Two-stage dynamic pressure gas suspension centrifugal compressor, refrigerant circulation system and refrigeration equipment

Abstract

The present disclosure relates to a compressor, a refrigerant circulation system and a refrigeration device. The compressor includes: a housing and a motor drive system; the motor drive system includes a compressor rotor and a motor stator, the housing has a motor accommodating chamber and a compression chamber, the motor stator is fixedly arranged in the motor accommodating chamber and has a rotor mounting hole, and the compressor rotor is rotatably arranged in the housing; the motor stator is provided with a reflux flow hole extending along the axial direction of the compressor rotor, and part of the fluid in the motor accommodating chamber flows from one end of the motor stator to the other end of the motor stator through the reflux flow hole. The present disclosure can improve the internal cooling effect of the compressor.

Description

Technical Field

[0001] The present disclosure relates to the field of compressors, and in particular to a two-stage dynamic pressure gas suspension centrifugal compressor, a refrigerant circulation system and a refrigeration device. Background Art

[0002] Centrifugal refrigeration compressors are high-speed compressors. The compressor rotor rotates at high speed during operation, and reliable bearings are required to support the rotor. The bearings used for conventional rotors mainly include rolling bearings, oil film bearings, and magnetic bearings. For rolling bearings and oil film bearings, the compressor requires an additional oil lubrication system and a complex oil supply system. At the same time, the refrigerant and lubricant must be compatible, and a separation system needs to be added to the system, which will make the entire system too complicated and large.

[0003] Due to the high bearing capacity of rolling bearings and oil film bearings, the motor rotors used in conventional centrifugal compressors are all one-piece structures. The compressor rotors of this structure are relatively heavy, which is not conducive to the improvement of the critical speed of the rotor. When making a larger rotor, the one-piece structure has a relatively complicated processing process and relatively high requirements for equipment, which will increase costs.

[0004] In addition, during the operation of the compressor, heat is generated due to mechanical loss, mainly due to the interaction between stator winding loss and rotor eddy current, which causes the temperature inside the compressor to rise sharply. If not cooled, excessive heat will affect the service life of the insulation material, reduce the output power of the motor, and cause the permanent magnet to demagnetize, and in severe cases burn the compressor parts.

[0005] Therefore, in order to solve the complex oil circuit system of the compressor, oil-free and environmentally friendly magnetic bearings have emerged. For magnetic bearings, the oil supply system and separation system are omitted, but a more complex control system is added. Since magnetic bearings require a stable power supply, a protection system needs to be added to prevent sudden power failure of the system, which increases the maintenance cost of the entire compressor and makes the structure more complicated.

[0006] In order to solve the critical speed problem of compressor rotors, existing compressors mainly increase the critical speed of the rotor by reducing the length of the rotor or increasing the stiffness of the bearings. However, reducing the length of the rotor is affected by the size of each component, and the degree of optimization that can be achieved is relatively small. Increasing the stiffness of the bearing requires increasing the volume of the bearing at high speeds, which will cause the compressor to become larger overall, contrary to the development trend of miniaturization.

[0007] As for the motor cooling problem, most of the centrifugal compressors in the prior art use evaporative or liquid spray cooling for the motor. This method mainly involves the liquid refrigerant passing through the motor cooling flow channel, absorbing the heat on the stator surface and turning into a gas. It is then discharged from the front end of the motor cavity, and returns to the rear end of the motor cavity through the gap between the stator and the rotor, and the surface of the motor rotor is cooled again. However, this cooling mainly involves the rotor and stator surfaces, and the internal cooling is not sufficient. There is temperature concentration inside the rotor. When the temperature is too high, it will cause the permanent magnet to demagnetize. Summary of the invention

[0008] In view of this, the embodiments of the present disclosure provide a compressor, a refrigerant circulation system and a refrigeration device, which can improve the cooling effect inside the compressor.

[0009] In one aspect of the present disclosure, a compressor is provided, comprising: a housing and a motor drive system; the motor drive system comprises a compressor rotor and a motor stator, the housing has a motor accommodating chamber and a compression chamber, the motor stator is fixedly arranged in the motor accommodating chamber and has a rotor mounting hole, and the compressor rotor is rotatably arranged in the housing;

[0010] The motor stator is provided with a reflux flow hole extending in the axial direction of the compressor rotor, and part of the fluid in the motor accommodating cavity flows from one end of the motor stator to the other end of the motor stator through the reflux flow hole.

[0011] In some embodiments, the return flow hole comprises:

[0012] a return air hole, located above the compressor rotor, for circulating gas; and / or,

[0013] The liquid return hole is located below the compressor rotor and is used for circulating liquid.

[0014] In some embodiments, a compression system is also included, the compression system including a volute, the volute having at least two volute profiles in different angular ranges.

[0015] In some embodiments, the at least two volute profiles include a first volute profile and a second volute profile distributed along the airflow direction inside the volute, and the parting interface between the first volute profile and the second volute profile is 80° to 100° relative to the direction of the airflow outlet of the volute pointing vertically from the center of the volute.

[0016] In some embodiments, the first volute profile is D-shaped, trapezoidal or elliptical, and the second volute profile is a circle with an angle greater than 180°.

[0017] In some embodiments, the compressor rotor comprises:

[0018] a motor rotor, located in the motor accommodating cavity and penetrating the rotor mounting hole, having a hollow portion and a vent hole, wherein the vent hole is connected to both the hollow portion and the motor accommodating cavity; and

[0019] The rotating part of the compression unit is located in the compression chamber, fixedly connected to the end of the motor rotor and forming an air intake passage connected to the hollow part with the motor rotor. The fluid in the compression chamber enters the hollow part through the air intake passage and enters the motor accommodating chamber through the air vent.

[0020] In some embodiments, the compressor rotor includes: a motor rotor, located in the motor accommodating cavity and penetrating the rotor mounting hole, having a hollow portion and a vent, wherein the vent is connected to both the hollow portion and the motor accommodating cavity; the motor rotor includes:

[0021] permanent magnet;

[0022] A first end shaft segment, fixedly disposed at a first end of the permanent magnet; and

[0023] The second end shaft segment is fixedly disposed on the second end of the permanent magnet.

[0024] In some embodiments, the compressor is a centrifugal compressor, and the rotating part of the compression unit is an impeller.

[0025] In some embodiments, a gas bearing is further included, and the compressor rotor is rotatably supported in the casing through the gas bearing.

[0026] In some embodiments, the first end shaft segment includes a first axial hole and a plurality of first through holes connecting the first axial hole and the motor accommodating cavity, the hollow portion includes the first axial hole, and the vent hole includes the first through hole; and / or,

[0027] The second end shaft segment includes a second axial hole and a plurality of second through holes connecting the second axial hole and the motor accommodating cavity, the hollow portion includes the second axial hole, and the vent hole includes the second through holes.

[0028] In some embodiments, an axial recess for cooperating with the rotating part of the compression unit is provided at the end of the motor rotor, a first leakage groove recessed radially outward is provided on the side wall of the axial recess, and the intake passage includes the first leakage groove; and / or

[0029] The end surface of the compression unit rotating part cooperates with the end surface of the motor rotor, the end surface of the compression unit rotating part is provided with a second leakage groove, and the intake passage includes the second leakage groove; and / or

[0030] The end surface of the rotating part of the compression unit cooperates with the end surface of the motor rotor, the end surface of the motor rotor is provided with a third leakage groove, and the intake passage includes the third leakage groove.

[0031] In some embodiments, the housing is provided with:

[0032] a cooling fluid inlet;

[0033] a spiral groove, disposed on the inner wall of the housing, and forming a spiral cooling channel with the outer peripheral surface of the motor stator, wherein a first end of the spiral cooling channel is communicated with the cooling fluid inlet, and a second end of the spiral cooling channel is communicated with the motor accommodating cavity at one end of the motor stator; and

[0034] The cooling fluid outlet is communicated with the motor accommodating cavity at the other end of the motor stator.

[0035] Therefore, according to the embodiment of the present disclosure, a recirculation hole extending along the axial direction of the compressor rotor is provided in the motor stator so that part of the fluid in the motor accommodating cavity flows from one end of the motor stator to the other end of the motor stator through the recirculation hole. In this way, the internal cooling of the motor stator is achieved by utilizing the recirculation hole, and the flow area of ​​the fluid during reflow is increased, which is beneficial to the heat dissipation of the motor. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] The accompanying drawings, which constitute a part of the specification, illustrate embodiments of the present disclosure and, together with the description, serve to explain the principles of the present disclosure.

[0037] The present disclosure may be more clearly understood from the following detailed description with reference to the accompanying drawings, in which:

[0038] Figure 1 is a schematic structural diagram of some embodiments of the compressor according to the present disclosure;

[0039] Figure 2-Figure 3 They are schematic diagrams of the structures of two motor rotors in some embodiments of the compressor according to the present disclosure;

[0040] Figure 4a and Figure 4b They are respectively a cross-sectional view and a structural schematic view of a volute in some embodiments of a compressor according to the present disclosure;

[0041] Figure 5a and Figure 5b They are cross-sectional schematic diagrams of a motor rotor and a motor stator according to some embodiments of the compressor disclosed herein;

[0042] Figure 6 is a schematic diagram of internal cooling fluid circulation in some embodiments of the compressor according to the present disclosure;

[0043] Figure 7 is a schematic structural diagram of a compressor rotor according to some embodiments of the compressor disclosed herein;

[0044] Figure 8 yes Figure 7 A schematic cross-sectional view of a motor rotor in an embodiment;

[0045] Fig. 9 yes Figure 7 A schematic structural diagram of the movable protrusion of the locking rod in the embodiment;

[0046] Fig.10 is a schematic structural diagram of a compressor rotor according to some embodiments of the compressor disclosed herein;

[0047] Fig.11 is a schematic structural diagram of a connecting rod in a compressor rotor according to some embodiments of the compressor disclosed herein;

[0048] Fig.12 is a schematic structural diagram of a locking nut in a compressor rotor according to some embodiments of the compressor disclosed herein;

[0049] Fig.13 is a schematic structural diagram of a compressor rotor according to other embodiments of the compressor disclosed herein;

[0050] Fig.14 is a schematic structural diagram of other embodiments of the compressor according to the present disclosure;

[0051] Fig.15 is a schematic structural diagram of a compressor rotor according to some embodiments of the compressor disclosed herein;

[0052] Fig.16 is a schematic structural diagram of a compressor rotor according to other embodiments of the compressor disclosed herein;

[0053] Figure 17-Figure 20 They are schematic diagrams of the structures of various motor rotors in some embodiments of the compressor disclosed herein;

[0054] Fig.21 is a schematic structural diagram of some further embodiments of the compressor according to the present disclosure;

[0055] Figure 22-Figure 23 They are schematic diagrams of the structures of two compressor rotors according to some embodiments of the compressor disclosed herein;

[0056] Fig.24 is a schematic structural diagram of some other embodiments of the compressor according to the present disclosure;

[0057] Fig.25 yes Fig.24 Schematic diagram of internal cooling fluid circulation in the embodiment;

[0058] Fig.26 is a schematic diagram of a cross-sectional structure of a motor rotor in some embodiments of the compressor disclosed herein;

[0059] Figure 27-Figure 29 They are schematic diagrams of three protrusion structures on the surface of the motor rotor in some embodiments of the compressor disclosed herein;

[0060] Fig.30 is a schematic structural diagram of other embodiments of the compressor according to the present disclosure;

[0061] Fig.31 yes Fig.30 A schematic diagram of the assembly of the bearing and the bearing support in the embodiment;

[0062] Fig.32 and Fig.33 They are respectively a three-dimensional structure and a cross-sectional schematic diagram of a bearing support according to some embodiments of the compressor disclosed herein;

[0063] Fig.34 is a partial structural schematic diagram of some embodiments of the compressor according to the present disclosure;

[0064] Fig.35 is a schematic diagram of the combined structure of a fixing plate and a bearing support in a bearing support assembly according to some embodiments of the compressor disclosed herein;

[0065] Fig.36 yes Fig.35 A schematic diagram of the bearing support structure in the embodiment;

[0066] Fig.37 is a structural schematic diagram of the assembly processing of the bearing support assembly according to some embodiments of the compressor disclosed herein;

[0067] Fig.38 and Fig.39 They are respectively a three-dimensional structure and a cross-sectional schematic diagram of a bearing support according to other embodiments of the compressor disclosed herein;

[0068] Fig.40 is a partial structural schematic diagram of other embodiments of the compressor according to the present disclosure;

[0069] Fig.41 is a schematic structural diagram of some embodiments of the compressor according to the present disclosure;

[0070] Fig.42 and Fig.43 They are respectively schematic cross-sectional and lateral structural diagrams of diffusers in some embodiments of the compressor according to the present disclosure;

[0071] Fig.44 is a partial structural schematic diagram of some embodiments of the compressor according to the present disclosure;

[0072] Fig.45 is a schematic structural diagram of other embodiments of the compressor according to the present disclosure;

[0073] Fig.46 is a schematic structural diagram of some further embodiments of the compressor according to the present disclosure;

[0074] Fig.47 is a schematic diagram of the installation structure of the diffuser, the thrust plate and the fixing plate in some other embodiments of the compressor disclosed herein;

[0075] Fig.48 is a schematic diagram of the installation structure of a diffuser, a thrust plate, a fixing plate and a bearing support in some other embodiments of the compressor disclosed herein;

[0076] Fig.49 is a schematic diagram of a fixed plate and a bearing support adopting an integrated structure according to some other embodiments of the compressor disclosed herein;

[0077] Fig.50 is a schematic diagram of the installation structure of the bearing support and the housing in some other embodiments of the compressor disclosed herein;

[0078] Fig.51 1 is a schematic structural diagram of a sealing structure in some further embodiments of the compressor disclosed herein.

[0079] It should be understood that the size of each part shown in the accompanying drawings is not drawn according to the actual proportional relationship. In addition, the same or similar reference numerals represent the same or similar components. DETAILED DESCRIPTION

[0080] Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative and is in no way intended to limit the present disclosure and its application or use. The present disclosure can be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are provided to make the present disclosure thorough and complete and to fully express the scope of the present disclosure to those skilled in the art. It should be noted that unless otherwise specifically stated, the relative arrangement of the components and steps, the composition of the materials, the numerical expressions and the numerical values ​​set forth in these embodiments should be interpreted as being merely exemplary and not as limiting.

[0081] The words "first", "second" and similar words used in this disclosure do not indicate any order, quantity or importance, but are only used to distinguish different parts. The words "include" or "comprise" and similar words mean that the elements before the word include the elements listed after the word, and do not exclude the possibility of including other elements. "Up", "down", "left", "right" and the like are only used to indicate relative positional relationships. When the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0082] In the present disclosure, when a specific device is described as being located between a first device and a second device, there may or may not be an intermediate device between the specific device and the first device or the second device. When a specific device is described as being connected to other devices, the specific device may be directly connected to the other device without an intermediate device, or may not be directly connected to the other device but have an intermediate device.

[0083] All terms (including technical terms or scientific terms) used in the present disclosure have the same meanings as those understood by ordinary technicians in the field to which the present disclosure belongs, unless otherwise specifically defined. It should also be understood that terms defined in general dictionaries, such as general dictionaries, should be interpreted as having meanings consistent with their meanings in the context of the relevant technology, and should not be interpreted in an idealized or extremely formal sense, unless explicitly defined herein.

[0084] Technologies, methods, and equipment known to ordinary technicians in the relevant art may not be discussed in detail, but where appropriate, the technologies, methods, and equipment should be considered as part of the specification.

[0085] like Figure 1 FIG. 1 is a schematic diagram of the internal structure of some embodiments of the compressor disclosed herein. Figure 1 and Figure 2-Figure 6 The present disclosure provides a compressor, including: a housing A-10, a compression system, a motor drive system, and a circulating air supply self-cooling system. Figure 1 In the embodiment, the housing A-10 has a motor accommodating chamber A-14 and a compression chamber.

