid filling method or three-dimensional coordinate scanning calculation method. d is the diameter of the exhaust port 21, in meters, which can be obtained using a high-precision digital micrometer or optical image measuring instrument. L is the overall length of the exhaust valve plate 41, in meters, which can be obtained using a high-precision digital micrometer or optical image measuring instrument. L1 is the length of the fixing part 411 of the exhaust valve plate 41, in meters, which can be obtained using a high-precision digital micrometer or optical image measuring instrument. t is the thickness of the exhaust valve plate 41, in meters, which can be obtained using a high-precision digital micrometer or optical image measuring instrument. L3 is the minimum width of the exhaust valve plate 41, in meters, which can be obtained using a high-precision digital micrometer or optical image measuring instrument. E is the Young's modulus of the material of the exhaust valve plate 41, in Pa, which can be determined by tensile testing according to the standard GB / T 22315-2008 "Metallic Materials - Test Method for Elastic Modulus and Poisson's Ratio"; n represents the compressor's rotational speed, measured in rps, which can be read using a non-contact photoelectric tachometer or the encoder signal of the compressor's drive motor.

[0037] Preferably, the volume of the compression chamber 30 is Vst (m³), satisfying: 4*10 -5 ≤Vst≤6.5*10 -5 .

[0038] The preferred compressor displacement range of this application is Vst, which is 0.00004m³ to 0.000065m³ (i.e., 40cc to 65cc). Within this displacement range, the dynamic characteristics of the exhaust valve plate 41 are most sensitive to fluctuations in gas pressure. By limiting 7000 < K*t / Vst < 11000, a significant noise reduction effect can be achieved at 4 to 8 rps.

[0039] Preferably, the diameter of the exhaust port 21 is d (m), satisfying: 0.01 ≤ d ≤ 0.012. The diameter d (m) of the exhaust port 21 is in the range of 0.01m to 0.012m (i.e., 10mm to 12mm), which ensures that the exhaust flow velocity U is within a reasonable range. Specifically, if the diameter of the exhaust port 21 is too small, it will lead to increased exhaust resistance and excessively high flow velocity, exacerbating the impact on the exhaust valve plate 41; if the diameter of the exhaust port 21 is too large, it will make it difficult for the exhaust valve plate 41 to open.

[0040] See Figures 5 to 6 The fixed part 411 includes a root section 4111 and a first waist section 4112 connected along the length direction X of the exhaust valve plate 41. The movable part 412 includes a second waist section 4121 and a head section 4122 connected along the length direction X of the exhaust valve plate 41. The head section 4122 is disposed opposite to the exhaust port 21. The end of the second waist section 4121 away from the head section 4122 is connected to the first waist section 4112. The second waist section 4121 has a minimum width L3 and is a structure with equal width.

[0041] The equal-width second waist section 4121 avoids stress concentration at abrupt width changes in the variable-width structure, resulting in a longer fatigue life and better reliability for the exhaust valve plate 41 during repeated opening and closing. Furthermore, the equal-width structure allows for a smoother stiffness change in the exhaust valve plate 41 during opening and closing, preventing nonlinear vibrations that might be caused by the variable-width structure. This reduces high-frequency harmonic components generated when the exhaust valve plate 41 collides with the lift limit plate 42, further reducing exhaust noise.

[0042] More preferably, the minimum width of the second waist segment 4121 is equal to the width of the first waist segment 4112.

[0043] Preferably, 0.033≤L2≤0.038. By limiting the length of the movable part 412, L2 (m), to the range of 0.033m to 0.038m (i.e. 33mm to 38mm), and combining it with conventional valve plate materials (such as spring steel with a Young's modulus of approximately 210GPa), compressor products with excellent low-noise performance can be manufactured conveniently and reliably.

[0044] L2 is the main deformation area of ​​the valve plate. The larger the L2 value, the better the flexibility of the exhaust valve plate 41, the smaller the driving force required to open, that is, the easier the exhaust valve plate 41 is to open.

[0045] More preferably, 0.04875≤L≤0.059 and 0.0155≤L1≤0.021. L and L1 together determine the length L2 of the movable part 412, which in turn affects the elastic coefficient K of the valve plate. By limiting the total length L (m) of the exhaust valve plate 41 to the range of 0.04875m to 0.059m (i.e., 48.75mm to 59mm) and the length L1 (m) of the fixed part 411 to the range of 0.0155m to 0.021m (i.e., 15.5mm to 21mm), the lengths of the fixed part 411 and the movable part 412 can be well balanced, which helps to conveniently and reliably manufacture compressor products with excellent low-noise performance.

