Vibration adjustment method, device, medium, controller and product for scroll compressor

Abstract

The application provides a kind of vibration adjusting method, device, medium, controller and product of scroll compressor, crankshaft of the scroll compressor is respectively provided with first counterweight and second counterweight;The first counterweight and second counterweight can be axially moved along the crankshaft;Method includes: obtaining the noise vibration data of the scroll compressor, and according to the noise vibration data, it is judged whether the scroll compressor appears abnormal noise vibration;If it is judged that the scroll compressor appears abnormal noise vibration, then according to the internal parameters and stress data of the scroll compressor, the position of the first counterweight and / or second counterweight is determined;The position of the first counterweight and / or second counterweight is adjusted, so that the first counterweight and / or second counterweight moves to the determined position.The scheme provided by the application can determine the position of the counterweight that the current scroll compressor satisfies dynamic balance state, and automatically adjusts, real-time optimization dynamic balance.

Description

Technical Field

[0001] This invention relates to the field of control, and more particularly to a vibration regulation method, apparatus, medium, controller, and product for a scroll compressor, specifically to a vibration regulation method, apparatus, storage medium, controller, and computer program product for a scroll compressor. Background Technology

[0002] Noise and vibration problems in scroll compressors typically manifest at the first and integer harmonics of the crankshaft frequency, one of the main causes being the dynamic balance issue of the shaft system. Related technologies usually do not consider the influence of gas forces during dynamic balancing design, instead designing balance blocks solely by balancing eccentric forces and moments.

[0003] However, during the actual operation of a scroll compressor, it is inevitably affected by tangential and radial gas forces, which are often constantly changing. This makes it difficult to avoid mechanical imbalances during actual operation of the scroll compressor, even with dynamic balancing design. Once the frequency of the imbalance approaches the modal frequency of the scroll compressor components, resonance may occur, leading to more serious noise and vibration problems. Summary of the Invention

[0004] The main objective of this invention is to overcome the deficiencies of the aforementioned related technologies and provide a vibration adjustment method, device, storage medium, controller, and computer program product for a scroll compressor, so as to solve the problem that even when a balance block is used, it is difficult to ensure dynamic balance in the operation of a scroll compressor in the related technologies.

[0005] This invention provides a vibration adjustment method for a scroll compressor, comprising: a first balance block and a second balance block are respectively provided at both ends of the crankshaft of the scroll compressor; the first balance block is disposed at one end near the main bearing of the scroll compressor, and the second balance block is disposed at one end near the auxiliary bearing of the scroll compressor; the first balance block and the second balance block are axially movable along the crankshaft; the vibration adjustment method comprises: acquiring noise vibration data of the scroll compressor, and determining whether the scroll compressor has abnormal noise vibration based on the noise vibration data; if it is determined that the scroll compressor has abnormal noise vibration, determining the position of the first balance block and / or the second balance block based on the internal parameters and force data of the scroll compressor; adjusting the position of the first balance block and / or the second balance block to move the first balance block and / or the second balance block to the determined position.

[0006] Optionally, the internal parameters of the scroll compressor include: main shaft rotation angle, crankshaft angular velocity, cross-slip ring inner diameter, cross-slip ring mass, the mass of the second balance block, and the eccentricity of the second balance block; the internal force data of the scroll compressor includes: the tangential gas force on the moving disk of the scroll compressor and the centrifugal inertial force generated by the crankshaft eccentricity; determining the position of the first balance block and / or the second balance block based on the internal parameters and force data of the scroll compressor includes: acquiring the tangential gas force on the moving disk of the scroll compressor, the centrifugal inertial force generated by the crankshaft eccentricity, the main shaft rotation angle, the crankshaft angular velocity, the cross-slip ring inner diameter, and the centrifugal inertial force generated by the crankshaft eccentricity. The mass of the cross-slip ring, the mass of the second balance block, and the eccentricity of the second balance block are used to calculate the position of the first balance block and / or the position of the second balance block based on the tangential gas force on the moving disk, the centrifugal inertial force generated by the crankshaft eccentricity, the main shaft rotation angle, the crankshaft angular velocity, the inner diameter of the cross-slip ring, the mass of the cross-slip ring, the mass of the second balance block, and the eccentricity of the second balance block. The position of the first balance block includes the axial distance between the first balance block and the center of mass of the crankshaft eccentricity. The position of the second balance block includes the axial distance between the second balance block and the center of mass of the crankshaft eccentricity.

[0007] Optionally, the first and second balance blocks are provided with adjustment devices to adjust the positions of the first and / or second balance blocks so that the first and / or second balance blocks move to a predetermined position, including: adjusting the positions of the first and / or second balance blocks through the adjustment devices so that the first and / or second balance blocks move to a predetermined position.

[0008] Optionally, the adjusting device includes an electromagnet and a spring.

[0009] Another aspect of the present invention provides a vibration adjustment device for a scroll compressor, comprising: a first balance block and a second balance block respectively disposed at both ends of the crankshaft of the scroll compressor; the first balance block is disposed at one end near the main bearing of the scroll compressor, and the second balance block is disposed at one end near the auxiliary bearing of the scroll compressor, the first balance block and the second balance block being axially movable along the crankshaft; the vibration adjustment device comprises: a judgment unit, configured to acquire noise vibration data of the scroll compressor and determine whether the scroll compressor exhibits abnormal noise vibration based on the noise vibration data; a determination unit, configured to determine the positions of the first balance block and the second balance block based on the internal parameters and force data of the scroll compressor if the judgment unit determines that the scroll compressor exhibits abnormal noise vibration; and an adjustment unit, configured to adjust the positions of the first balance block and / or the second balance block to move the first balance block and / or the second balance block to the determined positions.

[0010] Optionally, the internal parameters of the scroll compressor include: main shaft rotation angle, crankshaft angular velocity, cross-slip ring inner diameter, cross-slip ring mass, second balance block mass, and eccentricity of the second balance block; the internal force data of the scroll compressor includes: the tangential gas force on the moving disk of the scroll compressor and the centrifugal inertial force generated by the crankshaft eccentricity; the determining unit determines the position of the first balance block and / or the second balance block based on the internal parameters and force data of the scroll compressor, including: acquiring the tangential gas force on the moving disk of the scroll compressor, the centrifugal inertial force generated by the crankshaft eccentricity, the main shaft rotation angle, the crankshaft angular velocity, and the cross-slip ring inner diameter, the cross-slip ring mass, the second balance block mass, and the second balance block eccentricity distance; The inner diameter of the cross-slip ring, the mass of the second balance block, and the eccentricity of the second balance block are used to calculate the position of the first balance block and / or the position of the second balance block based on the tangential gas force on the moving disk, the centrifugal inertial force generated by the crankshaft eccentricity, the main shaft rotation angle, the crankshaft angular velocity, the inner diameter of the cross-slip ring, the mass of the cross-slip ring, the mass of the second balance block, and the eccentricity of the second balance block. The position of the first balance block includes the axial distance between the first balance block and the center of mass of the crankshaft eccentricity. The position of the second balance block includes the axial distance between the second balance block and the center of mass of the crankshaft eccentricity.

