Stator tooth labyrinth seal design gap determination method, compressor and PDH device

Abstract

The invention provides a stator tooth labyrinth seal design gap determination method, a compressor and a PDH device. The method comprises the steps that the numerical range of an inter-stage seal gap is selected; an interstage minimum sealing gap allowable value is obtained; the amplitude of the interstage sealing position is obtained; on the basis of the interstage minimum sealing gap allowable value and the amplitude of the interstage sealing position, whether the numerical range of the interstage sealing gap meets the requirement or not is verified; selecting a numerical range of an impeller wear ring sealing gap; obtaining an allowable value of the minimum sealing gap of the impeller wear ring; the amplitude of the impeller wear ring sealing position is obtained; the radial deformation of the impeller wear ring sealing position is obtained; and based on the allowable value of the minimum sealing gap of the impeller wear-ring, the amplitude of the sealing position of the impeller wear-ring and the radial deformation of the sealing position of the impeller wear-ring, verifying whether the numerical range of the sealing gap of the impeller wear-ring meets the requirement or not. A stator tooth labyrinth seal design gap can be accurately determined, and faults of a rotor and a stator are avoided; and meanwhile, the pneumatic efficiency of the compressor is ensured.

Description

Technical Field

[0001] This application belongs to the technical field of compressors, and particularly relates to a method for determining the design clearance of a stator tooth labyrinth seal, a compressor, and a PDH device. Background Art

[0002] The compressors used in propane dehydrogenation to propylene (hereinafter referred to as PDH) are mainly ultra-large heavy-duty product gas compressors, propylene compressors, and ethylene compressors. With the continuous development of PDH compressor units towards high production and large-scale, during the product design process, especially when the rotor of the product gas compressor is relatively heavy, the design difficulty, especially the design of the seal clearance, is very high in the structural design.

[0003] Sealing is an important structure of fluid machinery, and its function is to reduce or prevent the leakage of process gas, ensure the high-quality and efficient operation of the unit, reduce energy consumption, prevent environmental pollution, and ensure personal and equipment safety. The most commonly used seal form in compressors is the stator tooth labyrinth seal. The schematic diagram of the seal position is as Figure 1 shown. Based on the different seal positions, it can generally be divided into impeller gland seal, inter-stage seal, and balance disk seal.

[0004] Analyzing from the root cause, the rotor vibration is relatively large, mainly because the rotor is heavy, especially the amplitude at the center position of the span is relatively large. At this time, the clearance between the rotor and the stator seal will become smaller and smaller. If the designed seal clearance is small, when the rotor flexes, is eccentric, or undergoes whirling, the clearance value between the stator seal and the rotor will be further reduced. When the rotor vibration is too large, it will cause rubbing between the rotor and the stator, resulting in failures of the rotor and stator. If the designed seal clearance is too large, the gas leakage will increase, which will reduce the pneumatic efficiency of the unit. Therefore, for PDH compressor units with heavy rotors, the seal clearances calculated by relevant design schemes can no longer meet the standard requirements. Summary of the Invention

[0005] Therefore, the purpose of this application is to provide a method for determining the design clearance of a centrifugal compressor stator tooth labyrinth seal and a PDH device, which can at least solve one technical problem existing in the prior art.

[0006] To solve the above problems, the first aspect of this application provides a method for determining the design clearance of a stator tooth labyrinth seal, including:

[0007] Determination of the numerical range of the inter-stage seal clearance

[0008] Select the numerical range of the inter-stage seal clearance; obtain the allowable value of the minimum inter-stage seal clearance; obtain the amplitude of the inter-stage seal position;

[0009] Based on the allowable value of the minimum inter-stage seal clearance and the amplitude of the inter-stage seal position, verify whether the numerical range of the inter-stage seal clearance meets the requirements;

[0010] Determination of the numerical range of the impeller shroud seal clearance

[0011] Select the numerical range of the impeller shroud seal clearance; obtain the allowable value of the minimum seal clearance of the impeller shroud; obtain the amplitude of the impeller shroud seal position; obtain the radial deformation of the impeller shroud seal position;

[0012] Based on the allowable value of the minimum seal clearance of the impeller shroud, the amplitude of the impeller shroud seal position, and the radial deformation of the impeller shroud seal position, verify whether the numerical range of the impeller shroud seal clearance meets the requirements.

