Compressor

Abstract

The compressor includes a drive motor and a windwheel 1, the drive motor having a casing 2 and a rotor 3, the rotor 3 rotatably disposed within the casing 2, the windwheel 1 attached to a first axial end of the rotor 3, a thrust disk 4 also provided at the first axial end of the rotor 3, an axial bearing assembly 28 disposed between the thrust disk 4 and the windwheel 1, the axial bearing assembly 28 fixedly disposed relative to the casing 2, a first gap formed between the first end of the axial bearing assembly 28 and the windwheel 1, and a second gap formed between the second end of the axial bearing assembly 28 and the thrust disk 4. The air compressor reduces tolerance accumulation caused by the cooperation of parts in the axial bearing assembly 28 and ensures a more precise effective working clearance.

Description

[Technical Field]

[0001] This disclosure is based on and claims priority from Chinese Patent Application No. 202011002421.X, filed on September 22, 2020, which is incorporated herein by reference in its entirety.

[0002] The present disclosure relates to the field of air compression technology, and in particular to compressors. [Background technology]

[0003] In the process of variable frequency regulation of the centrifugal compressor, the outlet pressure gradually increases with the increase of power. After the gas is compressed by the centrifugal compressor, high pressure is formed in the air pressure cavity, and a pressure difference is formed between the high pressure behind the impeller and the atmospheric pressure at the intake port, thereby generating a forward axial force along the impeller in the whole axial system.

[0004] To achieve this goal, the associated air suspension centrifugal compressor uses dual radial air suspension bearings and dual axial air suspension bearings to operate with five degrees of freedom, with the front and rear radial bearings located on both sides of the motor stator and the front and second axial bearings located on both sides of the thrust disk. The requirements for the effective working clearance between the axial air suspension bearings and the thrust surfaces during operation are very strict. The effective working clearance is typically on the order of microns. This directly affects the load-bearing capacity and bearing life of the axial air suspension bearings. The adopted compressor integration solution has strict requirements for the thickness of the thrust disk and the size of the positioning step surfaces of the front and second axial bearing assemblies to ensure the effective working clearance of the axial air suspension bearings. However, assembling too many parts results in tolerance accumulation, making it impossible to guarantee the effective working clearance of the axial air suspension bearings. Summary of the Invention

[0005] The present disclosure provides a compressor including a drive motor and a wind wheel, wherein the drive motor includes a casing and a rotor, the rotor is rotatably disposed within the casing, the wind wheel is attached to a first axial end of the rotor, a thrust disk is also provided on the first axial end of the rotor, an axial bearing assembly is disposed between the thrust disk and the wind wheel, the axial bearing assembly is fixedly disposed relative to the casing, a gap is formed between a first end of the axial bearing assembly and the wind wheel, and a gap is formed between a second end of the axial bearing assembly and the thrust disk.

[0006] In some embodiments, the axial bearing assembly includes an annular fixed seat, the annular bearing seat disposed on an inner peripheral wall of the fixed seat, a first axial bearing disposed at a first end of the bearing seat, a second axial bearing disposed at a second end of the bearing seat, a gap formed between the first axial bearing and the windwheel, and a gap formed between the second axial bearing and the thrust disk.

[0007] In some embodiments, the first end of the bearing seat cooperates with an inner peripheral wall of the fixed seat to form a first annular slot, and the first axial bearing is mounted in the first annular slot.

[0008] In some embodiments, the windwheel is at least partially mounted within the first annular slot and has an annular seal fit with an inner peripheral wall of the fixed seat.

[0009] In some embodiments, the second end of the bearing seat cooperates with an inner peripheral wall of the fixed seat to form a second annular slot, and the second axial bearing is mounted in the second annular slot.

[0010] In some embodiments, the diameter of the thrust disk is less than or equal to the diameter of the second annular slot, and / or the thrust disk is at least partially mounted in the second annular slot.

[0011] In some embodiments, the radial displacement sensor is provided on the inner peripheral wall of a fixed seat corresponding to the thrust disk.

[0012] In some embodiments, the wind wheel includes an axial flange protruding toward the thrust disk, the thrust disk including a first locating surface facing the axial bearing assembly, the axial flange being disposed on an inner peripheral side of the axial bearing assembly, and the locating end side of the axial flange facing the thrust disk abutting the first locating surface.

[0013] In some embodiments, a mounting shaft is provided at a first axial end of the rotor, and the windwheel is attached to the mounting shaft.

[0014] In some embodiments, a locating boss is further provided on the first axial end of the rotor, the mounting shaft is located on the locating boss, the diameter of the locating boss is smaller than the diameter of the rotor, the diameter of the mounting shaft is smaller than the diameter of the locating boss, and the thrust disk is attached to the locating boss, the thickness of the locating boss is smaller than the thickness of the thrust disk.

[0015] In some embodiments, the wind wheel is surrounded on the outside by a volute (volute casing), and an impeller diffuser is provided on the side of the fixed seat facing the volute, and the impeller diffuser cooperates with the volute to form an air pressure flow path.

[0016] In some embodiments, the impeller diffuser is a vaneless diffuser, and the fixed seat has a mounting shoulder on which the volute is mounted.

[0017] In some embodiments, a cooling passage is formed in the axial bearing assembly, the cooling passage including a first fluid passage port, a second fluid passage port, and a circulation hole, and the first fluid passage port and the second fluid passage port are in communication with each other via the circulation hole.