[0086] The motor drive system may include a motor stator A-30 and a compressor rotor A-20. The motor stator A-30 may be fixedly disposed in the motor accommodation chamber A-14 and has a rotor mounting hole A-31. The compressor rotor A-20 may be rotatably disposed in the housing A-10, including the motor rotor A-21 and the compression unit rotating part.

[0087] The motor rotor A-21 is located in the motor accommodating cavity A-14 and is inserted into the rotor mounting hole A-31. The motor rotor A-21 has a hollow portion and a vent hole ( Figure 1The vent hole is not shown), and the vent hole is connected to the hollow portion and the motor accommodating chamber A-14.

[0088] The compression system may include a volute, a diffuser, a bearing support, etc. The housing A-10 includes a motor barrel A-11 and a volute disposed at at least one axial end of the motor barrel A-11. The volute may have at least two volute profiles in different angle ranges. For example, the housing A-10 includes a motor barrel A-11 and a first volute A-12 and a second volute A-13 disposed at both axial ends of the motor barrel A-11.

[0089] refer to Figure 4a and Figure 4b In some embodiments, at least two volute profiles include a first volute profile A-1a and a second volute profile A-1b distributed along the airflow direction inside the volute, and the parting interface between the first volute profile A-1a and the second volute profile A-1b is 80° to 100° relative to the direction from the center of the volute to the airflow outlet of the volute, so as to ensure that the flow rate in the volute does not change too drastically. The parting interface is preferably 90° relative to the direction from the center of the volute to the airflow outlet of the volute. Taking 90° as an example, the first volute profile at 0° to 90° can be D-shaped, that is, similar to the shape of a capital letter D. This shape makes it easy to clean the sand from the volute during casting, and the structure is simpler. In addition to the D-shape, the first volute profile can also be trapezoidal or elliptical. The second volute profile of 90° to 360° is preferably a circle greater than 180°. In other words, most of the circular volute profile is located inside the volute, which can reduce the size of the outer wall of the volute, thereby making the volute more miniaturized. In addition, the volute can be subdivided into multiple transition sections at the parting interface to achieve a uniform transition between the two volute profiles, thereby eliminating fluctuations in the airflow when it flows through the parting interface.

[0090] The rotating part of the compression unit is located in the compression chamber, fixedly connected to the end of the motor rotor A-21 and forming an air intake passage connected to the hollow part between the motor rotor A-21. The fluid in the compression chamber enters the hollow part through the air intake passage and enters the motor accommodating chamber A-14 through the air vent.

[0091] The compressor of the disclosed embodiment has a hollow portion and an air vent connected to the hollow portion and the motor accommodating chamber A-14 in the motor rotor A-21, and an air intake passage connected to the hollow portion is formed between the compression unit rotating portion and the motor rotor A-21. The fluid in the compression unit rotating portion can enter the hollow portion through the air intake passage. As the motor rotor A-21 rotates, the fluid can flow out from the air vent to the motor accommodating chamber A-14, thereby cooling the inside of the motor rotor A-21. This can solve the problem of concentrated heat generation in the motor rotor A-21, and is beneficial to ensuring sufficient cooling of the motor in the compressor, thereby achieving efficient and reliable operation.

[0092] like Figure 1 As shown, in some embodiments, the compressor may be a centrifugal compressor, and the compression unit rotating part is an impeller of the centrifugal compressor. The compression unit rotating part may be provided only on one side of the motor rotor, or on both sides of the motor rotor. The compression unit rotating part on each side may be single-stage or multi-stage. For example, when the compression unit rotating part is an impeller, the number of impellers on one side of the motor rotor may be one or more than two.

[0093] like Figure 1 As shown, in some embodiments, the compressor rotor A-20 includes a motor rotor A-21, a primary impeller A-22 and a secondary impeller A-23. The compressor rotor A-20 also includes a first locking rod A-24, a second locking rod A-25, a first locking nut A-26 and a second locking nut A-27. The primary impeller A-22 is fixed to the left end of the motor rotor A-21 by the first locking rod A-24 and the first locking nut A-26, and the secondary impeller A-23 is fixed to the right end of the motor rotor A-21 by the second locking rod A-25 and the second locking nut A-27. The first locking rod A-24 and the second locking rod A-25 can be integrally arranged with the motor rotor A-21, or they can be separately arranged and then connected together by a connection method such as a threaded connection. Corresponding to the primary impeller A-22 and the secondary impeller A-23, there are two compression chambers, namely the primary compression chamber A-15 and the secondary compression chamber A-16. The first-stage impeller A-22 is located in the first-stage compression chamber A-15, and the second-stage impeller A-23 is located in the second-stage compression chamber A-16.

[0094] In some embodiments not shown in the figure, the compressor may have other compression unit rotating parts, such as the compression unit rotating part may be a screw, and the movable scroll, roller, etc. are not excluded.

[0095] like Figure 1 As shown, in some embodiments, the compressor also includes a motor stator A-30, a first diffuser A-40, a first bearing support A-50, a first radial bearing A-60, a second diffuser A-60, a second bearing support A-80 and a second radial bearing A-90 and unmarked first thrust bearings and second thrust bearings.

[0096] like Figure 1 and Figure 6 As shown, the motor stator A-30 is fixed to the housing A-10 and has a rotor mounting hole A-31, and the motor rotor A-21 is inserted into the rotor mounting hole A-31.

[0097] The first bearing support A-50 and the second bearing support A-80 are respectively fixed inside the motor barrel A-11 of the housing A-10 and are respectively located at the axial ends of the motor stator A-30. The first radial bearing A-60 is located in the first bearing support A-50, and the second radial bearing A-90 is located in the second bearing support A-80. The first radial bearing A-60 and the second radial bearing A-90 are respectively supported at the axial ends of the motor rotor A-21, thereby supporting the motor rotor A-21 in the motor accommodating cavity A-14 in the motor barrel A-11 of the housing A-10.

[0098] The compressor rotor A-20 also includes a motor rotor A-21 disposed at one axial end ( Figure 1 A thrust plate A-28 is provided between the first bearing support A-50 and the thrust plate A-28, and a second thrust bearing is provided at one end of the first diffuser A-40 away from the diffuser structure on the diffuser A-40, so that the motor rotor A-21 is located in the motor accommodating cavity A-14 of the housing A-10 at the axial upper limit.

[0099] The first diffuser A-40 and the second diffuser A-70 respectively have a diffusion structure, such as a blade or a diffusion surface, and an integrated sealing structure, such as a comb tooth, so that the first diffuser A-40 and the second diffuser A-70 are also used to isolate the first-stage compression chamber A-15 from the motor accommodating chamber A-14 and to isolate the space where the second impeller A-23 of the second-stage compression chamber A-16 is located from the motor accommodating chamber A-14, to prevent the fluid in the first-stage compression chamber A-15 and the second-stage compression chamber A-16 from leaking into the motor accommodating chamber A-14 through the gap between the compressor rotor A-20 and the first diffuser A-40 and the gap between the compressor rotor A-20 and the second diffuser A-70.

[0100] like Figures 1 to 3 , Figure 6 As shown, in some embodiments, the motor rotor includes a permanent magnet A-211. The permanent magnet A-211 can generate a magnetic field for driving the motor rotor A-21 and the compressor rotor A-20 to rotate when the winding of the motor stator A-30 is energized.

[0101] The disclosed embodiments are applicable to motor cooling of various compressors, and are particularly applicable to motor cooling of compressors using permanent magnet synchronous motors. This helps solve the problem of uniformity in motor cooling and helps avoid motor damage caused by demagnetization of the permanent magnets of the motor rotor due to long-term operation in a high-temperature environment.

[0102] like Figures 1 to 3 , Figure 6 As shown, in some embodiments, the motor rotor A-21 includes a permanent magnet A-211, a first end shaft segment A-212, and a second end shaft segment A-213.

[0103] The permanent magnet A-211 can be Figure 2 The solid cylinder shown can also be Figure 3 The hollow cylinder with through holes shown. The permanent magnet A-211 as the motor rotor A-21 and the motor stator A-30 together form a motor that drives the compressor rotor A-20 to rotate. The material of the permanent magnet A-211 is, for example, magnetic steel.

[0104] The first end shaft segment A-212 is fixedly disposed at the first end of the permanent magnet A-211. The second end shaft segment A-213 is fixedly disposed at the second end of the permanent magnet A-211.

[0105] like Figure 2 and Figure 3 As shown, in some embodiments, the motor rotor A-21 further includes a mounting sleeve A-214 integrally provided at one end of the first end shaft segment A-212 close to the permanent magnet A-211. The permanent magnet A-211 and the second end shaft segment A-213 are fixedly mounted in the mounting sleeve A-214 by means of shrink fitting.

[0106] In some embodiments not shown in the figure, an independent mounting sleeve may be provided, and the first end shaft segment, the permanent magnet and the second end shaft segment are all mounted in the mounting sleeve by means of shrink fitting.

[0107] like Figure 2 and Figure 3 As shown, in some embodiments, the first end shaft segment A-212 includes a first axial hole A-2121 and a plurality of first through-holes A-2122 connecting the first axial hole A-2121 and the motor accommodating cavity A-14, the hollow portion includes the first axial hole A-2121, and the vent includes the first through-hole A-2122. The second end shaft segment A-213 includes a second axial hole A-2131 and a plurality of second through-holes A-2132 connecting the second axial hole A-2131 and the motor accommodating cavity A-14, the hollow portion includes the second axial hole A-2131, and the vent includes the second through-hole A-2132.

[0108] like Figure 2 , Figure 3 and Figure 6 As shown, the hollow part and the vent holes are axially symmetrically distributed. The hollow part is an axial hole, and the vent holes are radial holes. Multiple vent holes are evenly distributed on the corresponding shaft segments along the axial direction and the circumferential direction. The number of vent holes on the shaft segments at both ends can also be set to be the same and / or the angles can be set to be the same. The above various settings are conducive to the dynamic balance of the motor rotor A-21.

[0109] The multiple vents of the motor rotor A-21 can be arranged neatly, staggered, or spirally, etc. The cross-sectional shape of the vent is not limited, for example, it can be circular, square, triangular, etc.

[0110] like Figure 2 As shown, in some embodiments, the first axial hole A-2121 and the second axial hole A-2131 are both axial through holes. Figure 2 In the embodiment, the permanent magnet A-211 is a solid cylinder made of permanent magnets. At this time, air intake passages need to be provided at both ends of the motor rotor, and each air intake passage supplies fluid to the hollow portion of the corresponding end for cooling the motor rotor A-21.

[0111] For better cooling, one or more holes can be opened on the permanent magnet. On the one hand, these holes can allow fluid to enter the permanent magnet to better cool the motor rotor. On the other hand, the hole or holes connecting the two axial end faces of the permanent magnet can also play the role of connecting the hollow parts on both sides of the motor rotor. At this time, the air intake passages can be correspondingly arranged at both ends of the motor rotor, or the air intake passage can be arranged only at one end of the motor rotor.

[0112] like Figure 3 As shown, in some embodiments, one of the first axial hole A-2121 and the second axial hole A-2131 is an axial through hole, and the other is a blind hole with an open end facing the permanent magnet A-211, and the permanent magnet A-211 has a third axial hole A-2111 connecting the first axial hole A-2121 and the second axial hole A-2131. Influenced by the material of the permanent magnet, the size of the third axial hole A-2111 is preferably less than or equal to 4 mm in diameter.

[0113] like Figures 1 to 3 , Figure 6 As shown, in some embodiments, the end of the motor rotor A-21 is provided with an axial notch for cooperating with the rotating part of the compression unit, and the side wall of the axial notch is provided with a first leakage groove recessed radially outward, and the intake passage includes the first leakage groove. Figure 2 or Figure 3 In the figure, a first axial recess A-2123 is provided at the left end of the first end shaft segment A-211 at the left end of the motor rotor A-21, and a second axial recess A-2133 is provided at the right end of the second end shaft segment A-212 at the right end of the motor rotor A-21.

[0114] Combine the following Figure 5a The first leakage groove of an embodiment is described by taking the left end surface of the motor rotor A-21 as an example. Figure 5a As shown, four first leakage grooves A-2124 are arranged on the side wall of the first axial recess A-2123 at the left end of the first end shaft section A-211 at the left end of the motor rotor A-21. The four first leakage grooves A-2124 are evenly distributed along the axial direction of the motor rotor A-21. The cross-sectional shape of the first leakage grooves A-2124 is V-shaped.

[0115] exist Figure 2 In the embodiment shown, first leakage grooves are provided in the axial recesses at both left and right ends of the motor rotor A-21. Figure 3 In the illustrated embodiment, a first leakage groove is provided in an axial recess A-2133 at the right end of the motor rotor A-21.

[0116] like Figure 2 As shown, the first axial recess A-2123 is disposed at the end of the first axial hole A-2121, and the second axial recess A-2133 is disposed at the end of the first axial hole A-2131.

[0117] like Figure 3 As shown, the first axial recess A-2123 and the first axial hole A-2121 are respectively arranged at the two ends of the first end shaft segment A-212, and separated in the middle by a partition wall A-2125. The second axial recess A-2133 is arranged at the end of the first axial hole A-2131.

[0118] In some embodiments, the end surface of the rotating part of the compression unit cooperates with the end surface of the motor rotor A-21, and a second leakage groove is set on the end surface of the rotating part of the compression unit, and the intake passage includes the second leakage groove.

[0119] In some embodiments, the end surface of the rotating part of the compression unit cooperates with the end surface of the motor rotor A-21, and the end surface of the motor rotor A-21 is provided with a third leakage groove, and the intake passage includes the third leakage groove.

[0120] In order to allow the intake passage to introduce the fluid in the compression chamber into the hollow portion of the motor rotor A-21, in some embodiments, two or three of the first leakage groove, the second leakage groove and the third leakage groove may be included simultaneously.

[0121] The cross-sectional shapes of the aforementioned various leakage grooves are not limited, and in addition to the V-shape, they can also be, for example, arc-shaped, square-shaped, trapezoidal, U-shaped, etc. The number of the aforementioned various leakage grooves is also not limited, and for example, it can be less than 4 or greater than 4. The cross-sectional size of the leakage groove is preferably sufficient to allow the fluid used for cooling the motor rotor A-21 to pass through.

[0122] In the above embodiment, the motor rotor A-21 includes a three-section structure, the left and right end shaft sections are processed into a hollow structure, and the middle is an integral permanent magnet, which is conducive to simplifying the structure and reducing assembly. The motor rotor A-21 is provided with a plurality of vents, and a plurality of perforations are made on the motor rotor A-21 to form a honeycomb-like pore. When the motor rotor A-21 rotates at a high speed, the heat inside the motor rotor A-21 can be taken away by flowing a refrigerant or other fluid through the hollow part and the vents.

[0123] like Figure 1 , Figure 5b and Figure 6As shown, in some embodiments, the motor stator A-30 has a reflux hole arranged in the axial direction. The fluid in the motor accommodating chamber A-14 partially flows from one end of the motor stator A-30 to the other end of the motor stator A-30 through the reflux hole, and partially flows from one end of the motor stator A-30 to the other end of the motor stator A-30 through the matching gap A-311 between the rotor mounting hole A-31 and the motor rotor A-21.

[0124] like Figure 1 , Figure 5 and Figure 6 As shown, the return flow holes include: a gas return hole A-32, located above the compressor rotor A-20, for circulating gas; and / or, a liquid return hole A-33, located below the compressor rotor A-20, for circulating liquid. Referring to FIG5, in some embodiments, the return flow holes include three gas return holes A-32 and three liquid return holes A-33.

[0125] The provision of the reflux flow hole can cool the inside of the motor stator A-30, and also increases the flow area when the fluid refluxes, which is beneficial to the heat dissipation of the motor.

