Vibration adjusting method and device of scroll compressor, medium, controller and product

Abstract

The invention provides a vibration adjusting method and device of a scroll compressor, a medium, a controller and a product. A first balance block and a second balance block are arranged at the two ends of a crankshaft of the scroll compressor correspondingly. The first balance block and the second balance block can axially move along the crankshaft; the method comprises the following steps: acquiring noise vibration data of the scroll compressor, and judging whether abnormal noise vibration occurs in the scroll compressor or not according to the noise vibration data; if it is judged that abnormal noise vibration occurs in the scroll compressor, the position of a first balance block and / or a second balance block is determined according to internal parameters and stress data of the scroll compressor; and the position of the first balance block and / or the position of the second balance block are / is adjusted, so that the first balance block and / or the second balance block are / is moved to the determined position. According to the scheme provided by the invention, the supposed position of the balance block of the current scroll compressor meeting the dynamic balance state can be determined, automatic adjustment is carried out, and dynamic balance is optimized in real time.

Description

Technical Field

[0001] The present invention relates to the field of control, and in particular to a vibration regulation method, device, medium, controller and product of a scroll compressor, and specifically to a vibration regulation method, device, storage medium, controller and computer program product of a scroll compressor. Background Art

[0002] The noise and vibration problems of scroll compressors are usually reflected in the single frequency and integer multiple frequency of the crankshaft rotation frequency. One of the main reasons is the dynamic balance problem of the shaft system. In the related technology, the influence of gas force is usually not considered in the dynamic balance design, and the balance block is designed only by balancing the eccentric force and eccentric torque.

[0003] However, in the actual working process of the scroll compressor, it is inevitably affected by the tangential and radial gas forces, and they are often constantly changing. This makes it difficult to avoid the mechanical imbalance during the actual operation of the scroll compressor even if a dynamic balancing design is done. Once its frequency is close to the modal frequency of the scroll compressor components, it may cause resonance, causing more serious noise and vibration problems. Summary of the invention

[0004] The main purpose of the present invention is to overcome the defects of the above-mentioned related technologies and to provide a vibration regulation method, device, storage medium, controller and computer program product for a scroll compressor so as to solve the problem in the related technologies that it is difficult to ensure dynamic balance during operation of the scroll compressor even if a balancing block is used.

[0005] On one hand, the present invention provides a vibration regulation method for a scroll compressor, comprising: a first balancing block and a second balancing block are respectively provided at both ends of a crankshaft of the scroll compressor; the first balancing block is arranged at one end close to a main bearing of the turbine compressor, and the second balancing block is arranged at one end close to a secondary bearing of the turbine compressor, and the first balancing block and the second balancing block can move axially along the crankshaft; the vibration regulation method comprises: obtaining noise and vibration data of the scroll compressor, and judging whether abnormal noise and vibration occur in the scroll compressor according to the noise and vibration data; if it is judged that abnormal noise and vibration occur in the scroll compressor, determining the position of the first balancing block and / or the second balancing block according to internal parameters and force data of the scroll compressor; and adjusting the position of the first balancing block and / or the second balancing block so that the first balancing block and / or the second balancing block move to a determined position.

[0006] Optionally, the internal parameters of the scroll compressor include: the main shaft 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 balancing block and the eccentric distance of the second balancing block; the internal force data of the scroll compressor include: the tangential gas force on the moving disk of the scroll compressor and the centrifugal inertia force generated by the eccentric part of the crankshaft; according to the internal parameters and force data of the scroll compressor, determining the position of the first balancing block and / or the second balancing block includes: obtaining the tangential gas force on the moving disk of the scroll compressor, the centrifugal inertia force generated by the eccentric part of the crankshaft, the main shaft 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 balancing block and the eccentric distance of the second balancing block; the position of the first balancing block and / or the position of the second balancing block are calculated according to the tangential gas force on the moving disk, the centrifugal inertia force generated by the eccentric part of the crankshaft, the main shaft angle, the angular velocity of the crankshaft, the inner diameter of the cross slip ring, the mass of the cross slip ring, the mass of the second balancing block and the eccentric distance of the second balancing block; the position of the first balancing block includes: the axial distance between the first balancing block and the center of mass of the eccentric part of the crankshaft; the position of the second balancing block includes: the axial distance between the second balancing block and the center of mass of the eccentric part of the crankshaft.

[0007] Optionally, the first balancing block and the second balancing block are provided with an adjusting device, and the position of the first balancing block and / or the second balancing block is adjusted to move the first balancing block and / or the second balancing block to a determined position, including: adjusting the position of the first balancing block and / or the second balancing block by the adjusting device to move the first balancing block and / or the second balancing block to the determined position.

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

[0009] On the other hand, the present invention provides a vibration adjustment device for a scroll compressor, comprising: a first balancing block and a second balancing block are respectively provided at both ends of the crankshaft of the scroll compressor; the first balancing block is arranged at one end close to the main bearing of the turbine compressor, and the second balancing block is arranged at one end close to the secondary bearing of the turbine compressor, and the first balancing block and the second balancing block can move axially along the crankshaft; the vibration adjustment device comprises: a judgment unit, used to obtain noise and vibration data of the scroll compressor, and judge whether the scroll compressor has abnormal noise and vibration according to the noise and vibration data; a determination unit, used to determine the positions of the first balancing block and the second balancing block according to the internal parameters and force data of the scroll compressor if the judgment unit judges that the scroll compressor has abnormal noise and vibration; an adjustment unit, used to adjust the position of the first balancing block and / or the second balancing block, so that the first balancing block and / or the second balancing block moves to a determined position.