[0013] Optionally, obtain the allowable value of the minimum inter-stage seal clearance, specifically including:

[0014] The numerical range of the inter-stage seal clearance includes the minimum inter-stage seal clearance value, and the allowable value of the minimum inter-stage seal clearance is calculated based on the minimum inter-stage seal clearance value.

[0015] Optionally, obtain the amplitude of the inter-stage seal position, specifically including:

[0016] Based on the unbalance excitation of the rotor, analyze the unbalance response of the rotor to obtain the amplitude of the inter-stage seal position.

[0017] Optionally, based on the allowable value of the minimum inter-stage seal clearance and the amplitude of the inter-stage seal position, verify whether the numerical range of the inter-stage seal clearance meets the requirements, specifically including:

[0018] Compare the amplitude of the inter-stage seal position with the allowable value of the minimum inter-stage seal clearance; if the amplitude of the inter-stage seal position is greater than the allowable value of the minimum inter-stage seal clearance, further increase the minimum inter-stage seal clearance value of the numerical range of the inter-stage seal clearance.

[0019] Optionally, obtain the allowable value of the minimum impeller shroud seal clearance, specifically including:

[0020] The numerical range of the impeller shroud seal clearance includes the minimum impeller shroud seal clearance value, and the allowable value of the minimum impeller shroud seal clearance is calculated based on the minimum impeller shroud seal clearance value.

[0021] Optionally, obtain the amplitude of the impeller shroud seal position, specifically including:

[0022] Based on the unbalance excitation of the rotor, analyze the unbalance response of the rotor to obtain the amplitude of the impeller shroud seal position.

[0023] Optionally, obtain the radial deformation of the impeller shroud seal position, specifically including:

[0024] Perform a deformation analysis on the impeller under the action of centrifugal force to obtain the radial deformation amount at the seal position of the impeller mouth ring.

[0025] Optionally, based on the allowable value of the minimum seal clearance of the impeller mouth ring, the amplitude at the seal position of the impeller mouth ring, and the radial deformation amount at the seal position of the impeller mouth ring, verify whether the numerical range of the seal clearance of the impeller mouth ring meets the requirements, specifically including:

[0026] Compare the allowable value of the minimum seal clearance of the impeller mouth ring with the sum of the amplitude at the seal position of the impeller mouth ring and the radial deformation amount at the seal position of the impeller mouth ring; if the sum of the amplitude at the seal position of the impeller mouth ring and the radial deformation amount at the seal position of the impeller mouth ring is greater than the allowable value of the minimum seal clearance of the impeller mouth ring, then further increase the minimum seal clearance value of the numerical range of the seal clearance of the impeller mouth ring.

[0027] The second aspect of the present application provides a compressor, which is processed according to the stator tooth labyrinth seal design clearance determination method described in any one of the above.

[0028] The third aspect of the present application provides a PDH device, including the compressor described above.

[0029] By means of the above technical solutions, the invention of the present application has at least the following beneficial effects:

[0030] A stator tooth labyrinth seal design clearance determination method provided by an embodiment of the present application can accurately determine the stator tooth labyrinth seal design clearance by determining the numerical range of the inter-stage seal clearance and the numerical range of the impeller mouth ring seal clearance, so that rubbing between the rotor and stator does not occur at the seal position, avoiding rotor-stator failures; at the same time, the gas leakage amount is not increased at the seal position, ensuring the pneumatic efficiency of the compressor. Description of the Drawings

[0031] Figure 1 It is a schematic diagram of different seal positions of the stator teeth of a centrifugal compressor. Detailed Embodiments

[0032] In the description of the present application, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present invention.

[0033] In addition, the terms "first" and "second" are only used for descriptive purposes and should not be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, "a plurality of" means two or more unless otherwise specifically defined.

[0034] In this application, unless otherwise clearly specified and defined, terms such as "installed", "connected", "connected to", "fixed", etc. should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0035] The preferred embodiments of the present invention will be described below in conjunction with the accompanying drawings. It should be understood that the preferred embodiments described herein are only for the purpose of illustrating and explaining the present invention and are not used to limit the present invention.