[0126] like Figure 6 As shown, in some embodiments, the housing A-10 is further provided with a cooling fluid inlet A-111, a spiral groove A-112 and a cooling fluid outlet A-113. The spiral groove A-112 is provided on the inner wall of the motor barrel A-11 of the housing A-10, and forms a spiral cooling channel with the outer peripheral surface of the motor stator A-30. The first end of the spiral cooling channel is connected to the cooling fluid inlet A-111, and the second end of the spiral cooling channel is connected to one end of the motor stator A-30 ( Figure 6 The cooling fluid outlet A-113 is connected to the other end (left end) of the motor stator A-30. Figure 6 The cooling fluid outlet A-113 is arranged at the right end of the motor cylinder A-11.

[0127] After the gas in the compression chamber leaks into the hollow part of the motor rotor A-21 through the air intake passage at one or both ends of the motor rotor, the motor rotor A-21 is cooled. Then, under the action of the high-speed rotation of the motor rotor A-21, the gas is thrown out from the air vent on the motor rotor A-21 into the motor accommodating chamber A-14, taking away the heat inside the motor rotor A-21, and mixing with the fluid entering the left end of the motor accommodating chamber A-14 through the spiral cooling flow channel, and then flows to the right end of the motor accommodating chamber through the reflux hole and the fitting gap A-311 between the rotor mounting hole A-31 and the motor rotor A-21, and then flows out of the compressor through the cooling fluid outlet A-113.

[0128] In the compressor of the present disclosure, the rotor may be supported on the housing by various types of bearings, such as sliding bearings, rolling bearings, hydraulic bearings, magnetic bearings, and the like.

[0129] In some embodiments, the compressor includes a gas bearing, and the compressor rotor A-20 is rotatably supported on the housing A-10 through the gas bearing. The gas bearing is, for example, a dynamic pressure gas bearing, or a static pressure gas bearing. The use of the gas bearing can use the same gas as the working gas compressed by the compressor as the suspension gas, so that the setting position of the vent hole of the motor rotor does not need to avoid the installation position of the gas bearing.

[0130] Since the motor rotor has a hollow portion, it is beneficial to reduce the weight of the motor rotor and is more suitable for gas bearing applications.

[0131] like Figure 1 As shown, in some embodiments, the first radial bearing A-60, the second radial bearing A-90, the first thrust bearing and the second thrust bearing are all hydrodynamic gas bearings.

[0132] Combine the following Figures 1 to 6 The compressors of the above embodiments are taken as refrigeration compressors used in a refrigerant circulation system as an example to illustrate the working process and principle of the motor cooling fluid circulation.

[0133] The refrigerant as cooling fluid enters the spiral cooling channel through the cooling fluid inlet A-111, and the cooling fluid flows in a spiral between the motor barrel A-11 and the motor stator A-30. The cooling fluid flowing in the spiral channel continuously absorbs heat and reduces the surface temperature of the motor stator A-30. The refrigerant as cooling fluid leaked from both ends of the motor rotor A-21 enters the hollow part of the motor rotor A-21, absorbs the heat inside the motor rotor A-21, and then is thrown out from the vent hole of the motor rotor A-21 under the action of high-speed rotation to cool the inside of the motor rotor A-21. After the refrigerant gathers at the left end of the motor accommodating chamber A-14, a part of it flows to the right end of the motor accommodating chamber A-14 through the matching gap A-311 between the motor stator A-30 and the motor rotor A-21, absorbing the heat of the outer surface of the motor rotor A-21. At the same time, since the motor stator A-30 is provided with an air return hole A-32 on the upper part and a liquid return hole A-33 on the lower part, the gaseous refrigerant at the left end of the motor accommodating chamber A-14 will also flow to the right end of the motor accommodating chamber A-14 through the air return hole A-32, and the liquid refrigerant at the left end of the motor accommodating chamber A-14 will flow to the right end of the motor accommodating chamber A-14 through the liquid return hole A-33, taking away the internal heat of the motor stator A-30 and making the motor cooling more sufficient.

[0134] When each radial bearing and each thrust bearing is a gas bearing, since each gas bearing is located in the motor accommodating chamber A-14, the refrigerant in the motor accommodating chamber A-14 can directly supply gas to the gas bearing and cool the gas bearing. Therefore, the compressor of the above embodiment is not only conducive to solving the internal cooling problem of the motor rotor A-21, but also can supply gas to the gas bearing of the compressor, eliminating the need for an external gas supply device, and further improving the working stability and reliability of the compressor.

[0135] The compressor of the disclosed embodiment can cool the motor rotor evenly, eliminate the phenomenon of local high temperature caused by concentrated heat, and help ensure the safe and reliable operation of the compressor.

[0136] In the above embodiment, combined with Figure 1-3 and Figure 6 The structure of the compressor rotor and the motor rotor in the motor drive system is shown. Figure 1 Also shown are assembly structures such as gas bearings, diffusers, and bearing supports. The following will describe other possible deformation structures of structures such as compressor rotors and motor rotors, motor drive systems, gas bearings, diffusers, and bearing supports, and assembly structures therebetween through multiple embodiments. It should be noted that the various specific technical features described in these embodiments of the present disclosure can be combined in any suitable manner without contradiction. In order to avoid unnecessary repetition, the various possible combinations will not be described separately in the embodiments of the present utility model.

[0137] Rotor structure modification example 1

[0138] refer to Figure 7-Figure 9 In some embodiments, a compressor rotor is provided, including a motor rotor B-10, a locking rod B-20, a compression unit rotating part and a locking component.

[0139] like Figure 7 As shown, the motor rotor B-10 includes a plurality of rotor segments fixedly connected in the axial direction, and the plurality of rotor segments have an axial through hole B-15. The locking rod B-20 passes through the axial through hole B-15. The compression unit rotating part is located at the end of the motor rotor B-10 and is connected to the locking rod B-20. The locking component locks the compression unit rotating part to the locking rod B-20. The locking rod, the compression unit rotating part and the locking component form a compression structure that applies pressure toward the axial inner side to the motor rotor B-10.

[0140] In the compressor rotor disclosed in the present invention, the motor rotor B-10 includes a plurality of rotor segments fixedly connected along the axial direction, and a locking rod B-20 is passed through the inside of the motor rotor B-10. The locking rod, the compression unit rotating part and the locking component form a clamping structure for applying axial pressure to the motor rotor B-10 toward the inner side. While the motor rotor B-10 can be processed in sections, the connection between the rotor segments of the motor rotor B-10 having multiple rotor segments can be made more reliable and firm.

[0141] like Figure 7 As shown, in some embodiments, the compressor may be a centrifugal compressor, and the compression unit rotating part is a centrifugal impeller of the centrifugal compressor. The compression unit rotating part may be arranged only on one side of the motor rotor, or on both sides of the motor rotor. The compression unit rotating part on each side may be single-stage or multi-stage. For example, when the compression unit rotating part is an impeller, the number of impellers on one side of the motor rotor may be one or more than two.

[0142] In some embodiments, both ends of the locking rod B-20 are respectively connected to the rotating part of the compression unit.

[0143] In some embodiments, an end of the locking rod B-20 is provided with an external thread, and the locking component includes a locking nut that cooperates with the external thread of the locking rod B-20.

[0144] like Figure 7 As shown, in some embodiments, the compressor rotor includes a motor rotor B-10, a primary centrifugal impeller B-30 and a secondary centrifugal impeller B-50. The left and right ends of the locking rod B-20 are respectively provided with external threads. The primary centrifugal impeller B-30 is locked to the left end of the locking rod B-20 by a first locking nut B-40 as a locking component. The secondary centrifugal impeller B-50 is locked to the right end of the locking rod B-20 by a second locking nut B-60 as a locking component.

[0145] like Figure 7 and Figure 8 As shown, in some embodiments, the axial through hole B-15 includes a small diameter section B-151 and a large diameter section having a diameter larger than the small diameter section B-151.

[0146] The axial through hole B-15 includes a small diameter section B-151 and a large diameter section whose diameter is larger than that of the small diameter section B-151. The motor rotor can be made into a hollow structure as much as possible according to the properties of each rotor section of the motor rotor B-10, thereby helping to reduce the overall weight of the motor rotor B-10 and the compressor rotor, and helping to increase the critical speed of the compressor rotor.

[0147] In some embodiments, the locking rod B-20 includes a rod body B-21 and a protrusion. The rod body B-21 cooperates with the small diameter section B-151 of the axial through hole B-15. The protrusion is arranged on the rod body B-21, protruding radially outward from the rod body B-21, and cooperates with the large diameter section of the axial through hole B-15.

[0148] The protrusion can improve the overall stiffness of the locking rod B-20 without increasing the overall weight of the compressor rotor too much, thereby facilitating the dynamic balance of the compressor rotor.

[0149] In some embodiments, the protrusion is a convex ring, which can provide support for the rod body B-21 at various circumferential positions, thereby facilitating the dynamic balance of the compressor rotor.

[0150] In some embodiments, the axial middle portion of the motor rotor B-10 includes a permanent magnet B-11, the small diameter segment B-151 is located in the axial middle portion of the axial through hole B-15, and the two large diameter segments are located at both ends of the axial through hole B-15. Figure 7 and Figure 8 As shown, the two large diameter sections are respectively a first large diameter section B-152 located at the left end of the motor rotor and a second large diameter section B-153 located at the right end of the motor rotor B-10.

[0151] For the motor rotor B-10 with multiple rotor segments, the axial middle portion is generally the location where the permanent magnet is set. The small diameter segment is set in this portion to reduce the impact of the axial through hole on the permanent magnet. The axial ends of the motor rotor B-10 are non-magnetic bodies. The large diameter segment is set in this portion to reduce the overall weight of the motor rotor and the compressor rotor, thereby facilitating the increase of the critical speed of the compressor rotor.

[0152] like Figure 7 As shown, the locking rod B-20 includes two protrusions, and the two protrusions are respectively matched with the two large diameter sections. This arrangement is conducive to improving the overall rigidity of the locking rod B-20, thereby facilitating the dynamic balance of the compressor rotor.

[0153] like Figure 7 As shown, one of the two protrusions is a fixed protrusion B-22 fixed on the rod body B-21, and the other is a movable protrusion B-23 movable relative to the rod body B-21. The fixed protrusion B-22 and the movable protrusion B-23 are respectively provided to facilitate the assembly of the locking rod B-20 and the motor rotor B-10.

[0154] like Figure 7 In the illustrated embodiment, the fixed protrusion B-22 cooperates with the first large diameter section B-152, and the movable protrusion B-23 cooperates with the second large diameter section B-153.

[0155] In some embodiments not shown in the figures, both of the two protrusions may be movable protrusions that are movable relative to the rod body.

[0156] In some embodiments, the movable protrusion B-23 is key-matched with the inner wall of the axial through hole B-15 to limit the circumferential position of the movable protrusion B-23 relative to the axial through hole B-15.

[0157] like Figures 7 to 9 As shown, a keyway B-1531 is provided on the hole wall of the second large diameter section B-153, and a key B-232 is provided on the outer periphery of the movable protrusion B-23. When the central hole B-231 of the movable protrusion B-23 is inserted between the rod body B-21 which has been penetrated in the axial through hole B-15 of the motor rotor B-10 and the inner wall of the second large diameter section B-153, the key B-232 cooperates with the keyway B-1531, and the circumferential position of the movable protrusion B-23 is limited.

[0158] Figures 7 to 9 Only the square key is shown in the figure. In the embodiment not shown in the figure, the key can also be fixed on the motor rotor and a groove is provided on the movable protrusion; the key can also be independent, and a key groove is provided on the motor rotor B-10 and the movable protrusion respectively. The key is not limited to the square key, and can also be a round key, a semicircular key or a spline, etc.

[0159] like Figure 7 As shown, in some embodiments, a shaft shoulder is provided on the rod body B-21, and the movable protrusion B-23 is located between the end surface of one end of the motor rotor B-10 and the shaft shoulder. For example, the movable protrusion B-23 can abut against the shaft shoulder. This arrangement is conducive to limiting the axial position of the movable protrusion B-23 and ensuring the stability of the rigidity of the locking rod B-20.

[0160] In some embodiments, the compression unit rotating part at one end of the motor rotor B-10 where the movable protrusion B-23 is located includes an axial boss extending into the axial through hole B-15, and the movable protrusion B-23 is axially limited between the aforementioned shaft shoulder and the end face of the axial boss.

[0161] like Figure 7 As shown, the left end of the second centrifugal impeller B-50 has an axial boss, the outer periphery of which cooperates with the inner wall of the right end of the second large diameter section B-153, and the left end face of the axial boss and the shaft shoulder on the rod body B-21 can limit the axial position of the movable protrusion B-23 within a certain range. When the distance between the left end face of the axial boss and the shaft shoulder is set equal to or slightly larger than the distance between the axial ends of the movable protrusion B-23, the axial position of the movable protrusion B-23 is basically determined, which is conducive to ensuring the stability of the rigidity of the locking rod B-20, thereby facilitating the dynamic balance of the compressor rotor.

[0162] In some embodiments, the matching clearance between the fixing protrusion B-22 and the corresponding large diameter section is smaller than the matching clearance between the rod body B-21 and the small diameter section B-151. This arrangement facilitates the rapid assembly of the compressor rotor.

[0163] In some embodiments, the movable protrusion B-23 is interference-fitted with the corresponding large-diameter section; the movable protrusion B-23 is clearance-fitted with the rod body B-21. This arrangement facilitates rapid assembly of the compressor rotor.

[0164] like Figure 7 As shown, in some embodiments, the multiple rotor segments of the motor rotor B-10 include a permanent magnet B-11, a first end shaft segment B-12, and a second end shaft segment B-13. The first end shaft segment B-12 is fixedly disposed at one end of the permanent magnet B-11. The second end shaft segment B-13 is fixedly disposed at the other end of the permanent magnet B-11.

[0165] The permanent magnet B-11 can be a hollow cylinder with an axial through hole. The permanent magnet B-11, as the motor rotor B-10, together with the motor stator of the compressor, constitutes a motor that drives the compressor rotor to rotate. The material of the permanent magnet B-11 is, for example, magnetic steel.

[0166] like Figure 7 As shown, in some embodiments, the motor rotor B-10 also includes a mounting sleeve B-14 integrally provided at one end of the first end shaft segment B-12 close to the permanent magnet B-11. The permanent magnet B-11 and the second end shaft segment B-13 are fixedly mounted in the mounting sleeve B-14 by shrink fitting.

[0167] In some embodiments not shown in the figure, an independent mounting sleeve may be provided, and the first end shaft segment, the permanent magnet and the second end shaft segment are all mounted in the mounting sleeve by means of shrink fitting.

[0168] The following combination Figures 7 to 9 Some embodiments of the present disclosure are described in more detail.

[0169] like Figures 7 to 9 As shown, the motor rotor B-10 of the compressor rotor of the embodiment of the present disclosure includes three rotor segments, namely, a permanent magnet B-11, a first end shaft segment B-12 and a second end shaft segment B-13, and a mounting sleeve B-14. The left end of the mounting sleeve B-14 is integrally arranged with the right end of the first end shaft segment B-12. The first end shaft segment B-12, the second end shaft segment B-13 and the permanent magnet B-11 are all processed into a hollow structure with an axial through hole. The second end shaft segment B-13 is similar in structure to the first end shaft segment B-12 but is symmetrically arranged, and the left end of the second end shaft segment B-13 is in the form of a step, which is beneficial for the outer diameter of the motor rotor B-10 to be equal after the three rotor segments are connected.