[0010] Optionally, the internal parameters of the scroll compressor include: the main shaft 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 balancing block and the eccentric distance of the second balancing block; the internal force data of the scroll compressor include: the tangential gas force on the moving disk of the scroll compressor and the centrifugal inertia force generated by the eccentric part of the crankshaft; the determination unit determines the position of the first balancing block and / or the second balancing block according to the internal parameters and force data of the scroll compressor, including: obtaining the tangential gas force on the moving disk of the scroll compressor, the centrifugal inertia force generated by the eccentric part of the crankshaft, the main shaft angle, the crankshaft angular velocity, the cross slip ring, the mass of the second balancing block, and the eccentric distance of the second balancing block. The method comprises the following steps: calculating the position of the first balancing block and the position of the second balancing block according to the obtained tangential gas force on the moving disk, the centrifugal inertia force generated by the eccentric part of the crankshaft, the main shaft rotation angle, the angular velocity of the crankshaft, the inner diameter of the cross slip ring, the mass of the cross slip ring, the mass of the second balancing block and the eccentric distance of the second balancing block; the position of the first balancing block comprises the axial distance between the first balancing block and the center of mass of the eccentric part of the crankshaft; and the position of the second balancing block comprises the axial distance between the second balancing block and the center of mass of the eccentric part of the crankshaft.

[0011] Optionally, the first balancing block and / or the second balancing block is provided with an adjusting device, and the position of the first balancing block and / or the second balancing block is adjusted to move the first balancing block and / or the second balancing block to a determined position, including: adjusting the position of the first balancing block and / or the second balancing block by the adjusting device to move the first balancing block and / or the second balancing block to the determined position.

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

[0013] Another aspect of the present invention provides a storage medium having a computer program stored thereon, wherein the program implements the steps of any of the aforementioned methods when executed by a processor.

[0014] In another aspect, the present invention provides a controller, comprising a processor, a memory, and a computer program stored in the memory and executable on the processor, wherein the processor implements the steps of any of the aforementioned methods when executing the program.

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

[0016] In yet another aspect, the present invention provides a computer program product, comprising a computer program, wherein when the computer program is executed by a processor, the steps of any of the aforementioned methods are implemented.

[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 and adjusting the position and angle of the balancing block, an ideal dynamic balance condition can be achieved to the greatest extent possible, thereby achieving vibration reduction and noise reduction.

[0018] According to the technical solution of the present invention, the position and angle of the balancing block that the current scroll compressor should be in in order to meet the dynamic balance state are calculated, the position of the balancing block is automatically or semi-automatically adjusted, and the dynamic balance is optimized in real time. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] The drawings described herein are used to provide a further understanding of the present invention and constitute a part of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

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

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

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

[0023] Figure 3b The schematic diagram of the tangential force of the moving disk is shown;

[0024] Figure 3c A top view of the force on the moving plate is shown;

[0025] Figure 4 The force diagram of the cross slip ring is shown;

[0026] Figure 5a A schematic diagram of radial force on the crankshaft is shown;

[0027] Figure 5b A schematic diagram of the tangential force of the crankshaft is shown;

[0028] Figure 6 A schematic diagram showing the deflection angles of the first balancing block and the second balancing block and the eccentric portion of the crankshaft is shown;

[0029] Figure 7 It is a structural block diagram of an embodiment of a vibration regulating device for a scroll compressor provided by the present invention. DETAILED DESCRIPTION

[0030] In order to make the purpose, technical solution and advantages of the present invention clearer, the technical solution of the present invention will be clearly and completely described below in conjunction with the specific embodiments of the present invention and the corresponding drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present invention.

[0031] It should be noted that the terms "first", "second", etc. in the specification and claims of the present invention and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the data used in this way can be interchanged where appropriate, so that the embodiments of the present invention described herein can be implemented in an order other than those illustrated or described herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions, for example, a process, method, system, product or device that includes a series of steps or units is not necessarily limited to those steps or units that are clearly listed, but may include other steps or units that are not clearly listed or inherent to these processes, methods, products or devices.

[0032] In the related art, when a conventional scroll compressor is working, the noise is generated by the rotational unbalanced inertial force caused by factors such as gas force. As an eccentric mechanism, the scroll compressor is unbalanced during operation. Even if a balancing block is used, it is difficult to ensure dynamic balance during operation under the influence of changing factors such as gas force. Since dynamic balance is difficult to achieve, the scroll compressor often produces a single-frequency vibration problem during operation, which is transmitted through the shell and may affect the normal operation of the scroll compressor.

[0033] The excitation force generated by the mechanical imbalance of the scroll compressor may excite the natural frequency of its internal components, and then produce severe noise and vibration due to resonance, which may affect the working state of the scroll compressor and even shorten the service life of the scroll compressor.

[0034] Since the gas force is constantly changing and difficult to calculate, and after the preliminary design of the dynamic balance is completed, the mass and shape of the balance block are difficult to change. Therefore, the balance block needs to be adjusted to the appropriate position at any time to minimize the abnormal noise and vibration problems caused by imbalance.

[0035] The invention provides a vibration regulating method for a scroll compressor.

[0036] The first balancing block and the second balancing block are respectively provided at both ends of the crankshaft of the scroll compressor, which are used for dynamic balancing adjustment of the scroll compressor. The positions of the first balancing block and the second balancing block can be referred to as shown in Figure 5. As shown in Figure 5, a main bearing 5 and a secondary bearing 6 are installed on the crankshaft 3 of the scroll compressor, and a first balancing block 4 and a second balancing block 7 are respectively provided at both ends of the crankshaft 3. The first balancing block 4 is arranged at one end close to the main bearing 5 of the turbine compressor, and the second balancing block 7 is arranged at one end close to the secondary bearing 6 of the turbine compressor, and the first balancing block 4 and the second balancing block 7 can move axially along the crankshaft 3. The mass of the first balancing block is greater than the mass of the second balancing block.

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

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

[0039] Step S110, acquiring noise and vibration data of the scroll compressor, and determining whether abnormal noise and vibration occur in the scroll compressor according to the noise and vibration data.

[0040] Specifically, the noise and vibration data of the scroll compressor are monitored in real time to determine whether the scroll compressor has abnormal noise and vibration. Specifically, the sensor can be used to capture the first harmonic and harmonic abnormal signals. More specifically, the noise and vibration signals are collected by the sensor, and the time domain signals are converted into frequency domain signals using FFT. By observing the characteristic frequencies of the spectrum, mainly the first harmonic and integer harmonic, it is determined whether there is an abnormality.

[0041] Step S120: If it is determined that the scroll compressor has abnormal noise and vibration, the position of the first balancing block and / or the second balancing block is determined according to the internal parameters and force data of the scroll compressor.