[0011] Optionally, the first balance block and / or the second balance block are provided with an adjustment device. Adjusting the position of the first balance block and / or the second balance block to move the first balance block and / or the second balance block to a determined position includes: adjusting the position of the first balance block and / or the second balance block through the adjustment device to move the first balance block and / or the second balance block to a determined position.

[0012] Optionally, the adjusting device includes an electromagnet and a spring.

[0013] In another aspect, the present invention provides a storage medium having a computer program stored thereon, which, when executed by a processor, implements the steps of any of the methods described above.

[0014] In another aspect, the present invention provides a controller including a processor, a memory, and a computer program stored in the memory that can run on the processor, wherein the processor executes the program to implement the steps of any of the methods described above.

[0015] In another aspect, the present invention provides a controller comprising the vibration regulating device for any of the aforementioned scroll compressors.

[0016] In another aspect, the present invention provides a computer program product, including a computer program that, when executed by a processor, implements the steps of any of the methods described above.

[0017] According to the technical solution of the present invention, by real-time monitoring of the noise, vibration and force data of the scroll compressor, and by calculating and analyzing the position and angle of the balance block, the ideal dynamic balance can be approached to the greatest extent, thereby achieving vibration reduction and noise reduction.

[0018] According to the technical solution of the present invention, the position and angle of the balance block should be calculated to achieve the dynamic balance state of the current scroll compressor, and the position of the balance block is automatically or semi-automatically adjusted to optimize the dynamic balance in real time. Attached Figure Description

[0019] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this invention, illustrate exemplary embodiments of the invention and are used to explain the invention, but do not constitute an undue limitation of the invention. In the drawings:

[0020] Figure 1 This is a schematic diagram of an embodiment of the vibration adjustment method for a scroll compressor provided by the present invention;

[0021] Figure 2 The curve showing the relationship between tangential gas force and rotation angle is shown;

[0022] Figure 3a A schematic diagram of the radial force on the moving disk is shown;

[0023] Figure 3b A schematic diagram of the tangential forces acting on the moving disk is shown.

[0024] Figure 3c A top view showing the forces acting on the moving disk is shown;

[0025] Figure 4 A schematic diagram of the forces acting on the cross-shaped slip ring is shown.

[0026] Figure 5a A schematic diagram of the radial forces acting on the crankshaft is shown.

[0027] Figure 5b A schematic diagram of the tangential forces acting on the crankshaft is shown.

[0028] Figure 6 A schematic diagram showing the deflection angles of the first and second balance blocks relative to the crankshaft eccentricity is shown.

[0029] Figure 7 This is a structural block diagram of an embodiment of the vibration adjustment device for a scroll compressor provided by the present invention. Detailed Implementation

[0030] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below in conjunction with specific embodiments and corresponding drawings. Obviously, the described embodiments are only a part of the embodiments of this invention, and not all of them. Based on the embodiments of this invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this invention.

[0031] It should be noted that the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this invention are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of the invention described herein can be implemented in orders other than those illustrated or described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover a non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0032] In related technologies, conventional scroll compressors generate noise due to rotational imbalance and inertial forces caused by factors such as gas forces during operation. As an eccentric mechanism, the scroll compressor is unbalanced during operation, and even with counterweights, it is difficult to maintain dynamic balance under the influence of changing gas forces. Because dynamic balance is difficult to achieve, scroll compressors often experience first-harmonic vibrations during operation, which are transmitted through the casing and may affect the normal operation of the scroll compressor.

[0033] The excitation force generated by mechanical imbalance in scroll compressors may stimulate the natural frequency of its internal components, which in turn may cause severe noise and vibration due to resonance, which may affect the working condition of the scroll compressor and even shorten its service life.

[0034] Because the gas force is constantly changing, it is difficult to calculate. Furthermore, after the initial dynamic balancing design is completed, the mass and shape of the balance block are difficult to change. Therefore, the balance block needs to be able to adjust to a suitable position at any time to minimize the abnormal noise and vibration problems caused by imbalance.

[0035] This invention provides a vibration regulation method for a scroll compressor.

[0036] The scroll compressor has a first balance block and a second balance block at each end of its crankshaft, used for dynamic balance adjustment of the scroll compressor. The positions of the first and second balance blocks can be referenced. Figure 5a As shown. Figure 5aAs shown, the crankshaft 3 of the scroll compressor is equipped with a main bearing 5 and a secondary bearing 6. A first balance block 4 and a second balance block 7 are respectively located at both ends of the crankshaft 3. The first balance block 4 is positioned near the main bearing 5 of the scroll compressor, and the second balance block 7 is positioned near the secondary bearing 6 of the scroll compressor. The first balance block 4 and the second balance block 7 are capable of axial movement along the crankshaft 3. The mass of the first balance block is greater than the mass of the second balance block.

[0037] Figure 1 This is a schematic diagram of an embodiment of the vibration adjustment method for a scroll compressor provided by the present invention.

[0038] like Figure 1 As shown, according to an embodiment of the present invention, the vibration adjustment method of the scroll compressor includes at least steps S110, S120 and S130.

[0039] Step S110: Obtain the noise and vibration data of the scroll compressor, and determine whether the scroll compressor has abnormal noise and vibration based on the noise and vibration data.

[0040] Specifically, the noise and vibration data of the scroll compressor are monitored in real time to determine whether abnormal noise and vibration are occurring. Specifically, sensors can be used to capture first harmonic and harmonic abnormal signals. More specifically, noise and vibration signals are collected by sensors, and the time-domain signal is converted into a frequency-domain signal using FFT. By observing its spectral characteristic frequencies, mainly the first harmonic and integer harmonics, it is determined whether any abnormalities exist.

[0041] Step S120: If it is determined that the scroll compressor is experiencing abnormal noise and vibration, then the positions of the first balance block and / or the second balance block are determined based on the internal parameters and force data of the scroll compressor.

[0042] (1) Analysis of gas force correlation

[0043] Based on the gas force calculation formula, it can be found that the tangential gas force on the moving disk is a force that changes continuously with the rotation of the spindle and the change of the rotation angle. (Refer to...) Figure 2 As shown, Figure 2 The curve showing the relationship between tangential gas force and spindle rotation angle is presented.