[0018] In some embodiments, when the axial bearing assembly includes a fixed seat and a bearing seat, the first fluid passage port and the second fluid passage port are provided in the fixed seat, and the circulation hole passes through the fixed seat and / or the bearing seat.

[0019] In some embodiments, a plurality of circulation holes are provided, the plurality of circulation holes are connected to a first fluid passage port via a first communication passage, and the plurality of circulation holes are connected to a second fluid passage port via a second communication passage, and the first communication passage and the second communication passage are isolated from each other.

[0020] In some embodiments, the first fluid passage port extends in the axial direction of the fixed seat, the second fluid passage port extends in the axial direction of the fixed seat, the circulation hole extends in the radial direction of the fixed seat, the first communication passage is provided on the outer circumferential side of the fixed seat, and the second communication passage is provided on the outer circumferential side of the fixed seat.

[0021] In some embodiments, the first communication passage is located on the outer peripheral side of the circulation hole and extends circumferentially around the fixed seat, the second communication passage is located on the outer peripheral side of the circulation hole and extends circumferentially around the fixed seat, the first communication passage is located at a first end of the diameter of the fixed seat, and the second communication passage is located at a second end of the diameter.

[0022] In some embodiments, the first communication passage forms an open slot in the outer circumferential surface of the fixed seat, and / or the second communication passage forms an open slot in the outer circumferential surface of the fixed seat.

[0023] In some embodiments, the circulation holes are V-shaped, arc-shaped, or linear.

[0024] In some embodiments, a radial air bearing is provided at each end of the rotor, and the rotor is rotatably sleeved in the radial air bearing.

[0025] In some embodiments, a radial air bearing located at a first axial end of the rotor is positioned on a side of the thrust disk remote from the axial bearing assembly, and an axial displacement sensor is positioned on the end side of the radial air bearing facing the thrust disk.

[0026] The present disclosure provides a compressor including a drive motor and a wind wheel, wherein the drive motor includes a casing and a rotor, the rotor is rotatably disposed within the casing, the wind wheel is attached to a first end of the rotor, a thrust disk is also provided on the first end of the rotor, an axial bearing assembly is disposed between the thrust disk and the wind wheel, the axial bearing assembly is fixedly disposed relative to the casing, a gap is formed between the first end of the axial bearing assembly and the wind wheel, and a gap is formed between a second end of the axial bearing assembly and the thrust disk. In the case of a compressor, the axial bearing assembly is installed between the thrust disk and the wind wheel, so that the axial end side of the thrust disk and the wind wheel facing the axial bearing assembly form a thrust surface, and further, the front axial bearing assembly and the rear axial bearing assembly are arranged back to back in one axial bearing assembly, so that the measurement of the distance between the two bearing surfaces of the front axial bearing assembly and the rear axial bearing assembly is easier and more accurate, and precise control of the distance between the two bearing surfaces is achieved, so that in the design of the gap, it is necessary to ensure the spacing between the thrust disk and the wind wheel, and when precise adjustment of the gap between the axial bearing assembly and the thrust disk and the gap between the axial bearing assembly and the wind wheel is achieved, fewer positioning parameters and fewer parts are required, so that the accumulation of tolerances due to the assembly of parts is smaller, which reduces the accumulation of tolerances caused by the cooperation of parts between the axial bearing assemblies and more precisely ensures the effective working clearance. [Brief explanation of the drawings]

[0027] [Figure 1] FIG. 2 is a cross-sectional structural view of a compressor provided in some embodiments of the present disclosure. [Figure 2] FIG. 2 is a cross-sectional structural view of a compressor provided in some other embodiments of the present disclosure. [Figure 3] FIG. 2 is an enlarged structural view of FIG. 1 at the mounting position of the axial bearing assembly. [Figure 4] FIG. 2 is a cross-sectional view of an axial bearing assembly of a compressor according to some embodiments of the present disclosure. [Figure 5] FIG. 5 is a cross-sectional structural view taken along the line AA in FIG. [Figure 6] FIG. 10 is a cross-sectional structural view of an axial bearing assembly of a compressor provided in some other embodiments of the present disclosure. [Figure 7] FIG. 2 is a cross-sectional structural view of a wind wheel of a compressor provided in some embodiments of the present disclosure. [Figure 8] FIG. 2 is a cross-sectional structural view of a thrust disk of a compressor provided in some embodiments of the present disclosure. [Figure 9] FIG. 2 is a cross-sectional structural view of a radial air bearing of a compressor provided in some embodiments of the present disclosure. [Figure 10] FIG. 10 is a cross-sectional structural view of a radial air bearing of a compressor provided in some other embodiments of the present disclosure. [Figure 11] FIG. 2 is a cross-sectional structural view of a rotor of a compressor provided in some embodiments of the present disclosure. [Figure 12] FIG. 2 is an assembly diagram of a rotor, windwheel, and axial bearing assembly of a compressor provided in some embodiments of the present disclosure. [Figure 13] FIG. 2 is a cross-sectional structural view of a volute of a compressor provided in some embodiments of the present disclosure. DETAILED DESCRIPTION OF THE INVENTION

[0028] 1 to 13 in combination, according to an embodiment of the present disclosure, a compressor includes a drive motor and a windwheel 1, and the drive motor includes a casing 2 and a rotor 3. The rotor 3 is rotatably disposed within the casing 2, the windwheel 1 is attached to a first axial end of the rotor 3, and a thrust disk 4 is also provided on the first axial end of the rotor 3. An axial bearing assembly 28 is disposed between the thrust disk 4 and the windwheel 1, and the axial bearing assembly 28 is fixedly disposed relative to the casing 2. A first gap is formed between a first end of the axial bearing assembly 28 and the windwheel 1, and a second gap is formed between a second end of the axial bearing assembly 28 and the thrust disk 4.