[0046] Preferably, 0.008 ≤ L3 ≤ 0.0103. By limiting the minimum width L3 (m) of the exhaust valve plate 41 to the range of 0.008m to 0.0103m (i.e. 8mm to 10.3mm), the exhaust valve plate 41 can ensure sufficient bending strength while avoiding difficulty in opening at ultra-low speeds due to excessive stiffness, thereby ensuring that K*t / Vst can fall within the protection range and achieving the noise reduction target.

[0047] L3 determines the stiffness at the root of the exhaust valve plate 41. The larger the L3 value, the higher the bending stiffness of the exhaust valve plate 41, and the greater the driving force required for the exhaust valve plate 41 to open, meaning the valve plate is more difficult to open. An excessively large L3 will cause the valve plate to retain too much force, generating a violent impact at the moment of exhaust, thereby inducing a whistling sound.

[0048] Preferably, 0.000406≤t≤0.000508.

[0049] The thickness of the exhaust valve plate 41 is a sensitive parameter affecting the valve plate stiffness (proportional to t³), and even a small change in t will significantly change the K value. By limiting the range of the thickness t (m) of the exhaust valve plate 41 to 0.000406m to 0.000508m (i.e., 0.406mm to 0.508mm), it is possible to ensure that the exhaust valve plate 41 has sufficient structural strength to withstand high-frequency opening and closing impacts, while also avoiding excessive valve plate holding force due to excessive thickness of the exhaust valve plate 41, which would cause exhaust noise.

[0050] Preferably, 2.0 × 10 11 ≤E≤2.2×10 11 .

[0051] The materials for the exhaust valve plate 41 that conform to the Young's modulus range of the present invention include, but are not limited to, the following types: (1) martensitic stainless steel with a Young's modulus of approximately 1.93 × 10⁻⁶. 11 Pa ~2.0×10 11 Pa (close to the lower limit, requires a thicker size setting); by appropriately increasing the thickness t or reducing the length L2 of the movable part 412, K can fall within the scope of this invention. (2) Precipitation hardening stainless steel, Young's modulus approximately 1.95×10¹¹ Pa~2.05×10¹¹ Pa. (3) High-performance spring steel, Young's modulus approximately 2.05×10¹¹ Pa~2.1×10¹¹ Pa. (4) Special alloys (such as nickel-based alloys, titanium alloys), Young's modulus approximately 2.0×10¹¹ Pa (titanium alloys approximately 1.1×10¹¹ Pa, which needs to be selected according to the specific grade).

[0052] Preferably, the refrigerant is one of R290, R32 or R410A.

[0053] To verify the technical effect of the present invention, the inventors conducted multiple sets of experiments using compressors with different displacements and different exhaust valve plate parameters 41. The experiments employed standard noise testing methods, measuring the exhaust noise of the compressors operating at ultra-low speeds (4-8 rpm) in an anechoic chamber environment. The parameters and test results are as follows: Figures 7 to 8 , and as shown in Tables 1 to 4 below.

[0054] This application provides four embodiments and four comparative examples. The unit of Vst in Table 1 below is m. 3 The unit of n is rps, the unit of d is m, and the unit of E is pa. The specific data of Vst, n, and E for the four embodiments and four comparative examples are shown in Table 1 below:

[0055] Table 1 It should be noted that the material of the exhaust valve plate 41 in Table 1 is spring steel with a material modulus of 210 GPa (i.e., 2.1 × 10¹¹ Pa).

[0056] It should be noted that Comparative Examples 1 and 2 are the specific data of the 40cc compressor before improvement at 4 rpm and 8 rpm, respectively; Examples 1 and 2 are the specific data of the improved 40cc compressor at 4 rpm and 8 rpm, respectively; Comparative Examples 3 and 4 are the specific data of the 65cc compressor before improvement at 4 rpm and 8 rpm, respectively; Examples 3 and 4 are the specific data of the improved 65cc compressor at 4 rpm and 8 rpm, respectively.

