Low-noise air valve of micro-piston compressor and optimization design method

Abstract

The present application relates to the field of compressor, in particular to a kind of low-noise air valve of micro piston compressor and optimization design method, comprising the following components: valve plate, its surface is equipped with inlet hole and exhaust hole;Inlet valve, cover on inlet hole, with elasticity and can be relative to the elastic opening and closing action of valve plate;Exhaust valve, cover on exhaust hole, with elasticity and can be relative to the elastic opening and closing action of valve plate;Lift limiter, arranged on the surface of valve plate to limit the maximum opening height of inlet valve and / or exhaust valve.The present application greatly suppresses the generation of noise.

Description

Technical Field

[0001] This invention relates to the field of compressors, specifically to a low-noise valve for a miniature piston compressor and its optimized design method. Background Technology

[0002] An oil-free piston compressor is a type of fluid machinery that elevates a low-pressure medium to a high-pressure medium. It draws in a low-temperature, low-pressure medium through an intake pipe, and the rotation of the motor drives the piston-connecting rod mechanism, converting the rotational motion of the motor into the reciprocating motion of the piston. The piston compresses the low-pressure medium into a high-temperature, high-pressure medium within the cylinder, and the compressed medium provides power to the downstream gas system.

[0003] In recent years, with the increasing demands for environmental protection and comfort, stricter requirements have been placed on noise suppression and emission standards for oil-free compressors. Research on noise reduction technologies for the entire oil-free compressor and its key components, and the development of high-performance, low-noise oil-free compressors, is an urgent need in the compressor industry both domestically and internationally. For newly designed and developed miniature oil-free piston compressors, a significant amount of noise is generated at the valves during operation. Controlling the generation and suppressing the propagation of valve noise has a significant effect on improving the overall noise level of the compressor. However, how to suppress noise generation at the valves has always been a challenging problem in the industry and urgently needs to be solved. Summary of the Invention

[0004] To avoid and overcome the technical problems existing in the prior art, this invention provides a low-noise valve for a miniature piston compressor, which significantly suppresses noise generation. This invention also provides an optimized design method for the low-noise valve of a miniature piston compressor.

[0005] To achieve the above objectives, the present invention provides the following technical solution:

[0006] A low-noise valve for a miniature piston compressor and its optimized design method, comprising the following components:

[0007] The valve plate has an air inlet and an air outlet on its surface.

[0008] The intake valve plate covers the intake port, is elastic, and can elastically open and close relative to the valve plate.

[0009] The exhaust valve plate covers the exhaust port, is elastic, and can elastically open and close relative to the valve plate;

[0010] A lift limiter is arranged on the valve plate surface to limit the maximum opening height of the intake valve plate and / or exhaust valve plate.

[0011] As a further aspect of the present invention: the total area A of the air inlet or exhaust port v The range is:

[0012]

[0013] Among them, C m This refers to the piston speed of the compressor.

[0014] F p The piston area;

[0015] M max The maximum Mach number of the airflow passing through the intake or exhaust port;

[0016] M min The minimum Mach number for airflow through the intake or exhaust port;

[0017] a v For flow coefficient;

[0018] K is the adiabatic index;

[0019] T is the thermodynamic temperature of the gas in the valve gap;

[0020] R is the gas constant.

[0021] As a further aspect of the present invention: the Mach number M of the airflow through the air inlet or exhaust port is:

[0022]

[0023] Where C0 is the speed of sound of the airflow at the air intake or exhaust port;

[0024] C1 is the average velocity of the airflow passing through the air inlet or exhaust port;

[0025]

[0026] λ is the ratio of the compressor's crank radius to its connecting rod length;

[0027] θ is the crank angle;

[0028] r is the crank radius;

[0029] ω is the angular velocity of the compressor.

[0030] As a further aspect of the present invention: both the air inlet and the exhaust outlet are oblong-shaped holes, and the total area A of the air inlet or the exhaust outlet is... v for:

[0031]

[0032] Where n is the number of waist-shaped holes;

[0033] d i Let be the width of the i-th oblong hole;

[0034] li Let be the length of the rectangular cross-section of the i-th waist-shaped hole;

[0035] h i Let be the valve plate lift height at the i-th waist-shaped hole.