[0036] According to the first aspect of the embodiments of the present application, a method for determining the design clearance of a stator tooth labyrinth seal is provided, including:

[0037] Step S1, determination of the numerical range of the inter-stage seal clearance

[0038] Step S11, select the numerical range of the inter-stage seal clearance; obtain the allowable value of the minimum inter-stage seal clearance; obtain the amplitude of the inter-stage seal position;

[0039] Step S12, based on the allowable value of the minimum inter-stage seal clearance and the amplitude of the inter-stage seal position, verify whether the numerical range of the inter-stage seal clearance meets the requirements;

[0040] Step S2, determination of the numerical range of the impeller shroud seal clearance

[0041] Step S21, select the numerical range of the impeller shroud seal clearance; obtain the allowable value of the minimum impeller shroud seal clearance; obtain the amplitude of the impeller shroud seal position; obtain the radial deformation amount of the impeller shroud seal position;

[0042] Step S22, based on the allowable value of the minimum impeller shroud seal clearance, the amplitude of the impeller shroud seal position, and the radial deformation amount of the impeller shroud seal position, verify whether the numerical range of the impeller shroud seal clearance meets the requirements.

[0043] By determining the numerical range of the inter-stage seal clearance and the numerical range of the impeller shroud seal clearance, the design clearance of the stator tooth labyrinth seal can be accurately determined, preventing rubbing between the rotor and stator at the seal position and avoiding rotor-stator failures. At the same time, the gas leakage rate is not increased at the seal position, ensuring the pneumatic efficiency of the compressor.

[0044] Furthermore, select the numerical range of the inter-stage seal clearance. That is, the numerical range of the inter-stage seal clearance preliminarily selected according to the product design specifications. This numerical range includes two endpoints, and the smaller endpoint is the minimum inter-stage seal clearance value.

[0045] Furthermore, obtain the allowable value of the minimum inter-stage seal clearance. That is, to ensure that there is no friction between the rotor and stator during rotor operation, it is necessary to check the selected minimum inter-stage seal clearance value. Therefore, based on the requirements specified in API617 standard, the allowable value of the minimum inter-stage seal clearance should be 75% of the minimum inter-stage seal clearance value.

[0046] Furthermore, select the numerical range of the impeller shroud seal clearance. That is, the numerical range of the impeller shroud seal clearance preliminarily selected according to the product design specifications. This numerical range includes two endpoints, and the smaller endpoint is the minimum impeller shroud seal clearance value.

[0047] Furthermore, obtain the allowable value of the minimum impeller shroud seal clearance. That is, to ensure that there is no friction between the rotor and stator during rotor operation, it is necessary to check the selected minimum impeller shroud seal clearance value. Therefore, based on the requirements specified in API617 standard, the allowable value of the minimum impeller shroud seal clearance should be 75% of the minimum impeller shroud seal clearance value.

[0048] Obtain the allowable value of the minimum inter-stage seal clearance, which specifically includes:

[0049] The numerical range of the inter-stage seal clearance includes the minimum inter-stage seal clearance value, and the allowable value of the minimum inter-stage seal clearance is calculated based on the minimum inter-stage seal clearance value.

[0050] Furthermore, calculate the allowable value of the minimum inter-stage seal clearance based on the minimum inter-stage seal clearance value. That is, by calculating 75% of the minimum inter-stage seal clearance value, the allowable value of the minimum inter-stage seal clearance can be obtained to ensure that an accurate numerical range of the inter-stage seal clearance can be designed.

[0051] Obtain the amplitude at the inter-stage seal position, which specifically includes:

[0052] Analyze the unbalanced response of the rotor based on the unbalanced excitation of the rotor to obtain the amplitude at the inter-stage seal position.

[0053] Furthermore, after all rotors are processed and manufactured, there will be machining errors, that is, the center of gravity of the rotor will not be located on the center line of the rotating shaft, which is usually referred to as the unbalance of the rotor. If the unbalance is large, the amplitude generated during the operation of the rotor will be large; if the unbalance is small, the amplitude generated during the operation of the rotor will be small.

[0054] Therefore, to simulate the influence of unbalance on the vibration of the rotor, it is necessary to apply the unbalance to a certain position of the rotor analysis model (applied to the center of the rotor span in this embodiment), and then through the unbalance response analysis, the vibration amplitude of each point of the rotor under the action of this unbalance can be obtained, that is, the amplitude at the inter-stage seal position can be obtained.