[0042] (1) Analysis of gas force correlation

[0043] According to 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 main shaft and the change of the rotation angle. Figure 2 As shown, Figure 2 The relationship curve between the tangential gas force and the main shaft angle is shown.

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

[0045] F t1 =a(4π-2α)h(p1-p2)

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

[0047] F t2 =a(8π-2α)h(p2-p3)

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

[0049] F ti =a(4iπ-2α)h(p i -p i+1 )

[0050] Where h is the height of the vortex; p i is the gas pressure in the i-th compression chamber; a is the base circle radius; α is the main axis rotation angle; therefore, when there are N compression chambers, the tangential gas force on the moving disk is:

[0051]

[0052] Where:

[0053] p s is the suction 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 angle (varies with time and is related to the speed), ρ i is the pressure ratio between the two compression chambers ρ N+1 =1; κ is the isentropic index (adiabatic index refers to the index of the reversible adiabatic process of an ideal gas, denoted by κ. Generally speaking, the adiabatic index K of a monatomic gas is 1.66, and the adiabatic index K of a diatomic gas is 1.41); α s Exhaust angle α s =α-2π.

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

[0055] F r =2ahp s (ρ1-1)

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

[0057] (2) Force analysis of 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 inertia force Fc, the force Fs exerted by the eccentric part of the crankshaft 3 on the moving disk 1, and the forces F1 and F2 exerted by the cross ring 2 on the moving disk 1. The angle between the radial gas force and the cross ring 2 in the x direction is θ (variable), m0 is the mass of the cross ring 2, Fsr is the radial force exerted by the eccentric part of the crankshaft 3 on the moving disk 1, and Fst is the axial force exerted by the eccentric part of the crankshaft 3 on the moving disk 1. For details, please refer to 3a, 3b, and 3c. Figure 3a The figure shows the radial force diagram of the moving disk. Figure 3b The figure shows the schematic diagram of the tangential force of the moving disk. Figure 3c A top view of the force on the moving plate 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 cross slip ring

[0062] Figure 4 The force diagram of the cross slip ring is shown. Figure 4 The figure shows the force on the cross ring 2 that reciprocates in the y direction (friction is not considered, and the compressor is a vertical structure and gravity is not considered). The force acting on the moving plate 1 by the cross ring 2 is F1 and F2, and the motion equation is:

[0063] The force balance in the y direction is

[0064] in,

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

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

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

[0068] F st =F t -m0ω 2 R o sinθcosθ

[0069] (4) Force analysis of crankshaft 3

[0070] The stress analysis of crankshaft 3 is as follows: Figure 5a , Figure 5b As shown, Figure 5a The radial force diagram of the crankshaft is shown. Figure 5b The diagram shows the tangential force of the crankshaft. Fs is the force of the eccentric part of the crankshaft 3 on the moving disk 1 (calculated by the tangential radial gas force in the above formula), and Fcq is the centrifugal inertia force generated by the eccentric part of the crankshaft 3, which is equal to the eccentric mass mcq of the eccentric part of the crankshaft multiplied by the eccentric distance rcq and then multiplied by the square of the angular velocity of the crankshaft ω 2 , that is, Fcq = mcq·rcq·ω 2 , where the eccentric 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 balancing block 4, Fdr is the inertial centrifugal force of the first balancing 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 secondary bearing 6, Fft is the tangential support reaction force of the secondary bearing 6, Fx is the centrifugal force of the second balancing block 7, and Fxr is the inertial centrifugal force of the second balancing block. Wherein, the subscript r represents radial direction, and t represents tangential direction.

[0071] In order to make the reaction force of the main and auxiliary bearings 5 ​​and 6 as small as possible, let Fz = 0, Ff = 0. According to the above formulas, the inertial centrifugal force of the first and second balancing blocks 4 and 7 can be calculated:

[0072] As shown in Figure 5, L1 is the distance between the first balancing block and the eccentric part of the crankshaft, that is, the axial distance between the first balancing block 4 and the center of mass of the eccentric part of the crankshaft 3, L2 is the distance between the first balancing block and the main bearing; L3 is the distance between the main bearing and the secondary bearing, which is fixed and unchanged, and L4 is the distance between the second balancing block and the secondary bearing.

[0073] Inertial centrifugal force of the first balancing weight 4:

[0074]

[0075] Inertial centrifugal force of the second balancing weight 7:

[0076]

[0077] Solve for the mass of the first balance block 4 m d , the second balance block has a mass of 7 m x :

[0078]

[0079]

[0080] Among them, r dis the eccentric distance of the first balancing block, that is, the radial distance between the center of mass of the first balancing block and the center of mass of the crankshaft, r x is the eccentric distance of the second balancing mass, that is, the radial distance between the mass center of the second balancing mass and the mass center of the crankshaft.

[0081] The initial position of the balancing block is determined according to different structures of different types of scroll compressors during initial design. The mass of the first balancing block 4 and the mass of the second balancing block 7 can be calculated by the above-mentioned mass calculation formula of the first balancing block 4 and the mass calculation formula of the second balancing block 7. Then, when the mass of the first balancing block and the second balancing block is known, according to the above-mentioned mass calculation formula of the second balancing block, the tangential gas force Ft received by the moving disk during actual operation is the value that changes with the main shaft rotation angle α:

[0082]

[0083] Therefore, in order to ensure that the equation still holds true when the mass mx of the second balancing block remains unchanged, if Ft in the right-hand equation increases, L1 must decrease. Since the bearing position remains unchanged, the decrease in L1 is accompanied by the increase in L2. However, it may be difficult to balance only by changing L1 and L2, that is, the change in the position of the first balancing block, so it is necessary to change L4, that is, the position of the second balancing block. Due to the limitation of the design space of the scroll compressor, the axial movable distance of the first and second balancing blocks is not infinite, so this balancing design is only to minimize the impact of dynamic imbalance.

[0084] According to the second balance block mass calculation formula, after the balance block design is completed, the second balance block mass m x is a fixed value m x0 , Ft is a function related to the spindle angle α, set to F(α), -m0ω 2 R0sinαcosα+Fcq and r x ω 2 is a function related to the angular velocity ω, and is set to F1(ω)=-m0ω 2 R0sinαcosα+Fcq,F2(ω)=r x ω 2 .

