WO2026000620A1 - 离心压缩机以及控制方法 - Google Patents

离心压缩机以及控制方法

Info

Publication number
WO2026000620A1
WO2026000620A1 PCT/CN2024/117253 CN2024117253W WO2026000620A1 WO 2026000620 A1 WO2026000620 A1 WO 2026000620A1 CN 2024117253 W CN2024117253 W CN 2024117253W WO 2026000620 A1 WO2026000620 A1 WO 2026000620A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
rotor
axial
top foil
radial
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
PCT/CN2024/117253
Other languages
English (en)
French (fr)
Inventor
岳宝
刘鹏辉
于兆凯
贺伟衡
李镇杉
胡雄
刘楠
陈续朗
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GD Midea Heating and Ventilating Equipment Co Ltd
Chongqing Midea General Refrigeration Equipment Co Ltd
Original Assignee
GD Midea Heating and Ventilating Equipment Co Ltd
Chongqing Midea General Refrigeration Equipment Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by GD Midea Heating and Ventilating Equipment Co Ltd, Chongqing Midea General Refrigeration Equipment Co Ltd filed Critical GD Midea Heating and Ventilating Equipment Co Ltd
Publication of WO2026000620A1 publication Critical patent/WO2026000620A1/zh
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/008—Stop safety or alarm devices, e.g. stop-and-go control; Disposition of check-valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/0563—Bearings cartridges
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G01M13/04—Bearings
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01R—MEASURING ELECTRIC VARIABLES; MEASURING MAGNETIC VARIABLES
    • G01R31/00—Arrangements for testing electric properties; Arrangements for locating electric faults; Arrangements for electrical testing characterised by what is being tested not provided for elsewhere
    • G01R31/50—Testing of electric apparatus, lines, cables or components for short-circuits, continuity, leakage current or incorrect line connections
    • G01R31/54—Testing for continuity
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01R—MEASURING ELECTRIC VARIABLES; MEASURING MAGNETIC VARIABLES
    • G01R31/00—Arrangements for testing electric properties; Arrangements for locating electric faults; Arrangements for electrical testing characterised by what is being tested not provided for elsewhere
    • G01R31/50—Testing of electric apparatus, lines, cables or components for short-circuits, continuity, leakage current or incorrect line connections
    • G01R31/66—Testing of connections, e.g. of plugs or non-disconnectable joints

Definitions

  • This application relates to the field of centrifugal compressor bearing technology, and in particular to a centrifugal compressor and a control method thereof.
  • Gas hydrodynamic bearings are a type of sliding bearing. Their structure and working principle are similar to liquid sliding bearings, but they use gas (mostly air) as the lubricating medium. They offer advantages such as extremely low friction, no need for lubricating fluid, a wide operating speed range, and a broad applicable temperature range. Therefore, they are widely used in high-speed rotating machinery, for example, in conjunction with the rotor in centrifugal compressors.
  • Foil gas hydrodynamic bearings are another type of gas hydrodynamic bearing. Due to their complex structural characteristics and operating environment, foil gas hydrodynamic bearings are prone to failure.
  • One objective of this application is to provide a centrifugal compressor that can protect the first top foil and the first wave foil and can identify and predict the life of the first bearing in advance.
  • Another objective of this application is to provide a control method for the aforementioned centrifugal compressor.
  • a centrifugal compressor includes: a housing, a rotor, a stator, a first bearing, and a second bearing.
  • the housing has a radial bearing chamber.
  • the rotor and the stator are both disposed in the housing.
  • the first bearing is disposed in the radial bearing chamber and includes: a first bearing seat, a first corrugated foil, and a first top foil.
  • the first corrugated foil is located between the first top foil and the first bearing seat and elastically abuts against the first top foil.
  • the first top foil is radially opposite to the rotor.
  • the second bearing is disposed in the housing and radially opposite to the rotor. In the radial direction of the centrifugal compressor, the radial clearance between the second bearing and the rotor, minus the radial clearance between the first top foil and the rotor, is less than the thickness of the first top foil.
  • the centrifugal compressor of this application embodiment by setting a first bearing and a second bearing, and defining the relationship between the radial clearance between the second bearing and the rotor, and the radial clearance between the first top foil and the rotor and the thickness of the first top foil, the first top foil and the first top foil can provide good protection for the first top foil and the first top foil during rotor instability impacts. This can improve the reliability and lifespan of the first bearing, and enhance the rotor's working performance and stability. Furthermore, it can also identify in advance whether the first top foil of the first bearing needs to be replaced. After the first bearing wears out due to frequent start-stop cycles and prolonged use under abnormal operating conditions, the lifespan of the first bearing can be effectively predicted, and the first bearing, sealing components, and other parts can be effectively protected, reducing maintenance costs.
  • the centrifugal compressor further includes: an impeller disposed on the rotor, and the housing further includes: a wheel cover, wherein a wheel cover seal is provided on one side of the impeller opposite to the wheel cover, and a wheel back seal is provided on the other side.
  • the radial clearance between the second bearing and the rotor is smaller than the radial clearance between the wheel cover seal and the impeller, and the radial clearance between the second bearing and the rotor.
  • the radial clearance between the second bearing and the rotor is also smaller than the radial clearance between the wheel back seal and the rotor.
  • the rotor is provided with a rotor bushing, and the radial clearance between the rotor bushing and the second bearing, minus the radial clearance between the first top foil and the rotor bushing, is less than the thickness of the first top foil.
  • the radial clearance between the second bearing and the rotor bushing is smaller than the radial clearance between the wheel back seal and the rotor.
  • the radial clearance between the second bearing and the rotor bushing is smaller than the radial clearance between the wheel cover seal and the impeller.
  • the radial clearance between the first top foil and the rotor is greater than or equal to the radial clearance between the second bearing and the rotor.
  • the second bearing is connected to the wheel back seal via a first potting layer.
  • a first sensor is disposed within the first potting layer.
  • the first sensor is adapted to detect the radial pressure borne by the second bearing and is triggered when the rotor presses against the second bearing.
  • the centrifugal compressor further includes: a third bearing and a thrust plate; the housing also has an axial bearing chamber; the third bearing is disposed in the axial bearing chamber; the thrust plate is connected to the rotor; the third bearing includes: a second bearing seat, a second corrugated foil, and a second top foil; the second corrugated foil is located between the second top foil and the second bearing seat and elastically abuts against the second top foil; the second top foil and the thrust plate are axially opposite each other; the third bearing and the thrust plate are axially opposite each other; wherein, in the axial direction of the centrifugal compressor, the axial clearance between the second bearing and the rotor, minus the axial clearance between the second top foil and the thrust plate, is less than the thickness of the second top foil.
  • the rotor is provided with a rotor bushing, and in the axial direction of the centrifugal compressor, the axial clearance between the second bearing and the rotor bushing, minus the axial clearance between the second top foil and the thrust plate, is less than the thickness of the second top foil.
  • the axial clearance between the third bearing and the rotor is smaller than the axial clearance between the wheel cover seal and the impeller, and the axial clearance between the third bearing and the rotor is also smaller than the axial clearance between the wheel back seal and the impeller.
  • the axial clearance between the thrust plates is smaller than the axial clearance between the thrust plates.
  • the axial clearance between the second bearing and the rotor is less than or equal to the axial clearance between the second top foil and the thrust plate.
  • the second bearing and the wheel back seal are further provided with a second potting layer, and the second potting layer is integrally potted with the first potting layer.
  • a second sensor is provided within the second potting layer.
  • the second sensor is adapted to detect the axial pressure borne by the second bearing and is triggered when the thrust plate presses against the second bearing.
  • the rotor includes a primary rotor and a secondary rotor.
  • the radial bearing chamber includes a primary radial bearing chamber corresponding to the primary rotor and a secondary radial bearing chamber corresponding to the secondary rotor.
  • a first bearing is disposed in the primary radial bearing chamber and a first bearing is disposed in the secondary radial bearing chamber.
  • the axial bearing chamber includes a primary axial bearing chamber corresponding to the primary rotor and a secondary axial bearing chamber corresponding to the secondary rotor.
  • a third bearing is disposed in the primary axial bearing chamber and a third bearing is disposed in the secondary axial bearing chamber. The two third bearings are located on opposite axial sides of the thrust plate.
  • a second bearing is disposed at one end of the primary rotor and a second bearing is disposed at the other end of the secondary rotor.
  • the primary axial bearing chamber and the secondary axial bearing chamber are located on opposite axial sides of the housing, and the thrust plate includes: a first thrust plate and a second thrust plate.
  • the primary rotor is provided with the first thrust plate, and the secondary rotor is provided with the second thrust plate.
  • the primary axial bearing chamber and the secondary axial bearing chamber are located on the same axial side of the housing, and the two third bearings are located on opposite axial sides of the thrust plate.
  • the first bearing is constructed as a radial dynamic pressure bearing
  • the second bearing is constructed as a ball bearing
  • the third bearing is constructed as an axial dynamic pressure bearing
  • a control method includes: acquiring the trigger duration and trigger count of a first sensor and a second sensor; if the trigger duration exceeds a duration threshold or the trigger count exceeds a first-time trigger count threshold, a fault is reported and the system is shut down.
  • the duration threshold is 30s to 60s, and the first number threshold is 8 to 12 times.
  • control method further includes: acquiring the trigger counts of the first sensor and the second sensor; if the trigger count of the first sensor exceeds a second threshold within a first time threshold, then a first bearing damage alarm is reported and the machine is shut down urgently; if the trigger count of the second sensor exceeds a second threshold within the first time threshold, then a third bearing damage alarm is reported and the machine is shut down urgently.
  • Figure 1 is a side view of a centrifugal compressor according to some embodiments of this application.
  • Figure 2 is a cross-sectional view along line A-A in Figure 1;
  • Figure 3 is an enlarged view of point B in Figure 2;
  • Figure 4 is an enlarged view of point C in Figure 2;
  • Figure 5 is an enlarged view of point D in Figure 2;
  • Figure 6 is a schematic diagram of the cooperation between the second bearing and the first sensor, the second sensor, etc., according to some embodiments of this application;
  • FIG. 7 is a flowchart of a control method according to some embodiments of this application.
  • centrifugal compressor 1 and control method according to embodiments of this application are described below with reference to Figures 1-7.
  • the centrifugal compressor 1 includes: a housing 11, a rotor, a stator 13, a first bearing, and a second bearing 15.