[0055] Verify whether the numerical range of the inter-stage seal clearance meets the requirements based on the allowable value of the minimum inter-stage seal clearance and the amplitude at the inter-stage seal position, specifically including:

[0056] Compare the amplitude at the inter-stage seal position with the allowable value of the minimum inter-stage seal clearance; if the amplitude at the inter-stage seal position is greater than the allowable value of the minimum inter-stage seal clearance, then further increase the minimum inter-stage seal clearance value in the numerical range of the inter-stage seal clearance.

[0057] Furthermore, by comparing the amplitude at the inter-stage seal position with the allowable value of the minimum inter-stage seal clearance, it is judged whether the minimum inter-stage seal clearance value in the numerical range of the inter-stage seal position meets the requirements. In the actual working process, once the minimum inter-stage seal clearance value cannot meet the requirements, it will lead to the rubbing of the rotor and stator and cause failures. Therefore, it is necessary to verify the minimum inter-stage seal clearance value in the numerical range of the inter-stage seal position here.

[0058] In the process of numerical comparison, two situations will occur:

[0059] First, the amplitude at the inter-stage seal position is greater than the allowable value of the minimum inter-stage seal clearance. Here, it means that the minimum inter-stage seal clearance value in the numerical range of the inter-stage seal position does not meet the requirements. Therefore, it is necessary to further increase the minimum inter-stage seal clearance value in the numerical range of the inter-stage seal clearance to determine the numerical range of the inter-stage seal clearance (that is, the inter-stage seal design clearance).

[0060] Specifically, the amplitude value can be less than 0.75 times the improved minimum inter-stage seal clearance value.

[0061] Second, the amplitude at the inter-stage seal position is less than the allowable value of the minimum inter-stage seal clearance. Here, it means that the minimum inter-stage seal clearance value in the numerical range of the inter-stage seal position meets the requirements, and there is no need to further adjust the minimum inter-stage seal clearance value in the numerical range of the inter-stage seal clearance.

[0062] Obtain the allowable value of the minimum seal clearance of the impeller mouth ring, specifically including:

[0063] The numerical range of the impeller shroud seal clearance includes the minimum impeller shroud seal clearance value, and the allowable value of the minimum impeller shroud seal clearance is calculated based on the minimum impeller shroud seal clearance value.

[0064] Furthermore, the allowable value of the minimum impeller shroud seal clearance is calculated based on the minimum impeller shroud seal clearance value. That is to say, by calculating 75% of the minimum impeller shroud seal clearance value, the allowable value of the minimum impeller shroud seal clearance can be obtained to ensure that an accurate numerical range of the impeller shroud seal clearance can be designed.

[0065] Obtain the amplitude of the impeller shroud seal position, specifically including:

[0066] Based on the unbalance excitation of the rotor, analyze the unbalance response of the rotor to obtain the amplitude of the impeller shroud seal position.

[0067] Furthermore, for both the amplitude of the impeller shroud seal position and the vibration of the inter-stage seal position, they both rely on the rotation of the rotor and the application of an eccentricity excitation at the center of the rotor span. Only the values of the amplitudes of the two impeller shroud seal positions and the inter-stage seal position are different. Therefore, the specific principle is not elaborated here.

[0068] Obtain the radial deformation of the impeller shroud seal position, specifically including:

[0069] Conduct a deformation analysis of the impeller under the action of centrifugal force to obtain the radial deformation of the impeller shroud seal position.

[0070] Furthermore, the specific principle of obtaining the radial deformation:

[0071] Build an impeller model in the simulation software in a one-to-one manner; apply the actual rotational speed, impeller material, working temperature, and contact conditions with the rotor in the simulation software, and conduct a simulation analysis on the impeller model; through the simulation analysis, obtain the radial deformation of each position under the working conditions of the impeller; after the analysis is completed, only extract the radial deformation of the impeller shroud seal position.

[0072] Based on the allowable value of the minimum impeller shroud seal clearance, the amplitude of the impeller shroud seal position, and the radial deformation of the impeller shroud seal position, verify whether the numerical range of the impeller shroud seal clearance meets the requirements, specifically including:

[0073] Compare the allowable value of the minimum impeller shroud seal clearance with the sum of the amplitude of the impeller shroud seal position and the radial deformation of the impeller shroud seal position; if the sum of the amplitude of the impeller shroud seal position and the radial deformation of the impeller shroud seal position is greater than the allowable value of the minimum impeller shroud seal clearance, then further increase the minimum value of the numerical range of the impeller shroud seal clearance.