[0085] L1 is the axial distance between the first balancing block 4 and the mass center of the eccentric portion of the crankshaft 3, (L2+L3+L4) is the axial distance between the mass centers of the first balancing block 4 and the second balancing block 7, and L is the axial distance between the mass center of the eccentric portion of the crankshaft 3, then L2+L3+L4=L-L1, and the mass calculation formula of the second balancing block 7 can be simplified to:

[0086]

[0087] Then we can get the relationship between L1, L and the main axis angle α:

[0088]

[0089] The right side of the equation is a function related to the main shaft angle α, and the left side is the axial distance from the first and second balancing blocks to the center of mass of the eccentric part of the crankshaft. The appropriate value is obtained by calculation, that is, the distance that the first and second balancing blocks should move axially.

[0090] Thus, the main shaft rotation angle α is obtained, and the tangential gas force Ft on the moving plate of the scroll compressor is calculated, that is, the above-mentioned function F(α) related to the main shaft rotation angle is obtained; according to the eccentric mass mcq of the eccentric part of the crankshaft multiplied by the eccentric distance rcq multiplied by the square of the crankshaft angular velocity ω 2 Calculate the centrifugal inertia force generated by the eccentric part of the crankshaft, and then combine the mass m0 of the cross ring, the angular velocity ω of the crankshaft, and the inner diameter R0 of the cross ring to obtain the angular velocity related function F1(ω)=-m0ω 2 R0sinαcosα+Fcq; then according to the eccentric distance of the second balancing block and the crankshaft angular velocity ω, the angular velocity related function F2(ω)=r x ω 2 , and then according to F1(ω), F2(ω) and the mass of the second balancing block, the optimal solution of the axial distance between the first balancing block and the center of mass of the eccentric part of the crankshaft and / or the axial distance L between the second balancing block and the center of mass of the eccentric part of the crankshaft is obtained, and then the position of the first balancing block and / or the position of the second balancing block is obtained, and according to the original position of the first balancing block and / or the original position of the second balancing block, the distance that the first balancing block and / or the second balancing block should be adjusted is obtained.

[0091] Preferably, since the mass of the first balancing block is greater than that of the second balancing block, the position of the first balancing block is kept unchanged when adjusting the position of the balancing block, that is, L1 is a constant, from which the value of L changing with θ can be calculated, thereby obtaining the distance that the second balancing block should be adjusted.

[0092] Based on this, the internal parameters of the scroll compressor that need to be obtained include: the main shaft 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 balancing block, and the eccentric distance of the second balancing block; the internal force data of the scroll compressor that need to be obtained include: the tangential gas on the moving disk of the scroll compressor and the centrifugal inertia force generated by the eccentric part of the crankshaft. Obtain the tangential gas force on the moving disk of the scroll compressor, the centrifugal inertia force generated by the eccentric part of the crankshaft, the main shaft 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 balancing block, and the eccentric distance of the second balancing block; calculate the position of the first balancing block and / or the second balancing block according to the tangential gas force on the moving disk, the centrifugal inertia force generated by the eccentric part of the crankshaft, the main shaft 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 balancing block, and the eccentric distance of the second balancing block.

[0093] The angle between the first balancing block 4 and the eccentric part of the crankshaft 2 (the angle between the line connecting the center of mass of the balancing 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 balancing block 7 and the eccentric part of the crankshaft 2 are as follows:

[0094]

[0095] Figure 6 A schematic diagram of the deflection angles of the first balancing weight 4 and the second balancing weight 7 and the eccentric portion of the crankshaft 2 is shown.

[0096] From the above formula, it can be found that the masses of the first balancing block 4 and the second balancing block 7 are related to the tangential gas force, radial gas force, the relevant parameters of the moving plate 1, the cross slip ring 2, the crankshaft 3, and the position and geometry of the balancing block itself.

[0097] Since the size and shape of most parts of the scroll compressor do not change after it is designed, and the gas force changes with the crankshaft angle, in order to maintain dynamic balance, the first and second balancing blocks must be able to change their positions automatically or semi-automatically.

[0098] Step S130: adjusting the positions of the first balancing weight and the second balancing weight so that the first balancing weight and the second balancing weight are moved to determined positions.

[0099] In a specific embodiment, the first balancing block and the second balancing block are provided with an adjusting device, and the positions of the first balancing block and the second balancing block are adjusted by the adjusting device to move the first balancing block and the second balancing block to a certain position. In a specific embodiment, the adjusting device includes: an electromagnet and a spring.

[0100] Specifically, an electromagnet is fixedly installed on the axial side of the balancing block on the crankshaft and connected to the balancing block with a spring. By adjusting the magnetic force of the electromagnet, the elastic force of the spring will also change to ensure balance, and its length will change, causing the spring to push or pull the balancing block to displace it axially to reach the calculated position.

[0101] The axial position of the balance block is controlled by the electromagnetic spring, that is, the electromagnetic force is controlled to balance the elastic force, so that the radial position of the balance block changes. The change of the axial position of the balance block can affect the dynamic balance, thereby solving the dynamic balance problem caused by the actual gas force change during the operation of the compressor.

[0102] The method of the present invention may also include: after adjusting the first balancing block and the second balancing block, if there are still abnormal noise vibrations, then the adjustment is performed by avoiding the modal resonance point or by modifying the relevant parameters of the driver. For example, the current working state may excite a certain order mode, and if there are still abnormal noise vibrations that cannot be allowed after automatically adjusting the position of the balancing block, the working conditions are appropriately adjusted to ensure that the scroll compressor can maintain a good mechanical balance state. For example, the current working state may excite a certain order mode, so the modal resonance point can be avoided by changing the rotation speed. Or if there is an abnormal frequency of electromagnetic noise, it can be adjusted by modifying the relevant parameters of the driver.

[0103] The invention also provides a vibration regulating device for a scroll compressor.