[0036] As a further aspect of the present invention: the thickness t of the intake valve plate or exhaust valve plate is:

[0037]

[0038] Where L is the length of the valve plate;

[0039] K0 is the stiffness coefficient per unit width of the valve plate;

[0040] E is the elastic modulus of the valve plate material;

[0041] β is the thrust coefficient of the valve plate.

[0042] As a further aspect of the present invention: the lift range h of the intake valve plate or exhaust valve plate e for:

[0043]

[0044] Among them, V e The equivalent impact velocity of the intake or exhaust valve plate;

[0045] δ represents the compressor speed.

[0046] As a further aspect of the present invention: the stiffness coefficient K0 per unit width of the valve plate is:

[0047]

[0048] Where μ is the elastic force ratio of the valve plate;

[0049] F gmax The maximum gas thrust of the intake or exhaust valve plate:

[0050]

[0051] p represents the intake or exhaust pressure;

[0052] The frontal area A of the air intake or exhaust port p for:

[0053]

[0054] As a further embodiment of the present invention: the lift limiter is fixed on the valve plate and there is a V-shaped opening and closing area between the valve plate and the exhaust valve plate is arranged in the V-shaped opening and closing area and matches the size and position of the lift limiter.

[0055] An optimized design method for a low-noise valve in a miniature piston compressor, characterized by the following steps:

[0056] S1. Confirm the basic parameters of the compressor and preliminarily calculate the main structural parameters of the valve;

[0057] S2. Conduct tests and optimization simulations on the air valve;

[0058] S3. Select the optimal structural parameters based on experimental and optimized simulation data;

[0059] S4. Conduct noise tests to verify the optimal structural parameters and finally determine the specific parameter values.

[0060] As a further aspect of the present invention: S21, conduct a noise orthogonal test on the air valve, and determine the key air valve structural parameters that affect the noise collected by the element through range and variance analysis;

[0061] S22. Conduct pressure pulsation tests on the air valve at different Mach numbers during the intake and exhaust processes, analyze the pressure pulsation intensity, and determine the key air valve structural parameters that affect the pressure pulsation intensity during the intake and exhaust processes.

[0062] S23. Conduct compressor noise impact tests on the air valve at different Mach numbers, analyze the time and frequency domains of the noise signal, and determine the influence of the air valve structural parameters on the compressor frequency domain characteristics.

[0063] S24. Perform vector simulations of speed, pressure, and temperature during the operation of the air valve, as well as simulations of the air valve lift height, valve plate deformation, and stress variation with crank angle.

[0064] Compared with the prior art, the beneficial effects of the present invention are:

[0065] 1. This invention selects the Mach number of the airflow in the valve gap, the equivalent impact velocity of the valve plate, and the stiffness coefficient of the valve plate in the reed valve of a miniature reciprocating piston compressor based on empirical data. Combined with the geometric shape of the reed valve, it reverse designs specific geometric parameters such as the thickness of the valve plate, the area of ​​the valve orifice, and the lift height of the intake and exhaust valves. This reduces the number of iterations in the valve design process and significantly suppresses the generation of valve noise.

[0066] 2. This invention uses the main structural parameters of the valve as the test factors, the structural size range corresponding to each structural parameter as the test level, and the overall noise of the compressor as the result judgment condition. It designs an orthogonal test on the influence of the main structural parameters of the valve on the compressor noise, performs range analysis on the test results, analyzes the key excitation structural parameters that affect the compressor noise, and optimizes the combination of valve structural parameters that minimizes the overall noise of the compressor. Thus, the overall noise of the compressor is improved by matching the optimal valve geometric structural parameters.

[0067] 3. This invention reduces pressure pulsations in the valve gap and on both sides of the valve during intake and exhaust by changing the valve orifice area and valve plate lift height. Based on optimized valve geometry parameters, pressure signals from the intake, exhaust, and compression chambers are collected to calculate and analyze the intensity of pressure pulsations during intake and exhaust. By combining theoretical calculation parameters with pressure pulsations, the effective flow area of ​​the valve gap is increased, and the gas velocity and Mach number at the valve gap are reduced, thus stabilizing the airflow pressure changes in the compressor during intake and exhaust, thereby reducing the generation and radiation of airflow pulsation noise at the valve.