[0074] Further, by comparing the allowable value of the minimum sealing clearance of the impeller mouth ring with the sum of the amplitude at the sealing position of the impeller mouth ring and the radial deformation at the sealing position of the impeller mouth ring, to determine whether the minimum sealing clearance value of the impeller mouth ring within the numerical range of the sealing position of the impeller mouth ring meets the requirements. During the actual working process, once the minimum sealing clearance value of the impeller mouth ring cannot meet the requirements, it will lead to rubbing between the rotor and the stator and cause failures. Therefore, it is necessary to verify the minimum sealing clearance value of the impeller mouth ring within the numerical range of the sealing position of the impeller mouth ring here.

[0075] During the numerical comparison process, two situations will occur:

[0076] First, the sum of the amplitude at the sealing position of the impeller mouth ring and the radial deformation at the sealing position of the impeller mouth ring (the calculated value of the clearance at the sealing position) is greater than the allowable value of the minimum sealing clearance of the impeller mouth ring. Here, it means that the minimum sealing clearance value of the impeller mouth ring within the numerical range of the sealing position of the impeller mouth ring does not meet the requirements. Therefore, it is necessary to further increase the minimum sealing clearance value within the numerical range of the impeller mouth ring sealing clearance to determine the numerical range of the impeller mouth ring sealing clearance (that is, the impeller mouth ring sealing design clearance).

[0077] Specifically, it is sufficient that the sum of the amplitude value and the radial deformation of the impeller is less than 0.75 times the improved minimum sealing clearance value of the impeller mouth ring.

[0078] Second, the sum of the amplitude at the sealing position of the impeller mouth ring and the radial deformation at the sealing position of the impeller mouth ring is less than the allowable value of the minimum sealing clearance of the impeller mouth ring. Here, it means that the minimum sealing clearance value of the impeller mouth ring within the numerical range of the sealing position of the impeller mouth ring meets the requirements, and there is no need to further adjust the minimum sealing clearance value within the numerical range of the impeller mouth ring sealing clearance.

[0079] The existing sealing clearance analysis mainly considers three factors: the circumferential speed of the rotor at the sealing position, the sealing material, and the bearing clearance. Based on the influence of the above three factors, and considering the corresponding safety factor for each item, the overall influence is superimposed, and finally the designed clearance range of the seal is calculated. For other types of compressor units, or for PDH centrifugal compressor units with low annual output and light weight, the sealing clearances calculated by the above design method can meet the requirements of API617 standard. However, for PDH compressor units with a rotor weight greater than 10 tons, the sealing clearances calculated by the above design scheme can no longer meet the standard requirements.

[0080] By adding the analysis of the inter-stage seal clearance and the impeller shroud seal clearance on the basis of the existing technology, compared with the conventional seal clearance determination method, the stator and rotor will not rub against each other at the seal position, and there will be no excessive gas leakage. Therefore, the performance indicators of the centrifugal compressor unit are greatly improved. Table 1 shows the amplitudes and radial deformations of the labyrinth seals at different positions in a PDH unit; Table 2 shows the comparison of the minimum seal clearance values and the clearance calculation values of the labyrinth seals at different positions (radius values). Based on the analysis results in Table 2 and considering the influence of the seal leakage, the seal clearance values that do not meet the requirements are improved; Table 3 shows the improvement of the minimum seal clearance values based on the clearance calculation values at the seal positions.

[0081] Table 1 Amplitudes and Radial Deformations of Labyrinth Seals at Different Positions

[0082]

[0083] Table 2 Comparison of the Minimum Seal Clearance Values and the Clearance Calculation Values of Labyrinth Seals at Different Positions (Radius Values)

[0084]

[0085] Table 3 Improvement of the Minimum Seal Clearance Values Based on the Clearance Calculation Values at the Seal Positions

[0086]

[0087] The second aspect of the embodiments of the present application provides a compressor, which is processed according to the stator tooth labyrinth seal design clearance determination method in any one of the above.

[0088] The compressor processed by the above method is more conducive to the long-term safe and stable operation of the unit.

[0089] The third aspect of the embodiments of the present application provides a PDH unit, including the compressor in the above.

[0090] It is easy for those skilled in the art to understand that, on the premise of no conflict, the above advantageous ways can be freely combined and superimposed.