[0104] The first balancing block and the second balancing block are respectively provided at both ends of the crankshaft of the scroll compressor, which are used for dynamic balancing adjustment of the scroll compressor. The positions of the first balancing block and the second balancing block can be referred to as shown in Figure 5. As shown in Figure 5, a main bearing 5 and a secondary bearing 6 are installed on the crankshaft 3 of the scroll compressor, and a first balancing block 4 and a second balancing block 7 are respectively provided at both ends of the crankshaft 3. The first balancing block 4 is arranged at one end close to the main bearing 5 of the turbine compressor, and the second balancing block 7 is arranged at one end close to the secondary bearing 6 of the turbine compressor, and the first balancing block 4 and the second balancing block 7 can move axially along the crankshaft 3. The mass of the first balancing block is greater than the mass of the second balancing block.

[0105] Figure 7 FIG. 1 is a structural block diagram of an embodiment of a vibration regulating 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 .

[0106] The judgment unit 110 is used to obtain noise and vibration data of the scroll compressor, and judge whether abnormal noise and vibration occur in the scroll compressor according to the noise and vibration data.

[0107] Specifically, the noise and vibration data of the scroll compressor are monitored in real time to determine whether the scroll compressor has abnormal noise and vibration. Specifically, the sensor can be used to capture the first harmonic and harmonic abnormal signals. More specifically, the noise and vibration signals are collected by the sensor, and the time domain signals are converted into frequency domain signals using FFT. By observing the characteristic frequencies of the spectrum, mainly the first harmonic and integer harmonic, it is determined whether there is an abnormality.

[0108] The determination unit 120 is configured to determine the position of the first balancing block and / or the second balancing block according to the internal parameters and force data of the scroll compressor if the determination unit determines that the scroll compressor has abnormal noise and vibration.

[0109] (1) Analysis of gas force correlation

[0110] According to 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 main shaft and the change of the rotation angle. Figure 2 As shown, Figure 2 The relationship curve between the tangential gas force and the main shaft angle is shown.

[0111] The calculation formula for the tangential gas force in the first compression chamber is:

[0112] F t1 =a(4π-2α)h(p1-p2)

[0113] The calculation formula for the tangential gas force in the second compression chamber is:

[0114] F t2 =a(8π-2α)h(p2-p3)

[0115] The calculation formula for the tangential gas force in the i-th compression chamber is:

[0116] F ti =a(4iπ-2α)h(p i -p i+1 )

[0117] Where h is the height of the vortex; p i is the gas pressure in the i-th compression chamber; a is the base circle radius; α is the main axis rotation angle; therefore, when there are N compression chambers, the tangential gas force on the moving disk is:

[0118]

[0119] Where:

[0120] p sis the suction 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 angle (varies with time and is related to the speed), ρ i is the pressure ratio between the two compression chambers ρ N+1 =1; κ is the isentropic index (adiabatic index refers to the index of the reversible adiabatic process of an ideal gas, denoted by κ. Generally speaking, the adiabatic index K of a monatomic gas is 1.66, and the adiabatic index K of a diatomic gas is 1.41); α s Exhaust angle α s =α-2π.

[0121] The radial gas force on the moving disk is mainly related to the exhaust pressure. The radial gas force Fr on the moving disk is:

[0122] F r =2ahp s (ρ1-1)

[0123] a is the base circle radius (mm), p s is the suction pressure (Pa), p d is the exhaust pressure (Pa); ρ1 is the ratio of exhaust pressure to suction pressure, ρ1 = p d / p s ;

[0124] (2) Force analysis of the moving disk:

[0125] The main forces acting on the moving disk 1 include the tangential gas force Ft, the radial gas force Fr, the centrifugal inertia force Fc, the force Fs exerted by the eccentric part of the crankshaft 3 on the moving disk 1, and the forces F1 and F2 exerted by the cross ring 2 on the moving disk 1. The angle between the radial gas force and the cross ring 2 in the x direction is θ (variable), m0 is the mass of the cross ring 2, Fsr is the radial force exerted by the eccentric part of the crankshaft 3 on the moving disk 1, and Fst is the axial force exerted by the eccentric part of the crankshaft 3 on the moving disk 1. For details, please refer to 3a, 3b, and 3c. Figure 3a The figure shows the radial force diagram of the moving disk. Figure 3b The figure shows the schematic diagram of the tangential force of the moving disk. Figure 3c A top view of the force on the moving plate is shown.

[0126] Radial direction: F c -F r +(F1-F2)sinθ-F sr =0

[0127] Tangential direction: -F t +(F1-F2)cosθ+F st =0

[0128] (3) Force analysis of cross slip ring

[0129] Figure 4 The force diagram of the cross slip ring is shown. Figure 4 The figure shows the force on the cross ring 2 that reciprocates in the y direction (friction is not considered, and the compressor is a vertical structure and gravity is not considered). The force acting on the moving plate 1 by the cross ring 2 is F1 and F2, and the motion equation is:

[0130] The force balance in the y direction is

[0131] in,

[0132] The radial force Fsr of the eccentric part of the crankshaft 3 on the moving plate 1 is obtained as follows:

[0133] F sr =F c -F r +m0ω 2 R o sin 2 θ

[0134] The axial force Fst of the eccentric part of the crankshaft 3 on the moving plate 1 is obtained as:

[0135] F st =F t -m0ω 2 R o sinθcosθ

[0136] (4) Force analysis of crankshaft 3

[0137] The stress analysis of crankshaft 3 is as follows: Figure 5a , Figure 5b As shown, Figure 5a The radial force diagram of the crankshaft is shown. Figure 5b The diagram shows the tangential force of the crankshaft. Fs is the force of the eccentric part of the crankshaft 3 on the moving disk 1 (calculated by the tangential radial gas force in the above formula), and Fcq is the centrifugal inertia force generated by the eccentric part of the crankshaft 3, which is equal to the eccentric mass mcq of the eccentric part of the crankshaft multiplied by the eccentric distance rcq and then multiplied by the square of the angular velocity of the crankshaft ω 2 , that is, Fcq = mcq·rcq·ω 2 , where the eccentric 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 balancing block 4, Fdr is the inertial centrifugal force of the first balancing 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 secondary bearing 6, Fft is the tangential support reaction force of the secondary bearing 6, Fx is the centrifugal force of the second balancing block 7, and Fxr is the inertial centrifugal force of the second balancing block. Wherein, the subscript r represents radial direction, and t represents tangential direction.