  • the housing 11 is provided with a radial bearing chamber; the rotor and stator 13 are both disposed in the housing 11; the first bearing is disposed in the radial bearing chamber, and the first bearing includes: a first bearing seat, a first corrugated foil and a first top foil, the first corrugated foil is located between the first top foil and the first bearing seat and elastically pushes against the first top foil, the first top foil is radially opposite to the rotor; the second bearing 15 is disposed in the housing 11, and the second bearing 15 is radially opposite to the rotor; in the radial direction of the centrifugal compressor 1, the radial clearance between the second bearing 15 and the rotor, minus the radial clearance between the first top foil and the rotor, is less than the thickness of the first top foil.
  • both the stator 13 and the rotor are housed within the housing 11.
  • the stator 13 and the rotor work together to enable the centrifugal compressor 1 to compress gas.
  • the first bearing can be housed in the radial bearing chamber of the housing 11 to achieve a preset position for installation and fixation within the housing 11.
  • the first bearing housing can provide mounting positions for some other components (such as the first corrugated foil and the first top foil) and can also support, fix, and protect some other components in the first bearing.
  • the first corrugated foil and the first top foil can both be housed radially inside the first bearing housing.
  • the first top foil is sleeved on the outer periphery of the rotor and is radially spaced from the rotor to support the rotor's radial suspension.
  • the first corrugated foil is located between the first top foil and the first bearing housing.
  • the first corrugated foil can be an elastic corrugated structure with good deformation performance, which can improve load-bearing capacity and performance stability.
  • the second bearing 15 can be housed in the housing 11 and is radially opposite to the rotor. The second bearing 15 is used for rotor support and positioning.
  • the inventors of this application have noted that in the related art, when the first bearing used to support the radial suspension of the rotor becomes unstable due to a sudden power outage or a strong external impact, the rotor will impact the first top foil of the first bearing, forcing the first top foil to deform outward and compress the first wave foil located outside the first top foil. The first wave foil will then experience significant deformation due to the rotor impact. The deformation or even collapse of the bearing caused the first bearing to fail.
  • the first top foil is the component that contacts the rotor first. Therefore, the first top foil can be protected by the second bearing 15 to avoid continuous deformation or damage to the first top foil, and thus the first wave foil can also be protected.
  • this application further makes the radial clearance between the second bearing 15 and the rotor, minus the radial clearance between the first top foil and the rotor, smaller than the thickness of the first top foil.
  • the second bearing 15 can be sequentially arranged axially with the first bearing.
  • the rotor is located on the inner circumference of the second bearing 15 and the first top foil.
  • the first top foil may experience some wear, causing the radial clearance between the first top foil and the rotor to shorten.
  • the radial clearance between the second bearing 15 and the rotor minus the radial clearance between the first top foil and the rotor is less than the thickness of the first top foil. This allows the second bearing 15 to contact the rotor when the first top foil reaches a certain degree of wear after long-term operation.
  • the second bearing 15 can also provide support and protection between the rotor and the first top foil and the first corrugated foil. This protects the deformation of the first top foil and the first corrugated foil from being within the design range and prevents the first corrugated foil located outside the first top foil from being excessively deformed due to rotor impact and losing its elasticity.
  • the centrifugal compressor 1 of this application by setting a first bearing and a second bearing 15, and defining the radial clearance between the second bearing 15 and the rotor, and the radial clearance between the first top foil and the rotor, and the relationship between the thickness of the first top foil and the rotor, the first top foil and the first corrugated foil can provide good protection for the first top foil and the first corrugated foil during rotor instability impacts. This can improve the reliability and lifespan of the first bearing, and enhance the rotor's working performance and stability. Furthermore, it can identify in advance whether the first top foil of the first bearing needs replacement. After the first bearing wears out due to frequent start-stop cycles and long-term abnormal operating conditions, it can effectively predict the lifespan of the first bearing and effectively protect the first bearing, sealing components, and other parts, reducing maintenance costs.
  • the centrifugal compressor 1 further includes: an impeller 16 disposed on the rotor, and the housing 11 further includes: a wheel cover, with a wheel cover seal 17 disposed on one side of the impeller 16 opposite to the wheel cover, and a wheel back seal 18 disposed on the other side.
  • Impeller 16 is mounted on rotor. Rotation of rotor drives impeller 16 to rotate, thereby achieving gas flow and compression. Impeller cover is used for support, connection and sealing of impeller 16, and helps to maintain rotor balance and reduce vibration caused by uneven mass distribution. Impeller cover seal 17 is provided on the side of impeller 16 opposite to impeller cover, and impeller back seal 18 is provided on the side of impeller 16 away from impeller cover. Both impeller cover seal 17 and impeller back seal 18 can improve structural airtightness, enhance the prevention of gas and liquid leakage, and improve the compression efficiency of centrifugal compressor 1.
  • the radial clearance between the second bearing 15 and the rotor is smaller than the radial clearance between the wheel cover seal 17 and the impeller 16.
  • the radial clearance between the wheel cover seal 17 and the impeller 16 is less than or equal to the radial clearance between the second bearing 15 and the rotor, it will result in poor gas and liquid leakage prevention performance and reduce the overall structural operational stability. Therefore, by limiting the relationship between the radial clearance between the wheel cover seal 17 and the impeller 16 and the radial clearance between the second bearing 15 and the rotor within the above range, the radial clearance between the wheel cover seal 17 and the impeller 16 is small, which helps to optimize sealing performance, improve gas leakage prevention performance, increase working efficiency, and improve rotor operational stability.
  • the radial clearance between the second bearing 15 and the rotor is also smaller than the radial clearance between the wheel back seal 18 and the rotor.
  • the radial clearance between the wheel back seal 18 and the rotor is less than or equal to the radial clearance between the second bearing 15 and the rotor, it will result in poor gas and liquid leakage prevention performance and reduce the overall structural operational stability. Therefore, by limiting the relationship between the radial clearance between the wheel back seal 18 and the rotor and the radial clearance between the second bearing 15 and the rotor within the above range, the radial clearance between the wheel back seal 18 and the rotor is made smaller, which helps to optimize the sealing performance, improve the gas leakage prevention performance, increase working efficiency, and improve the rotor's operational stability.
  • a rotor bushing 25 is provided on the rotor, and the radial clearance between the rotor bushing 25 and the second bearing 15, minus the radial clearance between the first top foil and the rotor bushing 25, is less than the thickness of the first top foil.
  • At least a portion of the outer periphery of the rotor may be fitted with a rotor bushing 25, which is located between the rotor and the second bearing 15. In this way, the rotor bushing 25 can reduce the friction between the rotor and the second bearing 15, save energy loss, and provide good protection.
  • the radial clearance between the rotor bushing 25 and the second bearing 15, minus the radial clearance between the first top foil and the rotor bushing 25, is less than the thickness of the first top foil.
  • the rotor bushing 25 is located on the inner circumference of the second bearing 15 and the first top foil. After long-term operation, the first top foil may experience some wear, causing the radial clearance between the first top foil and the rotor bushing 25 to shorten.
  • the second bearing 15 can contact the rotor bushing 25 when the first top foil reaches a certain degree of wear after long-term operation. This allows for early identification of whether the first top foil of the first bearing needs to be replaced, preventing further wear and even severe wear or wear through the first top foil, and ensuring the normal and reliable operation of the first top foil.
  • the radial clearance between the second bearing 15 and the rotor bushing 25 is smaller than the radial clearance between the wheel back seal 18 and the rotor.
  • the radial clearance between the second bearing 15 and the rotor bushing 25 is smaller than the radial clearance between the wheel cover seal 17 and the impeller 16.
  • the radial clearance between the wheel cover seal 17 and the impeller 16 is less than or equal to the radial clearance between the second bearing 15 and the rotor bushing 25, it will result in poor gas and liquid leakage prevention performance and reduce the overall structural operational stability. Therefore, by limiting the relationship between the radial clearance between the wheel cover seal 17 and the impeller 16 and the radial clearance between the second bearing 15 and the rotor bushing 25 within the above range, the radial clearance between the wheel cover seal 17 and the impeller 16 is small, which helps to optimize sealing performance, improve gas leakage prevention performance, increase working efficiency, and improve rotor operational stability.
  • the radial clearance between the first top foil and the rotor is greater than or equal to the radial clearance between the second bearing 15 and the rotor.
  • the first top foil When the first top foil is unworn or only slightly worn, it normally suspends and supports the rotor. The outer circumference of the rotor does not contact the radially spaced second bearing 15, and the first top foil, first wave foil, and rotor all operate normally and safely.
  • the rotor suddenly becomes unstable due to power failure or external impact, causing radial movement that puts the first top foil in a state of extreme compression, or when the first top foil wears down after long-term operation, the distance between the rotor and the first top foil will shorten.
  • the radial clearance between the first top foil and the rotor will be greater than or equal to the radial clearance between the second bearing 15 and the rotor.
  • the radial distance between the second bearing 15 and the rotor will be equal to or shorter than the radial distance between the first top foil and the rotor. In this case, when the rotor moves outward radially, it will first contact the second bearing 15, which has a shorter distance.
  • the second bearing 15 can provide support and protection between the rotor and the first top foil and the first wave foil, keeping the deformation of the first top foil and the first wave foil within the design range, and protecting the first wave foil located outside the first top foil from excessive deformation due to rotor impact, preventing it from losing its elasticity.
  • the second bearing 15 and the wheel back seal 18 are connected through the first potting layer 19.
  • the first potting layer 19 can be an insulating potting compound, specifically epoxy resin, silicone rubber, polyurethane, or other materials with good electrical insulation and sealing properties.
  • the first potting layer 19 is located between the second bearing 15 and the wheel back seal 18, which can separate the second bearing 15 from the wheel back seal 18.
  • the first potting layer 19 can play a good buffering role. When the second bearing 15 is subjected to rotor impact during the protection process, the first potting layer 19 can buffer the impact, reduce the damage to the second bearing 15, and thus improve the life of the second bearing 15.
  • the insulating potting compound is initially liquid and only begins to cure after potting. Therefore, it can also serve to fix the second bearing 15 and improve the stability of the second bearing 15 installation.
  • second bearing 15 and the wheel back seal 18 in this application can also be connected by other processes, such as injection molding.
  • the first potting layer 19 is provided with a first...
  • a sensor 20 is provided, which is adapted to detect the radial pressure on the second bearing 15 and is triggered when the rotor presses against the second bearing 15.