[0029] In the case of the compressor, the axial bearing assembly 28 is installed between the thrust disk and the wind wheel 1, so that the axial end sides of the thrust disk and the wind wheel 1 facing the axial bearing assembly 28 form thrust surfaces; furthermore, the first axial bearing 7 and the second axial bearing 8 are arranged back to back in one axial bearing assembly 28, and the thrust surfaces of the thrust disk and the wind wheel 1 cooperate with one axial bearing assembly 28 to implement axial restriction, so that the distance between the two bearing surfaces of the first axial bearing 7 and the second axial bearing 8 Measurement of the gap between the two bearing surfaces is easier and more accurate, precise control of the distance between the two bearing surfaces is achieved, and when designing the first and second gaps, precise adjustment of the first and second gaps is achieved by controlling the spacing between the thrust disk and the wind wheel 1, requiring fewer positioning parameters and fewer parts, resulting in smaller tolerance accumulation due to assembly of parts, which reduces the tolerance accumulation caused by the cooperation of parts between the axial bearing assembly 28 and allows for more precise adjustment of the effective working clearance.

[0030] The axial bearing assembly 28 includes a fixed seat 5 , a bearing seat 6 , a first axial bearing 7 and a second axial bearing 8 .

[0031] The axial bearing assembly 28 includes a bearing mounting seat including an annular fixed seat 5 and an annular bearing seat 6. The annular bearing seat 6 is disposed on the inner peripheral wall of the fixed seat 5, a first axial bearing 7 is disposed on a first end of the bearing seat 6, and a second axial bearing 8 is disposed on a second end of the bearing seat 6. A first gap is formed between the first axial bearing 7 and the windwheel 1, and a second gap is formed between the second axial bearing 8 and the thrust disk 4.

[0032] In some embodiments, the first axial bearing 7 and the second axial bearing 8 are integrated on the same bearing seat 6. One bearing seat 6 is used to implement two axial suspension controls, the back surface of the wind wheel 1 is used as a thrust surface, and the thrust surface of the thrust disk 4 cooperates with the thrust surface of the wind wheel 1 to form two thrust surfaces for axial restriction, thereby reducing the number of axial bearing assemblies 28, simplifying the structure of the axial bearing assemblies 28, and also reducing the overall axial thickness of the axial bearing assemblies 28, reducing the axial length of the rotor 3, and avoiding problems such as a decrease in the natural frequency of the rotor-shaft system and insufficient design allowance due to the axial length of the shaft system being too long, as well as an increase in the volume of the air compressor due to the rotor length being too long.

[0033] 3 and 4, the axial dimension of the bearing seat 6 is smaller than the axial dimension of the fixed seat 5, and the bearing seat 6 is located axially intermediate the fixed seat 5. Therefore, in the axial direction of the bearing seat 6, the bearing seat 6 and the fixed seat 5 form two annular slots, a first annular slot 9 and a second annular slot 10. A first end of the bearing seat 6 cooperates with the inner peripheral wall of the fixed seat 5 to form the first annular slot 9, and the first axial bearing 7 is mounted in the first annular slot 9. A second end of the bearing seat 6 cooperates with the inner peripheral wall of the fixed seat 5 to form the second annular slot 10, and the second bearing 8 is mounted in the second annular slot 10.

[0034] Since the bearing seat is disposed at a distance between the first axial bearing 7 and the second axial bearing 8, the operations of the first axial bearing 7 and the second axial bearing 8 do not interfere with each other, and the bearing seat 6 also cooperates with the fixing seat 5 to form annular slots for mounting the first axial bearing 7 and the second axial bearing 8, thereby facilitating the installation and fixing of the first axial bearing 7 and the second axial bearing 8.

[0035] The windwheel 1 is at least partially mounted in the first annular slot 9 and fits into an annular sealing fit with the inner peripheral wall of the fixed seat 5, so that the fixed seat 5 forms an annular seal with the windwheel 1. Mounting the windwheel 1 at least partially in the first annular slot 9 reduces the axial space of the rotor 3 occupied by the windwheel 1, so that the overall axial structure of the rotor 3 becomes more compact.

[0036] In an air compressor, the side where the windwheel 1 runs at high speed and compresses gas is the high-pressure gas side, i.e., the pneumatic section, while the side that drives the windwheel 1 and rotates at high speed is the low-pressure gas side, i.e., the motor side. As is well known, to ensure that the compressor's performance meets the required standards, in addition to carefully designing the overall compressor solution, it is also necessary to control the amount of compressed gas leakage—i.e., the amount of high-pressure gas leaking from the high-pressure side to the low-pressure side during compressor operation. To effectively suppress high-pressure gas leakage from the high-pressure gas side, in some embodiments, an annular sealing position is designed between the annular peripheral wall of the first annular slot 9 and the outer peripheral wall of the windwheel 1. The annular sealing position is used to position an annular seal. In some embodiments, the annular seal is an assembled part. In other embodiments, the annular seal is machined immediately after the tolerance is set at the annular seal position. There are various implementations of the sealing structure of the annular seal, and its structure and design depend on the usage requirements. The provided annular seal cooperates with the annular sealing surface formed by the outer peripheral wall of the windwheel 1 or the annular sealing surface formed by the annular peripheral wall of the first annular slot 9 to form an overall annular sealing arrangement.