[0138] In order to make the reaction force of the main and auxiliary bearings 5 ​​and 6 as small as possible, let Fz = 0, Ff = 0. According to the above formulas, the inertial centrifugal force of the first and second balancing blocks 4 and 7 can be calculated:

[0139] As shown in Figure 5, L1 is the distance between the first balancing block and the eccentric part of the crankshaft, that is, the axial distance between the first balancing block 4 and the center of mass of the eccentric part of the crankshaft 3, L2 is the distance between the first balancing block and the main bearing; L3 is the distance between the main bearing and the secondary bearing, which is fixed and unchanged, and L4 is the distance between the second balancing block and the secondary bearing.

[0140] Inertial centrifugal force of the first balancing weight 4:

[0141]

[0142] Inertial centrifugal force of the second balancing weight 7:

[0143]

[0144] Solve for the mass of the first balance block 4 m d , the second balance block has a mass of 7 m x :

[0145]

[0146]

[0147] Among them, r d is the eccentric distance of the first balancing block, that is, the radial distance between the center of mass of the first balancing block and the center of mass of the crankshaft, r x is the eccentric distance of the second balancing mass, that is, the radial distance between the mass center of the second balancing mass and the mass center of the crankshaft.

[0148] The initial position of the balancing block is determined according to different structures of different types of scroll compressors during initial design. The mass of the first balancing block 4 and the mass of the second balancing block 7 can be calculated by the above-mentioned mass calculation formula of the first balancing block 4 and the mass calculation formula of the second balancing block 7. Then, when the masses of the first balancing block and the second balancing block are known, according to the above-mentioned mass calculation formula of the second balancing block, the tangential gas force Ft received by the moving disk during actual operation is the value that changes with the main shaft rotation angle α:

[0149]

[0150] Therefore, in order to ensure that the equation still holds true when the mass mx of the second balancing block remains unchanged, if Ft in the right-hand equation increases, L1 must decrease. Since the bearing position remains unchanged, the decrease in L1 is accompanied by the increase in L2. However, it may be difficult to balance only by changing L1 and L2, that is, the change in the position of the first balancing block, so it is necessary to change L4, that is, the position of the second balancing block. Due to the limitation of the design space of the scroll compressor, the axial movable distance of the first and second balancing blocks is not infinite, so this balancing design is only to minimize the impact of dynamic imbalance.

[0151] According to the second balance block mass calculation formula, after the balance block design is completed, the second balance block mass m x is a fixed value m x0 , Ft is a function related to the spindle angle α, set to F(α), -m0ω 2 R0sinαcosα+Fcq and r x ω 2 is a function related to the angular velocity ω, and is set to F1(ω)=-m0ω 2 R0sinαcosα+Fcq,F2(ω)=r x ω 2 .

[0152] L1 is the axial distance between the first balancing block 4 and the mass center of the eccentric portion of the crankshaft 3, (L2+L3+L4) is the axial distance between the mass centers of the first balancing block 4 and the second balancing block 7, and L is the axial distance between the mass center of the eccentric portion of the crankshaft 3, then L2+L3+L4=L-L1, and the mass calculation formula of the second balancing block 7 can be simplified to:

[0153]

[0154] Then we can get the relationship between L1, L and the main axis angle α:

[0155]

[0156] The right side of the equation is a function related to the main shaft angle α, and the left side is the axial distance from the first and second balancing blocks to the center of mass of the eccentric part of the crankshaft. The appropriate value is obtained by calculation, that is, the distance that the first and second balancing blocks should move axially.

[0157] Thus, the main shaft rotation angle α is obtained, and the tangential gas force Ft on the moving plate of the scroll compressor is calculated, that is, the above-mentioned function F(α) related to the main shaft rotation angle is obtained; according to the eccentric mass mcq of the eccentric part of the crankshaft multiplied by the eccentric distance rcq multiplied by the square of the crankshaft angular velocity ω 2 Calculate the centrifugal inertia force generated by the eccentric part of the crankshaft, and then combine the mass m0 of the cross ring, the angular velocity ω of the crankshaft, and the inner diameter R0 of the cross ring to obtain the angular velocity related function F1(ω)=-m0ω2 R0sinαcosα+Fcq; then according to the eccentric distance of the second balancing block and the crankshaft angular velocity ω, the angular velocity related function F2(ω)=r x ω 2 , and then according to F1(ω), F2(ω) and the mass of the second balancing block, the optimal solution of the axial distance between the first balancing block and the center of mass of the eccentric part of the crankshaft and / or the axial distance L between the second balancing block and the center of mass of the eccentric part of the crankshaft is obtained, and then the position of the first balancing block and / or the position of the second balancing block is obtained, and according to the original position of the first balancing block and / or the original position of the second balancing block, the distance that the first balancing block and / or the second balancing block should be adjusted is obtained.

[0158] Preferably, since the mass of the first balancing block is greater than that of the second balancing block, the position of the first balancing block is kept unchanged when adjusting the position of the balancing block, that is, L1 is a constant, from which the value of L changing with θ can be calculated, thereby obtaining the distance that the second balancing block should be adjusted.

[0159] Based on this, the internal parameters of the scroll compressor that need to be obtained include: the main shaft 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 balancing block, and the eccentric distance of the second balancing block; the internal force data of the scroll compressor that need to be obtained include: the tangential gas on the moving disk of the scroll compressor and the centrifugal inertia force generated by the eccentric part of the crankshaft. Obtain the tangential gas force on the moving disk of the scroll compressor, the centrifugal inertia force generated by the eccentric part of the crankshaft, the main shaft 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 balancing block, and the eccentric distance of the second balancing block; calculate the position of the first balancing block and / or the second balancing block according to the tangential gas force on the moving disk, the centrifugal inertia force generated by the eccentric part of the crankshaft, the main shaft 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 balancing block, and the eccentric distance of the second balancing block.

[0160] The angle between the first balancing block 4 and the eccentric part of the crankshaft 2 (the angle between the line connecting the center of mass of the balancing 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 balancing block 7 and the eccentric part of the crankshaft 2 are as follows:

[0161]

[0162] Figure 6 A schematic diagram of the deflection angles of the first balancing weight 4 and the second balancing weight 7 and the eccentric portion of the crankshaft 2 is shown.