[0044] The formula for calculating the tangential gas force in the first compression chamber is:

[0045]

[0046] The formula for calculating the tangential gas force in the second compression chamber is:

[0047]

[0048] The formula for calculating the tangential gas force in the i-th compression chamber is:

[0049]

[0050] In the formula, h is the height of the vortex body; p i Let be the gas pressure in the i-th compression chamber; 'a' be the base circle radius; and 'α' be the principal shaft rotation angle. Therefore, when there are N compression chambers, the tangential gas force on the moving disk is:

[0051]

[0052] In the formula:

[0053] p s Where ρ is the intake pressure (Pa), P is the vortex pitch (mm), h is the vortex height, N is the number of compression chambers, i is the i-th compression chamber, α is the main shaft rotation angle (varying with time and related to the rotational speed), and ρ is the intake pressure (Pa). i The pressure ratio between the two compression chambers κ is the isentropic exponent (adiabatic exponent, which refers to the exponent of a reversible adiabatic process of an ideal gas, denoted by κ. Generally speaking, the adiabatic exponent K for monatomic gases is 1.66, and the adiabatic exponent K for diatomic gases is 1.41); α s For exhaust angle α s =α-2π.

[0054] The radial gas force on the moving plate is mainly related to the exhaust pressure. The radial gas force Fr on the moving plate is:

[0055] F r =2ahp s (ρ1-1)

[0056] a is the base circle radius (mm), p s p is the inhalation pressure (Pa). d ρ is the exhaust pressure (Pa); ρ1 is the ratio of exhaust pressure to intake pressure, ρ1 = p d / p s ;

[0057] (2) Perform force analysis on the moving disk:

[0058] The main forces acting on the moving disk 1 include the tangential gas force Ft, the radial gas force Fr, the centrifugal inertial force Fc, the force Fs exerted on the moving disk 1 by the eccentric part of crankshaft 3, and the forces F1 and F2 exerted on the moving disk 1 by the cross-slip ring 2. The angle between the radial gas force and the x-direction of the cross-slip ring 2 is θ (a variable), m0 is the mass of the cross-slip ring 2, Fsr is the radial force exerted on the moving disk 1 by the eccentric part of crankshaft 3, and Fst is the axial force exerted on the moving disk 1 by the eccentric part of crankshaft 3. See diagrams 3a, 3b, and 3c for details. Figure 3aA schematic diagram of the radial force on the moving disk is shown. Figure 3b A schematic diagram of the tangential forces acting on the moving disk is shown. Figure 3c A top view showing the forces acting on the moving disc is shown.

[0059] Radial direction: F c -F r +(F1-F2)sinθ-F sr =0

[0060] Tangential direction: -F t +(F1-F2)cosθ+F st =0

[0061] (3) Force analysis of the cross slip ring

[0062] Figure 4 A schematic diagram of the forces acting on the cross-shaped slip ring is shown. Figure 4 The forces acting on the cross-slip ring 2 reciprocating in the y-direction are shown (friction is neglected; the compressor is a vertical structure, so gravity is not considered). The forces exerted by the cross-slip ring 2 on the moving disk 1 are F1 and F2, and the equation of motion is:

[0063] Forces in the y-direction are balanced.

[0064] in,

[0065] The radial force Fsr exerted by the eccentric part of crankshaft 3 on moving disk 1 is obtained as follows:

[0066] F sr =F c -F r +m0ω 2 R o sin 2 θ

[0067] The axial force Fst exerted by the eccentric part of crankshaft 3 on moving disk 1 is obtained as follows:

[0068] F st =F t -m0ω 2 R o sinθcosθ

[0069] (4) Force analysis of crankshaft 3

[0070] Force analysis of crankshaft 3 as follows Figure 5a , Figure 5b As shown, Figure 5a A schematic diagram of the radial forces acting on the crankshaft is shown. Figure 5bA schematic diagram of the tangential forces acting on the crankshaft is shown. Fs represents the force exerted by the eccentric portion of crankshaft 3 on the moving disk 1 (calculated using the above formula for tangential radial gas force), and Fcq represents the centrifugal inertial force generated by the eccentric portion of crankshaft 3, which is equal to the eccentric mass m of the eccentric portion of the crankshaft. cq Multiply by the eccentricity r cq Multiply by the square of the crankshaft angular velocity ω 2 That is, Fcq = m cq ·r cq ·ω 2 Wherein, the eccentricity distance is the radial distance between the eccentric part of the crankshaft and the center of mass of the crankshaft; Fd is the centrifugal force of the first balance block 4; Fdr is the inertial centrifugal force of the first balance block; Fzr is the radial support reaction force of the main bearing 5; Fzt is the tangential support reaction force of the main bearing 5; Ffr is the radial support reaction force of the auxiliary bearing 6; Fft is the tangential support reaction force of the auxiliary bearing 6; Fx is the centrifugal force of the second balance block 7; and Fxr is the inertial centrifugal force of the second balance block. The subscript r indicates radial direction, and t indicates tangential direction.

[0071] To minimize the reaction forces of the main and auxiliary bearings 5 ​​and 6, let Fz = 0 and Ff = 0. Based on the above formulas, the inertial centrifugal forces of the first and second balance blocks 4 and 7 can be calculated:

[0072] like Figure 5a As shown, L1 is the distance between the first balance block and the eccentric part of the crankshaft, that is, the axial distance between the center of mass of the first balance block 4 and the eccentric part of the crankshaft 3; L2 is the distance between the first balance block and the main bearing; L3 is the distance between the main bearing and the auxiliary bearing, which remains constant; and L4 is the distance between the second balance block and the auxiliary bearing.

[0073] The inertial centrifugal force of the first balancing block 4:

[0074]

[0075] The inertial centrifugal force of the second balancing block 7:

[0076]

[0077] The mass m of the first balance block is 4. d The second balance block has a mass of 7 m. x :

[0078]

[0079] Where, r d The eccentricity distance of the first counterweight, i.e., the radial distance between the center of mass of the first counterweight and the center of mass of the crankshaft, is r. x This is the eccentricity distance of the second balance block, that is, the radial distance between the center of mass of the second balance block and the center of mass of the crankshaft.

[0080] The initial position of the balance block is determined based on the different structures of different scroll compressor models during initial design. Using the aforementioned formulas for calculating the mass of the first balance block 4 and the second balance block 7, the masses of the first and second balance blocks can be calculated. Then, given the masses of the first and second balance blocks, according to the aforementioned formula for calculating the mass of the second balance block, the tangential gas force Ft acting on the moving plate during actual operation is a value that varies with the spindle rotation angle α.