[0037] The annular seal is attached to the outer circumferential surface of the wind wheel 1 or the inner circumferential surface of the annular peripheral wall of the first annular slot 9. The specific structural form of the annular seal is, for example, a comb-tooth structure filled with a sealing filler, and the annular rotational seal between the wind wheel 1 and the fixed seat 5 is achieved by the sealing filler.

[0038] In some embodiments, the diameter of the thrust disk 4 is equal to or less than the diameter of the second annular slot 10. The thrust disk 4 is at least partially mounted in the second annular slot 10, allowing the thrust disk 4 to be mounted within the second annular slot 10, thereby saving axial space in the rotor 3 and shortening the required axial length of the rotor 3, resulting in a more compact compressor structure. In some embodiments, the distance between the open end side of the second annular slot 10 and the bearing surface of the second axial bearing 8 is greater than the sum of the axial thickness of the thrust disk 4 and the air gap, and the entire thrust disk 4 is mounted within the second annular slot 10.

[0039] When assembling the complete compressor structure, the rotor's rotation axis must be taken into consideration. The inner diameter of the axial bearing assembly 28 must not be smaller than the diameter of the radial air bearing rotor. In the prior art shaft system solution, an axial bearing assembly is provided at each end of the thrust disk to axially restrict the thrust disk. In addition to the aforementioned problem of serious tolerance accumulation due to the large number of assembly parts, this structure also has the disadvantage that the inner diameter of the axial bearing assembly must not be smaller than the diameter of the radial air bearing rotor due to the rotor structure. Therefore, the thrust disk located inside the rotor's outer circle is not included in the cooperation area with the second axial bearing. Therefore, to ensure a sufficient cooperation area between the thrust disk and the axial bearing, the diameter of the thrust disk must be larger, which in turn requires a larger designed size for the thrust disk of the rotor-shaft system.

[0040] When designing rotor shaft system solutions for high speed or even ultra high speed, the designed outer diameter of the thrust disk is determined not to be too small due to the limitation of rotor diameter, because the smaller the outer diameter for assembling the parts, the higher the designed strength of the parts will be and the more it will help improve the performance of the rotor shaft system.

[0041] In the technical solution of the present disclosure, the back-to-back arrangement of the first axial bearing 7 and the second axial bearing 8 is implemented by using one axial bearing assembly 28, where the first axial bearing 7 is mounted in the first annular slot 9 described below, and the second axial bearing is mounted in the second annular slot 10. Both the first axial bearing 7 and the second axial bearing 8 are mounted between the thrust disk 4 and the windwheel 1. During assembly, first, the rotor with the thrust disk 4 is mounted vertically, then the bearing mounting seat for the intermediate axial bearing installed with the first axial bearing 7 and the second axial bearing 8 is mounted on the thrust disk 4, and then the windwheel 1 is assembled and locked to the rotor to form an integrated assembly. Next, the rotating shaft is assembled as shown in FIG. 12. In this way, the rotating shaft of the rotor does not need to pass through the first axial bearing 7 and the second axial bearing 8, and the first axial bearing 7 and the second axial bearing 8 do not need to be designed with a larger size to avoid the rotor. Therefore, a small size design of the shaft system components is achieved, and the modal performance and safety tolerance of the overall shaft system are guaranteed.

[0042] A radial displacement sensor 11 is provided on the inner peripheral wall of the fixed seat 5 corresponding to the thrust disk 4 , and the radial displacement of the rotor 3 is detected by the thrust disk 4 .

[0043] The windwheel 1 includes an axial flange 12 protruding toward the thrust disk 4, and the thrust disk 4 includes a first positioning surface 13 facing the axial bearing assembly 28. The axial flange 12 is disposed on the inner circumferential side of the axial bearing assembly 28, and a positioning end side 14 of the axial flange 12 facing the thrust disk 4 abuts against the first positioning surface 13. The axial flange 12 protrudes from the thrust surface of the windwheel 1 and protrudes toward the thrust surface of the thrust disk 4, i.e., the first positioning surface 13, thereby ensuring a gap between the positioning end side 14 of the axial flange 12 and the first positioning surface 13, thereby achieving precise adjustment of the cooperating gap of the axial bearing assembly 28, which is simpler in design and more convenient in implementation.

[0044] A mounting shaft 15 is provided on a first axial end of the rotor 3, and the windwheel 1 is attached to the mounting shaft 15. A positioning boss 16 is further provided on the first axial end of the rotor 3. The mounting shaft 15 is located on the positioning boss 16, and the diameter of the positioning boss 16 is smaller than the diameter of the rotor 3, and the diameter of the mounting shaft 15 is smaller than the diameter of the positioning boss 16. The thrust disk 4 is attached to the positioning boss 16, and the axial height h1 of the positioning boss 16 is smaller than the thickness of the thrust disk 4, so that the first positioning surface 13 of the thrust disk 4 is higher than the end side of the positioning boss 16, thereby avoiding the positioning boss 16 from interfering with the cooperation of the first positioning surface 13 and the positioning end side 14.