  • the first sensor 20 will continuously monitor the pressure accordingly, including after shutdown (after shutdown, the pressure is due to the rotor's weight). This indicates that the first top foil is severely worn due to start-stop operation. Therefore, the first sensor 20 can also remind that the first top foil needs to be replaced. It can monitor and intelligently diagnose the first top foil, the first wavy foil, and the second bearing 15 to achieve predictive maintenance. This can prevent further damage to parts such as the rotor, impeller 16, and wheel back seal 18 caused by high-speed operation after the first top foil is damaged. This can improve the operational reliability of the centrifugal compressor 1 and save maintenance costs.
  • the first sensor 20 by placing the first sensor 20 on the outside of the second bearing 15 in the first potting layer 19, on the one hand, it can fix the first sensor 20 and improve the installation stability of the first sensor 20; on the other hand, the first potting layer 19 can also provide good insulation and sealing protection, which can protect the first sensor 20 and its wiring harness from damage, and improve the working reliability, safety and durability of the first sensor 20.
  • the first sensor 20 can be constructed in multiple ways. Preferably, as shown in FIG6, the first sensor 20 is constructed in three equally spaced positions arranged around the second bearing 15 to increase the detection range of the first sensor 20 and improve the detection accuracy.
  • the centrifugal compressor 1 further includes a third bearing and a thrust plate 22.
  • the housing 11 also has an axial bearing chamber 112.
  • the third bearing is disposed in the axial bearing chamber 112.
  • the thrust plate 22 is connected to the rotor.
  • the third bearing includes a second bearing seat, a second corrugated foil, and a second top foil.
  • the second corrugated foil is located between the second top foil and the second bearing seat and elastically pushes against the second top foil.
  • the second top foil and the thrust plate 22 are axially opposite each other.
  • the third bearing and the thrust plate 22 are axially opposite each other.
  • the stop pusher 22 is connected to the rotor to bear the axial force generated by the rotor due to gas compression, thereby improving the rotor's operational stability;
  • the third bearing can be disposed in the axial bearing chamber 112 of the housing 11, and in the third bearing, the second bearing seat can be some other components of the axial dynamic pressure bearing (such as the second wave foil, the second top foil). It provides an installation position and can support, fix and protect some other components in the axial dynamic pressure bearing.
  • the second corrugated foil and the second top foil can both be set at one end of the second bearing housing in the axial direction.
  • the second top foil and the thrust plate 22 are opposite each other in the axial direction and are spaced a certain distance apart, supporting the thrust plate 22 and the rotor to axially suspend.
  • the second corrugated foil is set between the second top foil and the second bearing housing.
  • the second corrugated foil can be an elastic corrugated structure with good deformation performance, which can improve the load-bearing capacity and performance stability.
  • the second top foil in this application may experience some wear after long-term operation, which will shorten the axial clearance between the second top foil and the thrust plate 22.
  • the difference between the axial clearance between the second top foil and the thrust plate 22 and the axial clearance between the second top foil and the rotor is less than the thickness of the second top foil. This allows the second bearing 15 to contact the rotor after the second top foil has reached a certain degree of wear during long-term operation. This can help identify the replacement cycle of the second top foil of the third bearing in advance, prevent the second top foil from continuing to wear out and even wear through, and ensure that the second top foil works normally and reliably.
  • the second bearing 15 can also support and protect the second top foil, the second wave foil, etc. It can protect the deformation of the second top foil and the second wave foil within the design range, and protect the second wave foil located on one side of the second top foil from excessive deformation due to rotor impact and loss of elasticity. In this way, the reliability and life of the second top foil and the second wave foil can be improved, the working performance and stability of components such as rotor, impeller 16, wheel back seal 18, wheel cover seal 17 can be improved, and maintenance costs can be saved.
  • a rotor bushing 25 is provided on the rotor.
  • the axial clearance between the second bearing 15 and the rotor bushing 25, minus the axial clearance between the second top foil and the thrust plate 22, is less than the thickness of the second top foil.
  • the rotor bushing 25 when a rotor bushing 25 is provided on the rotor, the rotor bushing 25 is located between the rotor and the second bearing 15.
  • the axial clearance between the second bearing 15 and the rotor bushing 25, minus the axial clearance between the second top foil and the thrust plate 22, is less than the thickness of the second top foil.
  • the axial clearance between the third bearing and the rotor is less than the axial clearance between the wheel cover seal 17 and the impeller 16, and the axial clearance between the third bearing and the rotor is also less than the axial clearance between the wheel back seal 18 and the thrust plate 22.
  • the axial clearance between the wheel cover seal 17 and the impeller 16, as well as the axial clearance between the wheel back seal 18 and the thrust plate 22, are small, which helps to optimize sealing performance, improve gas leakage prevention performance, increase working efficiency, and improve rotor running stability.
  • the second bearing 15 and the wheel back seal 18 are further provided with a second potting layer 23, which is integrally potted with the first potting layer 19.
  • the second potting layer 23 can be an insulating potting compound, such as epoxy resin, silicone rubber, polyurethane, or other materials with good electrical insulation and sealing properties.
  • the second potting layer 23 is located between the second bearing 15 and the wheel back seal 18.
  • the second potting layer 23 can separate the second bearing 15 from the wheel back seal 18.
  • the second potting layer 23 can play a good buffering role. When the second bearing 15 is subjected to rotor impact during the protection process, the second potting layer 23 can buffer the impact, reduce the damage to the second bearing 15, and thus improve the life of the second bearing 15.
  • a second sensor 24 is provided in the second potting layer 23.
  • the second sensor 24 is adapted to detect the axial pressure borne by the second bearing 15 and is triggered when the thrust plate 22 presses against the second bearing 15.
  • the second sensor 24 will continuously monitor the pressure accordingly, and can continue to monitor the continuous pressure after restarting, indicating that the second top foil is severely worn due to start-stop operation. Therefore, the second sensor 24 can also remind you to replace the second top foil. It can monitor and intelligently diagnose the second top foil, the second wave foil, and the second bearing 15 to achieve predictive maintenance. It can prevent further damage to parts such as the thrust plate 22, rotor, impeller 16, and wheel back seal 18 caused by high-speed operation after the second top foil is damaged. This can improve the working reliability of the centrifugal compressor 1 and save maintenance costs.
  • the second potting layer 23 can fix the second sensor 24 and improve the installation stability of the second sensor 24; on the other hand, the second potting layer 23 can also provide good insulation and sealing protection, which can protect the second sensor 24 and the wiring harness of the second sensor 24 from damage, and improve the working reliability, safety and durability of the first sensor 20.
  • the rotor includes a primary rotor 12a and a secondary rotor 12b.
  • the radial bearing chamber includes a primary radial bearing chamber 111a corresponding to the primary rotor 12a and a secondary radial bearing chamber 111b corresponding to the secondary rotor 12b.
  • a first bearing is disposed in the primary radial bearing chamber 111a and a first bearing is disposed in the secondary radial bearing chamber 111b.
  • the axial bearing chamber 112 includes a primary axial bearing chamber corresponding to the primary rotor 12a and a secondary axial bearing chamber corresponding to the secondary rotor 12b.
  • the primary rotor 12a and the secondary rotor 12b can be arranged coaxially and connected.
  • the primary radial bearing chamber 111a corresponds to the primary rotor 12a
  • the secondary radial bearing chamber 111b corresponds to the secondary rotor 12b.
  • Both the primary radial bearing chamber 111a and the secondary radial bearing chamber 111b are equipped with a first bearing to cooperate with the primary rotor 12a and the secondary rotor 12b respectively, so as to improve the rotor working performance and running stability.
  • the primary axial bearing chamber corresponds to the primary rotor 12a
  • the secondary axial bearing chamber corresponds to the secondary rotor 12b.
  • Both the primary axial bearing chamber and the secondary axial bearing chamber are equipped with a third bearing to cooperate with the primary rotor 12a and the secondary rotor 12b respectively, so as to improve the rotor working performance and running stability.
  • the first bearing pair disposed in the primary radial bearing chamber 111a It should have a first-stage bearing housing 141a, a first-stage top foil 143a, and a first-stage corrugated foil 142a; the first bearing located in the second-stage radial bearing chamber 111b should have a second-stage bearing housing 141b, a second-stage top foil 143b, and a second-stage corrugated foil 142b.
  • the primary axial bearing chamber and the secondary axial bearing chamber are located on opposite axial sides of the housing 11.
  • the thrust plate 22 includes a first thrust plate and a second thrust plate.
  • the primary rotor 12a is provided with the first thrust plate
  • the secondary rotor 12b is provided with the second thrust plate.
  • the primary axial bearing chamber and the secondary axial bearing chamber are located on the same axial side of the housing 11, and two third bearings are located on opposite axial sides of the thrust plate 22.
  • the thrust plate 22, the primary axial bearing chamber, and the secondary axial bearing chamber can be arranged in various ways.
  • both the primary rotor 12a and the secondary rotor 12b are provided with thrust plates 22, which correspond to the first thrust plate and the second thrust plate, respectively.
  • the primary axial bearing chamber and the secondary axial bearing chamber can be located on opposite axial sides of the housing 11, so that the two third bearings are located on opposite axial sides of the housing 11, respectively, to cooperate with the first thrust plate and the second thrust plate, thereby optimizing the rotor's working performance and balance.
  • only one of the primary rotor 12a and the secondary rotor 12b is provided with a thrust plate 22, that is, the thrust plate 22 is provided on either the primary rotor 12a or the secondary rotor 12b.
  • the primary axial bearing chamber and the secondary axial bearing chamber can be located on the same axial side of the housing 11, and the two third bearings are located on the same axial side of the housing 11. At the same time, the two third bearings are located on opposite axial sides of the thrust plate 22, to cooperate with the thrust plate 22, thereby optimizing the rotor's working performance and balance.
  • a second bearing seat, a second wave foil, a second top foil, and other structures are provided on both sides of the thrust plate 22 in the axial direction.
  • the second bearing seat includes a first side second bearing seat 211c and a second side second bearing seat 211d located on both sides of the thrust plate 22
  • the second wave foil includes a first side second wave foil 212c and a second side second wave foil 212d located on both sides of the thrust plate 22
  • the second top foil includes a first side second top foil 213c and a second side second top foil 213d located on both sides of the thrust plate 22.