[0163] From the above formula, it can be found that the masses of the first balancing block 4 and the second balancing block 7 are related to the tangential gas force, radial gas force, the relevant parameters of the moving plate 1, the cross slip ring 2, the crankshaft 3, and the position and geometry of the balancing block itself.

[0164] Since the size and shape of most parts of the scroll compressor do not change after it is designed, and the gas force changes with the crankshaft angle, in order to maintain dynamic balance, the first and second balancing blocks must be able to change their positions automatically or semi-automatically.

[0165] The adjusting unit 130 is used to adjust the positions of the first balancing weight and the second balancing weight so that the first balancing weight and the second balancing weight are moved to determined positions.

[0166] In a specific embodiment, the first balancing block and the second balancing block are provided with an adjusting device, and the positions of the first balancing block and the second balancing block are adjusted by the adjusting device to move the first balancing block and the second balancing block to a certain position. In a specific embodiment, the adjusting device includes: an electromagnet and a spring.

[0167] Specifically, an electromagnet is fixedly installed on the axial side of the balancing block on the crankshaft and connected to the balancing block with a spring. By adjusting the magnetic force of the electromagnet, the elastic force of the spring will also change to ensure balance, and its length will change, causing the spring to push or pull the balancing block to displace it axially to reach the calculated position.

[0168] The axial position of the balance block is controlled by the electromagnetic spring, that is, the electromagnetic force is controlled to balance the elastic force, so that the radial position of the balance block changes. The change of the axial position of the balance block can affect the dynamic balance, thereby solving the dynamic balance problem caused by the actual gas force change during the operation of the compressor.

[0169] The adjustment unit is also used for: after adjusting the first balancing block and the second balancing block, if there are still abnormal noise and vibration, then the adjustment is performed by avoiding the modal resonance point or by modifying the relevant parameters of the driver. For example, the current working state may excite a certain order mode. If there are still abnormal noise and vibration that cannot be allowed after automatically adjusting the position of the balancing block, the working condition is appropriately adjusted to ensure that the scroll compressor can maintain a good mechanical balance state. For example, the current working state may excite a certain order mode, so the modal resonance point can be avoided by changing the speed. Or if there is an abnormal frequency of electromagnetic noise, it can be adjusted by modifying the relevant parameters of the driver.

[0170] The present invention also provides a storage medium corresponding to the vibration regulation method of the scroll compressor, on which a computer program is stored, and when the computer program is executed by a processor, the steps of any of the aforementioned methods are implemented.

[0171] 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 and executable on the processor, wherein the processor implements the steps of any of the aforementioned methods when executing the computer program.

[0172] The present invention also provides a controller corresponding to the vibration regulating device of the scroll compressor, comprising any of the aforementioned vibration regulating devices.

[0173] The present invention also provides a computer program product corresponding to the vibration regulation method of the scroll compressor, comprising a computer program, and when the computer program is executed by a processor, the steps of any of the aforementioned methods are implemented.

[0174] Based on this, the solution provided by the present invention achieves the greatest possible approach to the ideal dynamic balance and realizes vibration and noise reduction by real-time monitoring of the noise, vibration and force data of the scroll compressor and adjusting the position and angle of the balancing block through calculation and analysis.

[0175] According to the technical solution of the present invention, the position and angle of the balancing block that the current scroll compressor should be in in order to meet the dynamic balance state are calculated, the position of the balancing block is automatically or semi-automatically adjusted, and the dynamic balance is optimized in real time.

[0176] According to the technical solution of the present invention, it is possible to effectively reduce the abnormal noise and vibration problems caused by failure to effectively achieve dynamic balancing, especially the dynamic balancing problems that are difficult to handle due to the time-varying characteristics of gas forces. At the same time, due to real-time monitoring, it is possible to effectively avoid the resonance phenomenon that may be excited under certain working conditions, timely discover abnormal problems and feedback processing, and avoid abnormal working or failures that reduce the service life.

[0177] According to the technical solution of the present invention, sensors are used to capture the noise and vibration signals of the scroll compressor and related force information such as gas force in real time, and an algorithm is used to calculate the reasonable range of the position and deflection angle of the balancing block of the current dynamic balance state of the scroll compressor, and the noise and vibration data obtained are used to determine whether there are abnormal noise and vibration conditions, such as exciting a certain order mode to produce resonance.

[0178] According to the technical solution of the present invention, an automatic or semi-automatic adjustment device such as an electromagnet-spring structure is used to adjust the position or angle of the balancing weight.

[0179] The functions described herein may be implemented in hardware, software executed by a processor, firmware, or any combination thereof. If implemented in software executed by a processor, the functions may be stored as one or more instructions or codes on a computer-readable medium or transmitted via a computer-readable medium. Other examples and implementations are within the scope and spirit of the present invention and the appended claims. For example, due to the nature of software, the functions described above may be implemented using software executed by a processor, hardware, firmware, hard wiring, or a combination of any of these. In addition, each functional unit may be integrated into a processing unit, each unit may exist physically separately, or two or more units may be integrated into one unit.

[0180] In the several embodiments provided in this application, it should be understood that the disclosed technical content can be implemented in other ways. Among them, the device embodiments described above are only schematic. For example, the division of the units can be a logical function division. There may be other division methods in actual implementation. For example, multiple units or components can be combined or integrated into another system, or some features can be ignored or not executed. Another point is that the mutual coupling or direct coupling or communication connection shown or discussed can be through some interfaces, indirect coupling or communication connection of units or modules, which can be electrical or other forms.

[0181] The units described as separate components may or may not be physically separated, and the components of the control device may or may not be physical units, that is, they may be located in one place or distributed in multiple units. Some or all of the units may be selected according to actual needs to achieve the purpose of the present embodiment.

[0182] If the integrated unit is implemented in the form of 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 the relevant technology or all or part of the technical solution can be embodied in the form of a software product, and the computer software product is stored in a storage medium, including a number of instructions to enable a computer device (which can be a personal computer, a server or a network device, etc.) to perform all or part of the steps of the method described in each embodiment of the present invention. The aforementioned storage medium includes: U disk, read-only memory (ROM, Read-Only Memory), random access memory (RAM, Random Access Memory), mobile hard disk, disk or optical disk and other media that can store program codes.