[0045] In an air bearing-supported compressor, the assembly adjustment of the effective working clearance of the axial bearing assembly 28 is one of the most important processes. The first axial bearing 7 is mounted at the first axial bearing mounting position of the centrally mounted bearing mounting seat, and the second axial bearing 8 is mounted at the second axial bearing mounting position, so that the two axial bearing assemblies 28, which would have been mounted on both sides of the thrust disk 4 and attached to the two parts respectively, are arranged back-to-back on one part, making it easier and more accurate to measure the distance between the bearing surface of the first axial bearing 7 and the bearing surface of the second axial bearing 8 after installation. Here, the second axial bearing 8 forms an effective working clearance with the thrust surface of the thrust disk 4, and the first axial bearing 7 forms an effective working clearance with the thrust surface of the windwheel 1.

[0046] Two axial bearing thrust surfaces are distributed on the thrust disk 4 and the windwheel 1, respectively. The windwheel 1 is made of, for example, a bearing-supporting alloy steel material. In some embodiments, a wear-resistant alloy steel material is added to the bearing surface to function as a bearing surface from the viewpoint of lightweighting. The thrust disk 4 is made of alloy steel material. The effective working clearance between the thrust surface of the windwheel 1 and the thrust surface of the thrust disk 4 and the air axial bearing is determined by the first locating surface 13 of the thrust disk 4 and the axial flange height h2 of the windwheel 1. A certain tolerance is reserved for the axial flange 12 when the windwheel 1 is machined. Since the thrust disk 4 and windwheel 1 are both precision-machined parts, the distance between the two bearing surfaces of the axial bearing assembly 28 is accurately measured, and the effective working clearance of the axial bearing is added. Then, the height h2 of the axial flange is properly machined, and the axial height h1 of the rotor shaft positioning boss 16 is set smaller than the thickness of the thrust disk 4. The outer peripheral surface of the positioning boss 16 functions as the thrust disk assembly surface. The end side of the first end of the rotor functions as the thrust disk positioning surface, and the outer peripheral surface of the mounting shaft 15 functions as the impeller assembly surface. The machining accuracy of each assembly surface must be within the required range. The inner circular portion of the thrust surface of the thrust disk 4 also functions as the mounting and positioning surface for the axial flange 12 of the windwheel 1. By assembling the rotor 3, thrust disk 4, axial bearing assembly 28 and windwheel 1 in this order, the complete shaft system can be assembled, and the effective working clearance of the axial bearing assembly 28 is precisely adjusted by machining one dimension of one part (machining the axial flange height h2 of the windwheel 1), which not only optimizes and simplifies the machining process of the parts, but also simplifies the assembly and adjustment methods, greatly improving the process flow.

[0047] The wind wheel 1 is surrounded on the outside by a volute 17, and an impeller diffuser 18 is provided on the side of the fixed seat 5 facing the volute 17. The impeller diffuser 18 cooperates with the volute 17 to form an air pressure flow path. The impeller diffuser includes a vaned diffuser and a vaneless diffuser. In some embodiments, the impeller diffuser 18 is a vaneless diffuser, and the fixed seat 5 is provided with a mounting step 19, and the volute 17 is attached to the mounting step 19.

[0048] The intermediate mounted bearing mounting seat is machined with allowance set aside in the axial direction for machining the impeller diffuser 18. Since the impeller diffuser 18 needs to be combined with the volute 17 to form a complete flow path, in the split design the diffuser is designed as a flat surface and the complex structure is implemented in the volute 17, so the vaneless diffuser only needs to be machined into a flat surface, and then the impeller diffuser 18 and volute 17 are assembled and combined to form the complete air pressure flow path.

[0049] A cooling flow passage is formed in the axial bearing assembly 28, and the cooling flow passage includes a first fluid passage port 20, a second fluid passage port 21, and a circulation hole 22, and the first fluid passage port 20 and the second fluid passage port 21 are communicated via the circulation hole 22. The cooling flow passage is filled with a cooling fluid for cooling the axial bearing assembly 28.

[0050] In some embodiments, since the front axial bearing assembly and the rear axial bearing assembly are integrated to form one axial bearing assembly 28, the overall thickness of the fixed seat 5 for mounting the axial bearing assembly 28 is increased without increasing the axial length of the axial bearing assembly 28, thereby facilitating the design of the cooling system since both the fixed seat 5 and the bearing seat 6 have sufficient axial thickness to provide cooling channels.

[0051] When the compressor operates at high speeds, the working clearance between the thrust disk 4 and the axial bearing assembly 28 is very small, generally on the order of micrometers. High-speed friction between the high-pressure air and the surfaces of the axial bearing assembly 28 and the thrust disk 4 in such a small clearance generates a lot of heat, and a working clearance that is too small does not promote heat dissipation from the surfaces of the axial bearing assembly 28 and the thrust disk 4. After heating, the axial bearing assembly 28 and the thrust disk 4 deform due to axial thermal expansion. If the temperature becomes too high, the working clearance will be completely narrowed by the thermal expansion of the axial bearing assembly 28, resulting in locking. If the rotor suddenly locks at high speed, the entire compressor will be useless. If a foil-type axial bearing assembly 28 is used, its surface also has a layer of wear-resistant lubricating coating. If the temperature becomes too high, the wear-resistant lubricating coating may fail or even fall off, potentially causing serious damage to the compressor.

[0052] To address the above possibilities and reduce the temperature of the axial bearing assembly 28 during operation, the present disclosure provides cooling channels in the intermediately mounted bearing mounting seat to dissipate heat generated during operation of the axial bearing assembly 28 and thrust disk 4 by cooling fluid in the cooling channels, thereby effectively reducing the temperature of the axial bearing assembly 28 during operation.