[0068] 4. This invention, through a combination of theoretical calculations and experiments, can reduce the design error of geometric structural parameters caused by empirical parameters in the design process of air valves; reduce the mechanical noise of the valve plate striking the valve plate and the limiter by changing the valve plate stiffness and lift height; increase the effective geometric channel area of ​​the valve gap by changing the valve orifice channel and lift height, thereby reducing the generation of air valve pneumatic pressure pulsation and noise; and comprehensively solve the problem of geometric structural parameter optimization caused by the mutual interference and superposition of air valve mechanical noise and pneumatic noise. Attached Figure Description

[0069] Figure 1 This is a schematic diagram of the structure of the present invention.

[0070] Figure 2 This is a schematic diagram of the structure of the intake valve plate after installation in this invention.

[0071] Figure 3 This is a schematic diagram of the valve plate in this invention.

[0072] Figure 4 This is a schematic diagram of the structure of the exhaust valve plate in this invention.

[0073] Figure 5 This is a graph showing the results of the five-point method test for the average sound pressure level of the compressor at various points on the surface.

[0074] In the picture:

[0075] 1. Valve plate; 11. Air inlet; 12. Air outlet;

[0076] 2. Intake valve plate; 21. Through hole; 3. Exhaust valve plate; 4. Lift limiter. Detailed Implementation

[0077] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0078] Please see Figures 1-5 In this embodiment of the invention, a low-noise valve for a micro piston compressor and an optimized design method are provided. The valve includes a valve plate 1, and an air inlet 11 and an exhaust 12 are provided on the surface of the valve disc 1. The air inlet 11 and the exhaust 12 are preferably oblong holes.

[0079] The air intake 11 is preferably arranged in five groups, which are arranged in parallel to each other and in a V-shape.

[0080] An intake valve plate 2 is fixed to the front of the valve plate 1. The intake valve plate 2 is elastic and can completely cover each intake hole 11. The intake valve plate 2 can elastically open and close relative to the valve plate 1, lifting or closing on the surface of the valve plate 1.

[0081] The intake valve plate 2 has a through hole 21, which is arranged between each intake hole 11 and offset from the position of the intake hole 11. When the intake valve plate 2 is opened, the gas at the intake hole 11 can be discharged through the through hole 21, and can also be discharged outward through the gap between the intake valve plate 2 and the valve plate 1.

[0082] The exhaust holes 12 are preferably arranged in four groups, in a parallel distribution of two rows and two columns.

[0083] The exhaust valve plate 3 is arranged on the reverse side of the valve plate 1 and is in the shape of an I-beam. The positions of the exhaust holes 12 at its four extended ends correspond so that each exhaust hole 12 can be completely covered.

[0084] When the airflow direction is from the back of the valve plate 1 to the front, it is the intake process. At this time, the exhaust valve plate 3 covers and seals each exhaust hole 12, and the intake valve plate 2 is lifted by the airflow, so that the airflow can be discharged through the intake hole 11.

[0085] When the airflow direction is from the front to the back of the valve plate 1, it is the exhaust process. At this time, the intake valve plate 2 covers and seals each intake hole 11, and the exhaust valve plate 3 is lifted by the airflow, so that the airflow can be discharged through the exhaust hole 12.

[0086] To limit the maximum lift height of the intake valve plate 2 or the exhaust valve plate 3, a lift limiter 4 can be provided on the valve plate 1. In this invention, the lift limiter 4 is only provided on the exhaust valve plate 3. The lift limiter 4 has the same structure and position as the exhaust valve plate 3, and the lift limiter 4 is pre-set with a certain tilt height so that the exhaust valve plate 3 abuts against the lift limiter 4 after reaching the predetermined lift, thereby achieving the limiting effect.

[0087] In this invention, the compressor speed is below 1500 rpm, and the lift range h of the intake valve plate 2 or the exhaust valve plate 3 is... e for:

[0088]

[0089] Among them, V e The equivalent impact velocity of the intake valve plate 2 or the exhaust valve plate 3;

[0090] δ represents the compressor speed.

[0091] h e ≤2.6mm.

[0092] The stiffness coefficient K0 per unit width of the valve plate is:

[0093]

[0094] Where μ is the elastic force ratio of the valve plate; the elastic force ratio of the intake valve plate is μ _1 The preferred numerical range is 0.06-0.14, and the ratio of the elastic force of the exhaust valve plate is μ. _2 The preferred value range is 0.04-0.1.

[0095] The range of stiffness coefficient per unit width of intake valve plate 2 is:

[0096] 34.85≤K 0_1 ≤81.31

[0097] The range of the stiffness coefficient per unit width of the exhaust valve plate is:

[0098] 69.84≤K 0_2 ≤174.59.