[0081]

[0082] Therefore, to ensure the equation still holds, if Ft in the right-hand side of the equation increases while the mass mx of the second balance block remains constant, L1 must decrease. Since the bearing position remains unchanged, the decrease in L1 is accompanied by an increase in L2. However, it may be difficult to achieve balance simply by changing L1 and L2, i.e., changing the position of the first balance block. Therefore, it is necessary to change the position of L4, i.e., the second balance block. Due to the space limitations in the design of the scroll compressor, the axial movement distance of the first and second balance blocks is not infinite. Therefore, this balancing design only aims to minimize the impact of dynamic imbalance.

[0083] According to the formula for calculating the mass of the second balance block, after the balance block design is completed, the mass m of the second balance block... x For a constant value m x0 Ft is a function related to the principal spindle rotation angle α, denoted as F(α), -m0ω 2 R0sinαcosα+Fcq and r x ω 2 It is a function related to angular velocity ω, set as F1(ω)=-m0ω 2 R0sinαcosα+Fcq,F2(ω=r x ω 2 .

[0084] L1 is the axial distance between the center of mass of the first balance block 4 and the eccentric part of the crankshaft 3, and (L2+L3+L4) is the axial distance between the centers of mass of the first balance block 4 and the second balance block 7. Let L be the axial distance between the center of mass of the second balance block 7 and the eccentric part of the crankshaft 3, then L2+L3+L4=L-L1. Therefore, the formula for calculating the mass of the second balance block 7 can be simplified to:

[0085]

[0086] Then we can obtain the relationship between L1, L and the principal axis rotation angle α:

[0087]

[0088] The right side of the equation is a function related to the spindle rotation angle α, and the left side is the axial distance between the first and second balance blocks and the center of mass of the crankshaft eccentric part. The appropriate value is obtained by calculation, that is, the distance that the first and second balance blocks should move axially.

[0089] Therefore, by obtaining the main shaft rotation angle α, the tangential gas force Ft on the moving disk of the scroll compressor can be calculated, thus obtaining the function F(α) related to the main shaft rotation angle; based on the eccentric mass m of the crankshaft eccentric part... cq Multiply by the eccentricity r cq Multiplied by the square of the crankshaft angular velocity ω 2 Calculate the centrifugal inertial force generated by the crankshaft eccentricity, and then combine this with the cross ring mass m0, crankshaft angular velocity ω, and cross ring inner diameter R0 to obtain the angular velocity correlation function F1(ω)=-m0ω 2 R0sinαcosα+Fcq; then, based on the eccentricity of the second balance block and the crankshaft angular velocity ω, the angular velocity correlation function F2(ω)=r x ω 2 Then, based on F1(ω), F2(ω) and the mass of the second balance block, the optimal solution for the axial distance between the first balance block and the center of mass of the crankshaft eccentric part and / or the axial distance L between the second balance block and the center of mass of the crankshaft eccentric part is obtained. Then, the position of the first balance block and / or the position of the second balance block is obtained. Based on the original position of the first balance block and / or the original position of the second balance block, the distance that the first balance block and / or the second balance block should be adjusted is obtained.

[0090] Preferably, since the mass of the first balance block is greater than that of the second balance block, the position of the first balance block is kept stationary when adjusting the position of the balance block, that is, L1 is a constant value. From this, the value of L as a function of θ can be calculated, and thus the distance that the second balance block should be adjusted can be obtained.

[0091] Based on this, the internal parameters of the scroll compressor that need to be obtained include: main shaft rotation angle, crankshaft angular velocity, cross-slip ring inner diameter, cross-slip ring mass, the mass of the second balance block, and the eccentricity of the second balance block; the internal force data of the scroll compressor that need to be obtained include: the tangential gas force on the moving plate of the scroll compressor and the centrifugal inertial force generated by the crankshaft eccentricity. The tangential gas force on the moving plate of the scroll compressor, the centrifugal inertial force generated by the crankshaft eccentricity, the main shaft rotation angle, the crankshaft angular velocity, the cross-slip ring inner diameter, the cross-slip ring mass, the mass of the second balance block, and the eccentricity of the second balance block are obtained; the positions of the first balance block and / or the second balance block are calculated based on the tangential gas force on the moving plate, the centrifugal inertial force generated by the crankshaft eccentricity, the main shaft rotation angle, the crankshaft angular velocity, the cross-slip ring inner diameter, the cross-slip ring mass, the mass of the second balance block, and the eccentricity of the second balance block.

[0092] The angle between the first balance block 4 and the eccentric part of the crankshaft 2 (the angle between the line connecting the center of mass of the balance block and the axis of the non-eccentric part of the crankshaft, and the line connecting the center of mass of the eccentric part of the crankshaft and the axis of the non-eccentric part of the crankshaft), and the angle between the second balance block 7 and the eccentric part of the crankshaft 2 are as follows:

[0093]

[0094] Figure 6 A schematic diagram showing the deflection angles of the first balance block 4 and the second balance block 7 relative to the eccentric part of the crankshaft 2 is shown.

[0095] The above formula shows that the mass of the first balance block 4 and the second balance block 7 is related to the tangential gas force, the radial gas force, the relevant parameters of the moving disk 1, the cross slip ring 2, the crankshaft 3, as well as the position and geometry of the balance blocks themselves.

[0096] Since the dimensions and shapes of most components of a scroll compressor do not change after the design is finalized, while the gas force changes with the crankshaft angle, in order to maintain dynamic balance, the positions of the first and second balance blocks must be able to change automatically or semi-automatically.

[0097] Step S130: Adjust the positions of the first balance block and the second balance block to move them to a predetermined position.

[0098] In one specific embodiment, the first and second balance blocks are provided with an adjustment device, which adjusts the positions of the first and second balance blocks to move them to a predetermined position. In one specific embodiment, the adjustment device includes an electromagnet and a spring.

[0099] Specifically, an electromagnet is fixedly installed on the axial side of the balance block on the crankshaft and connected to the balance block with a spring. By adjusting the magnitude of the electromagnet's magnetic force, the spring force will also change to ensure balance. The length of the spring will change, causing the spring to push or pull the balance block to make it displace axially to reach the calculated position.

[0100] The axial position of the balance block is controlled by using an electromagnet and spring. This is achieved by controlling the magnitude of the electromagnetic force to balance the spring force, thereby causing a change in the radial position of the balance block. Changes in the axial position of the balance block affect the dynamic balance, thus resolving dynamic balance problems caused by actual gas force changes during compressor operation.