[0091] The above are only the preferred embodiments of the present application, and are not intended to limit the present application. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present application shall be included in the protection scope of the present application. The above is only the preferred implementation manner of the present application. It should be noted that for those of ordinary skill in the art, without departing from the technical principle of the present application, several improvements and variations can be made, and these improvements and variations should also be regarded as the protection scope of the present application.

Claims

1. A method for determining the design gap of a stator tooth labyrinth seal, characterized in that: include: Determination of the numerical range of interstage sealing gap Select the numerical range of the interstage sealing gap; obtain the minimum allowable value of the interstage sealing gap; obtain the amplitude of the interstage sealing position; Based on the allowable value of the interstage minimum sealing clearance and the amplitude of the interstage sealing position, verify whether the numerical range of the interstage sealing clearance meets the requirements; Determination of the numerical range of the impeller ring seal clearance Select the numerical range of the impeller mouth ring sealing clearance; obtain the minimum allowable value of the impeller mouth ring sealing clearance; obtain the amplitude of the impeller mouth ring sealing position; obtain the radial deformation of the impeller mouth ring sealing position; Based on the allowable value of the minimum sealing clearance of the impeller ring, the amplitude of the sealing position of the impeller ring and the radial deformation of the sealing position of the impeller ring, it is verified whether the numerical range of the impeller ring sealing clearance meets the requirements.

2. A method for determining the design gap of a stator tooth labyrinth seal according to claim 1, characterized in that: Get the minimum allowable value of the interstage sealing gap, including: The numerical range of the inter-stage sealing gap includes a minimum inter-stage sealing gap value, and the allowable value of the minimum inter-stage sealing gap is calculated based on the minimum inter-stage sealing gap value.

3. A method for determining the design gap of a stator tooth labyrinth seal according to claim 1, characterized in that: Get the amplitude of the interstage seal position, including: Based on the unbalanced excitation of the rotor, the unbalanced response of the rotor is analyzed to obtain the amplitude of the interstage seal position.

4. A method for determining the design gap of a stator tooth labyrinth seal according to claim 1, characterized in that: Verify whether the numerical range of the interstage sealing gap meets the requirements based on the allowable value of the interstage minimum sealing gap and the amplitude of the interstage sealing position, specifically including: Compare the amplitude of the interstage sealing position with the allowable value of the interstage minimum sealing gap; if the amplitude of the interstage sealing position is greater than the allowable value of the interstage minimum sealing gap, further increase the interstage minimum sealing gap value within the numerical range of the interstage sealing gap.

5. A method for determining the design gap of a stator tooth labyrinth seal according to claim 1, characterized in that: Obtain the minimum allowable value of the impeller ring seal clearance, including: The numerical range of the impeller ring sealing clearance includes the impeller ring minimum sealing clearance value, and the impeller ring minimum sealing clearance allowable value is calculated based on the impeller ring minimum sealing clearance value.

6. A method for determining the design gap of a stator tooth labyrinth seal according to claim 1, characterized in that: Obtain the amplitude of the impeller ring seal position, including: Based on the unbalanced excitation of the rotor, the unbalanced response of the rotor is analyzed to obtain the amplitude of the impeller ring sealing position.

7. A method for determining the design gap of a stator tooth labyrinth seal according to claim 1, characterized in that: Obtain the radial deformation of the impeller ring seal position, including: The deformation of the impeller under the action of centrifugal force is analyzed to obtain the radial deformation of the impeller mouth ring sealing position.

8. A method for determining the design gap of a stator tooth labyrinth seal according to claim 1, characterized in that: Based on the allowable value of the minimum sealing clearance of the impeller ring, the amplitude of the sealing position of the impeller ring, and the radial deformation of the sealing position of the impeller ring, verify whether the numerical range of the impeller ring sealing clearance meets the requirements, specifically including: Compare the allowable value of the minimum sealing clearance of the impeller ring with the sum of the amplitude of the impeller ring sealing position and the radial deformation of the impeller ring sealing position; if the sum of the amplitude of the impeller ring sealing position and the radial deformation of the impeller ring sealing position is greater than the allowable value of the minimum sealing clearance of the impeller ring, further increase the value range of the impeller ring sealing clearance and the minimum sealing clearance value of the impeller ring.

9. A compressor, characterized in that: The stator tooth labyrinth seal is manufactured according to the method for determining the design gap of the stator tooth labyrinth seal according to any one of claims 1 to 8.

10. A PDH device, characterized in that: Comprising the compressor as claimed in claim 9.

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