[0099] F gmax For the maximum gas thrust of intake valve plate 2 or exhaust valve plate:

[0100]

[0101] p represents the intake or exhaust pressure;

[0102] The frontal area A of the air intake 11 or the exhaust 12 p for:

[0103]

[0104] With a valve thrust coefficient β of 0.88 and an intake channel frontal area of ​​0.00034 m², 2 The windward area of ​​the exhaust channel is 0.00022m². 2The intake pressure is 1 bar, the exhaust pressure is 4 bar, the intake Mach number is 0.15, and the exhaust Mach number is 0.28.

[0105] Maximum gas thrust F of intake valve plate gmax_1 The maximum gas thrust F of the exhaust valve plate is 1.16 N. gmax_2 It is 2.62N.

[0106] The thickness t of either the intake valve plate 2 or the exhaust valve plate 3 is:

[0107]

[0108] Where L is the length of the valve plate;

[0109] E is the elastic modulus of the valve plate material;

[0110] β is the thrust coefficient of the valve plate.

[0111] The calculated thickness t1 range for the intake valve plate is:

[0112] 0.35mm≤t1≤0.54mm;

[0113] The calculated thickness t2 range for the intake valve plate is:

[0114] 0.3mm≤t2≤0.48mm.

[0115] The compression medium of this invention is air, with an adiabatic index K of approximately 1.4, and the average Mach number of the airflow through valve plate 1 is between 0.15 and 0.3.

[0116] The total area A of the air intake port 11 or the exhaust port 12 v The range is:

[0117]

[0118] Among them, C m This refers to the piston speed of the compressor.

[0119] F p The piston area;

[0120] M max The maximum Mach number of the airflow through the intake port 11 or the exhaust port 12;

[0121] M min The minimum Mach number for airflow through the intake port 11 or the exhaust port 12;

[0122] a v For flow coefficient;

[0123] K is the adiabatic index;

[0124] T is the thermodynamic temperature of the gas in the valve gap;

[0125] R is the gas constant.

[0126] The gas constant R is 287.2 J / (kg·K), the piston diameter is 80 mm, the flow coefficient is 0.65, and the piston velocity C... m It is 2.68 m / s;

[0127] When the intake temperature is 30℃, the intake area A of the intake port 11 is... v_1 The range is:

[0128]

[0129] When the exhaust temperature is 150℃, the exhaust area A of exhaust port 12 is... v_2 The range is:

[0130]

[0131] 197mm 2 ≤A v_1 ≤394mm 2 ;

[0132] 167mm 2 ≤A v_2 ≤243mm 2 .

[0133] The Mach number M of the airflow through the intake port 11 or the exhaust port 12 is:

[0134]

[0135] Wherein, C0 is the speed of sound of the airflow at the air intake 11 or the exhaust 12;

[0136] C1 is the average velocity of the airflow through the air inlet 11 or the air outlet 12;

[0137]

[0138] λ is the ratio of the compressor's crank radius to its connecting rod length;

[0139] θ is the crank angle;

[0140] r is the crank radius;

[0141] ω is the angular velocity of the compressor.

[0142] A was calculated v After the range is extended, since both the air intake 11 and the exhaust 12 are oblong-shaped holes,

[0143] but

[0144] Where n is the number of waist-shaped holes;

[0145] d i Let be the width of the i-th oblong hole;

[0146] l i Let be the length of the rectangular cross-section of the i-th waist-shaped hole;

[0147] h i Let be the valve plate lift height at the i-th waist-shaped hole.

[0148] The optimization design method for gas conversion valves includes the following steps:

[0149] S1. Confirm the basic parameters of the compressor and preliminarily calculate the main structural parameters of the valve;

[0150] The basic parameters of a compressor include speed δ, cylinder bore, stroke, intake and exhaust pressure p, intake temperature, and crankshaft-connecting rod ratio λ. The main structural parameters of the valves include the thickness of the intake and exhaust valve plates, the flow area, and the lift height h.

[0151] S2. Conduct tests and optimization simulations on the air valve;

[0152] S21. Conduct an orthogonal noise test on the air valve and determine the key air valve structural parameters that affect the noise collected by the element through range and variance analysis.