  • the first bearing is constructed as a radial dynamic pressure bearing
  • the second bearing 15 is constructed as a ball bearing
  • the third bearing is constructed as an axial dynamic pressure bearing
  • the radial dynamic pressure bearing uses gas as the lubricating medium. Constructing the first bearing as a radial dynamic pressure bearing enables radial suspension support of the rotor, which helps the rotor operate with low friction and high speed, saving energy and improving the rotor's working performance, stability, and lifespan. Similarly, constructing the third bearing as an axial dynamic pressure bearing enables axial suspension support of the rotor, which also helps the rotor operate with low friction and high speed, saving energy and improving the rotor's working performance, stability, and lifespan.
  • the second bearing 15 is constructed as a ball bearing.
  • the second bearing 15 can be an angular contact ball bearing.
  • the second bearing 15 as a ball bearing allows it to cooperate with the rotor, improving the rotor's working reliability and lifespan. It also ensures good protection for the first and third bearings during rotor impacts under harsh working conditions.
  • control method is applicable to the centrifugal compressor in any of the above embodiments.
  • the control method includes: acquiring the trigger duration and trigger count of the first sensor 20 and the second sensor 24; if the trigger duration exceeds the duration threshold or the trigger count exceeds the first count threshold, a fault is reported and the compressor is shut down.
  • the trigger duration of the first sensor 20 and the second sensor 24 exceeds a duration threshold, or the number of triggers of the first sensor 20 and the second sensor 24 exceeds a first-time threshold can be used as a criterion for whether to report a fault and shut down the machine.
  • the trigger duration exceeds the duration threshold or the number of triggers exceeds the first-time threshold a fault is reported and the machine is shut down, so as to carry out maintenance and replacement in a timely manner and improve the working performance, reliability and safety of the centrifugal compressor 1.
  • the trigger duration mentioned above can be the duration of a single trigger. If the duration of a single trigger exceeds the duration threshold, a fault can be reported and the system can be shut down.
  • the trigger duration mentioned above can be the sum of the durations of multiple triggers. If the sum of the durations of multiple triggers exceeds the duration threshold, a fault can be reported and the system can be shut down.
  • the duration threshold can be a single threshold, to be compared with the duration of a single trigger, or it can be cumulative, to be compared with the sum of the durations of multiple triggers, to determine whether a fault needs to be reported and the system shut down.
  • the duration threshold is 30s to 60s
  • the first count threshold is 8 to 12 times.
  • the duration threshold and the first-time count threshold are made to have reasonable range values.
  • the duration threshold can be 40s or 50s, and the first-time count threshold can be set to 9 or 10 times, etc. In this way, by comparing the trigger duration and trigger number of the first sensor 20 and the second sensor 24 with the duration threshold and the first-time count threshold, the accuracy of fault alarms can be improved, which is convenient for maintenance.
  • the control method further includes: obtaining the trigger counts of the first sensor 20 and the second sensor 24; if the trigger count of the first sensor 20 exceeds the second threshold within a first time threshold, then a first bearing damage alarm is reported and the machine is shut down urgently; if the trigger count of the second sensor 24 exceeds the second threshold within the first time threshold, then a third bearing damage alarm is reported and the machine is shut down urgently.
  • first sensor 20 and the second sensor 24 when the first sensor 20 and the second sensor 24 are triggered, it could be due to severe operating conditions causing impact deformation of the first and second top foils, triggering the rotor to press against the second bearing 15. Alternatively, it could be due to severe wear of the first and third bearings. In this case, the first sensor 20 and the second sensor 24 will trigger successively, requiring the customer to replace the first and third bearings (as their friction life is nearing its end). The difference between these two situations can be determined based on the first time threshold and the second number threshold. Specifically, if the number of triggers of the first sensor 20 exceeds the second number threshold within the first time threshold, a first bearing damage alarm will be issued, and an emergency shutdown will be initiated. If the number of triggers of the second sensor 24 exceeds the second number threshold within the first time threshold, a third bearing damage alarm will be issued. A fault warning was issued, and the machine was shut down immediately.