[0101] The method of the present invention may further include: if abnormal noise vibration still exists after adjusting the first and second balance blocks, adjustment is made by avoiding modal resonance points or by modifying relevant parameters of the driver. For example, if the current operating state may excite a certain mode, and unacceptable abnormal noise vibration still exists after automatically adjusting the balance block position, the operating conditions are appropriately adjusted to ensure that the scroll compressor can maintain a good mechanical balance. For example, if the current operating state may excite a certain mode, the modal resonance point can be avoided by changing the rotational speed, etc. Or, if there is an abnormal frequency of electromagnetic noise, it can be adjusted by modifying relevant parameters of the driver.

[0102] The present invention also provides a vibration adjustment device for a scroll compressor.

[0103] The scroll compressor has a first balance block and a second balance block at each end of its crankshaft, used for dynamic balance adjustment of the scroll compressor. The positions of the first and second balance blocks can be referenced. Figure 5a As shown. Figure 5a As shown, the crankshaft 3 of the scroll compressor is equipped with a main bearing 5 and a secondary bearing 6. A first balance block 4 and a second balance block 7 are respectively located at both ends of the crankshaft 3. The first balance block 4 is positioned near the main bearing 5 of the scroll compressor, and the second balance block 7 is positioned near the secondary bearing 6 of the scroll compressor. The first balance block 4 and the second balance block 7 are capable of axial movement along the crankshaft 3. The mass of the first balance block is greater than the mass of the second balance block.

[0104] Figure 7 This is a structural block diagram of an embodiment of the vibration adjustment device for a scroll compressor provided by the present invention. Figure 7 As shown, the vibration adjustment device 100 includes: a judgment unit 110, a determination unit 120, and an adjustment unit 130.

[0105] The judgment unit 110 is used to acquire the noise and vibration data of the scroll compressor and determine whether the scroll compressor has abnormal noise and vibration based on the noise and vibration data.

[0106] Specifically, the noise and vibration data of the scroll compressor are monitored in real time to determine whether abnormal noise and vibration are occurring. Specifically, sensors can be used to capture first harmonic and harmonic abnormal signals. More specifically, noise and vibration signals are collected by sensors, and the time-domain signal is converted into a frequency-domain signal using FFT. By observing its spectral characteristic frequencies, mainly the first harmonic and integer harmonics, it is determined whether any abnormalities exist.

[0107] The determining unit 120 is used to determine the position of the first balance block and / or the second balance block based on the internal parameters and force data of the scroll compressor if the determining unit determines that the scroll compressor has abnormal noise and vibration.

[0108] (1) Analysis of gas force correlation

[0109] Based on the gas force calculation formula, it can be found that the tangential gas force on the moving disk is a force that changes continuously with the rotation of the spindle and the change of the rotation angle. (Refer to...) Figure 2 As shown, Figure 2 The curve showing the relationship between tangential gas force and spindle rotation angle is presented.

[0110] The formula for calculating the tangential gas force in the first compression chamber is:

[0111]

[0112] The formula for calculating the tangential gas force in the second compression chamber is:

[0113]

[0114] The formula for calculating the tangential gas force in the i-th compression chamber is:

[0115]

[0116] In the formula, h is the height of the vortex body; p i Let be the gas pressure in the i-th compression chamber; 'a' be the base circle radius; and 'α' be the principal shaft rotation angle. Therefore, when there are N compression chambers, the tangential gas force on the moving disk is:

[0117]

[0118] In the formula:

[0119] p s Where ρ is the intake pressure (Pa), P is the vortex pitch (mm), h is the vortex height, N is the number of compression chambers, i is the i-th compression chamber, α is the main shaft rotation angle (varying with time and related to the rotational speed), and ρ is the intake pressure (Pa). i The pressure ratio between the two compression chambers κ is the isentropic exponent (adiabatic exponent, which refers to the exponent of a reversible adiabatic process of an ideal gas, denoted by κ. Generally speaking, the adiabatic exponent K for monatomic gases is 1.66, and the adiabatic exponent K for diatomic gases is 1.41); α s For exhaust angle α s =α-2π.

[0120] The radial gas force on the moving plate is mainly related to the exhaust pressure. The radial gas force Fr on the moving plate is:

[0121] F r=2ahp s (ρ1-1)

[0122] a is the base circle radius (mm), p s p is the inhalation pressure (Pa). d ρ is the exhaust pressure (Pa); ρ1 is the ratio of exhaust pressure to intake pressure, ρ1 = p d / p s ;

[0123] (2) Perform force analysis on the moving disk:

[0124] The main forces acting on the moving disk 1 include the tangential gas force Ft, the radial gas force Fr, the centrifugal inertial force Fc, the force Fs exerted on the moving disk 1 by the eccentric part of crankshaft 3, and the forces F1 and F2 exerted on the moving disk 1 by the cross-slip ring 2. The angle θ (variable) between the radial gas force and the x-direction of the cross-slip ring 2 is θ, m0 is the mass of the cross-slip ring 2, Fsr is the radial force exerted on the moving disk 1 by the eccentric part of crankshaft 3, and Fst is the axial force exerted on the moving disk 1 by the eccentric part of crankshaft 3. See diagrams 3a, 3b, and 3c for details. Figure 3a A schematic diagram of the radial force on the moving disk is shown. Figure 3b A schematic diagram of the tangential forces acting on the moving disk is shown. Figure 3c A top view showing the forces acting on the moving disc is shown.

[0125] Radial direction: F c -F r +(F1-F2)sinθ-F sr =0

[0126] Tangential direction: -F t +(F1-F2)cosθ+F st =0

[0127] (3) Force analysis of the cross slip ring

[0128] Figure 4 A schematic diagram of the forces acting on the cross-shaped slip ring is shown. Figure 4 The forces acting on the cross-slip ring 2 reciprocating in the y-direction are shown (friction is neglected; the compressor is a vertical structure, so gravity is not considered). The forces exerted by the cross-slip ring 2 on the moving disk 1 are F1 and F2, and the equation of motion is:

[0129] Forces in the y-direction are balanced.