[0153] S22. Conduct pressure pulsation tests on the air valve at different Mach numbers during the intake and exhaust processes, analyze the pressure pulsation intensity, and determine the key air valve structural parameters that affect the pressure pulsation intensity during the intake and exhaust processes.

[0154] S23. Conduct compressor noise impact tests on the air valve at different Mach numbers, analyze the time and frequency domains of the noise signal, and determine the influence of the air valve structural parameters on the compressor frequency domain characteristics.

[0155] S24. Perform vector simulations of speed, pressure, and temperature during the operation of the air valve, as well as simulations of the air valve lift height, valve plate deformation, and stress variation with crank angle.

[0156] S3. Select the optimal structural parameters based on experimental and optimized simulation data;

[0157] S4. Conduct noise tests to verify the optimal structural parameters and finally determine the specific parameter values.

[0158] The final determined parameter values ​​include the thickness of the valve plate, the channel area of ​​the valve orifice, and the lift height of the valve plate.

[0159] like Figure 5As shown, without the air valve installed, the entire compressor system can be considered to have no gas flow. At this time, the noise mainly consists of compressor mechanical noise, motor electromagnetic noise, and fan noise. The weighted sound pressure level of body A without the air valve is 75.71 dB(A). After installing the air valve, the increase in compressor system airflow noise and compressor mechanical noise caused by the load (discharge pressure) together lead to an increase in the overall compressor noise. It can be seen that compared to the original air valve, using the air valve of this invention reduces the overall compressor noise by 2.36 dB(A).

[0160] The formula for calculating the increase in the sound pressure level (Lps) of the compressor's overall noise caused by the installation of air valves is as follows:

[0161]

[0162] Where: L p1 The sound pressure level after installing the air valve; L p0 This represents the sound pressure level without the air valve installed.

[0163] The sound pressure level increment of the installed air valve calculated based on the above formula is shown in the table below:

[0164]

[0165] As shown in the table above, the A-weighted sound pressure level increases by 75.28 dB(A) and 65.99 dB(A) after installing the air valve and the preferred air valve of the present invention, respectively. This increase is the sum of the increases in aerodynamic and mechanical noise of the compressor caused by the air valve. The noise increase of the preferred air valve of the present invention is reduced by 9.29 dB(A) compared with the original air valve, effectively controlling the aerodynamic and mechanical noise of the compressor.

[0166] The basic principles of this application have been described above with reference to specific embodiments. However, it should be noted that the advantages, benefits, and effects mentioned in this application are merely examples and not limitations, and should not be considered as essential features of each embodiment of this application. Furthermore, the specific details disclosed above are for illustrative and facilitative purposes only, and are not limitations. These details do not limit the application to the necessity of employing the aforementioned specific details for implementation.

[0167] The block diagrams of devices, apparatuses, devices, and systems involved in this application are merely illustrative examples and are not intended to require or imply that they must be connected, arranged, or configured in the manner shown in the block diagrams. As those skilled in the art will recognize, these devices, apparatuses, devices, and systems can be connected, arranged, and configured in any manner. Words such as “comprising,” “including,” “having,” etc., are open-ended terms meaning “including but not limited to,” and are used interchangeably with them. The terms “or” and “and” as used herein refer to the terms “and / or,” and are used interchangeably with them unless the context clearly indicates otherwise. The term “such as” as used herein refers to the phrase “such as but not limited to,” and is used interchangeably with it.

[0168] It should also be noted that in the apparatus, equipment, and methods of this application, the components or steps can be disassembled and / or recombined. These disassemblies and / or recombinations should be considered as equivalent solutions of this application.

[0169] The above description of the disclosed aspects is provided to enable any person skilled in the art to make or use this application. Various modifications to these aspects will be readily apparent to those skilled in the art, and the general principles defined herein can be applied to other aspects without departing from the scope of this application. Therefore, this application is not intended to be limited to the aspects shown herein, but rather to be accorded the widest scope consistent with the principles and novel features disclosed herein.

[0170] The above description has been given for purposes of illustration and description. Furthermore, this description is not intended to limit the embodiments of this application to the forms disclosed herein. Although numerous exemplary aspects and embodiments have been discussed above, those skilled in the art will recognize certain variations, modifications, alterations, additions, and sub-combinations thereof.