  • both the first sensor 20 and the second sensor 24 are triggered, it indicates that both the first and third bearings are malfunctioning; if only the first sensor 20 is triggered, it indicates that only the first bearing is malfunctioning, while the third bearing is functioning normally; if only the second sensor 24 is triggered, it indicates that only the third bearing is malfunctioning, while the first bearing is functioning normally.
  • the first time threshold is 30-90 minutes
  • the second number threshold is 8-12 times
  • the second number threshold is greater than or equal to the first number threshold. Setting the first time threshold too small or too large, or the second number threshold too small or too large, will lead to inaccurate judgment of the first bearing and third bearing damage alarms, causing inconvenience for targeted maintenance and replacement.
  • the first time threshold and the second number threshold have reasonable range values.
  • the first time threshold can be 30 minutes or 60 minutes
  • the second number threshold can be 11 times or 12 times, etc. It can be understood that the second number threshold is greater than or equal to the first number threshold.
  • the maximum first number threshold is 11 times. In this way, by comparing the trigger duration and trigger number of the first sensor 20 and the second sensor 24 with the first time threshold and the second number threshold, the alarm accuracy can be improved, and the convenience and efficiency of maintenance and replacement can be improved.
  • the second threshold number mentioned above is compared with the number of times a single second bearing 15 is triggered, while the first threshold number is compared with the sum of the number of times the two second bearings 15 at both ends of the rotor are triggered.
  • references to terms such as “one embodiment,” “some embodiments,” “illustrative embodiment,” “example,” “specific example,” or “some examples,” etc. indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application.
  • the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example.
  • the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

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Abstract

一种离心压缩机以及控制方法，离心压缩机包括：第一轴承，第一轴承设置于径向轴承室，第一轴承包括：第一轴承座、第一波箔和第一顶箔；第二轴承(15)，第二轴承(15)与转子在径向上相对；其中在离心压缩机的径向方向上，第二轴承(15)与转子之间的径向间隙，减去第一顶箔与转子之间的径向间隙小于第一顶箔的厚度。

Description

离心压缩机以及控制方法
相关申请的交叉引用
本申请要求于2024年6月27日提交的申请号为202410847522.9、名称为“离心压缩机以及控制方法”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及离心压缩机轴承技术领域，尤其是涉及一种离心压缩机以及控制方法。
背景技术
气体动压轴承是滑动轴承形式当中的一种，其结构和工作原理与液体滑动轴承类似，不同的是采用气体(多为空气)作为润滑介质，其具有摩阻极低、无需润滑液体、使用速度范围大、适用温度范围广等优点，因此，被广泛用于高速旋转机械领域，例如，用于与离心压缩机中的转子配合。箔片气体动压轴承是气体动压轴承的一种，由于其复杂的结构特性和工作环境等因素，箔片气体动压轴承存在容易失效的问题。
发明内容
以下是对本文详细描述的主题的概述。本概述并非是为了限制权利要求的保护范围。
本申请的一个目的在于提出一种可以保护第一顶箔和第一波箔、可以提前识别预测第一轴承寿命的离心压缩机。
本申请的另一目的在于提出一种用于上述离心压缩机的控制方法。
一种离心压缩机，包括：壳体、转子、定子、第一轴承以及第二轴承，所述壳体设置有径向轴承室；所述转子和所述定子均设置于所述壳体；所述第一轴承设置于所述径向轴承室，所述第一轴承包括：第一轴承座、第一波箔和第一顶箔，所述第一波箔位于所述第一顶箔与所述第一轴承座之间，且弹性推抵于所述第一顶箔，所述第一顶箔与所述转子在径向上相对；所述第二轴承设置于所述壳体，所述第二轴承与所述转子在径向上相对；其中在所述离心压缩机的径向方向上，所述第二轴承与所述转子之间的径向间隙，减去所述第一顶箔与所述转子之间的径向间隙小于所述第一顶箔的厚度。
根据本申请实施例的离心压缩机，通过设置第一轴承和第二轴承，并限定第二轴承与转子间径向间隙、第一顶箔与转子间径向间隙与第一顶箔的厚度大小关系，可以在转子失稳冲击时，对第一顶箔、第一波箔等起到良好的保护作用，可以提高第一轴承可靠性和寿命，提升转子工作性能和稳定性。并且，还可以提前识别第一轴承的第一顶箔是否需要更换， 在第一轴承因长期频繁启停以及长期异常工况使用造成磨损后，能有效预测第一轴承的寿命，并有效保护第一轴承、密封部件等零件，减少维护成本。
根据本申请的一些实施例，所述离心压缩机还包括：设置于所述转子的叶轮，所述壳体还包括：轮盖，所述叶轮与轮盖相对一侧设置有轮盖密封，另一侧设置有轮背密封。
根据本申请的一些实施例，所述第二轴承与所述转子之间的径向间隙小于所述轮盖密封与所述叶轮之间的径向间隙，所述第二轴承与所述转子之间的径向间隙。
根据本申请的一些实施例，所述第二轴承与所述转子之间的径向间隙还小于轮背密封与所述转子之间的径向间隙。
根据本申请的一些实施例，所述转子上设置有转子轴套，所述转子轴套与所述第二轴承之间的径向间隙，减去所述第一顶箔与所述转子轴套之间的径向间隙，小于所述第一顶箔的厚度。
根据本申请的一些实施例，所述第二轴承与所述转子轴套之间的径向间隙，小于所述轮背密封与所述转子之间的径向间隙。
根据本申请的一些实施例，所述第二轴承与所述转子轴套之间的径向间隙，小于所述轮盖密封与所述叶轮之间的径向间隙。
根据本申请的一些实施例，在所述第一顶箔处于极限压缩状态或磨损后，所述第一顶箔与所述转子之间的径向间隙大于等于所述第二轴承与所述转子之间的径向间隙。
根据本申请的一些实施例，所述第二轴承与所述轮背密封通过第一灌封层相连。
根据本申请的一些实施例，所述第一灌封层内设置有第一传感器，所述第一传感器适于检测所述第二轴承承受的径向压力，并在所述转子压抵所述第二轴承时触发。
根据本申请的一些实施例，所述离心压缩机还包括：第三轴承和止推盘，所述壳体还具有轴向轴承室，所述第三轴承设置于所述轴向轴承室，所述止推盘与所述转子相连，所述第三轴承包括：第二轴承座、第二波箔和第二顶箔，所述第二波箔位于所述第二顶箔与所述第二轴承座之间，且弹性推抵于所述第二顶箔，所述第二顶箔与所述止推盘在轴向上相对，所述第三轴承与所述止推盘在轴向上相对；其中在所述离心压缩机的轴向方向上，所述第二轴承与所述转子之间的轴向间隙，减去所述第二顶箔与所述止推盘之间的轴向间隙小于所述第二顶箔的厚度。
根据本申请的一些实施例，所述转子上设置有转子轴套，在所述离心压缩机的轴向方向上，所述第二轴承与所述转子轴套之间的轴向间隙，减去所述第二顶箔与所述止推盘之间的轴向间隙小于所述第二顶箔的厚度。
根据本申请的一些实施例，所述第三轴承与所述转子之间的轴向间隙小于所述轮盖密封与所述叶轮之间的轴向间隙，所述第三轴承与所述转子之间的轴向间隙还小于轮背密封与 所述止推盘之间的轴向间隙。
根据本申请的一些实施例，在所述第二顶箔处于极限压缩状态或磨损后，所述第二轴承与所述转子之间的轴向间隙小于等于所述第二顶箔与所述止推盘之间的轴向间隙。
根据本申请的一些实施例，所述第二轴承与所述轮背密封还设置有第二灌封层，所述第二灌封层与所述第一灌封层一体灌封。
根据本申请的一些实施例，所述第二灌封层内设置有第二传感器，所述第二传感器适于检测所述第二轴承承受的轴向压力，并在所述止推盘压抵所述第二轴承时触发。
根据本申请的一些实施例，所述转子包括一级转子和二级转子，所述径向轴承室包括对应所述一级转子的一级径向轴承室和对应所述二级转子的二级径向轴承室，所述一级径向轴承室内设置有一个所述第一轴承，所述二级径向轴承室内设置有一个所述第一轴承，所述轴向轴承室包括对应所述一级转子的一级轴向轴承室和对应所述二级转子的二级轴向轴承室，所述一级轴向轴承室内设置有一个所述第三轴承，所述二级轴向轴承室内设置有一个所述第三轴承，两个所述第三轴承位于所述止推盘的轴向两侧，所述一级转子的一端设置有一个所述第二轴承，所述二级转子的另一端设置有一个所述第二轴承。