[0053] In some embodiments, the first fluid passage port 20 and the second fluid passage port 21 are provided in the fixed seat 5, and the circulation hole 22 passes through the fixed seat 5 and / or the bearing seat 6. In some embodiments, the first fluid passage port 20 and the second fluid passage port 21 are provided in the fixed seat 5, and the circulation hole 22 passes through the fixed seat 5 and the bearing seat 6, thereby effectively cooling the entire bearing mounting seat and reducing the temperature of the bearing mounting seat during operation.

[0054] A plurality of circulation holes 22 are provided. The plurality of circulation holes 22 are connected to the first fluid passage port 20 via first communication passages 23, and the plurality of circulation holes 22 are connected to the second fluid passage port 21 via second communication passages 24. The first communication passage 23 and the second communication passage 24 are isolated from each other. The first communication passage 23 and the second communication passage 24 are connected only via the circulation holes 22, so that the cooling fluid cannot directly enter the second communication passage 24 via the first communication passage 23, or enter the first communication passage 23 via the second communication passage 24. Only after arriving at one of the communication passages from the fluid inlet, the cooling fluid is distributed by the communication passage. The cooling fluid enters each of the circulation holes 22 evenly, then flows from the circulation holes 22 to the other communication passages, converges through the other communication passages, and then flows out of the fluid outlet, thereby achieving cooling of the bearing mounting seat.

[0055] The first fluid passage port 20 extends in the axial direction of the fixed seat 5, the second fluid passage port 21 extends in the axial direction of the fixed seat 5, the circulation hole 22 extends in the radial direction of the fixed seat 5, the first communication passage 23 is provided on the outer circumferential side of the fixed seat 5, and the second communication passage 24 is provided on the outer circumferential side of the fixed seat 5. In some other embodiments, the first fluid passage port 20 and the second fluid passage port 21 extend in the radial direction, the first communication passage 23 extends in the circumferential direction, and the second communication passage 24 extends in the circumferential direction, so that the first fluid passage port 20, the first communication passage 23, the circulation hole 22, the second communication passage 24, and the second fluid passage port 21 are communicated to achieve a cooling flow path design.

[0056] The first communicating passage 23 is located on the outer peripheral side of the circulation hole 22 and extends in the circumferential direction of the fixed seat 5, the second communicating passage 24 is located on the outer peripheral side of the circulation hole 22 and extends in the circumferential direction of the fixed seat 5, the first communicating passage 23 is located at the first end of the diameter of the fixed seat 5, and the second communicating passage 24 is located at the second end of the diameter, so that the circulation hole 22 passes through the bearing mounting seat to the maximum extent and cools the entire bearing mounting seat more effectively, thereby improving the cooling effect.

[0057] In some embodiments, the first communicating passage 23 forms an open slot on the outer peripheral surface of the fixed seat 5, and the second communicating passage 24 forms an open slot on the outer peripheral surface of the fixed seat 5, thereby facilitating machining of the communicating passages. The communicating passages are provided in the mounting step 19 of the fixed seat 5. During installation, the volute 17 is fixedly disposed on the mounting step 19 after machining of the communicating passages is completed. Sealing of the first communicating passage 23 and the second communicating passage 24 is achieved by the cooperating mounting surfaces of the volute 17. To improve the sealing effect, seal rings, sealing grooves, etc. are provided on both sides of the first communicating passage 23 and the second communicating passage 24.

[0058] The circulation holes 22 can be V-shaped, arc-shaped, or straight. The above shapes can be formed by machining using simple machining methods with low machining costs. In some other embodiments, other forming methods are used to machine different circulation hole 22 configurations, such as serpentine circulation holes 22 or zigzag circulation holes 22.

[0059] A radial air bearing 25 is provided at each end of the rotor 3, the rotor 3 is rotatably sleeved in the radial air bearing 25, the radial air bearing 25 is fixed to the casing 2, and the fixed seat 5 is fixedly attached to the radial air bearing 25.

[0060] The fluid passage holes of the fixed seat 5 are connected to fluid passages pre-formed at corresponding positions in the liquid-cooled casing 2 and the radial air bearing 25 of the compressor in this embodiment. The outer hole of the fluid passage hole and the end side of the radial air bearing 25 are sealed by sealing grooves in combination with rubber rings to prevent leakage. The inner hole of the fluid passage hole is connected to a communication passage, which in turn communicates with all the circulation holes 22 to form a complete cooling cycle structure. Here, the communication passage is designed as an annular semi-open cooling passage for ease of machining. The sealing grooves on both sides of the communication passage are used in combination with the rubber rings and the annular sealing surfaces of the volute 17 to form a complete closed cooling passage to prevent cooling fluid leakage at the intermediate bearing mounting seat.