[0130] in,

[0131] The radial force Fsr exerted by the eccentric part of crankshaft 3 on moving disk 1 is obtained as follows:

[0132] F sr =F c -Fr +m0ω 2 R o sin 2 θ

[0133] The axial force Fst exerted by the eccentric part of crankshaft 3 on moving disk 1 is obtained as follows:

[0134] F st =F t -m0ω 2 R o sinθcosθ

[0135] (4) Force analysis of crankshaft 3

[0136] Force analysis of crankshaft 3 as follows Figure 5a , Figure 5b As shown, Figure 5a A schematic diagram of the radial forces acting on the crankshaft is shown. Figure 5b A schematic diagram of the tangential forces acting on the crankshaft is shown. Fs represents the force exerted by the eccentric portion of crankshaft 3 on the moving disk 1 (calculated using the above formula for tangential radial gas force), and Fcq represents the centrifugal inertial force generated by the eccentric portion of crankshaft 3, which is equal to the eccentric mass m of the eccentric portion of the crankshaft. cq Multiply by the eccentricity r cq Multiply by the square of the crankshaft angular velocity ω 2 That is, Fcq = m cq ·r cq ·ω 2 Wherein, the eccentricity distance is the radial distance between the eccentric part of the crankshaft and the center of mass of the crankshaft; Fd is the centrifugal force of the first balance block 4; Fdr is the inertial centrifugal force of the first balance block; Fzr is the radial support reaction force of the main bearing 5; Fzt is the tangential support reaction force of the main bearing 5; Ffr is the radial support reaction force of the auxiliary bearing 6; Fft is the tangential support reaction force of the auxiliary bearing 6; Fx is the centrifugal force of the second balance block 7; and Fxr is the inertial centrifugal force of the second balance block. The subscript r indicates radial direction, and t indicates tangential direction.

[0137] To minimize the reaction forces of the main and auxiliary bearings 5 ​​and 6, let Fz = 0 and Ff = 0. Based on the above formulas, the inertial centrifugal forces of the first and second balance blocks 4 and 7 can be calculated:

[0138] like Figure 5a As shown, L1 is the distance between the first balance block and the eccentric part of the crankshaft, that is, the axial distance between the center of mass of the first balance block 4 and the eccentric part of the crankshaft 3; L2 is the distance between the first balance block and the main bearing; L3 is the distance between the main bearing and the auxiliary bearing, which remains constant; and L4 is the distance between the second balance block and the auxiliary bearing.

[0139] The inertial centrifugal force of the first balancing block 4:

[0140]

[0141] The inertial centrifugal force of the second balancing block 7:

[0142]

[0143] The mass m of the first balance block is 4. d The second balance block has a mass of 7 m. x :

[0144]

[0145] Where, r d The eccentricity distance of the first counterweight, i.e., the radial distance between the center of mass of the first counterweight and the center of mass of the crankshaft, is r. x This is the eccentricity distance of the second balance block, that is, the radial distance between the center of mass of the second balance block and the center of mass of the crankshaft.

[0146] The initial position of the balance block is determined based on the different structures of different scroll compressor models during initial design. Using the mass calculation formulas for the first balance block 4 and the second balance block 7 mentioned above, the masses of the first and second balance blocks can be calculated. Then, given the masses of the first and second balance blocks, according to the above formula for calculating the mass of the second balance block, the tangential gas force Ft acting on the moving plate during actual operation is a value that varies with the spindle rotation angle α.

[0147]

[0148] Therefore, to ensure the equation still holds, if Ft in the right-hand side of the equation increases while the mass mx of the second balance block remains constant, L1 must decrease. Since the bearing position remains unchanged, the decrease in L1 is accompanied by an increase in L2. However, it may be difficult to achieve balance simply by changing L1 and L2, i.e., changing the position of the first balance block. Therefore, it is necessary to change the position of L4, i.e., the second balance block. Due to the space limitations in the design of the scroll compressor, the axial movement distance of the first and second balance blocks is not infinite. Therefore, this balancing design only aims to minimize the impact of dynamic imbalance.

[0149] According to the formula for calculating the mass of the second balance block, after the balance block design is completed, the mass m of the second balance block... x For a constant value m x0 Ft is a function related to the principal spindle rotation angle α, denoted as F(α), -m0ω 2 R0sinαcosα+Fcq and r x ω 2 It is a function related to angular velocity ω, set as F1(ω)=-m0ω 2 R0sinαcosα+Fcq,F2(ω=r x ω2 .

[0150] L1 is the axial distance between the center of mass of the first balance block 4 and the eccentric part of the crankshaft 3, and (L2+L3+L4) is the axial distance between the centers of mass of the first balance block 4 and the second balance block 7. Let L be the axial distance between the center of mass of the second balance block 7 and the eccentric part of the crankshaft 3, then L2+L3+L4=L-L1. Therefore, the formula for calculating the mass of the second balance block 7 can be simplified to:

[0151]

[0152] Then we can obtain the relationship between L1, L and the principal axis rotation angle α:

[0153]

[0154] The right side of the equation is a function related to the spindle rotation angle α, and the left side is the axial distance between the first and second balance blocks and the center of mass of the crankshaft eccentric part. The appropriate value is obtained by calculation, that is, the distance that the first and second balance blocks should move axially.

[0155] Therefore, by obtaining the main shaft rotation angle α, the tangential gas force Ft on the moving disk of the scroll compressor can be calculated, thus obtaining the function F(α) related to the main shaft rotation angle; based on the eccentric mass m of the crankshaft eccentric part... cq Multiply by the eccentricity r cq Multiplied by the square of the crankshaft angular velocity ω 2 Calculate the centrifugal inertial force generated by the crankshaft eccentricity, and then combine this with the cross ring mass m0, crankshaft angular velocity ω, and cross ring inner diameter R0 to obtain the angular velocity correlation function F1(ω)=-m0ω 2 R0sinαcosα+Fcq; then, based on the eccentricity of the second balance block and the crankshaft angular velocity ω, the angular velocity correlation function F2(ω)=r x ω 2 Then, based on F1(ω), F2(ω) and the mass of the second balance block, the optimal solution for the axial distance between the first balance block and the center of mass of the crankshaft eccentric part and / or the axial distance L between the second balance block and the center of mass of the crankshaft eccentric part is obtained. Then, the position of the first balance block and / or the position of the second balance block is obtained. Based on the original position of the first balance block and / or the original position of the second balance block, the distance that the first balance block and / or the second balance block should be adjusted is obtained.

[0156] Preferably, since the mass of the first balance block is greater than that of the second balance block, the position of the first balance block is kept stationary when adjusting the position of the balance block, that is, L1 is a constant value. From this, the value of L as a function of θ can be calculated, and thus the distance that the second balance block should be adjusted can be obtained.