Claims

1. An optimized design method for a low-noise valve of a miniature piston compressor, characterized in that, Includes the following steps: S1. Confirm the basic parameters of the compressor and preliminarily calculate the main structural parameters of the valve; The air valve includes the following components: The valve plate (1) has an air inlet (11) and an exhaust (12) on its surface. The intake valve plate (2) covers the intake hole (11), is elastic and can elastically open and close relative to the valve plate (1); The exhaust valve plate (3) covers the exhaust hole (12), is elastic and can elastically open and close relative to the valve plate (1); A lift limiter (4) is arranged on the surface of the valve plate (1) to limit the maximum opening height of the intake valve plate (2) and / or the exhaust valve plate (3); S2. Conduct tests and optimization simulations on the air valve; S21. Conduct an orthogonal noise test on the air valve and determine the key air valve structural parameters that affect the compressor noise through range and variance analysis. S22. Conduct pressure pulsation tests on the air valve at different Mach numbers during the intake and exhaust processes, analyze the pressure pulsation intensity, and determine the key air valve structural parameters that affect the pressure pulsation intensity during the intake and exhaust processes. S23. Conduct compressor noise impact tests on the air valve at different Mach numbers, analyze the time and frequency domains of the noise signal, and determine the influence of the air valve structural parameters on the compressor frequency domain characteristics. S24. Perform vector simulation of speed, pressure, and temperature during the operation of the air valve, as well as simulation of the air valve lift height, valve plate deformation, and stress variation with crank angle. S3. Select the optimal structural parameters based on experimental and optimized simulation data; S4. Conduct noise tests to verify the optimal structural parameters and finally determine the specific parameter values.

2. The optimized design method for a low-noise valve of a micro piston compressor according to claim 1, characterized in that, The total area of ​​the air inlet (11) or air outlet (12) A v The range is: in, This refers to the piston speed of the compressor. F p The piston area; M max The maximum Mach number of the airflow through the intake port (11) or exhaust port (12); M min The minimum Mach number of the airflow through the inlet (11) or outlet (12); For flow coefficient; K The adiabatic index; T The valve gap gas thermodynamic temperature; R is the gas constant.

3. The optimized design method for a low-noise valve of a micro piston compressor according to claim 2, characterized in that, The Mach number M of the airflow through the inlet (11) or outlet (12) is: in, The speed of sound of the airflow at the air inlet (11) or the exhaust port (12); The average velocity of the airflow passing through the air inlet (11) or the air outlet (12); This is the ratio of the compressor's crank radius to its connecting rod length. The crank angle; The crank radius; ω The compressor's angular velocity; A v The total area of ​​the vent hole (12) is denoted as .

4. The optimized design method for a low-noise valve of a micro piston compressor according to claim 3, characterized in that, Both the air inlet (11) and the exhaust outlet (12) are oblong holes, and the total area of ​​the air inlet (11) or the exhaust outlet (12) is... A v for: Where n is the number of waist-shaped holes; For the first i The width of the slotted hole; For the first i The length of the rectangular cross-section of the slotted hole; For the first i Valve plate lift height at the waist-shaped orifice.

5. The optimized design method for a low-noise valve of a micro piston compressor according to claim 4, characterized in that, The thickness of the intake valve plate (2) or exhaust valve plate (3) t for: in, L The length of the valve plate; K 0 This is the stiffness coefficient per unit width of the valve plate; E The elastic modulus of the valve plate material; This refers to the width of the valve plate.

6. The optimized design method for a low-noise valve of a micro piston compressor according to claim 5, characterized in that, Lift range of intake valve plate (2) or exhaust valve plate (3) h e for: in, The equivalent impact velocity of the intake valve plate (2) or the exhaust valve plate (3); δ This refers to the compressor speed.

7. The optimized design method for a low-noise valve of a micro piston compressor according to claim 6, characterized in that, Stiffness coefficient per unit width of valve plate K 0 for: in, μ This represents the ratio of the elastic force of the valve plate. F gmax For the maximum gas thrust of the intake valve plate (2) or the exhaust valve plate (3): P This refers to the intake or exhaust pressure. This represents the thrust coefficient of the valve plate. The windward area of ​​the air inlet (11) or exhaust (12) for: 。 8. The optimized design method for a low-noise valve of a micro piston compressor according to claim 1, characterized in that, The lift limiter (4) is fixed on the valve plate (1) and there is a V-shaped opening and closing area between it and the valve plate (1). The exhaust valve plate (3) is arranged in the V-shaped opening and closing area and matches the size and position of the lift limiter (4).

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