根据本申请的一些实施例，所述一级轴向轴承室和所述二级轴向轴承室位于所述壳体的轴向两侧，所述止推盘包括：第一止推盘和第二止推盘，所述一级转子设置有所述第一止推盘，所述二级转子设置有所述第二止推盘，或所述一级轴向轴承室和所述二级轴向轴承室位于所述壳体的轴向同一侧，且两个所述第三轴承位于所述止推盘的轴向两侧。
根据本申请的一些实施例，所述第一轴承构造为径向动压轴承，所述第二轴承构造为滚珠轴承，第三轴承构造为轴向动压轴承。
一种控制方法，包括：获取第一传感器和第二传感器的触发时长以及触发次数；触发时长超过时长阈值或触发次数超过第一次数阈值，则提报故障并停机。
根据本申请的一些实施例，所述时长阈值为30s～60s，所述第一次数阈值为8次～12次。
根据本申请的一些实施例，所述控制方法还包括：获取第一传感器以及第二传感器触发次数；在第一时间阈值内，所述第一传感器的触发次数超过第二次数阈值，则提报第一轴承损坏告警，并紧急停机；在第一时间阈值内，所述第二传感器的触发次数超过第二次数阈值，则提报第三轴承损坏告警，并紧急停机。
本申请的附加方面和优点将在下面的描述中部分给出，部分将从下面的描述中变得明显，或通过本申请的实践了解到。
附图说明
图1是根据本申请一些实施例的离心压缩机侧视图；
图2是图1中A-A截面图；
图3是图2中B处放大图；
图4是图2中C处放大图；
图5是图2中D处放大图；
图6是根据本申请一些实施例的第二轴承与第一传感器、第二传感器等配合示意图；
图7是根据本申请一些实施例的控制方法流程图。
具体实施方式
下面详细描述本申请的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，旨在用于解释本申请，而不能理解为对本申请的限制。
下面参考图1-图7描述根据本申请实施例的离心压缩机1以及控制方法。
如图1和图2所示，根据本申请第一方面实施例的离心压缩机1，离心压缩机1包括：壳体11、转子、定子13、第一轴承以及第二轴承15。
壳体11设置有径向轴承室；转子和定子13均设置于壳体11；第一轴承设置于径向轴承室，第一轴承包括：第一轴承座、第一波箔和第一顶箔，第一波箔位于第一顶箔与第一轴承座之间，且弹性推抵于第一顶箔，第一顶箔与转子在径向上相对；第二轴承15设置于壳体11，第二轴承15与转子在径向上相对；在离心压缩机1的径向方向上，第二轴承15与转子之间的径向间隙，减去第一顶箔与转子之间的径向间隙小于第一顶箔的厚度。
本申请中定子13和转子均设置于壳体11内，定子13和转子可共同配合实现离心压缩机1具有压缩气体功能；第一轴承可以设置于壳体11的径向轴承室内，以实现安装固定于壳体11的预设位置，在第一轴承中，第一轴承座可以为第一轴承中部分其他部件(如第一波箔、第一顶箔)提供安装位，并可对第一轴承中部分其他部件起支撑、固定及保护作用，第一波箔与第一顶箔可以均设置于第一轴承座径向内侧，第一顶箔套设于转子外周，并与转子在径向上间隔一定距离，支撑转子径向悬浮，第一波箔设置于第一顶箔和第一轴承座之间，第一波箔可以为弹性波纹结构，具有良好的形变性能，可提升承载能力和性能稳定性；第二轴承15可以设置于壳体11，并与转子在径向上相对，第二轴承15用于转子的支撑以及定位。
本申请发明人注意到，相关技术中用于支撑转子径向悬浮的第一轴承，在因突然断电或者外界强烈的冲击导致转子失稳时，转子会撞击到第一轴承的第一顶箔上，迫使第一顶箔向外变形，挤压位于第一顶箔外侧的第一波箔，第一波箔会因转子撞击而出现大 的变形甚至塌陷，导致第一轴承失效。
对于上述现象，本申请发明人经过研究后，发现可以利用第一顶箔与第一波箔的位置关系，第一顶箔与第一波箔中第一顶箔为先与转子接触的部件，因此可以通过第二轴承15防护第一顶箔，以避免第一顶箔持续变形或损伤，进而也可以实现保护第一波箔。
基于此，本申请进一步使第二轴承15与转子之间的径向间隙，减去第一顶箔与转子之间的径向间隙小于第一顶箔的厚度。
本申请中第二轴承15可与第一轴承在轴向上依次设置，转子位于第二轴承15和第一顶箔内周，第一顶箔长期运行后可能具有一定磨损，使得第一顶箔与转子之间的径向间隙变短，而通过设置在离心压缩机1的径向方向上，第二轴承15与转子之间的径向间隙，减去第一顶箔与转子之间的径向间隙小于第一顶箔的厚度，使得当第一顶箔长期运行达到一定磨损程度后，第二轴承15可与转子接触，由此可以提前识别第一轴承的第一顶箔是否即将需要更换，可以防止第一顶箔继续磨损出现磨损严重甚至磨穿情况，可以保障第一顶箔正常且可靠工作。另外，当转子失稳(如：由突然断电或外界冲击等导致)在径向上向外移动，第二轴承15也可以在转子与第一顶箔、第一波箔之间起支撑和保护作用，可以保护第一顶箔和第一波箔的变形处于设计范围内，并保护位于第一顶箔外侧的第一波箔不会因受到转子冲击变形过度而无法恢复弹性。
根据本申请的离心压缩机1，通过设置第一轴承和第二轴承15，并限定第二轴承15与转子间径向间隙、第一顶箔与转子间径向间隙与第一顶箔的厚度大小关系，可以在转子失稳冲击时，对第一顶箔、第一波箔等起到良好的保护作用，可以提高第一轴承可靠性和寿命，提升转子工作性能和稳定性。并且，还可以提前识别第一轴承的第一顶箔是否需要更换，在第一轴承因长期频繁启停以及长期异常工况使用造成磨损后，能有效预测第一轴承的寿命，并有效保护第一轴承、密封部件等零件，减少维护成本。
如图2所示，根据本申请的一些实施例，离心压缩机1还包括：设置于转子的叶轮16，壳体11还包括：轮盖，叶轮16与轮盖相对一侧设置有轮盖密封17，另一侧设置有轮背密封18。
叶轮16设置于转子，转子转动可带动叶轮16转动，以实现气体导流及压缩；轮盖用于叶轮16的支撑、连接以及密封，且有助于保持转子的平衡，减少由于质量分布不均导致的振动；其中，叶轮16与轮盖相对的一侧设置有轮盖密封17，叶轮16背离轮盖的一侧设置有轮背密封18，轮盖密封17和轮背密封18均可以提高结构气密性，增强防气液泄漏作用，可以提高离心压缩机1的压缩效率。
如图2所示，根据本申请的一些实施例，第二轴承15与转子之间的径向间隙小于轮盖密封17与叶轮16之间的径向间隙。
当轮盖密封17与叶轮16之间的径向间隙小于等于第二轴承15与转子之间的径向间隙，会导致防气液泄漏性能差，且会降低整体结构运行稳定性，因此，通过将轮盖密封17与叶轮16之间的径向间隙和第二轴承15与转子之间的径向间隙大小关系限定在上述范围内，使得轮盖密封17与叶轮16之间的径向间隙小，有助于优化密封性能，提升防气体泄漏性能，提高工作效率，并提高转子运行稳定性。
如图2所示，根据本申请的一些实施例，第二轴承15与转子之间的径向间隙还小于轮背密封18与转子之间的径向间隙。
当轮背密封18与转子之间的径向间隙小于等于第二轴承15与转子之间的径向间隙，会导致防气液泄漏性能差，且会降低整体结构运行稳定性，因此，通过将轮背密封18与转子之间的径向间隙和第二轴承15与转子之间的径向间隙大小关系限定在上述范围内，使得轮背密封18与转子之间的径向间隙小，有助于优化密封性能，提升防气体泄漏性能，提高工作效率，并提高转子运行稳定性。
如图5所示，根据本申请的一些实施例，转子上设置有转子轴套25，转子轴套25与第二轴承15之间的径向间隙，减去第一顶箔与转子轴套25之间的径向间隙，小于第一顶箔的厚度。
转子的至少部分外周可套设有转子轴套25，转子轴套25位于转子与第二轴承15之间，这样，转子轴套25可以减小转子与第二轴承15之间的摩擦，可节省能量损耗并可起良好的保护作用。
转子轴套25与第二轴承15之间的径向间隙，减去第一顶箔与转子轴套25之间的径向间隙，小于第一顶箔的厚度。类似地，转子轴套25位于第二轴承15和第一顶箔内周，第一顶箔长期运行后可能具有一定磨损，使得第一顶箔与转子轴套25之间的径向间隙变短，而通过设置转子轴套25与第二轴承15之间的径向间隙，减去第一顶箔与转子轴套25之间的径向间隙，小于第一顶箔的厚度，使得当第一顶箔长期运行达到一定磨损程度后，第二轴承15可与转子轴套25接触，由此可以提前识别第一轴承的第一顶箔是否即将需要更换，可以防止第一顶箔继续磨损出现磨损严重甚至磨穿情况，可以保障第一顶箔正常且可靠工作。
如图5所示，根据本申请的一些实施例，第二轴承15与转子轴套25之间的径向间隙，小于轮背密封18与转子之间的径向间隙。
当轮背密封18与转子之间的径向间隙小于等于第二轴承15与转子轴套25之间的径向间隙，会导致防气液泄漏性能差，且会降低整体结构运行稳定性，因此，通过将轮背密封18与转子之间的径向间隙和第二轴承15与转子轴套25之间的径向间隙大小关系限定在上述范围内，使得轮背密封18与转子之间的径向间隙小，有助于优化密封性 能，提升防气体泄漏性能，提高工作效率，并提高转子运行稳定性。
如图5所示，根据本申请的一些实施例，第二轴承15与转子轴套25之间的径向间隙，小于轮盖密封17与叶轮16之间的径向间隙。
当轮盖密封17与叶轮16之间的径向间隙小于等于第二轴承15与转子轴套25之间的径向间隙，会导致防气液泄漏性能差，且会降低整体结构运行稳定性，因此，通过将轮盖密封17与叶轮16之间的径向间隙和第二轴承15与转子轴套25之间的径向间隙大小关系限定在上述范围内，使得轮盖密封17与叶轮16之间的径向间隙小，有助于优化密封性能，提升防气体泄漏性能，提高工作效率，并提高转子运行稳定性。
如图2所示，根据本申请的一些实施例，在第一顶箔处于极限压缩状态或磨损后，第一顶箔与转子之间的径向间隙大于等于第二轴承15与转子之间的径向间隙。
在第一顶箔未磨损或磨损程度微小情况下，第一顶箔正常悬浮支撑转子，转子外周面不会与在径向间隔的第二轴承15接触，第一顶箔、第一波箔与转子等均正常安全工作；当转子因断电或受外界冲击等原因突然失稳产生径向移动致使第一顶箔处于极限压缩状态，以及当第一顶箔长期运行后磨损等，会造成转子与第一顶箔间距缩短，第一顶箔与转子之间的径向间隙大于等于第二轴承15与转子之间的径向间隙，第二轴承15与转子在径向上的间距较第一顶箔与转子在径向上的间距相等或更短，此情况下，当转子在径向上向外移动，转子会先与间距更短的第二轴承15接触，从而第二轴承15可以在转子与第一顶箔、第一波箔之间起支撑和保护作用，可以保护第一顶箔和第一波箔的变形处于设计范围内，并保护位于第一顶箔外侧的第一波箔不会因受到转子冲击变形过度而无法恢复弹性。
如图3-图5所示，根据本申请的一些实施例，第二轴承15与轮背密封18通过第一灌封层19相连。
第一灌封层19可以为绝缘灌封胶，具体可以用环氧树脂、硅橡胶、聚氨酯等具有良好电绝缘性和密封性的材料，第一灌封层19位于第二轴承15与轮背密封18之间，可以将第二轴承15与轮背密封18隔开，第一灌封层19可以起到良好的缓冲作用，当第二轴承15保护过程中受到转子冲击时，第一灌封层19能进行缓冲，可以降低第二轴承15受损程度，从而可以提高第二轴承15寿命。
可以理解的是，绝缘灌封胶开始是液态，灌封后才开始固化，因此，还可以起到固定第二轴承15的作用，可以提高第二轴承15安装稳固性。
需要指出的是，本申请中第二轴承15与轮背密封18也可以通过其他工艺实现连接，例如，可以通过注塑连接。
如图3、图5及图6所示，根据本申请的一些实施例，第一灌封层19内设置有第 一传感器20，第一传感器20适于检测第二轴承15承受的径向压力，并在转子压抵第二轴承15时触发。