[0170] Each rotor segment is processed separately and ensures reasonable accuracy, and then assembled to form the motor rotor B-10. During the assembly process of the motor rotor B-10, the permanent magnet B-11 and the second end shaft segment B-13 are first glued together. Then the first end shaft segment B-12 and the mounting sleeve B-14 are heated to a higher temperature, such as 700-900°C, and then the permanent magnet B-11 and the second end shaft segment B-13 are quickly inserted into the mounting sleeve B-14. This method can shorten the time of the heat-sleeve interference connection and improve the success rate of assembly. Since the motor rotor B-10 is subjected to centrifugal force during high-speed rotation, there is a phenomenon of material expansion. In order to prevent the parts from loosening after the interference is reduced, the interference should be larger.

[0171] Since the three rotor sections are all hollow structures, the gas generated during the shrink fitting process can be discharged from the axial through hole B-15 without adding additional exhaust holes, which facilitates processing and helps improve the production efficiency of the motor rotor B-10.

[0172] The diameter of the axial through hole inside the permanent magnet B-11 is roughly the same as the diameter of the corresponding rod section of the rod body B-21 of the locking rod B-20. Considering the properties of the permanent magnet material, the diameter of the axial through hole inside the permanent magnet B-11 is preferably 1 / 4 to 1 / 3 times the outer diameter of the permanent magnet. Figure 7 As shown, the axial through hole inside the permanent magnet B-11 constitutes a part of the small diameter section B-151 of the axial through hole B-15 of the motor rotor B-10.

[0173] The axial through hole inside the permanent magnet B-11 and the corresponding rod section of the rod body B-21 are clearance-matched, and the clearance can be, for example, 0.03-0.05 mm. The roughness of the surface where the axial through hole of the permanent magnet B-11 contacts the rod body B-21 can be 0.8-1.6 μm, and this roughness range is conducive to preventing the surface peak from affecting the assembly.

[0174] Since the wall thickness of the installation sleeve is relatively thin, there will be a certain degree of strength problem after the interference connection. Using a locking rod B-20 in the radial middle of the motor rotor B-20 can increase the connection reliability.

[0175] Considering that the length of the locking rod B-20 is relatively long, which will affect its rigidity and strength, a fixed protrusion B-22 in the form of a supporting positioning step is processed on its left end to increase the rigidity so as to reduce the deflection of the locking rod B-20. The fixed protrusion B-22 and the first large diameter section B-152 have a clearance fit. The fitting clearance between the fixed protrusion B-22 and the first large diameter section B-152 can be smaller than the fitting clearance between the permanent magnet B-11 and the corresponding rod section B-21 of the locking rod B-20. The fitting clearance between the fixed protrusion B-22 and the first large diameter section B-152 can be, for example, 0.01 to 0.03 mm.

[0176] The right end of the locking rod B-20 is radially positioned by a movable protrusion B-23. The center hole B-231 of the movable protrusion B-23 is clearance-matched with the corresponding rod section B-21 of the locking rod B-20. The movable protrusion B-23 and the inner wall of the second large diameter section B-153 disposed in the second end shaft section B-13 are interference-fitted with a small amount of interference to radially position the right end of the locking rod B-20.

[0177] like Figure 8 and Fig. 9 As shown, the circumferential positioning of the movable protrusion B-23 is achieved by the cooperation of the key B-232 fixedly arranged on the movable protrusion B-23 and the key groove B-1531 on the inner wall of the second large diameter section B-153.

[0178] The second large diameter section B-153 and the movable protrusion B-23 are interference fit, the diameter of the second large diameter section B-153 is a negative deviation, the outer diameter of the movable protrusion B-23 is a positive deviation, and the total interference amount can be 0.01 to 0.02 mm.

[0179] During the assembly process of the motor rotor B-10, the locking rod B-20 and the centrifugal impeller, the movable protrusion B-23 and the motor rotor B-10 are cold assembled. First, the movable protrusion B-23 is installed to the left along the direction of the keyway B-1531, and then the rod body B-21 of the locking rod B-20 is inserted into the axial through hole B-15 of the motor rotor B-10 at the left end of the motor rotor B-10, and then the first-stage centrifugal impeller B-30 and the second-stage centrifugal impeller B-50 are respectively installed at the left and right ends of the rod body B-21, and then the first-stage centrifugal impeller B-30 and the second-stage centrifugal impeller B-50 are respectively pressed against the left and right ends of the motor rotor B-10 by the first locking nut B-40 and the second locking nut B-60 in a reverse tightening manner. After assembly, the locking rod B-20, the first-stage centrifugal impeller B-30, the second-stage centrifugal impeller B-50, the first locking nut B-40 and the second locking nut B-60 form a compression structure, which applies axial inward pressure to the motor rotor B-10, thereby strengthening and stabilizing the connection columns between the rotor sections of the motor rotor B-10.

[0180] The two end shaft sections are respectively installed at the axial ends of the permanent magnet B-11, and a first-stage centrifugal impeller is respectively installed on the two axial end faces of the motor rotor. It can also effectively avoid the problem of the motor rotor being too long caused by the two-stage centrifugal impellers of the two-stage centrifugal compressor being installed at the same end of the motor rotor.

[0181] like Figure 7As shown, the two centrifugal impellers are respectively positioned at the hollow parts of the first end shaft segment B-12 and the second end shaft segment B-13, that is, at the axial ends of the axial through hole B-15, and the radial and axial positioning of the centrifugal impeller relative to the motor rotor B-10 is carried out by relying on the positioning stop on the back of the centrifugal impeller.

[0182] The right section of the rod body of the locking rod B-20 is provided with an axial shoulder, and the movable protrusion B-23 is located between the axial shoulder and the end face of the axial boss of the positioning stop of the secondary centrifugal impeller B-50. The axial boss of the positioning stop of the secondary centrifugal impeller B-50 is clearance-matched with the movable protrusion B-23, and the clearance is, for example, 0.01 to 0.02 mm. This setting can effectively prevent the movable protrusion B-23 from moving axially inside the second large diameter section B-153, and is also conducive to preventing the secondary centrifugal impeller B-50 from being over-positioned in the axial direction during assembly.

[0183] When the gap distance between the axial boss of the positioning stop of the secondary centrifugal impeller B-50 and the movable protrusion B-23 is a small gap match, the axial positioning of the locking rod B-20 can also be achieved through the shaft shoulder.

[0184] According to the above description, it can be seen that the compressor rotor of the above embodiments of the present invention can effectively improve the rotor segment connection strength of the motor rotor having multiple rotor segments, and can also increase the critical speed of the rotor by reducing the length of the cantilever end, thereby further improving the working stability and reliability of the compressor and its motor in which the compressor rotor is located, thereby achieving high-speed operation, and making the compressor structure simpler, the system more concise, and the compressor more miniaturized.

[0185] Based on the above description of the modified example of the rotor structure, the embodiment of the present disclosure also provides a compressor, including the compressor rotor of the aforementioned embodiment of the present disclosure. The compressor of the embodiment of the present disclosure has the same advantages as the compressor rotor of the embodiment of the present disclosure. Further, in some embodiments, the compressor may include a gas bearing, and the compressor rotor is supported on the gas bearing. The gas bearing may include a radial bearing and a thrust bearing. The gas bearing may be a hydrodynamic gas bearing or a static gas bearing. In the compressor of the embodiment of the present disclosure, its compressor rotor has high working stability and reliability, and is suitable for being supported by gas bearings. The use of gas bearings can use the compressed working fluid as the suspended gas, thereby eliminating the lubricating oil system and oil separation system required when using rolling bearings or oil film bearings, and can reduce the complexity and occupied space of the fluid system in which the compressor is located, such as the refrigerant circulation system.

[0186] Rotor structure modification example 2

[0187] refer to Fig.10As shown, in some embodiments, a compressor rotor is provided, which includes an impeller C-1, a rotor shaft C-2 and a connecting rod C-3, the impeller C-1 is provided with a first connecting hole C-11, the rotor shaft C-2 is provided with a second connecting hole C-21, one end of the connecting rod C-3 is inserted into the first connecting hole C-11, and the connecting rod C-3 is detachably connected to the impeller C-1; the other end of the connecting rod C-3 is inserted into the second connecting hole C-21, and the connecting rod C-3 is detachably connected to the rotor shaft C-2.

[0188] In the above embodiment, the compressor rotor includes a connecting rod C-3, one end of the connecting rod C-3 is inserted into the first connecting hole C-11 and is detachably connected to the impeller C-1, and the other end of the connecting rod C-3 is inserted into the second connecting hole C-21 and is detachably connected to the rotor shaft C-2, so that the installation and disassembly of the impeller C-1 and the rotor shaft C-2 are relatively convenient, which solves the problem of difficult disassembly in the shrink fit method in the prior art. At the same time, no heating equipment is required, which simplifies the process and equipment of the impeller assembly, effectively improves the assembly efficiency, and improves the operability of later maintenance.

[0189] Furthermore, if Fig.11 As shown, the circumferential side of the connecting rod C-3 is provided with a boss C-31 extending in the radial direction, and the boss C-31 is used to support the connecting rod C-3. The boss C-31 can support the connecting rod C-3, effectively preventing the connecting rod cantilever from being too long and causing a large deflection, and preventing the connecting rod C-3 from being deformed when the rotor shaft rotates at high speed, effectively increasing the strength of the connecting rod and improving the service life of the connecting rod. The boss C-31 is also conducive to ensuring the concentricity of the connecting rod C-3, the impeller C-1 and the rotor shaft C-2.

[0190] The bosses C-31 may be arranged at intervals or continuously in the circumferential direction to form a convex ring.

[0191] The number of bosses C-31 can be flexibly set as needed. For example, the number of bosses C-31 is one, and the boss C-31 is set in the middle section of the connecting rod C-3; the number of bosses C-31 can also be multiple, and multiple bosses C-31 can be set at the same axial position of the connecting rod C-3 and arranged at intervals in the radial direction, or they can be set respectively at different axial positions of the connecting rod C-3 to achieve better support.

[0192] In comparison, the axial length of the rotor shaft C-2 is longer than the axial length of the impeller C-1. Therefore, the length of the second connecting hole C-21 is set longer than the length of the first connecting hole C-11. At this time, the boss C-31 can be set in the second connecting hole C-21 and cooperate with the inner wall clearance of the second connecting hole C-21 to support the connecting rod C-3, which is conducive to achieving a more balanced supporting effect.

[0193] There is a clearance fit between the boss C-31 and the second connecting hole C-21, and the clearance is between 0.03 mm and 0.05 mm. To ensure effective support, the axial length of the boss C-31 can be optionally greater than 10 mm.

[0194] Optionally, the second connection hole C-21 is a blind hole. The advantages of setting the second connection hole C-21 as a blind hole are, firstly, it can facilitate the connection between the connection rod C-3 and the rotor shaft C-2; secondly, it can ensure that the rotor shaft C-2 has sufficient strength.

[0195] There are many options for connecting the connecting rod C-3 and the rotor shaft C-2. Optionally, the end of the second connecting hole C-21 away from the impeller C-1 is provided with an internal thread, and the end of the connecting rod C-3 away from the impeller C-1 is provided with an external thread, and the connecting rod C-3 and the rotor shaft C-2 are connected by threads. The threaded connection method is not only convenient for installation and disassembly, but also can alleviate the stress concentration problem compared to the key connection method, and effectively improve the strength of the connecting rod C-3. In order to ensure the reliability of the connection, after the connecting rod C-3 and the rotor shaft C-2 are tightened by threads, they can also be bonded and fixed by fixing glue.

[0196] Specifically, the second connecting hole C-21 includes a first hole segment, a second hole segment and a third hole segment, wherein the first hole segment is arranged close to the impeller C-1, the second hole segment is arranged on the side of the first hole segment away from the impeller C-1, and the diameter of the second hole segment is smaller than the diameter of the first hole segment, and the third hole segment is arranged on the side of the second hole segment away from the impeller C-1, and the diameter of the third hole segment is smaller than the diameter of the second hole segment, and its inner wall is provided with an internal thread.

[0197] Among them, the end of the first hole segment away from the impeller C-1 is provided with a chamfer, and the setting of the chamfer can facilitate the opening of the first hole segment and reduce the difficulty of processing.

[0198] Accordingly, if Fig.11 As shown, the connecting rod C-3 includes a first rod segment C-32, a second rod segment C-33 and a third rod segment C-34. The first rod segment C-32 is arranged in the first hole segment, and the end face of the first rod segment C-32 away from the impeller C-1 is in close contact with the end face of the first hole segment to axially position the connecting rod C-3. The end face of the first rod segment C-32 away from the impeller C-1 and the end face of the first hole segment have relatively high machining accuracy. For example, the roughness Ra of the two end faces should meet: Ra≤3.2um, and the coaxiality relative to the center line of the rotor shaft C-2 should be ≤0.05mm to achieve precise positioning.

[0199] The diameter of the second rod segment C-33 is smaller than the diameter of the first rod segment C-32. The second rod segment C-33 is arranged in the second hole segment, and the axial length of the second rod segment C-33 is less than or equal to the length of the second hole segment. The second rod segment C-33 is used to radially position the connecting rod C-3. There is a clearance fit between the second rod segment C-33 and the second hole segment, and the clearance is controlled at 0.01mm to 0.03mm. In order to achieve a better radial positioning effect, the length of the second rod segment C-33 can be selected to be greater than or equal to 10mm.

[0200] The diameter of the third rod segment C-34 is smaller than the diameter of the second rod segment C-33. The third rod segment C-34 is arranged in the third hole segment, and the outer periphery of the third rod segment C-34 is provided with an external thread, which is locked with the internal thread in the third hole segment.

[0201] like Fig.10 As shown, the first connection hole C-11 is a through hole. The advantage of this arrangement is that it is easy to connect the connecting rod C-3 to the impeller C-1, and the connection position is transferred from the smaller space between the impeller C-1 and the rotor shaft C-2 to the side of the impeller C-1 away from the rotor shaft C-2, which has a larger operating space and is convenient for achieving a more reliable connection.

[0202] like Fig.12 As shown, a force-applying section C-35 is provided on a side of the first section C-32 of the connecting rod C-3 away from the second section C-33, and a fourth section C-36 is provided on a side of the force-applying section C-35 away from the first section C-32.

[0203] The cross section of the force-applying section C-35 is hexagonal in shape, so as to be matched with the screwing tool. The diameter of the force-applying section C-35 is smaller than the diameter of the first rod section C-32, and the diameter of the fourth rod section C-36 is smaller than the diameter of the force-applying section C-35.

[0204] In order to match the diameter change of the force-applying section C-35 and the fourth section C-36 on the connecting rod C-3, the first connecting hole C-11 is also a stepped hole, and the diameter of the hole section close to the rotor shaft C-2 is larger than the diameter of the hole section far from the rotor shaft C-2. The first section C-32 of the connecting rod C-3 and the force-applying section C-35 are located in the hole section with a larger diameter of the first connecting hole C-11. The fourth section C-36 matches the hole section with a smaller diameter of the first connecting hole C-11.

[0205] The specific connection mode of the connecting rod C-3 and the impeller C-1 can also have multiple options. In order to facilitate operation and assembly and disassembly, the compressor rotor also includes a connecting piece, which is used to connect the connecting rod C-3 and the impeller C-1.

[0206] Optionally, the connecting piece is a locking nut C-4. By setting the locking nut C-4, the connection between the connecting rod C-3 and the impeller C-1 is realized by a threaded connection method, which is not only convenient for installation and disassembly, but also can alleviate the stress concentration problem compared with the key connection method, and effectively improve the strength of the connecting rod C-3.