[0157] Based on this, the internal parameters of the scroll compressor that need to be obtained include: main shaft rotation angle, crankshaft angular velocity, cross-slip ring inner diameter, cross-slip ring mass, the mass of the second balance block, and the eccentricity of the second balance block; the internal force data of the scroll compressor that need to be obtained include: the tangential gas force on the moving plate of the scroll compressor and the centrifugal inertial force generated by the crankshaft eccentricity. The tangential gas force on the moving plate of the scroll compressor, the centrifugal inertial force generated by the crankshaft eccentricity, the main shaft rotation angle, the crankshaft angular velocity, the cross-slip ring inner diameter, the cross-slip ring mass, the mass of the second balance block, and the eccentricity of the second balance block are obtained; the positions of the first balance block and / or the second balance block are calculated based on the tangential gas force on the moving plate, the centrifugal inertial force generated by the crankshaft eccentricity, the main shaft rotation angle, the crankshaft angular velocity, the cross-slip ring inner diameter, the cross-slip ring mass, the mass of the second balance block, and the eccentricity of the second balance block.

[0158] The angle between the first balance block 4 and the eccentric part of the crankshaft 2 (the angle between the line connecting the center of mass of the balance block and the axis of the non-eccentric part of the crankshaft, and the line connecting the center of mass of the eccentric part of the crankshaft and the axis of the non-eccentric part of the crankshaft), and the angle between the second balance block 7 and the eccentric part of the crankshaft 2 are as follows:

[0159]

[0160] Figure 6 A schematic diagram showing the deflection angles of the first balance block 4 and the second balance block 7 relative to the eccentric part of the crankshaft 2 is shown.

[0161] The above formula shows that the mass of the first balance block 4 and the second balance block 7 is related to the tangential gas force, the radial gas force, the relevant parameters of the moving disk 1, the cross slip ring 2, the crankshaft 3, as well as the position and geometry of the balance blocks themselves.

[0162] Since the dimensions and shapes of most components of a scroll compressor do not change after the design is finalized, while the gas force changes with the crankshaft angle, in order to maintain dynamic balance, the positions of the first and second balance blocks must be able to change automatically or semi-automatically.

[0163] The adjustment unit 130 is used to adjust the positions of the first balance block and the second balance block, so that the first balance block and the second balance block move to a certain position.

[0164] In one specific embodiment, the first and second balance blocks are provided with an adjustment device, which adjusts the positions of the first and second balance blocks to move them to a predetermined position. In one specific embodiment, the adjustment device includes an electromagnet and a spring.

[0165] Specifically, an electromagnet is fixedly installed on the axial side of the balance block on the crankshaft and connected to the balance block with a spring. By adjusting the magnitude of the electromagnet's magnetic force, the spring force will also change to ensure balance. The length of the spring will change, causing the spring to push or pull the balance block to make it displace axially to reach the calculated position.

[0166] The axial position of the balance block is controlled by using an electromagnet and spring. This is achieved by controlling the magnitude of the electromagnetic force to balance the spring force, thereby causing a change in the radial position of the balance block. Changes in the axial position of the balance block affect the dynamic balance, thus resolving dynamic balance problems caused by actual gas force changes during compressor operation.

[0167] The adjustment unit is further configured to: if abnormal noise vibration persists after adjusting the first and second balance blocks, adjust the operation by avoiding modal resonance points or by modifying relevant parameters of the driver. For example, if the current operating state may excite a certain mode, and unacceptable abnormal noise vibration still exists after automatically adjusting the balance block positions, adjust the operating conditions appropriately to ensure that the scroll compressor maintains a good mechanical balance. For example, if the current operating state may excite a certain mode, the modal resonance point can be avoided by changing the rotational speed. Alternatively, if there is an abnormal electromagnetic noise frequency, it can be adjusted by modifying relevant parameters of the driver.

[0168] The present invention also provides a storage medium corresponding to the vibration regulation method of the scroll compressor, wherein a computer program is stored thereon, and the computer program, when executed by a processor, implements the steps of any of the aforementioned methods.

[0169] The present invention also provides a controller corresponding to the vibration regulation method of the scroll compressor, comprising a processor, a memory, and a computer program stored in the memory that can run on the processor, wherein the processor executes the computer program to implement the steps of any of the aforementioned methods.

[0170] The present invention also provides a controller corresponding to the vibration adjustment device of the scroll compressor, including any of the aforementioned vibration adjustment devices.

[0171] The present invention also provides a computer program product corresponding to the vibration regulation method of the scroll compressor, comprising a computer program that, when executed by a processor, implements the steps of any of the aforementioned methods.

[0172] Accordingly, the solution provided by the present invention achieves vibration reduction and noise reduction by real-time monitoring of the noise, vibration and force data of the scroll compressor and by calculating and analyzing the position and angle of the balance block to achieve the closest possible dynamic balance.

[0173] According to the technical solution of the present invention, the position and angle of the balance block should be calculated to achieve the dynamic balance state of the current scroll compressor, and the position of the balance block is automatically or semi-automatically adjusted to optimize the dynamic balance in real time.

[0174] According to the technical solution of the present invention, abnormal noise and vibration problems caused by failure to achieve dynamic balance can be effectively reduced, especially dynamic balance problems that are difficult to handle due to the time-varying characteristics of gas forces. Simultaneously, due to real-time monitoring, resonance phenomena that may be triggered under certain operating conditions can be effectively avoided, abnormal problems can be detected and addressed promptly, and malfunctions that could lead to abnormal operation or reduced service life can be prevented.

[0175] According to the technical solution of the present invention, the noise and vibration signals of the scroll compressor and related force information such as gas force are captured in real time by sensors, and the algorithm is used to calculate the reasonable range of the position and deflection angle of the balance block in the current dynamic balance state of the scroll compressor. The obtained noise and vibration data are used to determine whether there is abnormal noise and vibration, such as exciting a certain mode to generate resonance.

[0176] According to the technical solution of the present invention, the position or angle of the balance block is adjusted by using an automatic or semi-automatic adjustment device, such as an electromagnet-spring structure.

[0177] The functions described herein can be implemented in hardware, software executed by a processor, firmware, or any combination thereof. If implemented in software executed by a processor, the functions can be stored as one or more instructions or codes on or transmitted via a computer-readable medium. Other examples and embodiments are within the scope and spirit of this invention and the appended claims. For example, due to the nature of software, the functions described above can be implemented using software executed by a processor, hardware, firmware, hardwired, or any combination thereof. Furthermore, the functional units can be integrated into a single processing unit, or each unit can exist physically separately, or two or more units can be integrated into a single unit.

[0178] In the several embodiments provided in this application, it should be understood that the disclosed technical content can be implemented in other ways. The device embodiments described above are merely illustrative; for example, the division of units can be a logical functional division, and in actual implementation, there may be other division methods. For instance, multiple units or components may be combined or integrated into another system, or some features may be ignored or not executed. Furthermore, the displayed or discussed mutual coupling, direct coupling, or communication connection may be through some interfaces; the indirect coupling or communication connection between units or modules may be electrical or other forms.