[0061] 1 and 4 in combination, in the installation of the complete compressor, the compressor is mounted and fixed with the rotor in a horizontal orientation, the lower fluid passage functions as the fluid inlet, and the upper fluid passage functions as the fluid outlet. The pressure of the complete compressor cooling system is used to push the cooling fluid through the fluid inlet at the bottom of the intermediate-mounted bearing mount, so that the cooling fluid fills the entire cooling channel and is then pushed out through the fluid outlet. This ensures full contact between the cooling fluid and the cooling channel to maximally remove heat generated by the axial bearing assembly 28 during operation and achieve maximum cooling of the axial bearing assembly 28 on the intermediate-mounted bearing mount. As an important component connecting the motor side and the pneumatic section, the intermediate-mounted bearing mount has an avoidance round hole in the center through which the rotor passes, so that the internal circulation holes 22 are not distributed completely vertically as expected. In the present disclosure, the circulation holes 22 are designed to be V-shaped, arc-shaped, or linear, so that the circulation holes 22 pass through the bearing mounting seats as much as possible while avoiding circular holes, thereby improving the cooling effect. The structural form of the internal circulation holes 22 is not limited to the above-mentioned concentrated form, and the shape and number of the fluid passages can be appropriately designed by the designer according to the actual application.

[0062] Furthermore, as the pneumatic section of the air compressor constantly operates with compressed air, the temperature in the pneumatic cavity gradually rises, and the increased temperature is transmitted to the motor side through the metal casing of the air compressor, but does not promote heat dissipation on the motor side of the compressor. The intermediate bearing mounting seat with a circulating cooling channel acts as a barrier, and its cooling effect is used to prevent the heat generated by the pneumatic section from being transmitted to the motor side of the compressor, thereby ensuring the cooling of the motor side of the compressor.

[0063] The radial air bearing 25 located at the first end of the rotor 3 is arranged on the side of the thrust disk 4 away from the axial bearing assembly 28, and the axial displacement sensor 26 is arranged on the end side of the radial air bearing 25 facing the thrust disk 4. In combination with the above-mentioned solution in which the radial displacement sensor 11 is provided on the inner side of the fixed base 5 and faces the outer surface of the thrust disk 4, it is achieved that detection of both radial and axial displacements of the rotor 3 is performed by a single component, namely the thrust disk 4.

[0064] Since the air compressor supported by air bearings is a turbomachine that operates at high speed and high precision, the rotor needs to be monitored in real time during the development and testing stage or some special occasions, and the performance and dynamic stability of the bearings are determined by determining the moving trajectory of the rotor at different speeds and different working conditions. In order to achieve the dynamic monitoring of the rotor of the air compressor supported by air bearings, in the present disclosure, improvements and adjustments are made to the axial bearing assembly 28 and the radial air bearings near the axial bearing seats mounted in the middle. First, the size of the side of the axial bearing assembly 28 closer to the pneumatic section is increased, and two opposing holes are formed on the side of the axial bearing assembly 28 closer to the pneumatic section as rotor axial displacement sensor mounting positions for arranging rotor axial displacement sensors 26 to monitor the axial state when the rotor is operating. Two opposing holes distributed symmetrically or four opposing holes distributed in a cross shape are radially formed on the inner peripheral wall of the fixed seat 5 for the axial bearing seat as rotor radial displacement sensor mounting positions for arranging radial displacement sensors 11 to monitor the movement trajectory of the shaft when the rotor is operating. Furthermore, the outer circle of the thrust disk 4 is used as a rotor radial displacement monitoring surface after precision machining, and similarly, the end side of the thrust disk 4 not cooperating with the axial bearing assembly 28 is used as a rotor axial displacement monitoring surface after precision machining. Since both the rotor radial displacement monitoring surface and the rotor axial displacement monitoring surface are provided on the thrust disk 4, the effects of errors arising from machining of rotor shaft system components and assembly of different shaft system components, as well as bending and deformation of the rotor, are reduced, improving the accuracy of monitoring.

[0065] In describing the present disclosure, it should be understood that the orientations or positional relationships indicated by terms such as "center," "longitudinal," "lateral," "front," "rear," "left," "right," "vertical," "horizontal," "upper," "lower," "inner," and "outer" are orientations or positional relationships shown based on the drawings, and are merely for the convenience of simplifying the explanation and description of the present disclosure, instead of indicating or implying that the depicted devices or elements have a particular orientation or must be constructed and operated in a particular orientation, and therefore, the terms cannot be construed to limit the scope of protection of the present disclosure.

[0066] Finally, it should be noted that the above examples are only used to explain, rather than limit, the technical solutions of the present disclosure. Although the present disclosure is described in detail with reference to preferred embodiments, it should be understood that those skilled in the art can make modifications to the specific implementations of the present disclosure or make equivalent substitutions to some of its technical features, and such modifications and equivalent substitutions should be included in the scope of the technical solutions sought for protection in the present disclosure as long as they do not deviate from the spirit of the technical solutions of the present disclosure.

Claims

1. a drive motor having a casing (2) and a rotor (3), said rotor (3) being rotatably arranged within said casing (2); a wind wheel (1) attached to a first axial end of the rotor (3); a thrust disk (4) disposed at the first axial end of the rotor (3); an axial bearing assembly (28) fixed to the casing (2), the axial bearing assembly (28) being disposed between the thrust disk (4) and the windwheel (1); In a compressor having a first gap is formed between the axial bearing assembly (28) and the wind wheel (1), and a second gap is formed between the axial bearing assembly (28) and the thrust disk (4); The compressor further comprises a mounting shaft (15) disposed at the first axial end of the rotor (3), the wind wheel (1) being mounted on the mounting shaft (15); The compressor further comprises a positioning boss (16) disposed at the first axial end of the rotor (3), the mounting shaft (15) is positioned on the positioning boss (16), the diameter of the positioning boss (16) is smaller than the diameter of the rotor (3), the diameter of the mounting shaft (15) is smaller than the diameter of the positioning boss (16), the thrust disk (4) is mounted on the positioning boss (16), and the axial dimension of the positioning boss (16) is smaller than the axial dimension of the thrust disk (4).