[0207] like Fig.12 As shown, the locking nut C-4 is provided with a connecting hole, and the connecting hole includes a first connecting hole section C-41 and a second connecting hole section C-42. The diameter of the first connecting hole section C-41 is larger than the diameter of the second connecting hole section C-42, and the first connecting hole section C-41 is closer to the impeller C-1 than the second connecting hole section C-42. This structural setting of the locking nut C-4 can make the locking nut C-4 pass through the connecting rod C-3 more smoothly, and the first connecting hole section C-41 with a larger diameter has a guiding effect; moreover, the connecting rod C-3 is threadedly matched with the second connecting hole section C-42, and the first connecting hole section C-41 is set as a light section, so that the end face of the locking nut C-4 can first contact and tighten with the end face of the impeller C-1, effectively avoiding interference with the root of the end of the external thread on the connecting rod C-3 or failure to tighten the impeller C-1, and ensuring the reliability of the connection.

[0208] The outer periphery of the fourth rod segment C-36 is provided with an external thread, and the inner wall of the second connecting hole segment C-42 of the locking nut C-4 is provided with an internal thread. The fourth rod segment C-36 and the locking nut C-4 are locked by threaded cooperation, and the locking nut C-4 is tightened on the end face of the impeller C-1 to achieve the locking of the connecting rod C-3 and the impeller C-1.

[0209] The specifications of the external threads on the fourth rod segment C-36 and the external threads on the third rod segment C-34 can be the same or different. The rotation direction of the external threads on the fourth rod segment C-36 and the external threads on the third rod segment C-34 is the same as the rotation direction of the rotor shaft C-2, which effectively prevents the threads from loosening during rotation.

[0210] Optionally, an insertion portion C-12 is provided at one end of the impeller C-1 close to the rotor shaft C-2, and the insertion portion C-12 is inserted into the second connection hole C-21. By providing the insertion portion C-12, the impeller C-1 and the rotor shaft C-2 can be pre-positioned to facilitate further connection.

[0211] The processing accuracy of the outer peripheral surface of the insertion part C-12 is higher than that of the non-insertion part, and the processing accuracy of the inner wall surface of the second connecting hole C-21 that matches the insertion part C-12 is higher than that of other parts of the inner wall surface, which is conducive to achieving precise positioning.

[0212] There is a clearance fit between the insertion portion C-12 and the second connection hole C-21, and the size of the clearance should be able to ensure smooth insertion while preventing the impeller C-1 from jumping too much during the rotation of the rotor shaft C-2.

[0213] Optionally, a first mating end surface is provided at one end of the impeller C-1 close to the rotor shaft C-2, and a second mating end surface is provided at one end of the rotor shaft C-2 close to the impeller C-1, and the first mating end surface is in tight contact with the second mating end surface.

[0214] The first mating end surface may be a boss protruding in the direction close to the rotor axis C-2 relative to the end surface of the impeller C-1 close to the rotor axis C-2, and the radial dimension of the boss is smaller than the radial dimension of the end surface of the impeller C-1. By setting the boss, only the end surface of the boss can be fine-machined, without the need to fine-machine the entire end surface of the impeller C-1, which is conducive to saving processing costs; at the same time, by setting the boss, processing can be facilitated and the processing difficulty can be reduced.

[0215] Similarly, the second mating end surface can be a section of a boss protruding in the direction close to the impeller C-1 relative to the end surface of the rotor shaft C-2 close to the impeller C-1, and the radial dimension of the boss is smaller than the radial dimension of the end surface of the rotor shaft C-2. By setting the boss, only the end surface of the boss can be fine-machined, and there is no need to fine-machine the entire end surface of the rotor shaft C-2, which is conducive to saving processing costs; at the same time, by setting the boss, processing can be facilitated and the processing difficulty can be reduced.

[0216] like Fig.13 As shown, the compressor rotor includes two sections of rotor shaft C-2, and a magnet is arranged between the two rotor shafts C-2. Among them, the right section of the rotor shaft C-2 on the left is provided with a receiving groove, and the magnet is arranged in the receiving groove, and the rotor shaft C-2 on the right is also at least partially located in the receiving groove, so that the connection between the two sections of the rotor shaft C-2 and the middle magnet is realized through the groove wall of the receiving groove. The diameter of the left section of the rotor shaft C-2 on the right is smaller than the diameter of the right section, so that when the left section is inserted into the receiving groove, it is limited by the step formed at the diameter change.

[0217] Correspondingly, the compressor rotor includes two impellers C-1, and the left rotor shaft C-2 can be connected to one of the impellers C-1 by the connection method in the above embodiment, and the right rotor shaft C-2 can also be connected to the other impeller C-1 by the connection method in the above embodiment.

[0218] Through the description of multiple compressor rotor embodiments corresponding to the rotor structure modification example, one or more of the following advantages can be known:

[0219] 1. The rotor shaft and the impeller are connected by a connecting rod, which is convenient for installation and disassembly, solving the problem that the shrink fit method is difficult to disassemble. At the same time, no heating equipment is required, which simplifies the impeller assembly process and equipment, effectively improves assembly efficiency, and facilitates later maintenance;

[0220] 2. A boss is provided on the connecting rod to support the connecting rod and improve the strength of the connecting rod;

[0221] 3. The connecting rod, impeller and rotor shaft are all connected by threads, which alleviates the stress concentration problem compared with the key connection method;

[0222] 4. The connecting rod is a stepped shaft, which can effectively position the connection of the connecting rod and help improve assembly efficiency;

[0223] 5. A stepped hole is provided inside the locking nut to effectively ensure that the locking nut is in tight contact with the impeller end face, achieving a better locking effect.

[0224] Based on the above description of the modified example of the rotor structure, the embodiment of the present disclosure also provides a compressor, including the compressor rotor of the aforementioned embodiment of the present disclosure. The compressor of the embodiment of the present disclosure has the same advantages as the compressor rotor of the embodiment of the present disclosure. In some embodiments, the compressor also includes a gas bearing, and the compressor rotor is supported on the gas bearing. The compressor can be a centrifugal compressor, and the connection reliability between the impeller and the rotor shaft is high, which is conducive to improving the refrigeration capacity of the compressor.

[0225] Rotor structure modification example 3

[0226] refer to Figure 14 to Figure 16 In some embodiments, a compressor rotor is provided, including a main shaft, an impeller D-14 and a locking component. A cavity D-111 is provided at the end of the main shaft to form a shaft core D-112 at the center of the main shaft, and the end of the shaft core D-112 extends out of the end of the main shaft so as to install the impeller D-14, and the shaft core D-112 serves as a supporting component of the impeller D-14; the impeller D-14 is sleeved on the outer end of the shaft core D-112 and axially positioned by the end of the outer ring of the main shaft; the locking component is used to lock the impeller D-14 on the shaft core D-112. The impeller D-14 can be installed at only one end of the main shaft, or at both ends at the same time.

[0227] The compressor rotor has at least one of the following advantages:

[0228] (1) The impeller and the main shaft are fixed by a locking component, so that the impeller is detachably arranged relative to the main shaft, which can reduce the difficulty of disassembling and assembling the impeller, simplify the assembly process and required equipment of the impeller, and improve the assembly efficiency and the operability of disassembly and maintenance.

[0229] (2) Compared with the shrink sleeve or keyway connection method, this installation method can not only prevent the main shaft or impeller from deformation, but also ensure the installation strength of the impeller and avoid stress concentration, thereby improving the compression capacity of the compressor.

[0230] (3) The shaft core is directly formed when the cavity is processed, so that the shaft core and the rest of the main shaft are processed into one piece. There is no need to install the shaft core in the cavity of the main shaft. This can further reduce the difficulty of assembly, increase the connection strength between the shaft core and the main shaft, and ensure the position accuracy of the shaft core. It can effectively solve the problem of the vibration of the front end of the rotor and reduce the length of the cantilever end, thereby improving the working stability and reliability of the compressor.

[0231] (4) By setting a cavity on the main shaft, the weight of the rotor can be reduced, the critical speed of the rotor can be increased, and the ultimate working capacity of the compressor can be further improved.

[0232] In some embodiments, the cavity D-111 is symmetrical with respect to the axis of the main shaft. When the rotor is working, the weight of the main shaft is evenly distributed, which can reduce the unbalanced force on the rotor during high-speed rotation.

[0233] For example, the cavity D-111 may be an annular groove concentric with the main shaft, and the annular groove is arranged along the entire circumference of the main shaft, which has a better weight reduction effect, is easy to form the shaft core D-112 after processing, and is conducive to the installation and positioning of the impeller D-14. Or the cavity D-111 includes a plurality of discrete holes, each hole is symmetrical with respect to the axis of the main shaft, and the hole can be a circular hole, a linear or arc-shaped oblong hole, etc. This structure can improve the rigidity of the main shaft and is easy to process.

[0234] like Fig.15 As shown, the inner end of the impeller D-14 is provided with a positioning portion D-141, which extends into the cavity D-111, and the outer wall of the positioning portion D-141 cooperates with the inner wall of the cavity D-111 to radially position the impeller D-14, and there is a gap between the inner wall of the positioning portion D-141 and the inner wall of the cavity D-111. In order to better solve the radial runout of the impeller D-14 at the front end, the length of the positioning portion D-141 embedded in the cavity D-111 can reach a preset length, for example, more than 20 mm.

[0235] This embodiment radially positions the impeller D-14 to ensure the radial installation accuracy of the impeller D-14 during the assembly process; moreover, there is a gap between the inner wall of the positioning portion D-141 and the inner wall of the cavity D-111, which can avoid over-positioning of the impeller D-14; in addition, the installation method in which the inner end of the impeller D-14 extends into the main shaft can improve the overall strength of the compressor rotor, reduce the deflection and deformation of the rotor end, and improve the stability of the rotor rotation.

[0236] In order to reduce the front end deflection problem caused by the excessive length of the shaft core D-112, the radial width of the cavity D-111 should be the same as the radial thickness of the impeller positioning portion D-141, and the accuracy should be precisely controlled, for example, a gap of 0.01-0.02mm can be guaranteed. In this structure, the positioning between the shaft core D-112, the impeller D-14 and the main shaft is mutually restricted, which can improve the overall rigidity of the structure.

[0237] For the embodiment in which the cavity D-111 is an annular groove, the positioning portion D-141 is a positioning ring, which extends into the annular groove. The outer wall of the positioning portion D-141 cooperates with the inner wall of the annular groove to radially position the impeller D-14. There is a gap between the inner wall of the positioning portion D-141 and the inner wall of the annular groove (i.e., the outer wall of the shaft core).

[0238] like Fig.15 As shown, the outer end of the shaft core D-112 is a threaded section, and the locking component includes a locking nut D-16, which is screwed on the outer end of the shaft core D-112 to lock the impeller D-14. The use of the locking nut D-16 is easy to disassemble and can ensure the locking reliability. Alternatively, the locking component can also be locked by a buckle or other structure.

[0239] Furthermore, the outer end of the shaft core D-112 exceeds the outer end of the locking nut D-16 to prevent the locking nut D-16 from retreating outward after long-term use, so as to ensure the locking reliability of the impeller D-14 when rotating at high speed. The extension length of the shaft core D-112 should meet the total length of the impeller locking thread section, the impeller positioning smooth section and the safety margin.

[0240] Still refer to Fig.15 The impeller D-14 is provided with a stepped hole with a gradually decreasing diameter from the inside to the outside, and the outer end of the shaft core D-112 is a stepped shaft with a gradually decreasing diameter from the inside to the outside. The hole section with the smallest diameter of the stepped hole matches the shaft section with the smallest diameter of the stepped shaft. Designing the shaft core D-112 as a stepped shaft can achieve weight reduction while ensuring structural strength, and gradually reduce the shaft diameter to a size that matches the installation hole of the impeller D-14, which can reduce the stress on the shaft core D-112.

[0241] exist Fig.15 In the figure, the stepped shaft includes, from the inside to the outside, a first shaft portion D-1121, a second shaft portion D-1122 and a third shaft portion D-1123, whose sizes gradually decrease. The impeller D-14 is mounted on the third shaft portion D-1123. The inner end of the third shaft portion D-1123 is a smooth axis, and the outer end is provided with a thread for mounting a locking nut D-16.

[0242] like Fig.15As shown, the main shaft is a segmented structure, including a first shaft segment D-11, a second shaft segment D-12 and a third shaft segment D-13 which are installed in sequence along the axial direction and have independent structures, and the second shaft segment D-12 is located between the first shaft segment D-11 and the third shaft segment D-13. Among them, the second shaft segment D-12 is a permanent magnet. As a magnetic steel, the segmented main shaft is conducive to setting the magnetic steel in the middle. The outer ends of the first shaft segment D-11 and the third shaft segment D-13 are both provided with a cavity D-111, and an impeller D-14 is installed on the corresponding shaft core D-112, which can be used in a two-stage compressor. The inner ends of the first shaft segment D-11 and the third shaft segment D-13 are solid structures, and their thickness directly affects the deflection and stability of the front end of the shaft core D-112, so they cannot be too thin, and the processing size can be above 30mm.

[0243] Furthermore, the main shaft also includes a connecting piece for connecting the first shaft section D-11, the second shaft section D-12 and the third shaft section D-13. The connecting piece can be a cylindrical structure, which can not only improve the connection strength of the rotor, but also protect the magnetic steel and reduce the vibration problem of the front end of the rotor.

[0244] like Fig.15 In the structure shown, the connecting member includes a first cylinder D-15, which is coaxially arranged on the first shaft segment D-11 near one end of the second shaft segment D-12, and the entire second shaft segment D-12 and at least part of the length of the third shaft segment D-13 are located in the first cylinder D-15. The first cylinder D-15 can be heat-shrink-fitted on the second shaft segment D-12 and the third shaft segment D-13 in a heated state to achieve reliable connection of the three parts.

[0245] Furthermore, the diameter of the portion of the third shaft section D-13 located inside the first cylinder D-15 is reduced to form a stepped shaft, so that the first cylinder D-15 is flush with the side of the portion of the third shaft section D-13 located outside the first cylinder D-15, which can effectively ensure the dynamic balance of the rotor during operation. Moreover, the first cylinder D-15 can be axially positioned by relying on the shaft shoulder of the third shaft section D-13.

[0246] Furthermore, a vent hole is provided at the bottom of the first shaft segment D-11 corresponding to the cavity D-111 along the axial direction. Since the end of the first shaft segment D-11 close to the first cylinder D-15 is a solid structure, when the second shaft segment D-12 and the third shaft segment D-13 are installed into the first cylinder D-15, the gas in the closed area formed by the second shaft segment D-12 and the first cylinder D-15 can be released for smooth installation.

[0247] like Fig.16As shown, the connecting member includes a second cylinder D-17, and the second cylinder D-17 is integrally sleeved on the side walls of the first shaft segment D-11, the second shaft segment D-12 and the third shaft segment D-13. The outer surface of the main shaft adopts an integral cylinder, which can ensure the overall continuity of the outer surface of the rotor, avoid the formation of gaps between the cylinder and some shaft segments, and achieve a better protection effect. For this structure, each shaft segment can also be installed in the second cylinder D-17 by shrink sleeve.

[0248] Furthermore, both ends of the second cylinder D-17 are flush with the outer edges of the contact surfaces of the first shaft segment D-11 and the third shaft segment D-13. Fig.14 and Fig.15 In order to make the thrust plate D-4 cooperate with the main shaft, a dimension reducing portion D-113 can be provided at the end of the main shaft. The dimension reducing portion D-113 forms a shoulder on the main shaft, and the second cylinder D-17 only needs to extend to the shoulder position.

[0249] Furthermore, a limiting portion is provided at the outer end of the contact surface between the first shaft section D-11 or the third shaft section D-13 and the second cylinder D-17, which is used to limit the axial position of the second cylinder D-17, making it easy to install and position the second cylinder D-17. The limiting portion may be stepped, and its outer diameter is consistent with the outer diameter of the second cylinder D-17.

[0250] The first cylinder D-15 and the second cylinder D-17 are used as magnetic steel sheaths. The thickness should not be too thick to avoid affecting the magnetism of the motor, nor too thin to affect the strength of the sheath itself. The range is 3mm to 5mm. Since the magnetic steel sheath has a connecting function, it can be processed with high-performance high-temperature alloy steel materials.