[0179] The units described as separate components may or may not be physically separate. Similarly, the components of the control device may or may not be physical units; they may be located in one place or distributed across multiple units. Some or all of the units can be selected to achieve the purpose of this embodiment, depending on actual needs.

[0180] If the integrated unit is implemented as a software functional unit and sold or used as an independent product, it can be stored in a computer-readable storage medium. Based on this understanding, the technical solution of the present invention, in essence, or the part that contributes to related technologies, or all or part of the technical solution, can be embodied in the form of a software product. This computer software product is stored in a storage medium and includes several instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) to execute all or part of the steps of the methods described in the various embodiments of the present invention. The aforementioned storage medium includes various media capable of storing program code, such as USB flash drives, read-only memory (ROM), random access memory (RAM), portable hard drives, magnetic disks, or optical disks.

[0181] The above description is merely an embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of the claims of the present invention.

Claims

1. A vibration regulation method for a scroll compressor, characterized in that, include: The crankshaft of the scroll compressor is provided with a first balance block and a second balance block at both ends; the first balance block is located at one end near the main bearing of the scroll compressor, and the second balance block is located at one end near the auxiliary bearing of the scroll compressor; the first balance block and the second balance block can move axially along the crankshaft. The vibration adjustment method includes: Obtain the noise and vibration data of the scroll compressor, and determine whether the scroll compressor has abnormal noise and vibration based on the noise and vibration data; If it is determined that the scroll compressor is experiencing abnormal noise and vibration, the positions of the first balance block and / or the second balance block are determined based on the internal parameters and force data of the scroll compressor. Adjust the position of the first balance block and / or the second balance block so that the first balance block and / or the second balance block move to a determined position; The internal parameters of the scroll compressor include: main shaft rotation angle, crankshaft angular velocity, cross slip ring inner diameter, cross slip ring mass, second balance block mass, and second balance block eccentricity distance; the internal force data of the scroll compressor include: tangential gas force on the moving disk of the scroll compressor and centrifugal inertial force generated by the crankshaft eccentricity. Determining the positions of the first balance block and / or the second balance block based on the internal parameters and force data of the scroll compressor includes: The following parameters are obtained: tangential gas force on the moving disk of the scroll compressor, centrifugal inertial force generated by the crankshaft eccentricity, main shaft rotation angle, crankshaft angular velocity, cross slip ring inner diameter, cross slip ring mass, second balance block mass, and eccentricity distance of the second balance block. The positions of the first balance block and / or the second balance block are calculated based on the tangential gas force on the moving disk, the centrifugal inertial force generated by the crankshaft eccentricity, the main shaft rotation angle, the crankshaft angular velocity, the inner diameter of the cross slip ring, the mass of the cross slip ring, the mass of the second balance block, and the eccentricity distance of the second balance block. The position of the first balance block includes the axial distance between the first balance block and the center of mass of the crankshaft eccentric portion; the position of the second balance block includes the axial distance between the second balance block and the center of mass of the crankshaft eccentric portion.

2. The method according to claim 1, characterized in that, The first and / or second balance blocks are provided with adjustment devices to adjust the positions of the first and / or second balance blocks, so that the first and / or second balance blocks move to a predetermined position, including: The position of the first balance block and / or the second balance block is adjusted by the adjustment device, so that the first balance block and / or the second balance block are moved to a determined position.

3. The method according to claim 2, characterized in that, The adjusting device includes an electromagnet and a spring.

4. A vibration regulating device for a scroll compressor, characterized in that, include: The crankshaft of the scroll compressor is provided with a first balance block and a second balance block at both ends; the first balance block is located at one end near the main bearing of the scroll compressor, and the second balance block is located at one end near the auxiliary bearing of the scroll compressor; the first balance block and the second balance block can move axially along the crankshaft. The vibration regulating device includes: The judgment unit is used to acquire the noise and vibration data of the scroll compressor and determine whether the scroll compressor has abnormal noise and vibration based on the noise and vibration data. The determining unit is used to determine the position of the first balance block and / or the second balance block based on the internal parameters and force data of the scroll compressor if the judging unit determines that the scroll compressor has abnormal noise and vibration. An adjustment unit is used to adjust the position of the first balance block and / or the second balance block, so that the first balance block and / or the second balance block moves to a certain position; The internal parameters of the scroll compressor include: main shaft rotation angle, crankshaft angular velocity, cross slip ring inner diameter, cross slip ring mass, second balance block mass, and second balance block eccentricity distance; the internal force data of the scroll compressor include: tangential gas force on the moving disk of the scroll compressor and centrifugal inertial force generated by the crankshaft eccentricity. The determining unit determines the positions of the first balance block and / or the second balance block based on the internal parameters and force data of the scroll compressor, including: The following parameters are obtained: tangential gas force on the moving disc of the scroll compressor, centrifugal inertial force generated by the crankshaft eccentricity, main shaft rotation angle, crankshaft angular velocity, cross slip ring inner diameter, cross slip ring mass, second balance block mass, and eccentricity distance of the second balance block. The positions of the first balance block and / or the second balance block are calculated based on the tangential gas force on the moving disk, the centrifugal inertial force generated by the crankshaft eccentricity, the main shaft rotation angle, the crankshaft angular velocity, the inner diameter of the cross slip ring, the mass of the cross slip ring, the mass of the second balance block, and the eccentricity distance of the second balance block. The position of the first balance block includes the axial distance between the first balance block and the center of mass of the crankshaft eccentric portion; the position of the second balance block includes the axial distance between the second balance block and the crankshaft eccentric portion.

5. The apparatus according to claim 4, characterized in that, The first and / or second balance blocks are provided with adjustment devices to adjust the positions of the first and / or second balance blocks, so that the first and / or second balance blocks move to a predetermined position, including: The position of the first balance block and / or the second balance block is adjusted by the adjustment device, so that the first balance block and / or the second balance block are moved to a determined position.

6. A storage medium, characterized in that, It stores a computer program that, when executed by a processor, implements the steps of the method according to any one of claims 1-3.

7. A controller, characterized in that, The controller includes a processor, a memory, and a computer program stored in the memory that can run on the processor. When the processor executes the program, it implements the steps of the method according to any one of claims 1-3. Alternatively, the controller includes a vibration regulating device for a scroll compressor according to any one of claims 4-5.

8. A computer program product, characterized in that, Includes a computer program, which, when executed by a processor, implements the steps of the method according to any one of claims 1-3.

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