[0057] This application provides specific data for exhaust valve plates 41 in four embodiments and four comparative examples. In Table 2 below, the units of L, t, L1, L2, and L3 are m. The specific data of L, t, L1, L2, and L3 for the exhaust valve plates 41 in the four embodiments and four comparative examples are shown in Table 2 below:

[0058] Table 2 This application provides four embodiments and four comparative examples. In Table 3 below, the unit of K is N / m, the unit of t is m, and the unit of Vst is m. 3 The specific data of K, t, Vst, and K*t / Vst obtained and calculated based on the specific data in Tables 1 and 2 are shown in Table 3 below:

[0059] Table 3 Noise tests were conducted on the four embodiments and four comparative examples, and the specific test results are shown in Table 4 below:

[0060] Table 4 It should be noted that the noise superimposed sound pressure level in Table 4 is a superimposed value. Specifically, if the noise sound pressure level at a noise frequency of 50 Hz is AdB, the noise sound pressure level at a noise frequency of 100 Hz is CdB, the noise sound pressure level at a noise frequency of 200 Hz is EdB, and the noise sound pressure level at a noise frequency of 2000 Hz is HdB, then the noise superimposed sound pressure level in Table 4 from 50 to 2000 Hz is defined as S.

[0061] Then S = 10 * log 10 (10 A / 10 +10 C / 10 +10 E / 10 +...10H / 10 ).

[0062] According to the data in Tables 1 and 2, Comparative Example 1 and Example 1 are identical in all parameters except for the thickness t of the exhaust valve plate 41. According to Tables 3 and 4, Comparative Example 1 does not meet the 7*10... 3 <K*t / Vst<1.1*10 4 The conditions are met, and Example 1 satisfies 7*10. 3 <K*t / Vst<1.1*10 4 The conditions were as follows: when the compressor displacement was 40cc and the speed was 4rpm, the noise superimposed sound pressure level of Example 1 was significantly lower than that of Comparative Example 1; according to the data in Tables 1 and 2, Comparative Example 2 and Example 2 were identical except for the thickness t of the exhaust valve plate 41; according to Tables 3 and 4, Comparative Example 2 did not meet the 7*10 condition. 3 <K*t / Vst<1.1*10 4 The conditions are met, while Example 2 satisfies 7*10. 3 <K*t / Vst<1.1*10 4 Under the following conditions: when the compressor displacement is 40cc and the speed is 8rpm, the noise superposition sound pressure level of Example 2 is significantly lower than that of Comparative Example 2.

[0063] According to the data in Tables 1 and 2, Comparative Example 3 and Example 3 are identical except for the thickness t of the exhaust valve plate 41. According to Tables 3 and 4, Comparative Example 3 does not meet the 7*10... 3 <K*t / Vst<1.1*10 4 The conditions are met, and Example 3 satisfies 7*10. 3 <K*t / Vst<1.1*10 4 The conditions were as follows: when the compressor displacement was 65cc and the speed was 4rpm, the noise superimposed sound pressure level of Example 3 was significantly lower than that of Comparative Example 3; according to the data in Tables 1 and 2, Comparative Example 4 and Example 4 were identical except for the thickness t of the exhaust valve plate 41. According to Tables 3 and 4, Comparative Example 4 did not meet the 7*10 condition. 3 <K*t / Vst<1.1*10 4 The conditions are met, and Example 4 satisfies 7*10. 3 <K*t / Vst<1.1*10 4 Under the following conditions: when the compressor displacement is 65cc and the speed is 8rpm, the noise superimposed sound pressure level of Example 2 is significantly lower than that of Comparative Example 2.

[0064] It should be noted that, Figure 7The graph shows a comparison of 1 / 3 OCT curves between the 40cc compressor improved using the technical solution of this invention and the 40cc compressor before improvement without the technical solution of this invention at a speed of 4 rpm. Figure 8 The graph shows a comparison of 1 / 3 OCT at 8 rpm between a 40cc compressor improved using the technical solution of this invention and a 40cc compressor before improvement using the technical solution of this invention. Figure 7 and Figure 8 As shown, the horizontal axis represents sound frequency (Hz), and the vertical axis represents sound pressure level (dB). The blue curve ("Before Improvement") represents a comparative example without the technical solution of this application. Figure 7 The blue curve in the figure represents the sound pressure level curve for Example 1 in the range of 50Hz to 2000Hz. Figure 8 The blue curve in the figure represents the sound pressure level curve of Example 2 from 50Hz to 2000Hz; the red curve (“Improved”) represents an embodiment using the technical solution of this application, wherein... Figure 7 The red curve in the figure represents the sound pressure level curve of Example 1 from 50Hz to 2000Hz. Figure 8 The red curve in the image represents the sound pressure level curve for Example 2 from 50Hz to 2000Hz. Figure 7 and Figure 8 It can be clearly seen that in the low-frequency range of 50–2000 Hz, which is sensitive to human hearing, the noise level of the compressor using the technical solution of this invention (after improvement) is lower than that of the existing compressor (before improvement), with a reduction of approximately 2–6 dB. The noise in this frequency range mainly originates from the opening impact of the exhaust valve plate 41 at ultra-low speeds. The compressor provided by this invention can suppress the energy in this frequency range, helping to reduce exhaust whistling. This application uses 7*10 3 <K*t / Vst<1.1*10 4 Within the preferred scope of the present invention, the exhaust noise of the compressor is improved when it operates at ultra-low speed (4-8 rpm), which helps to improve the user's auditory experience in the low-frequency range.