具体地，第一传感器20可以为压阻传感器，第一传感器20适于检测第二轴承15承受的径向压力，并在转子压抵第二轴承15时触发。当第一轴承在异常工况下受到转子剧烈冲击时，第一轴承的第一波箔被压缩，第一顶箔径向向外变形，转子冲击到第二轴承15上，此时第一传感器20监测到径向压力，可发出故障信号使离心压缩机1停机，从而能对第一轴承起到良好的保护作用；并且，当第一轴承的第一顶箔因启停磨损到一定程度后，第一顶箔与转子的径向间隙变大，转子易经常不间断地压抵第二轴承15，第一传感器20会对应不间断地监测到压力，包括在停机后第一传感器20能不间断地监测到压力(停机后是转子的重力)，说明第一顶箔因启停磨损严重，因此，第一传感器20还能起到提醒需更换第一顶箔，可以对第一顶箔、第一波箔以及第二轴承15起到监测和智能诊断的作用，以实现预测性维护，可以避免第一顶箔损坏后高速运转导致转子、叶轮16以及轮背密封18等零件进一步损坏，可以提高离心压缩机1工作可靠性，并节省维护成本。
可以理解的是，通过将第一传感器20布设于第二轴承15外侧的第一灌封层19，一方面，可以起到固定第一传感器20的作用，可以提高第一传感器20安装稳固性；另一方面，第一灌封层19还可以提供良好的绝缘和密封保护，可以保护第一传感器20以及第一传感器20的线束等不受损害，可以提高第一传感器20的工作可靠性、安全性以及耐用性。
需要指出的是，第一传感器20可构造为多个，优选地，如图6所示，第一传感器20构造为在第二轴承15周向上等距间隔设置的三个，以增大第一传感器20检测范围，并提高检测准确性。
如图2和图5所示，根据本申请的一些实施例，离心压缩机1还包括：第三轴承和止推盘22，壳体11还具有轴向轴承室112，第三轴承设置于轴向轴承室112，止推盘22与转子相连，第三轴承包括：第二轴承座、第二波箔和第二顶箔，第二波箔位于第二顶箔与第二轴承座之间，且弹性推抵于第二顶箔，第二顶箔与止推盘22在轴向上相对，第三轴承与止推盘22在轴向上相对。
其中，在离心压缩机1的轴向方向上，第二轴承15与转子之间的轴向间隙，减去第二顶箔与止推盘22之间的轴向间隙小于第二顶箔的厚度。
具体地，本申请中止推盘22与转子相连，用于承受转子由于气体压缩而产生的轴向力，以提高转子运行稳定性；第三轴承可以设置于壳体11的轴向轴承室112内，在第三轴承中，第二轴承座可以为轴向动压轴承中部分其他部件(如第二波箔、第二顶箔) 提供安装位，并可对轴向动压轴承中部分其他部件起支撑、固定及保护作用，第二波箔与第二顶箔可以均设置于第二轴承座在轴向上的一端，第二顶箔与止推盘22在轴向上相对，并间隔一定距离，支撑止推盘22与转子轴向悬浮，第二波箔设置于第二顶箔和第二轴承座之间，第二波箔可以为弹性波纹结构，具有良好的形变性能，可提升承载能力和性能稳定性。
类似地，本申请中第二顶箔长期运行后可能具有一定磨损，使得第二顶箔与止推盘22之间的轴向间隙变短，而通过设置在离心压缩机1的轴向方向上，第二轴承15与转子之间的轴向间隙，减去第二顶箔与止推盘22之间的轴向间隙小于第二顶箔的厚度，使得当第二顶箔长期运行达到一定磨损程度后，第二轴承15可与转子接触，以此可以提前识别第三轴承的第二顶箔需要更换周期，可以防止第二顶箔继续磨损出现磨损严重甚至磨穿情况，可以保障第二顶箔正常且可靠工作。另外，当转子失稳在轴向上移动，第二轴承15也可以对第二顶箔、第二波箔等起支撑和保护作用，可以保护第二顶箔和第二波箔的变形处于设计范围内，并保护位于第二顶箔一侧的第二波箔不会因受到转子冲击变形过度而无法恢复弹性，这样，可以提升第二顶箔、第二波箔可靠性和寿命，提高转子、叶轮16、轮背密封18、轮盖密封17等部件工作性能和稳定性，并节省维护成本。
如图2和图5所示，根据本申请的一些实施例，转子上设置有转子轴套25，在离心压缩机1的轴向方向上，第二轴承15与转子轴套25之间的轴向间隙，减去第二顶箔与止推盘22之间的轴向间隙小于第二顶箔的厚度。
具体地，在转子上设置有转子轴套25的情况下，转子轴套25位于转子与第二轴承15之间，通过设置在离心压缩机1的轴向方向上，第二轴承15与转子轴套25之间的轴向间隙，减去第二顶箔与止推盘22之间的轴向间隙小于第二顶箔的厚度，使得当第二顶箔长期运行达到一定磨损程度后，第二轴承15可与转子轴套25接触，以此可以提前识别第三轴承的第二顶箔需要更换周期，可以防止第二顶箔继续磨损出现磨损严重甚至磨穿情况，可以保障第二顶箔正常且可靠工作。
如图2所示，根据本申请的一些实施例，第三轴承与转子之间的轴向间隙小于轮盖密封17与叶轮16之间的轴向间隙，第三轴承与转子之间的轴向间隙还小于轮背密封18与止推盘22之间的轴向间隙。
具体地，当轮盖密封17与叶轮16之间的轴向间隙以及轮背密封18与止推盘22之间的轴向间隙小于等于第三轴承与转子之间的轴向间隙，会导致防气液泄漏性能差，且会降低整体结构运行稳定性，因此，通过将轮盖密封17与叶轮16之间的轴向间隙、轮背密封18与止推盘22之间的轴向间隙和第三轴承与转子之间的轴向间隙大小关系限 定在上述范围内，使得轮盖密封17与叶轮16之间的轴向间隙以及轮背密封18与止推盘22之间的轴向间隙小，有助于优化密封性能，提升防气体泄漏性能，提高工作效率，并提高转子运行稳定性。
如图2所示，根据本申请的一些实施例，在第二顶箔处于极限压缩状态或磨损后，第二轴承15与转子之间的轴向间隙小于等于第二顶箔与止推盘22之间的轴向间隙。
具体地，在第二顶箔未磨损或磨损程度微小情况下，第二顶箔正常悬浮支撑止推盘以及转子，转子不会在轴向上与第二轴承15接触，第二顶箔、第二波箔与转子等均正常安全工作；当转子因断电或受外界冲击等原因突然失稳产生轴向移动致使第二顶箔处于极限压缩状态，以及当第二顶箔长期运行后磨损等，会造成止推盘与第二顶箔间距缩短，第二顶箔与止推盘之间的轴向间隙大于等于第二轴承15与转子之间的轴向间隙，第二轴承15与转子在轴向上的间距较第二顶箔与止推盘在轴向上的间距相等或更短，此情况下，当转子轴向移动，转子会先与第二轴承15接触，从而第二轴承15可以对第二顶箔、第二波箔起良好的保护作用，可以保护第二顶箔和第二波箔的变形处于设计范围内，并保护位于第二顶箔外侧的第二波箔不会因受到转子冲击变形过度而无法恢复弹性。
如图3所示，根据本申请的一些实施例，第二轴承15与轮背密封18还设置有第二灌封层23，第二灌封层23与第一灌封层19一体灌封。
具体地，第二灌封层23可以为绝缘灌封胶，具体可以用环氧树脂、硅橡胶、聚氨酯等具有良好电绝缘性和密封性的材料，第二灌封层23位于第二轴承15与轮背密封18之间，同样地，第二灌封层23可以将第二轴承15与轮背密封18隔开，第二灌封层23可以起到良好的缓冲作用，当第二轴承15保护过程中受到转子冲击时，第二灌封层23能进行缓冲，可以降低第二轴承15受损程度，从而可以提高第二轴承15寿命。
需要指出的是，第二灌封层23与第一灌封层19一体灌封，其中，第二灌封层23可以沿径向延伸，第二灌封层23位于第二轴承15与轮背密封18之间的径向区域，第一灌封层19可以沿轴向延伸，第一灌封层19位于第二轴承15与轮背密封18之间的轴向区域，这样，第二轴承15与轮背密封18间径向和轴向区域均填充有绝缘灌封胶，可以进一步提高第二轴承15安装稳固性。
如图4和图6所示，根据本申请的一些实施例，第二灌封层23内设置有第二传感器24，第二传感器24适于检测第二轴承15承受的轴向压力，并在止推盘22压抵第二轴承15时触发。
具体地，第二传感器24可以为一个或多个，第二传感器24构造为压阻传感器，适于检测第二轴承15承受的轴向压力，并在止推盘22压抵第二轴承15时触发。当第三 轴承在异常工况下受到转子、止推盘22剧烈冲击时，第三轴承的第二波箔被压缩，第二顶箔变形，止推盘22冲击到第二轴承15上，第二传感器24监测到轴向压力，可发出故障信号使离心压缩机1停机，从而能对第三轴承起到良好的保护作用；并且，当第三轴承的第二顶箔因启停磨损到一定程度后，第二顶箔与止推盘22的轴向间隙变大，转子易经常不间断地压抵第二轴承15，第二传感器24会对应不间断地监测到压力，并且重新启动后仍能继续监测到持续的压力，说明第二顶箔因启停磨损严重，因此，第二传感器24还能起到提醒需更换第二顶箔，可以对第二顶箔、第二波箔以及第二轴承15起到监测和智能诊断的作用，以实现预测性维护，可以避免第二顶箔损坏后高速运转导致止推盘22、转子、叶轮16以及轮背密封18等零件进一步损坏，可以提高离心压缩机1工作可靠性，并节省维护成本。
同样地，通过将第二传感器24布设于第二灌封层23，一方面，可以起到固定第二传感器24的作用，可以提高第二传感器24安装稳固性；另一方面，第二灌封层23还可以提供良好的绝缘和密封保护，可以保护第二传感器24以及第二传感器24的线束等不受损害，可以提高第一传感器20的工作可靠性、安全性以及耐用性。
如图2所示，根据本申请的一些实施例，转子包括一级转子12a和二级转子12b，径向轴承室包括对应一级转子12a的一级径向轴承室111a和对应二级转子12b的二级径向轴承室111b，一级径向轴承室111a内设置有一个第一轴承，二级径向轴承室111b内设置有一个第一轴承，轴向轴承室112包括对应一级转子12a的一级轴向轴承室和对应二级转子12b的二级轴向轴承室，一级轴向轴承室内设置有一个第三轴承，二级轴向轴承室内设置有一个第三轴承，一级转子12a的一端设置有一个第二轴承15，二级转子12b的另一端设置有一个第二轴承15。
具体地，一级转子12a与二级转子12b可以同轴布置并相连，一级径向轴承室111a与一级转子12a对应、二级径向轴承室111b与二级转子12b对应，一级径向轴承室111a和二级径向轴承室111b均设有第一轴承，以分别与一级转子12a和二级转子12b配合，以提升转子工作性能和运行稳定性；一级轴向轴承室与一级转子12a对应、二级轴向轴承室与二级转子12b对应，一级轴向轴承室和二级轴向轴承室均设有第三轴承，以分别与一级转子12a和二级转子12b配合，以提升转子工作性能和运行稳定性。
需要指出的是，第一轴承和第三轴承可以在转子上相邻布置，第一轴承和第三轴承可以安装于同一轴承室，该轴承室作为径向轴承室和轴向轴承室112使用，以提高第一轴承和第三轴承集成性。示例性地，如图2所示，一级径向轴承室111a与轴向轴承室112可为同一轴承室。
此外，在本申请的一些具体实施例中，设置于一级径向轴承室111a的第一轴承对 应具有一级第一轴承座141a、一级第一顶箔143a、一级第一波箔142a；设置于二级径向轴承室111b的第一轴承对应具有二级第一轴承座141b、二级第一顶箔143b、二级第一波箔142b。
如图2所示，根据本申请的一些实施例，一级轴向轴承室和二级轴向轴承室位于壳体11的轴向两侧，止推盘22包括：第一止推盘和第二止推盘，一级转子12a设置有第一止推盘，二级转子12b设置有第二止推盘，或一级轴向轴承室和二级轴向轴承室位于壳体11的轴向同一侧，且两个第三轴承位于止推盘22的轴向两侧。具体地，止推盘22、一级轴向轴承室以及二级轴向轴承室等具有多种布设方式。在一些实施例中，一级转子12a和二级转子12b均设置有止推盘22，且分别对应为第一止推盘和第二止推盘，一级轴向轴承室和二级轴向轴承室可以分别位于壳体11的轴向两侧，从而两个第三轴承分别位于壳体11轴向两侧，以分别与第一止推盘和第二止推盘配合，以实现对转子工作性能和平衡性进行优化；在另一些实施例中，一级转子12a和二级转子12b仅其中一个设置有止推盘22，即止推盘22设置于一级转子12a或二级转子12b，一级轴向轴承室和二级轴向轴承室可以位于壳体11轴向同一侧，两个第三轴承位于壳体11轴向同一侧，同时，两个第三轴承位于止推盘22的轴向两侧，以与止推盘22配合，以实现对转子工作性能和平衡性进行优化。
此外，需要指出的是，根据本申请的第三轴承中，在止推盘22轴向上的两侧均设置有第二轴承座、第二波箔、第二顶箔等结构，每个第三轴承中，第二轴承座包括位于止推盘22两侧的第一侧第二轴承座211c和第二侧第二轴承座211d，第二波箔包括位于止推盘22两侧的第一侧第二波箔212c和第二侧第二波箔212d，第二顶箔包括位于止推盘22两侧的第一侧第二顶箔213c和第二侧第二顶箔213d。
如图2所示，根据本申请的一些实施例，第一轴承构造为径向动压轴承，第二轴承15构造为滚珠轴承，第三轴承构造为轴向动压轴承。