2. The axial bearing assembly (28) an annular fixed seat (5) fixed to the casing (2); an annular bearing seat (6) disposed on the inner peripheral wall of the annular fixed seat (5); a first axial bearing (7) disposed at a first axial end of the bearing seat (6); a second axial bearing (8) disposed at a second axial end of the bearing seat (6); and 2. The compressor according to claim 1, wherein the first air gap is formed between the first axial bearing (7) and the wind wheel (1), and the second air gap is formed between the second axial bearing (8) and the thrust disk (4).

3. 3. The compressor according to claim 2, wherein the axial dimension of the bearing seat (6) is smaller than the axial dimension of the fixed seat (5), the bearing seat (6) is located at the center of the fixed seat (5) in the axial direction, the first axial end of the bearing seat (6) and the inner peripheral wall of the fixed seat (5) form a first annular slot (9), and the first axial bearing (7) is installed in the first annular slot (9).

4. 4. The compressor according to claim 3, wherein the wind wheel (1) is at least partially mounted in the first annular slot (9) and is in annular sealing fit with the inner peripheral wall of the fixed seat (5).

5. 5. The compressor according to claim 2, wherein the second axial end of the bearing seat and the inner peripheral wall of the fixed seat form a second annular slot, and the second axial bearing is mounted in the second annular slot.

6. 6. The compressor of claim 5, wherein the diameter of the thrust disk (4) is equal to or less than the diameter of the second annular slot (10), and the thrust disk (4) is at least partially mounted within the second annular slot (10).

7. The device further includes a radial displacement sensor (11) disposed on the inner peripheral wall of the fixed seat (5), 7. The compressor according to claim 2, wherein the radial displacement sensor (11) is configured to detect the radial displacement of the rotor (3) by detecting the radial displacement of the thrust disk (4).

8. 8. The compressor according to claim 1, wherein the windwheel (1) has an axial flange (12) protruding toward the thrust disk (4), the thrust disk (4) has a first positioning surface (13) facing the axial bearing assembly (28), the axial flange (12) is arranged on an inner peripheral side of the axial bearing assembly (28), and a positioning end side (14) of the axial flange (12) facing the thrust disk (4) abuts against the first positioning surface (13).

9. a volute (17) surrounding the outside of the wind wheel (1); an impeller diffuser (18) arranged on the side of the fixed seat (5) facing the volute (17); and 8. The compressor of claim 2, wherein the impeller diffuser (18) cooperates with the volute (17) to define an air pressure flow path.

10. 10. The compressor according to claim 9, wherein a mounting step (19) is provided at a radial end of the fixed seat (5), and the volute (17) is mounted on the mounting step (19).

11. 3. The compressor according to claim 2, wherein a cooling passage is formed in the axial bearing assembly (28), the cooling passage having a first fluid passage port (20), a second fluid passage port (21), and a circulation hole (22), the first fluid passage port (20) and the second fluid passage port (21) being in communication with each other via the circulation hole (22).

12. 12. The compressor according to claim 11, wherein the first fluid passage port (20) and the second fluid passage port (21) are provided in the fixed seat (5), and the circulation hole (22) passes through the fixed seat (5) and / or the bearing seat (6).

13. 13. The compressor according to claim 11 or 12, wherein there are a plurality of circulation holes (22), the plurality of circulation holes (22) are in communication with the first fluid passage port (20) via a first communication passage (23), the plurality of circulation holes (22) are in communication with the second fluid passage port (21) via a second communication passage (24), and the first communication passage (23) and the second communication passage (24) are isolated from each other.

14. 14. The compressor according to claim 13, wherein the first fluid passage port (20) and the second fluid passage port (21) both extend in the axial direction of the fixed seat (5), the circulation hole (22) extends in the radial direction of the fixed seat (5), and the first communication passage (23) and the second communication passage (24) both are provided on the outer circumferential side of the fixed seat (5).

15. 15. The compressor according to claim 13 or 14, wherein the first communication passage (23) is located on an outer peripheral side of the circulation hole (22) and extends in a circumferential direction of the fixed seat (5), the second communication passage (24) is located on an outer peripheral side of the circulation hole (22) and extends in a circumferential direction of the fixed seat (5), the first communication passage (23) is located at a first radial end of the fixed seat (5), and the second communication passage (24) is located at a second radial end of the fixed seat (5).

16. 16. The compressor according to claim 13, wherein the first communication passage (23) is configured as an open slot formed in an outer peripheral surface of the fixed seat (5), and / or the second communication passage (24) is configured as an open slot formed in the outer peripheral surface of the fixed seat (5).

17. The compressor according to any one of claims 11 to 16, wherein the circulation holes (22) are configured in a V-shape, an arc shape or a straight line shape.

18. 18. The compressor according to claim 1, further comprising two radial air bearings (25), the radial air bearings (25) being arranged at both axial ends of the rotor (3), and the rotor (3) being rotatably sleeved in the radial air bearings (25).

19. 19. The compressor of claim 18, wherein the radial air bearing (25) located at the first axial end of the rotor (3) is arranged on a side of the thrust disk (4) remote from the axial bearing assembly (28), and an axial displacement sensor (26) is arranged on an end side of the radial air bearing (25) facing the thrust disk (4).

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