[0065] Furthermore, in the ultra-low speed operating range of 4–10 rpm, within the human ear-sensitive low-frequency range of 0–1000 Hz, the noise level of the compressor in this application is reduced by 2–6 dB compared to existing technologies. This improvement manifests as a reduction in the sound pressure level of exhaust noise, contributing to enhanced auditory comfort for users in the low-frequency range. In the higher speed range of 10–15 rpm, due to the overall optimization of the dynamic characteristics of the exhaust valve plate 41, the noise level of this application is also reduced by 2–6 dB compared to existing technologies over a wider frequency range of 0–2000 Hz.

[0066] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and substitutions can be made without departing from the technical principles of the present invention, and these improvements and substitutions should also be considered within the scope of protection of the present invention.

Claims

1. A compressor characterized by, include: cylinder; The bearing assembly is provided with an exhaust port; The piston is eccentrically rotatable within the cylinder; The cylinder, the bearing assembly, and the piston together form a compression chamber, the volume of which is Vst (m³). An exhaust valve assembly is disposed on the bearing assembly and is used to control the opening and closing of the exhaust port. The exhaust valve assembly includes an exhaust valve plate and a lift limit plate. The exhaust valve plate includes a fixed part and a movable part connected along the length direction of the exhaust valve plate. The fixed part is fitted and fixed to the lift limit plate. The total length of the exhaust valve plate is L (m) and the thickness is t (m). The length of the fixed part is L1 (m) and the length of the movable part is L2 (m), where L2 = L - L1. The minimum width of the movable part is L3 (m). The Young's modulus of the material of the exhaust valve plate is E (pa). The elastic coefficient K (N / m) of the exhaust valve piece, K = (E * L3* t 3 ) / (4 * L2 3 ); Satisfies: 7*10 3 <K*t / Vst < 1.1*10 4 .

2. The compressor of claim 1, wherein The volume of the compression chamber is Vst(m3), satisfying: 4*10 -5 ≤ Vst≤ 6.5*10 -5 .

3. The compressor of claim 1, wherein, The fixed part includes a root section and a first waist section connected along the length direction of the exhaust valve plate. The movable part includes a second waist section and a head section connected along the length direction of the exhaust valve plate. The head section is disposed opposite to the exhaust hole. The end of the second waist section away from the head section is connected to the first waist section. The second waist section has a minimum width L3 and is a structure with equal width.

4. The compressor of claim 1, wherein, The length of the fixed part is L1 (m), and the length of the movable part is L2 (m), satisfying: 0.033≤L2≤0.

038.

5. The compressor of claim 4, wherein, The total length of the exhaust valve plate is L (m), the length of the fixing part is L1 (m), and L2 = L - L1, satisfying: 0.04875 ≤ L ≤ 0.059, 0.0155 ≤ L1 ≤ 0.

021.

6. The compressor of claim 1, wherein, The minimum width of the movable part is L3 (m), which satisfies: 0.008≤L3≤0.0103.

7. The compressor of claim 1, wherein The thickness of the exhaust valve plate is t (m), which satisfies: 4.06*10 -4 ≤t≤5.08*10 -4 .

8. The compressor according to claim 1, characterized in that, The diameter of the exhaust port is d (m), which satisfies: 0.01≤d≤0.

012.

9. The compressor according to claim 1, characterized in that, The Young's modulus of the material of the exhaust valve plate is E (Pa), satisfying: 2.0*10 11 ≤E≤2.2*10 11 .

10. The compressor according to claim 1, characterized in that, The compressor uses one of the following refrigerants: R290, R32, or R410A.

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