[0251] Based on the above-mentioned various embodiments of the compressor rotor, the present disclosure further provides a compressor, including the compressor rotor D-1 of each of the above-mentioned embodiments. Fig.14 As shown, the compressor can be a centrifugal compressor. Alternatively, the compressor can also be a centrifugal refrigeration compressor or a screw refrigeration compressor.

[0252] Since the impeller installation method of the present invention can prevent the main shaft or impeller from deforming, it can also ensure the installation strength of the impeller and avoid stress concentration, thereby improving the compression capacity of the compressor and being easy to disassemble when maintenance is required; moreover, by arranging a cavity on the main shaft, the weight of the rotor can be reduced, the critical speed of the rotor can be increased, and the ultimate working capacity of the compressor can be further improved; in addition, by directly forming the shaft core through processing, the connection strength between the shaft core and the main shaft can be increased, and the position accuracy of the shaft core can be ensured, which can effectively solve the problem of the vibration of the front end of the rotor and improve the working stability and reliability of the compressor.

[0253] like Fig.14As shown, it is a two-stage centrifugal compressor, including a first volute D-2, a second volute D-8 and an intermediate casing D-6. The first volute D-2 and the second volute D-8 are respectively arranged at the two ends of the intermediate casing D-6 in the axial direction, and together form the compressor casing. The compressor rotor D-1 is arranged at the center of the compressor casing, and an impeller D-14 is respectively arranged at the two ends of the main shaft. A diffuser D-3 is arranged at the inner end of the impeller D-14. When the impeller D-14 rotates at a high speed, the gas rotates with it. Under the action of centrifugal force, the gas is thrown into the rear diffuser D-3 for expansion, and the gas with increased pressure is discharged from the volute.

[0254] In order to support the main shaft, radial bearings are provided at both ends of the main shaft, and the radial bearings are supported by bearing supports D-5, and the bearing supports D-5 are connected to the intermediate housing D-6. The radial bearings can be dynamic pressure gas bearings. A stator assembly D-7 is provided between the main shaft and the intermediate housing D-6.

[0255] Since the impeller D-14 generates axial force during operation, two thrust bearings are set at one end of the main shaft. The two thrust bearings can be fixed at the opposite ends of the diffuser D-3 and the bearing support D-5, respectively, and there is a gap between the two thrust bearings and both ends of the thrust plate D-4 to form a thrust bearing. This structure can balance the axial forces in two directions at the same time. In addition to air suspension bearings, radial bearings and thrust bearings can also be magnetic suspension bearings.

[0256] The working principle of this compressor is as follows: during the operation of the compressor, the compressor rotor D-1 rotates at high speed, causing the gas to enter the diffuser D-3 through the impeller D-14 on the left. After the first stage of compression, the gas enters the first volute D-2. The exhaust channel on the first volute D-2 guides the compressed gas to enter the right impeller D-14. After the centrifugal action of the right impeller D-14, the gas enters the right diffuser D-3. After the second stage of compression, the gas enters the second volute D-8 and is discharged from the compressor through the exhaust channel on the second volute D-8.

[0257] Rotor structure modification example 4

[0258] like Fig.17 FIG. 1 is a schematic diagram of the structure of some embodiments of the motor rotor disclosed in the present invention. Fig.17 In some embodiments, a motor rotor is provided, comprising a magnetic part E-1 for rotating under the action of an energized coil and a shaft E-2 connected to the magnetic part E-1 and extending away from the magnetic part E-1 along the axial direction of the motor rotor, wherein a cavity E-3 extending along the axial direction thereof is provided on the shaft E-2.

[0259] The motor rotor of the compressor of this embodiment is provided with a cavity E-3 extending along its axial direction, which reduces the weight of the electronic rotor and helps to increase the maximum speed of the motor rotor.

[0260] In this embodiment, the cavity E-3 extends from an end of the shaft E-2 away from the magnetic portion E-1 to an end of the shaft E-2 adjacent to the magnetic portion E-1.

[0261] like Fig.18 As shown, in another embodiment, the cavity includes a first cavity E-31 and a second cavity E-32 spaced apart from the first cavity E-31. A solid shaft is provided between the first cavity E-31 and the second cavity E-32, and the solid shaft plays a supporting role, which is beneficial to improving the structural strength of the motor rotor.

[0262] like Fig.19 As shown, in another embodiment, the cavity E-3 extends from the end of the shaft body E-2 away from the magnetic part E-1 toward the magnetic part E-1, and is spaced apart from the end of the shaft body E-2 adjacent to the magnetic part E-1, and a solid shaft body is between the cavity E-3 and the magnetic part E-1.

[0263] The shaft body E-2 includes a first shaft body E-21 arranged at the first end of the magnetic part E-1 along the axial direction of the motor rotor. The motor rotor also includes a sleeve E-4 connected to the first shaft body E-21, and the magnetic part E-1 is sleeved in the sleeve E-4.

[0264] In this embodiment, the sleeve E-4 and the first shaft body E-21 are integrally formed. In other optional embodiments, the first shaft body E-21 is partially or completely sleeved in the sleeve E-4.

[0265] The shaft body E-2 also includes a second shaft body E-22 disposed at the second end of the magnetic part E-1 along the axial direction of the motor rotor, and the second shaft body E-22 is at least partially sleeved in the sleeve E-4.

[0266] The motor rotor further includes a first flow channel for discharging gas in the sleeve E-4 when the magnetic portion E-1 is inserted into the sleeve E-4.

[0267] The first flow channel includes a cavity E-3 provided on the first shaft E-21. The cavity E-3 on the first shaft E-21 extends from one end of the first shaft E-21 adjacent to the magnetic part E-1 to the other end. In the process of shrink-fitting the magnetic part E-1 into the sleeve E-4, the gas in the sleeve E-4 is discharged through the cavity E-3 on the first shaft E-21.

[0268] In some embodiments, the cavity E-3 on the first shaft body E-21 extends from one end of the first shaft body E-21 adjacent to the magnetic part E-1 toward the other end, and the first shaft body E-21 is also provided with a through hole for connecting the cavity E-3 and the external space of the shaft body E-2, and the through hole optionally extends along the radial direction of the shaft body E-2. The above-mentioned cavity E-3 does not have to extend to the end of the first shaft body E-21 adjacent to the magnetic part E-1. In the process of heat-shrinking the magnetic part E-1 into the sleeve E-4, the gas in the sleeve E-4 is discharged through the cavity E-3 on the first shaft body E-21 and the above-mentioned through hole.

[0269] The motor rotor also includes a second flow channel for discharging the gas in the sleeve E-4 when the second shaft body E-22 is inserted into the sleeve E-4.

[0270] The second flow channel includes a cavity E-3 provided on the second shaft body E-22. The cavity E-3 on the second shaft body E-22 extends from one end of the second shaft body E-22 adjacent to the magnetic portion E-1 toward the other end. In the process of shrink-fitting the second shaft body E-22 into the sleeve E-4, the gas in the sleeve E-4 is discharged through the cavity E-3 provided on the second shaft body E-22.

[0271] In some embodiments, the cavity E-3 extends from one end adjacent to the magnetic portion E-1 toward the other end, and the second shaft body E-22 is also provided with a through hole connecting the cavity E-3 to the external space of the shaft body E-2. Optionally, the through hole extends along the radial direction of the second shaft body E-2. In the process of thermally sleeve the second shaft body E-22 in the sleeve E-4, the gas in the sleeve E-4 is discharged through the cavity E-3 and the through hole provided on the second shaft body E-22.

[0272] In some embodiments, the cavity E-3 extends from the end of the second shaft E-22 away from the magnetic part E-1 toward the magnetic part E-1, the cavity E-3 is separated from the magnetic part E-1, and exhaust holes are provided on the solid shaft of the cavity E-3 and the magnetic part E-1.

[0273] Fig.18 The schematic diagram of the structure of the motor rotor of another optional embodiment is shown. The motor rotor of this embodiment includes a first flow channel for discharging the gas in the sleeve E-4 when the magnetic part E-1 is thermally fitted into the sleeve E-4. The first flow channel includes a first hole E-5 provided on the magnetic part E-1. The first hole E-5 extends from one end of the magnetic part E-1 along the axial direction of the motor rotor to the other end. In the process of thermally fitting the magnetic part E-1 into the sleeve E-4, the gas in the sleeve E-4 can be discharged through the first hole E-5 on the magnetic part E-1.

[0274] like Fig.18As shown, the cavity E-3 provided on the first shaft body E-21 includes a first cavity E-31 and a second cavity E-32 spaced apart from the first cavity E-31.

[0275] The motor rotor also includes a second flow channel for discharging the gas in the sleeve E-4 during the process of inserting the second shaft E-22 into the sleeve E-4. The second flow channel includes a cavity E-3 arranged on the second shaft E-22, and the cavity E-3 extends from one end of the second shaft E-22 adjacent to the magnetic part E-1 to the other end.

[0276] In some embodiments, a through hole is provided on the second shaft E-22 for connecting the cavity E-3 and the external space of the shaft E-2. The cavity E-3 on the second shaft E-22 extends from one end adjacent to the magnetic portion E-1 toward the other end, and the cavity E-3 does not need to extend to the end of the second shaft E-22 away from the magnetic portion E-1.

[0277] Fig.19 A schematic structural diagram of a motor rotor of another optional embodiment is shown, in which the motor rotor of this embodiment includes a first flow channel for discharging gas in the sleeve E-4 when the magnetic part E-1 is thermally inserted into the sleeve E-4, and the first flow channel includes a cavity E-3 provided on the first shaft E-21 and a second channel E-6 for connecting the cavity E-3 and the inner cavity of the sleeve E-4.

[0278] In this embodiment, the cavity E-3 on the first shaft body E-21 extends from the end of the first shaft body E-21 away from the magnetic part E-1 toward the magnetic part E-1, and the cavity E-3 is separated from the inner cavity of the sleeve E-4. A second channel E-6 is provided on the solid shaft body between the cavity E-3 and the inner cavity of the sleeve E-4, and the two ends of the second channel E-6 are respectively connected to the inner cavity of the cavity E-3 and the sleeve E-4.

[0279] When the magnetic part E-1 is inserted into the sleeve E-4, the gas in the sleeve E-4 is discharged through the second channel E-6 and the cavity E-3 provided on the first shaft body E-21.

[0280] In some embodiments, the second flow channel for exhausting gas when the second shaft E-22 is inserted into the sleeve E-4 includes a first hole provided on the magnetic part E-1 and a cavity E-3 provided on the first shaft E-21.

[0281] Combination Figures 17 to 19 As shown, the motor rotor of this embodiment is mainly composed of three sections: the first shaft body E-21, the magnetic part E-1 and the second shaft body E-22, wherein the middle section is the magnetic part E-1, and the first shaft body E-21 and the second shaft body E-22 are provided with axially extending cavities E-3. The overall mass of the motor rotor is reduced, thereby increasing the critical speed of the rotor and improving the bearing capacity of the bearing.

[0282] The compressor using the modified example of the rotor structure can be a two-stage dynamic pressure gas suspension centrifugal compressor. The compressor includes a first compression part, a second compression part for compressing the refrigerant compressed by the first compression part, a motor for driving the first compression part and the second compression part, and a circulating air supply self-cooling system. The circulating air supply self-cooling system provides a refrigerant for cooling and / or lubricating the bearing E-12 in the compressor cavity.

[0283] The motor rotor system of the compressor mainly includes a centrifugal impeller of the first compression part, a hollow first shaft body E-21, a magnetic part E-1, a hollow second shaft body E-22, a centrifugal impeller of the second compression part, and a thrust bearing thrust body. Among them, the shaft body E-2 of the motor rotor of the compressor includes a hollow structure and a solid structure. The motor rotor of this structural type can be applied to rotating machinery such as centrifugal refrigeration compressors and screw refrigeration compressors.

[0284] The bearings involved in the scheme can be sliding bearings, rolling bearings, magnetic bearings or air bearings. Considering the oil-free, environmentally friendly and simple structure, air bearings are preferred.

[0285] The schematic diagram of the new three-stage hollow high-speed rotor structure is as follows Fig.18 As shown, the motor rotor is mainly composed of three sections: the first shaft body E-21, the magnetic part E-1 and the second shaft body E-22. The left and right sections of the shaft body E-2 are processed into a hollow structure, and the middle is the integral magnetic part E-1 without the middle core shaft, which is conducive to simplifying the structure and reducing assembly. The first shaft body E-21 at the left end is processed into a two-section hollow structure, the left end is a cooling gas channel, and the right end is a hollow sleeve for assembling the magnetic part E-1. Or the second shaft body E-22 at the right end is processed into a structure similar to the first shaft body E-21; the solid part of the first shaft body E-21 at the left end can be set at a position away from the magnetic part E-1, and the first channel E-5 is processed in the center of the magnetic part E-1. The first channel can be a smooth hole or a threaded hole. The number of first channels E-5 is reasonably arranged according to the spatial structure. Similarly, the second shaft body E-22 at the right end can use the same structure as the first shaft body E-21. The hollow structures of the first shaft body E-21 and the second shaft body E-22 at the left and right ends can also be processed into full holes or small holes or threaded holes in the solid part, but the diameter of the hole needs to be strictly controlled to prevent the contact area between the shaft and the magnetic part E-1 from being too small, thereby damaging the magnetic part E-1, i.e. D 孔 ≤(1 / 2)D 磁性部 The volumes of the cavities E-3 of the two sections of the shaft body E-2 are kept the same or differ by the volume of the sleeve section, or are adjusted through the solid section of the shaft body E-2 so that the center of gravity of the motor rotor is close to the center of the overall rotor.

[0286] The motor rotor is processed in separate parts. By processing the first shaft E-21, the second shaft E-22 and the magnetic part E-1 separately, the required key dimensions can be effectively guaranteed, the complexity of processing can be simplified, the rotor inspection can be facilitated, and the inspection accuracy can be improved. Small holes can be processed in the center of the two shafts E-2 and the magnetic part E-1, but due to the influence of the material of the magnetic part E-1, the size of the small holes cannot be too large, generally φD3 ≤ E-4mm is appropriate. Since there is gas that cannot be discharged during the shrink-fit process of the motor rotor, it is necessary to add small holes for exhaust in the solid part of the first shaft E-21 or the second shaft E-22, with a hole diameter of 2 to 3mm.

[0287] The above structure can not only effectively solve the bearing capacity problem of the bearing, but also increase the critical speed of the rotor by reducing the length of the cantilever end, thereby further improving the working stability and reliability of the motor.

[0288] Rotor structure modification example 5

[0289] Fig. 20 FIG. 1 shows a schematic diagram of the structure of the motor rotor of the compressor of this embodiment. Fig. 20 In some embodiments, the motor rotor includes a magnetic part F-1 for rotating under the action of the energized coil F-13 and a shaft body F-2 connected to the magnetic part F-1 and extending away from the magnetic part F-1 along the axial direction of the motor rotor. The shaft body F-2 includes a cavity F-3 extending along its axial direction and a connecting part F-5 for connecting a compression working component. The connecting part F-5 and the cavity F-3 are arranged at intervals. The connecting part F-5 is arranged at the end of the shaft body.

[0290] The motor rotor in this embodiment is provided with a cavity F-3 extending along its axial direction, which reduces the weight of the electronic rotor and helps to increase the maximum speed of the motor rotor.

[0291] The cavity F-3 is spaced apart from the connection part for connecting the compression working component. The motor rotor is provided with the weight-reducing cavity F-3 while retaining the connection part for installing the compression working component. The motor rotor has the advantages of simple structure, easy processing and low manufacturing cost.

[0292] The shaft body F-2 includes a first shaft body F-21 located at a first axial end of the magnetic part F-1 and a second shaft body F-22 located at a second axial end of the magnetic part F-1.