[0183] The above description is only an embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent substitution, improvement, etc. made within the spirit and principle of the present invention shall be included in the scope of the claims of the present invention.

Claims

1. A method for adjusting the vibration of a scroll compressor, characterized in that: include: A first balancing block and a second balancing block are respectively provided at both ends of the crankshaft of the scroll compressor; the first balancing block is provided at one end close to the main bearing of the turbo compressor, and the second balancing block is provided at one end close to the secondary bearing of the turbo compressor, and the first balancing block and the second balancing block can move axially along the crankshaft; The vibration adjustment method comprises: Acquiring noise and vibration data of the scroll compressor, and determining whether abnormal noise and vibration occur in the scroll compressor according to the noise and vibration data; If it is determined that the scroll compressor has abnormal noise and vibration, the position of the first balancing block and / or the second balancing block is determined according to the internal parameters and force data of the scroll compressor; The position of the first balancing weight and / or the second balancing weight is adjusted to move the first balancing weight and / or the second balancing weight to a determined position.

2. The method according to claim 1, characterized in that The internal parameters of the scroll compressor include: 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 balancing block, and the eccentric distance of the second balancing block; the internal force data of the scroll compressor include: the centrifugal inertia force generated by the tangential gas and the eccentric part of the crankshaft on the dynamic plate of the scroll compressor; Determining the position of the first balancing block and / or the second balancing block according to the internal parameters and force data of the scroll compressor includes: Obtaining the tangential gas force on the moving plate of the scroll compressor, the centrifugal inertia force generated by the eccentric portion of the crankshaft, the main shaft rotation angle, the crankshaft angular velocity, the inner diameter of the cross ring, the mass of the cross ring, the mass of the second balancing block, and the eccentric distance of the second balancing block; Calculating the position of the first balancing block and / or the position of the second balancing block according to the acquired tangential gas force on the moving plate, the centrifugal inertia force generated by the eccentric part of the crankshaft, the main shaft rotation angle, the crankshaft angular velocity, the inner diameter of the cross ring, the mass of the cross ring, the mass of the second balancing block, and the eccentric distance of the second balancing block; The position of the first balancing block includes: an axial distance between the first balancing block and the mass center of the eccentric portion of the crankshaft; the position of the second balancing block includes: an axial distance between the second balancing block and the mass center of the eccentric portion of the crankshaft.

3. The method according to claim 1 or 2, characterized in that: The first balancing block and / or the second balancing block are provided with an adjusting device, which adjusts the position of the first balancing block and / or the second balancing block so that the first balancing block and / or the second balancing block moves to a determined position, including: The position of the first balancing weight and / or the second balancing weight is adjusted by the adjusting device so that the first balancing weight and / or the second balancing weight is moved to a determined position.

4. The method according to claim 3, characterized in that: The regulating device comprises an electromagnet and a spring.

5. A vibration regulating device for a scroll compressor, characterized in that: include: A first balancing block and a second balancing block are respectively provided at both ends of the crankshaft of the scroll compressor; the first balancing block is provided at one end close to the main bearing of the turbo compressor, and the second balancing block is provided at one end close to the secondary bearing of the turbo compressor, and the first balancing block and the second balancing block can move axially along the crankshaft; The vibration adjustment device comprises: a judgment unit, configured to obtain noise and vibration data of the scroll compressor, and judge whether abnormal noise and vibration occur in the scroll compressor according to the noise and vibration data; a determination unit, configured to determine the position of the first balancing block and / or the second balancing block according to internal parameters and force data of the scroll compressor if the determination unit determines that the scroll compressor has abnormal noise and vibration; The adjusting unit is used to adjust the position of the first balancing weight and / or the second balancing weight so as to move the first balancing weight and / or the second balancing weight to a determined position.

6. The device according to claim 5, characterized in that The internal parameters of the scroll compressor include: 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 balancing block, and the eccentric distance of the second balancing block; the internal force data of the scroll compressor include: the centrifugal inertia force generated by the tangential gas and the eccentric part of the crankshaft on the dynamic plate of the scroll compressor; The determining unit determines the position of the first balancing block and / or the second balancing block according to the internal parameters and force data of the scroll compressor, including: Obtaining the tangential gas force on the moving plate of the scroll compressor, the centrifugal inertia force generated by the eccentric portion of the crankshaft, the main shaft rotation angle, the crankshaft angular velocity, the inner diameter of the cross ring, the mass of the cross ring, the mass of the second balancing block, and the eccentric distance of the second balancing block; Calculating the position of the first balancing mass and / or the second balancing mass according to the acquired tangential gas force on the moving plate, the centrifugal inertia force generated by the eccentric portion of the crankshaft, the main shaft rotation angle, the crankshaft angular velocity, the inner diameter of the cross ring, the mass of the cross ring, the mass of the second balancing mass, and the eccentric distance of the second balancing mass; The position of the first balancing block includes: an axial distance between the first balancing block and the center of mass of the eccentric portion of the crankshaft; the position of the second balancing block includes: an axial distance between the second balancing block and the eccentric portion of the crankshaft.

7. The method according to claim 5 or 6, characterized in that: The first balancing block and / or the second balancing block are provided with an adjusting device, which adjusts the position of the first balancing block and / or the second balancing block so that the first balancing block and / or the second balancing block moves to a determined position, including: The position of the first balancing weight and / or the second balancing weight is adjusted by the adjusting device so that the first balancing weight and / or the second balancing weight is moved to a determined position.

8. A storage medium, characterized in that: A computer program is stored thereon, and when the program is executed by a processor, the steps of any method described in claims 1-4 are implemented.

9. A controller, characterized in that: The invention comprises a processor, a memory and a computer program stored in the memory and executable on the processor, wherein when the processor executes the program, the steps of the method described in any one of claims 1 to 4 are implemented, including a vibration regulating device for a scroll compressor described in any one of claims 5 to 7.

10. A computer program product, characterized in that The invention comprises a computer program, which implements the steps of the method according to any one of claims 1 to 4 when being executed by a processor.

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