具体地，径向动压轴承使用气体作为润滑介质，将第一轴承构造为径向动压轴承，可以实现径向悬浮支撑转子，有助于转子低摩擦、高速运转，可以节省能耗，提升转子工作性能、稳定性以及寿命；类似地，将第三轴承构造为轴向动压轴承，可以实现轴向悬浮支撑转子，有助于转子低摩擦、高速运转，可以节省能耗，提升转子工作性能、稳定性以及寿命；第二轴承15构造为滚珠轴承，示例性地，第二轴承15可以为角接触球轴承，由于滚珠轴承具有承载能力高、摩擦系数低、精度高、寿命长以及易于维护的优点，因此，通过将第二轴承15构造为滚珠轴承，使得第二轴承15可与转子配合，可以提高转子工作可靠性和寿命，还可以保障在恶劣工况转子冲击时，能对第一轴承和第三轴承起良好保护作用。
如图7所示，根据本申请第二实施例的控制方法，适用于上述实施例中任一项所述的离心压缩机，控制方法包括：获取第一传感器20和第二传感器24的触发时长以及触发次数；触发时长超过时长阈值或触发次数超过第一次数阈值，则提报故障并停机。
具体地，根据本申请第二方面实施例的控制方法，可以根据所获取第一传感器20和第二传感器24的触发时长是否超过时长阈值，或根据所获取第一传感器20和第二传感器24的触发次数是否超过第一次数阈值，以作为是否提报故障并停机的判断准则，当触发时长超过时长阈值或触发次数超过第一次数阈值，则提报故障并停机，以及时进行维护更换，提升离心压缩机1工作性能、可靠性和安全性。
需要指出的是，上述的触发时长可以是单次触发时长，单次触发时长超过时长阈值时，可提报故障并停机，上述的触发时长也可以是多次触发时长的和，在多次触发时长之和超过时长阈值时，可提报故障并停机。
对应地，时长阈值可以是单次的，以与单次触发时长比较，时长阈值也可以是累积的，以与多次触发时长的和比较，以判断是否需要提报故障并停机。
如图7所示，根据本申请的一些实施例，时长阈值为30s～60s，第一次数阈值为8次～12次。
具体地，设置时长阈值过小或过大、第一次数阈值过小或过大，均会导致提报故障并停机的判定不准，影响提报准确性。通过将时长阈值、第一次数阈值设置在上述范围内，使得时长阈值以及第一次数阈值具有合理范围值，示例性地，时长阈值可以为40s或50s等，第一次数阈值可以设置为9次或10次等，这样，通过第一传感器20和第二传感器24的触发时长以及触发次数与时长阈值以及第一次数阈值进行比对，可以提高故障告警精准性，以便维护。
如图7所示，根据本申请的一些实施例，控制方法还包括：获取第一传感器20以及第二传感器24触发次数；在第一时间阈值内，第一传感器20的触发次数超过第二次数阈值，则提报第一轴承损坏告警，并紧急停机；在第一时间阈值内，第二传感器24的触发次数超过第二次数阈值，则提报第三轴承损坏告警，并紧急停机。
具体地，当第一传感器20和第二传感器24触发时，此时可能是恶劣工况造成有冲击第一顶箔和第二顶箔变形，转子压抵第二轴承15触发，也可能是第一轴承和第三轴承磨损严重，此时会陆续出现第一传感器20和第二传感器24触发，则需提示客户更换第一轴承和第三轴承(第一轴承、第三轴承摩擦寿命已开始接近尾声)，两种情况区别可据第一时间阈值以及第二次数阈值进行判定。具体判定体现为：在第一时间阈值内，第一传感器20的触发次数超过第二次数阈值，则提报第一轴承损坏告警，并紧急停机；在第一时间阈值内，第二传感器24的触发次数超过第二次数阈值，则提报第三轴承损 坏告警，并紧急停机。
可以理解的是，第一传感器20和第二传感器24均触发，说明第一轴承和第三轴承均出现异常；仅第一传感器20触发，说明仅第一轴承出现异常，而第三轴承正常；仅第二传感器24触发，说明仅第三轴承出现异常，而第一轴承正常。通过第一传感器20和第二传感器24的不同触发情况，可以准确知道具体哪部分轴承出现异常，可以有效提高维护便利性和效率。
此外，在本申请的一些具体实施例中，第一时间阈值为30min～90min，第二次数阈值为8次～12次，且第二次数阈值大于等于第一次数阈值。设置第一时间阈值过小或过大、第二次数阈值过小或过大，均会导致提报第一轴承、第三轴承损坏告警的判定不准，造成针对性维护更换不便。通过将第一时间阈值、第二次数阈值设置在上述范围内，使得第一时间阈值以及第二次数阈值具有合理范围值，示例性地，第一时间阈值可以为30min或60min等，第二次数阈值可以为11次或12次等，可以理解的是第二次数阈值大于等于第一次数阈值，例如，第二次数阈值为11次，则第一次数阈值最大为11次，这样，通过第一传感器20和第二传感器24的触发时长以及触发次数与第一时间阈值以及第二次数阈值进行比对，可以提高告警精准性，提高维护更换便利性和效率。
需要指出的是，上述的第二次数阈值是与单个第二轴承15触发次数比较，第一次数阈值是与转子两端的两个第二轴承15的触发次数所累积次数和比较。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示意性实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本申请的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
尽管已经示出和描述了本申请的实施例，本领域的普通技术人员可以理解：在不脱离本申请的原理和宗旨的情况下可以对这些实施例进行多种变化、修改、替换和变型，本申请的范围由权利要求及其等同物限定。

Claims (22)

  1. 一种离心压缩机，其中，包括：
    壳体，所述壳体设置有径向轴承室；
    转子和定子，所述转子和所述定子均设置于所述壳体；
    第一轴承，所述第一轴承设置于所述径向轴承室，所述第一轴承包括：第一轴承座、第一波箔和第一顶箔，所述第一波箔位于所述第一顶箔与所述第一轴承座之间，且弹性推抵于所述第一顶箔，所述第一顶箔与所述转子在径向上相对；
    第二轴承，所述第二轴承设置于所述壳体，所述第二轴承与所述转子在径向上相对；其中
    在所述离心压缩机的径向方向上，所述第二轴承与所述转子之间的径向间隙，减去所述第一顶箔与所述转子之间的径向间隙小于所述第一顶箔的厚度。
  2. 根据权利要求1所述的离心压缩机，其中，所述离心压缩机还包括：设置于所述转子的叶轮，所述壳体还包括：轮盖，所述叶轮与轮盖相对一侧设置有轮盖密封，另一侧设置有轮背密封。
  3. 根据权利要求2所述的离心压缩机，其中，所述第二轴承与所述转子之间的径向间隙小于所述轮盖密封与所述叶轮之间的径向间隙。
  4. 根据权利要求3所述的离心压缩机，其中，所述第二轴承与所述转子之间的径向间隙还小于轮背密封与所述转子之间的径向间隙。
  5. 根据权利要求2-4中任一项所述的离心压缩机，其中，所述转子上设置有转子轴套，所述转子轴套与所述第二轴承之间的径向间隙，减去所述第一顶箔与所述转子轴套之间的径向间隙，小于所述第一顶箔的厚度。
  6. 根据权利要求5所述的离心压缩机，其中，所述第二轴承与所述转子轴套之间的径向间隙，小于所述轮背密封与所述转子之间的径向间隙。
  7. 根据权利要求5所述的离心压缩机，其中，所述第二轴承与所述转子轴套之间的径向间隙，小于所述轮盖密封与所述叶轮之间的径向间隙。
  8. 根据权利要求2-7中任一项所述的离心压缩机，其中，在所述第一顶箔处于极限压缩状态或磨损后，所述第一顶箔与所述转子之间的径向间隙大于等于所述第二轴承与所述转子之间的径向间隙。
  9. 根据权利要求2-8中任一项所述的离心压缩机，其中，所述第二轴承与所述轮背密封通过第一灌封层相连。
  10. 根据权利要求9所述的离心压缩机，其中，所述第一灌封层内设置有第一传感器， 所述第一传感器适于检测所述第二轴承承受的径向压力，并在所述转子压抵所述第二轴承时触发。
  11. 根据权利要求9所述的离心压缩机，其中，还包括：第三轴承和止推盘，所述壳体还具有轴向轴承室，所述第三轴承设置于所述轴向轴承室，所述止推盘与所述转子相连，所述第三轴承包括：第二轴承座、第二波箔和第二顶箔，所述第二波箔位于所述第二顶箔与所述第二轴承座之间，且弹性推抵于所述第二顶箔，所述第二顶箔与所述止推盘在轴向上相对，所述第三轴承与所述止推盘在轴向上相对；其中
    在所述离心压缩机的轴向方向上，所述第二轴承与所述转子之间的轴向间隙，减去所述第二顶箔与所述止推盘之间的轴向间隙小于所述第二顶箔的厚度。
  12. 根据权利要求11所述的离心压缩机，其中，所述转子上设置有转子轴套，在所述离心压缩机的轴向方向上，所述第二轴承与所述转子轴套之间的轴向间隙，减去所述第二顶箔与所述止推盘之间的轴向间隙小于所述第二顶箔的厚度。
  13. 根据权利要求11所述的离心压缩机，其中，所述第三轴承与所述转子之间的轴向间隙小于所述轮盖密封与所述叶轮之间的轴向间隙，所述第三轴承与所述转子之间的轴向间隙还小于轮背密封与所述止推盘之间的轴向间隙。
  14. 根据权利要求11所述的离心压缩机，其中，在所述第二顶箔处于极限压缩状态或磨损后，所述第二轴承与所述转子之间的轴向间隙小于等于所述第二顶箔与所述止推盘之间的轴向间隙。
  15. 根据权利要求11所述的离心压缩机，其中，所述第二轴承与所述轮背密封还设置有第二灌封层，所述第二灌封层与所述第一灌封层一体灌封。
  16. 根据权利要求15所述的离心压缩机，其中，所述第二灌封层内设置有第二传感器，所述第二传感器适于检测所述第二轴承承受的轴向压力，并在所述止推盘压抵所述第二轴承时触发。
  17. 根据权利要求11所述的离心压缩机，其中，所述转子包括一级转子和二级转子，所述径向轴承室包括对应所述一级转子的一级径向轴承室和对应所述二级转子的二级径向轴承室，所述一级径向轴承室内设置有一个所述第一轴承，所述二级径向轴承室内设置有一个所述第一轴承，所述轴向轴承室包括对应所述一级转子的一级轴向轴承室和对应所述二级转子的二级轴向轴承室，所述一级轴向轴承室内设置有一个所述第三轴承，所述二级轴向轴承室内设置有一个所述第三轴承，所述一级转子的一端设置有一个所述第二轴承，所述二级转子的另一端设置有一个所述第二轴承。
  18. 根据权利要求17所述的离心压缩机，其中，所述一级轴向轴承室和所述二级轴向轴承室位于所述壳体的轴向两侧，所述止推盘包括：第一止推盘和第二止推盘，所述一级 转子设置有所述第一止推盘，所述二级转子设置有所述第二止推盘，或所述一级轴向轴承室和所述二级轴向轴承室位于所述壳体的轴向同一侧，且两个所述第三轴承位于所述止推盘的轴向两侧。
  19. 根据权利要求1-18中任一项所述的离心压缩机，其中，所述第一轴承构造为径向动压轴承，所述第二轴承构造为滚珠轴承，第三轴承构造为轴向动压轴承。
  20. 一种控制方法，适用于权利要求1-19中任一项所述的离心压缩机，其中，包括：
    获取第一传感器和第二传感器的触发时长以及触发次数；
    触发时长超过时长阈值或触发次数超过第一次数阈值，则提报故障并停机。
  21. 根据权利要求20所述的控制方法，其中，所述时长阈值为30s～60s，所述第一次数阈值为8次～12次。
  22. 根据权利要求21所述的控制方法，其中，所述控制方法还包括：
    获取第一传感器以及第二传感器触发次数；
    在第一时间阈值内，所述第一传感器的触发次数超过第二次数阈值，则提报第一轴承损坏告警，并紧急停机；
    在第一时间阈值内，所述第二传感器的触发次数超过第二次数阈值，则提报第三轴承损坏告警，并紧急停机。
PCT/CN2024/117253 2024-06-27 2024-09-05 离心压缩机以及控制方法 Pending WO2026000620A1 (zh)

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