[0293] The cavity F-3 on the first shaft body F-21 extends from one end of the first shaft body F-21 adjacent to the magnetic part F-1 toward the first end provided with the connecting part F-5. The cavity F-3 on the second shaft body F-22 extends from one end of the second shaft body F-22 adjacent to the magnetic part F-1 toward the other end. Optionally, the connecting part F-5 is provided at one end of the second shaft body F-22 away from the magnetic part F-1.

[0294] The motor rotor also includes a sleeve F-4 connected to the shaft body F-2, and the magnetic part F-1 is sleeved in the sleeve F-4. At least part of the first shaft body F-21 and at least part of the second shaft body F-22 are sleeved in the sleeve F-4.

[0295] During the process of assembling the motor rotor, the first shaft body F-21, the magnetic part F-1 and the second shaft body F-22 can be inserted as a whole into the sleeve F-4 with openings at both ends. During the process of installing the first shaft body F-21, the magnetic part F-1 and the second shaft body F-22 into the sleeve, the gas in the sleeve F-4 can be discharged through the port of the sleeve F-4, so there is no need to add an exhaust duct.

[0296] like Fig.21 As shown, in some embodiments, the sleeve F-4 and the first shaft body F-21 are integrated. The magnetic part F-1 and the second shaft body F-22 are sequentially inserted into the sleeve F-4. The motor rotor also includes a first flow channel for discharging the gas in the sleeve F-4 when the magnetic part F-1 is inserted into the sleeve F-4.

[0297] Optionally, the first flow channel includes a first hole provided on the magnetic part F-1, and the first hole extends from one end of the magnetic part F-1 along the axial direction of the motor rotor to the other end. When the magnetic part F-1 is inserted into the sleeve F-4, the gas in the sleeve F-4 is discharged through the first hole to the side of the magnetic part F-1 facing away from the first shaft body F-21.

[0298] Optionally, the first flow channel includes a second channel provided on the first shaft body F-21, and the second channel is connected to the cavity F-3 on the first shaft body F-21. When the magnetic part F-1 is inserted into the sleeve F-4, the gas in the sleeve F-4 is discharged through the cavity F-3 on the first shaft body F-21 and the second channel.

[0299] According to another aspect of the present invention, a compressor is provided. Fig.21 FIG. 2 shows a schematic diagram of the structure of the compressor of this embodiment. Fig.21 As shown, the compressor of this embodiment includes a motor rotor, and the motor rotor includes a magnetic part F-1 and a shaft F-2 connected to the magnetic part F-1.

[0300] The compressor also includes a centrifugal compression part driven by a motor rotor, which includes a centrifugal impeller F-8 mounted on a connecting part F-5 of the motor rotor, a diffuser F-9 for compressing the refrigerant accelerated by the centrifugal impeller F-8, and a volute F-10 for discharging the compressed refrigerant.

[0301] The centrifugal compression part includes a first centrifugal compression part arranged at the first end of the motor rotor and a second centrifugal compression part arranged at the second end of the motor rotor. The air intake port of the second centrifugal compression part is connected to the air exhaust port of the first centrifugal compression part, and the second centrifugal compression part is used to compress the refrigerant compressed by the first centrifugal compression part.

[0302] The compressor further comprises a bearing support F-11 and a bearing F-12 mounted on the bearing support F-11, wherein the bearing F-12 is used to carry the motor rotor. The bearing F-12 is an air suspension bearing. Preferably, the air suspension bearing is a dynamic pressure air suspension bearing.

[0303] like Fig. 20 As shown, the motor rotor of the compressor of this embodiment is mainly composed of three sections: the first shaft body F-21, the magnetic part F-1 and the second shaft body F-22, wherein the middle section is the magnetic part F-1, and the first shaft body F-21 and the second shaft body F-22 are provided with axially extending cavities F-3. The overall mass of the motor rotor is reduced, thereby increasing the critical speed of the rotor and improving the bearing capacity of the bearing.

[0304] The compressor of this embodiment is a two-stage dynamic pressure air suspension centrifugal compressor. The compressor includes a first compression part, a second compression part for compressing the refrigerant compressed by the first compression part, a motor for driving the first compression part and the second compression part, and a circulating air supply self-cooling system. The circulating air supply self-cooling system provides a refrigerant for cooling and / or lubricating the bearing F-12 in the compressor cavity.

[0305] The motor rotor system of the compressor mainly includes the centrifugal impeller F-8 of the first compression part, the hollow first shaft body F-21, the magnetic part F-1, the hollow second shaft body F-22, the centrifugal impeller F-8 of the second compression part and the thrust bearing thrust body. Among them, the shaft body F-2 of the motor rotor of the compressor includes a hollow structure and a solid structure. The motor rotor of this structural type can be applied to rotating machinery such as centrifugal refrigeration compressors and screw refrigeration compressors.

[0306] The bearings involved in the scheme can be sliding bearings, rolling bearings, magnetic bearings or air bearings. Considering the oil-free, environmentally friendly and simple structure, air bearings are preferred.

[0307] like Fig.21 As shown, the motor rotor is mainly composed of three sections: the first shaft body F-21, the magnetic part F-1 and the second shaft body F-22. The left and right shaft bodies F-2 are processed into hollow structures, and the middle is the integral magnetic part F-1, which eliminates the middle core shaft, which is conducive to simplifying the structure and reducing assembly. The connecting part F-5 for installing the impeller at one end of the first shaft body F-21 away from the magnetic part is a solid structure, and the cavity F-3 on the first shaft body F-21 extends from one end of the first shaft body F-21 adjacent to the magnetic part to the other end.

[0308] The second shaft F-22 at the right end has a similar structure to the first shaft F-21, and the first shaft F-21 and the second shaft F-22 are symmetrically arranged on both sides of the magnetic part F-1.

[0309] A sleeve F-4 is sleeved on the outer surface of the first shaft body F-21, the magnetic part F-1 and the second shaft body F-22 to connect the first shaft body F-21, the magnetic part F-1 and the second shaft body F-22 together. The above three components are connected with the sleeve by interference fit, and the sleeve F-4 passes through the three components as a whole. During the installation process, this structure does not need to add exhaust holes, which effectively prevents the heat-shrink jacket gas from being unable to be discharged.

[0310] The connection part F-5 at both ends of the motor rotor is a solid structure. The connection part F-5 is used to install the centrifugal impeller F-8. The centrifugal impeller F-8 and the connection part F-5 are axially locked using a locking nut, and the radial positioning of the centrifugal impeller F-8 can use interference or clearance connection.

[0311] The inner diameter of the cavity F-3 on the shaft body F-2 needs to be strictly controlled to prevent the contact area between the shaft body and the magnetic part F-1 from being too small, thereby damaging the magnetic part F-1, i.e. D 孔 ≤(1 / 2)D 磁性部 The volume of the cavity F-3 on the two shafts F-2 remains the same, or the center of gravity is adjusted by the solid section of the shaft to be close to the center of the whole rotor. The motor rotor is processed in a split manner. By processing the first shaft F-21, the second shaft F-22 and the magnetic part F-1 separately, the required key dimensions can be effectively guaranteed, the complexity of processing is simplified, the rotor inspection is convenient, and the inspection accuracy is improved. The hollow structure close to the magnetic part F-1 side can reduce the processing accuracy of the hole and improve the processing efficiency.

[0312] The above structure can not only effectively solve the bearing capacity problem of the bearing, but also increase the critical speed of the rotor by reducing the length of the cantilever end, thereby further improving the working stability and reliability of the motor.

[0313] The present invention uses a hydrodynamic air suspension bearing, which not only eliminates the need for lubricating oil and a control system for the compressor, but also makes the compressor more environmentally friendly and simpler in structure; it also solves the problem of difficulty in integrated processing and inspection of the compressor rotor, and effectively increases the critical speed of the rotor, ensures the reliability and safety of the shaft system, and reduces the maintenance cost of the compressor.

[0314] Rotor structure modification example 6

[0315] like Fig. 22 and Fig.23 As shown, an embodiment of the present invention discloses a compressor rotor, which includes a motor rotor G-10, a locking rod G-20, an impeller and a locking component G-40.

[0316] like Fig. 22 As shown, the motor rotor G-10 includes a plurality of rotor segments fixedly connected in the axial direction. The impeller is located at the end of the motor rotor G-10 and is connected to the locking rod G-20. The locking component G-40 locks the impeller to the locking rod G-20. The end shaft segment G-12 at one end of the motor rotor G-10 is provided with a first cavity G-121 at the outer end and a second cavity G-122 at the inner end, and a mounting portion G-123 is provided between the first cavity G-121 and the second cavity G-122, and the mounting portion G-123 is adjacent to one end of the motor rotor G-10, and the locking rod G-20 extends into the first cavity G-121 and is fixed to the mounting portion G-123 and is coaxial with the motor rotor G-10.

[0317] In some embodiments, the mounting portion G-123 is configured as an annular protrusion protruding inward, and the inner end of the locking rod G-20 is fixed in the center hole of the annular protrusion.

[0318] In some embodiments, the mounting portion G-123 is configured as a plurality of protrusions that protrude inwardly and are spaced apart in the circumferential direction, and the inner end portion of the locking rod G-20 is fixed between the plurality of protrusions.

[0319] An interference fit may be adopted between the inner end of the locking rod G-20 and the mounting portion G-123.

[0320] In the present invention, a first cavity G-121 and a second cavity G-122 are provided in the motor rotor G-10, so that the motor rotor G-10 is as light as possible, thereby facilitating the reduction of the overall weight of the motor rotor G-10 and the compressor rotor, and facilitating the improvement of the critical speed of the compressor rotor. Moreover, the mounting portion G-123 is adjacent to the end of the motor rotor, thereby reducing the cantilever length of the locking rod G-20, improving the impeller's beating problem, and improving the overall rigidity of the locking rod G-20, thereby facilitating the dynamic balance of the compressor rotor.

[0321] like Fig. 22 As shown, in some embodiments, the compressor may be a centrifugal compressor, and the impeller is a centrifugal impeller of the centrifugal compressor. It may also be other compressors such as a screw refrigeration compressor.

[0322] The impeller may be provided only on one side of the motor rotor G-10, or on both sides of the motor rotor G-10. The impeller on each side may be single-stage or multi-stage. For example, the number of impellers on one side of the motor rotor may be one, or may be more than two.

[0323] In some embodiments, Fig. 22 and Fig.23 As shown, both ends of the locking rod G-20 are connected to the impellers respectively.

[0324] The end of the locking rod G-20 is provided with an external thread, and the locking component includes a locking nut matched with the external thread of the locking rod G-20.

[0325] like Fig. 22 As shown, in some embodiments, the compressor rotor includes a motor rotor G-10, a primary centrifugal impeller G-30 and a secondary centrifugal impeller G-50. The left and right ends of the locking rod G-20 are respectively provided with external threads. The primary centrifugal impeller G-30 is locked to the left end of the locking rod G-20 by a locking nut G-40 as a locking component. The secondary centrifugal impeller G-50 is locked to the right end of the locking rod G-20 by a locking nut G-40 as a locking component.

[0326] like Fig. 22 As shown, in some embodiments, the multiple rotor segments of the motor rotor G-10 include a permanent magnet G-11 and two end shaft segments G-12. The two end shaft segments G-12 are fixed at both ends of the permanent magnet G-11.

[0327] The permanent magnet G-11 can be solid and its shape can be columnar. The permanent magnet G-11, as the motor rotor G-10, together with the motor stator of the compressor, constitutes a motor that drives the compressor rotor to rotate. The material of the permanent magnet G-11 is, for example, magnetic steel.

[0328] like Fig. 22 As shown, the motor rotor G-10 of the compressor rotor of the embodiment of the present invention includes a permanent magnet G-11, two end shaft segments G-12 and a magnetic steel sheath G-14. The left end of the magnetic steel sheath G-14 is integrally arranged with the right end of the first end shaft segment G-12, and the magnetic steel sheath G-14 is tightly mounted on the outer periphery of the permanent magnet and the right end shaft segment G-12 to connect the permanent magnet G-11 and the two end shaft segments G-12 together.

[0329] In some embodiments, Fig.23 As shown, the magnetic steel sheath G-14, the permanent magnet G-11 and the two end shaft segments G-12 are separated from each other, and the magnetic steel sheath G-14 is fastened and sleeved on the entire periphery of the permanent magnet G-11 and the two end shaft segments G-12, for example, by heat sleeve method, that is, heating the ceramic steel sheath G-14, and then sleeve the magnetic steel sheath on the permanent magnet G-11 and the two end shaft segments G-12.

[0330] Motor drive system modification

[0331] refer to Fig.24 and Fig.25In some embodiments, the motor drive system provided by the present disclosure may include: a motor barrel N-15, a motor stator N-16 and a motor rotor N-14. The motor barrel N-15 has a motor accommodating cavity. The motor stator N-16 is disposed in the motor accommodating cavity. The motor rotor N-14 is rotatably disposed in the motor accommodating cavity, the motor stator N-16 is sleeved on the outside of the motor rotor N-14, and an air gap channel Q is formed between the inner circumferential wall of the motor stator and the outer circumferential wall of the motor rotor N-14, and a cooling medium channel for cooling medium to flow through and bent is disposed in the air gap channel Q.

[0332] The cooling medium of the embodiment of the present invention can fully contact the outer peripheral wall of the motor rotor and the inner peripheral wall of the motor stator when passing along the bent cooling medium channel, thereby fully cooling the motor, thereby improving the cooling effect of the motor.

[0333] Specifically in this embodiment, Fig.25 and Fig.26 As shown, the cooling medium channel includes a first spiral groove N-144 disposed on the outer peripheral wall of the motor rotor N-14. The cooling medium passes through the air gap channel Q under the guidance of the first spiral groove N-144 to absorb the heat of the outer peripheral wall of the motor rotor so as to achieve more adequate cooling.

[0334] In this embodiment, the spiral direction of the first spiral groove N-144 is the same as the rotation direction of the motor rotor N-14.

[0335] like Figure 26 to Figure 29 As shown, the outer peripheral wall of the motor rotor N-14 is provided with a protrusion N-145 extending in a spiral shape, and a first spiral groove N-144 is formed between adjacent protrusions N-145. The cross section of the protrusion N-145 of this embodiment is a right-angled trapezoid ( Fig. 27 shown) or triangle ( Fig.28 shown) or round ( Fig.29 as shown) or a rectangle.

[0336] The first spiral groove of this embodiment can be a single spiral or a double spiral.

[0337] like Fig.26 As shown, the motor rotor N-14 of this embodiment includes a shaft body and a permanent magnet N-143 disposed in the shaft body, and a first spiral groove is disposed on the portion of the outer peripheral wall of the shaft body connected to the permanent magnet N-143. In this embodiment, the first spiral groove is disposed on the portion of the outer peripheral wall of the shaft body connected to the permanent magnet N-143 so that the cooling medium can fully cool the permanent magnet, which helps to avoid demagnetization of the permanent magnet due to excessive temperature and thus improve the reliability of the motor. Specifically in this embodiment, as Fig.26As shown, the shaft body includes a first end shaft segment N-141 and a second end shaft segment N-142, the first end shaft segment N-141 has a mounting sleeve, the permanent magnet N-143 and the second end shaft segment N-142 are both installed in the mounting sleeve, and the first spiral groove is arranged on the first end shaft segment N-141.

[0338] The shaft body of this embodiment further has a hollow portion located at the end and a vent hole communicating with the hollow portion and the motor accommodating cavity, and the cooling medium enters the motor accommodating cavity through the hollow portion and the vent hole.

[0339] like Fig.26 As shown, the first end shaft section N-141 of this embodiment includes a hollow portion N-146 and a vent hole N-147 connecting the hollow portion N-146 and the motor accommodating cavity. When the motor rotor N-14 rotates at a high speed, the heat inside the motor rotor N-14 can be taken away by passing a fluid such as a refrigerant through the hollow portion N-146 and the vent hole N-147. The second end shaft section N-142 of this embodiment is also symmetrically provided with a hollow portion and a vent hole.

[0340] In the above embodiment, the motor rotor N-14 includes a three-section structure, the left and right end shaft sections are processed into a hollow structure, and the middle is an integral permanent magnet, which is conducive to simplifying the structure and reducing assembly.

[0341] like Fig.25 As shown, the motor barrel N-15 of this embodiment is provided with: a cooling medium inlet N-152, a second spiral groove N-151 and a cooling medium outlet N-153. The second spiral groove N-151 is provided on the inner wall of the motor barrel N-15, and a motor barrel spiral flow channel is formed between the second spiral groove N-151 and the outer peripheral wall of the motor stator N-16. The cooling medium enters the motor barrel spiral channel through the cooling medium inlet N-152 to cool the motor stator N-16.

[0342] The cooling medium enters from the cooling medium inlet N-152 and enters into the left end of the motor accommodating chamber through the second spiral groove N-151. The cooling medium gathers at the left end of the motor accommodating chamber to form high pressure. Then, the cooling medium flows to the right end through the air gap channel between the motor stator and the motor rotor under the guidance of the second spiral groove on the outer peripheral wall of the motor rotor N-14. In this process, the heat of the outer surface of the motor rotor is absorbed to make the cooling more sufficient.

[0343] like Fig.24 As shown, this embodiment also provides a compressor, including the motor drive system of the above embodiment, respectively arranged at both ends of the axial direction of the motor cylinder N-15 ( Fig.24The compressor of this embodiment also includes a primary impeller N-20 and a secondary impeller N-21 respectively fixed to the two ends of the motor rotor N-14. Corresponding to the primary impeller N-20 and the secondary impeller N-21, there are two compression chambers, namely the primary compression chamber and the secondary compression chamber. The primary impeller N-20 is located in the primary compression chamber, and the secondary impeller N-21 is located in the secondary compression chamber.

[0344] The compressor of this embodiment also includes a first diffuser N-12, a first bearing support N-13, a first radial bearing N-22, a second diffuser N-18, a second bearing support N-17, a second radial bearing N-23, and a first thrust bearing and a second thrust bearing. The first bearing support N-13 and the second bearing support N-17 are respectively fixed inside the motor barrel N-15 and are respectively located at the axial ends of the motor stator N-16. The first radial bearing N-22 is located in the first bearing support N-13, and the second radial bearing N-23 is located in the second bearing support N-17. The first radial bearing N-22 and the second radial bearing N-23 are respectively supported at the axial ends of the motor rotor N-15, thereby supporting the motor rotor N-14 in the motor accommodating cavity of the motor barrel N-15.

[0345] The compressor also includes a motor rotor N-14 disposed at one axial end ( Fig.24 A thrust plate N-24 is provided between the first bearing support N-13 and the thrust plate N-24, and a second thrust bearing is provided at one end of the first diffuser N-12 away from the diffuser structure on the diffuser N-12, so that the motor rotor N-14 is located in the motor barrel N-15 at the upper axial limit.

[0346] The bearing of this embodiment may be a sliding bearing, a rolling bearing, a magnetic bearing or an air bearing.

[0347] When the bearing is an air suspension bearing, after the cooling medium enters the motor housing cavity of the motor barrel, since the radial bearing is located in the motor housing cavity, the cooling medium can directly supply air to the radial bearing and cool the radial bearing. At the same time, the cooling medium in the motor housing cavity can enter the left cavity through the upper edge opening of the bearing support under high pressure to supply air and cool the thrust bearing.

[0348] like Fig.24 As shown, in some embodiments, the compressor may be a centrifugal compressor.

[0349] Combine the following Figure 24 to Figure 26 The compressors of the above embodiments are taken as refrigeration compressors used in a refrigerant circulation system to illustrate the working process and principle of the motor cooling medium circulation. In this case, the cooling medium is refrigerant.

[0350] When the refrigerant enters the spiral flow channel of the motor barrel through the cooling medium inlet N-152, the refrigerant flows in a spiral between the motor barrel N-15 and the motor stator N-16. The refrigerant flowing in the spiral flow channel of the motor barrel continuously absorbs heat and reduces the surface temperature of the motor stator N-16. After continuous circulation, the refrigerant enters the left end of the motor accommodating cavity of the motor from the flow channel outlet N-154. When more refrigerant gathers in the left end cavity, it forms a high pressure. At the same time, under the guidance of the first spiral groove of the motor rotor N-14, it flows to the right end through the air gap channel Q between the motor stator N-16 and the motor rotor N-14, absorbing the heat of the outer surface of the motor rotor N-14, making the cooling more sufficient. A large amount of refrigerant gathers at the left end to form high pressure. At the same time, the motor rotor and the motor stator are designed to be in a spiral shape, which has a guiding effect on the refrigerant gathered at the left end. The refrigerant at the left end will flow to the right end through the air gap channel between the stator and the motor rotor under the action of rotation and high pressure, and cool the outer surface of the motor rotor and the inner surface of the motor stator again.

[0351] After passing through the spiral flow channel of the motor barrel, the refrigerant enters the motor housing chamber of the motor. Since the radial bearing is in the motor housing chamber, the refrigerant can directly supply air to the radial bearing and cool the radial bearing. At the same time, the refrigerant in the motor housing chamber, under the action of high pressure, supplies air to and cools the thrust bearing through the upper edge opening of the bearing support.

[0352] It can be seen from the above that the compressor of this embodiment not only effectively solves the cooling problem of the compressor, but also can supply air to the compressor bearings, eliminating the need for an external air supply device.

[0353] Bearing support structure modification example 1

[0354] like Figure 32-Figure 33 , which is a schematic diagram of the structure of some embodiments of the bearing support disclosed in the present invention. Fig.32 and Fig.33 In some embodiments, the present disclosure provides a bearing support H-2, including a first end and a second end. The second end and the first end of the bearing support H-2 may be two opposite ends along the axial direction of the bearing support H-2. Along the direction from the first end to the second end of the bearing support H-2, the radial dimension of at least part of the bearing support H-2 gradually increases. The axial direction of the bearing support H-2 is consistent with the axial direction of the shaft supported by the bearing. The radial direction of the bearing support H-2 is consistent with the radial direction of the shaft supported by the bearing. In some embodiments, the shaft supported by the bearing is the rotor H-8 of the compressor. In some embodiments, the radial dimension of the first end of the bearing support H-2 is smaller than the radial dimension of the second end. In some embodiments, the bearing support H-2 also includes a bearing hole H-21, which is used to install the bearing.

[0355] In some embodiments, the bearing support H-2 further comprises an annular groove H-22, and the annular groove H-22 is arranged around the bearing hole H-21. In some embodiments, the second end of the bearing support H-2 comprises a stopper H-23, and the stopper H-23 is used to abut against the inner side of the part to be installed.

[0356] In some embodiments, the second end of the bearing support H-2 includes a connecting portion H-24, which extends radially outward from the bearing support H-2 relative to the limiting portion H-23 and is used to connect with the part to be installed. In some embodiments, a stopper is formed between the limiting portion H-23 and the connecting portion H-24, which is used to cooperate with the part to be installed. In some embodiments, the part to be installed is the housing H-1 of the compressor. In some embodiments, the connecting portion H-24 is annular and is arranged along the circumference of the limiting portion H-23.

[0357] In some embodiments, the bearing support H-2 further includes a bearing hole H-21, which is arranged along the axial direction of the bearing support H-2 for mounting a bearing. In some embodiments, the bearing support H-2 further includes a vent hole H-25, which is arranged along the radial direction of the bearing support H-2, wherein a first end of the vent hole H-25 is connected to the bearing hole H-21, and a second end of the vent hole H-25 is connected to the radial outer portion of the bearing support H-2.

[0358] like Fig.30 FIG. 2 is a schematic diagram of a compressor provided in some embodiments. Fig.30 In some embodiments, the compressor includes a shell H-1. End covers may be provided at both ends of the shell H-1 along the central axis. The compressor may include a motor rotor H-8 and a motor stator H-9 disposed in the shell H-1. The motor rotor H-8 is disposed along the central axis of the shell H-1. The motor stator H-9 is disposed between the inner wall of the shell H-1 and the motor rotor H-8, and is fixedly connected to the inner wall of the shell H-1. In some embodiments, radial bearings H-3 and bearing supports H-2 are provided at both ends of the motor rotor H-8.

[0359] In some embodiments, the compressor includes a bearing support H-2, and the bearing support H-2 is disposed in the housing H-1. Further, the bearing support H-2 is suitable for a gas bearing, such as a hydrodynamic gas bearing. In some embodiments, a first end of the bearing support H-2 is adjacent to an end cover of the housing H-1, and a second end of the bearing support H-2 is connected to an inner wall of the housing H-1.

[0360] In some embodiments, the first end and the second end of the bearing support H-2 are two opposite ends along the axial direction of the bearing support H-2, and the first end of the bearing support H-2 is closer to the end of the housing H-1 relative to the second end of the bearing support H-2. The end of the housing H-1 is the end of the housing H-1 close to the bearing support H-2. In some embodiments, along the direction from the first end to the second end of the bearing support H-2, the radial size of at least part of the bearing support H-2 gradually increases.

[0361] The inventors found that the radial force borne by the bearing support H-2 is basically equal to the gravity of the rotor, and the radial load is relatively small, so the radial strength requirement of the bearing support H-2 is not high. However, when the bearing support H-2 bears radial load and axial load at the same time, the bearing support H-2 also needs to have a certain structural strength to withstand the radial load and axial load. Therefore, the radial dimension of at least part of the bearing support H-2 provided by the present invention gradually increases, which can meet the radial strength requirement, and the gradual increase in the radial dimension can improve the structural strength of the bearing support H-2.

[0362] In the related art, the radial dimensions of the entire bearing support H-2 are set to be consistent by increasing the wall thickness and additionally providing reinforcing ribs, thereby increasing the structural strength of the bearing support H-2, which results in increased equipment weight and increased costs.

[0363] The inventors also found that the axial load on the bearing support H-2 is greater than the radial load, and the axial load is transmitted to the bearing support H-2 through the thrust bearing H-4 and the thrust bearing fixing plate H-5. Therefore, the first end of the bearing support H-2 provided by the present invention cooperates with the thrust bearing fixing plate H-5 and the thrust bearing H-4, and the radial dimension of the first end of the bearing support H-2 is smaller than the radial dimension of the second end of the bearing support H-2 connected to the housing H-1, and along the direction from the first end to the second end of the bearing support H-2, the radial dimension of at least part of the bearing support H-2 gradually increases, which can well transmit the axial force to the housing H-1 of the compressor motor, thereby improving the strength and service life of the bearing support H-2.

[0364] In some embodiments, along the direction from the first end to the second end of the bearing support H-2, the radial dimension of the middle part of the bearing support H-2 between the first end and the second end gradually increases. The bearing support structure can not only meet the strength requirements, but also reliably deliver power.

[0365] In some embodiments, the bearing support H-2 is V-shaped, has high structural strength, and is easy to cast. It can not only ensure high-precision assembly of the hydrodynamic bearing, but also improve the stability of the bearing rotor system. In some embodiments, the radial dimension of the first end of the bearing support H-2 is smaller than the radial dimension of the second end of the bearing support H-2.

[0366] In some embodiments, the bearing support H-2 includes a bearing hole H-21, and the bearing hole H-21 is used to install a bearing. In some embodiments, the bearing support H-2 includes an annular groove H-22, and the annular groove H-22 is arranged around the bearing hole H-21. Optionally, the cross-section of the annular groove H-22 is V-shaped, which is compatible with the V-shaped structure of the bearing support H-2.

[0367] The bearing support H-2 is hollowed out around the bearing hole H-21 to form a V-shaped annular groove H-22 to ensure that the wall thickness of the casting is relatively uniform, which reduces the deadweight of the support and facilitates casting.

[0368] In some embodiments, the inner wall of the housing H-1 is provided with a mounting portion extending toward the center of the housing H-1, and the mounting portion is used to connect with the second end of the bearing support H-2. In some embodiments, the second end of the bearing support H-2 includes a limiting portion H-23, and the limiting portion H-23 abuts against the inner side of the mounting portion.

[0369] In some embodiments, the second end of the bearing support H-2 further includes a connecting portion H-24, which extends radially outward of the bearing support H-2 relative to the limiting portion H-23 for connection with the mounting portion.

[0370] In some embodiments, a stopper is formed between the limiting portion H-23 and the connecting portion H-24 for cooperating with the mounting portion for positioning. In some embodiments, the connecting portion H-24 is connected to the mounting portion provided on the inner wall of the housing H-1 through a pin, and the bearing support H-2 is positioned together by the pin and the provided mounting stopper, so that the bearing can be assembled with high precision.

[0371] In some embodiments, the connecting portion H-24 is annular and is arranged along the circumference of the limiting portion H-23. In some embodiments, the bearing support H-2 includes a bearing hole H-21, and the bearing hole H-21 is used to install the bearing. In some embodiments, the bearing support H-2 includes a vent hole H-25, and the vent hole H-25 is arranged along the radial direction of the bearing support H-2, and the first end of the vent hole H-25 is connected to the bearing hole H-21, and the second end of the vent hole H-25 is connected to the radial outside of the bearing support H-2.

[0372] In some embodiments, the compressor includes a radial bearing H-3, which is disposed in the bearing hole H-21. Further, the radial bearing H-3 is connected to the bearing support H-2 by an interference fit.

[0373] In some embodiments, the compressor further includes a thrust bearing H-4, which is disposed at the first end of the bearing support H-2. The vent hole H-25 connects the space where the radial bearing H-3 is located with the space where the thrust bearing H-4 is located, which can ensure that the working back pressures of the thrust bearing H-4 and the radial bearing H-3 are consistent, thereby improving the stability of the bearing rotor system.

[0374] Optionally, 4 to 12 vent holes H-25 are evenly distributed on the bearing support H-2, connecting the space where the radial bearing H-3 is located and the space where the thrust bearing H-4 is located, which can ensure that the radial bearing H-3 and the thrust bearing H-4 are in the same working environment and improve the stability of the bearing rotor system.

[0375] In some embodiments, the compressor includes a thrust bearing fixing plate H-5, which is disposed between the thrust bearing H-4 and the first end of the bearing support H-2. The thrust bearing fixing plate H-5 is fixedly connected to the first end of the bearing support H-2. The thrust bearing H-4 is fixedly connected to the thrust bearing fixing plate H-5.

[0376] The thrust bearing fixing plate H-5 is provided with a matching portion, which extends outward and is used to match with the hole set on the first end of the bearing support H-2. Further, the bearing hole H-21 set in the bearing support H-2 includes a first hole and a second hole, the first hole is closer to the first end of the bearing support H-2 relative to the second hole, the aperture of the first hole is larger than the aperture of the second hole, the radial bearing H-3 is set in the bearing hole H-21, and the gap between the radial bearing H-3 and the first hole is used to accommodate the matching portion set on the thrust bearing fixing plate H-5.

[0377] The first end of the bearing support H-2 is the mounting end of the thrust bearing fixing plate H-5, and the thrust bearing H-4 is locked on the thrust bearing fixing plate H-5 by screws.

[0378] The radial bearing H-3 is installed in the bearing hole H-21 in the bearing support H-2. The bearing support H-2 is doubly positioned on the housing H-1 of the compressor motor through a pin and a stop. The function of the vent hole H-25 set on the bearing support H-2 is to ensure that the working air pressure environment of the thrust bearing H-4 and the radial bearing H-3 is consistent.

[0379] In some embodiments, the compressor includes a rotor H-8 and a stator H-9. The rotor H-8 is arranged along the central axis of the housing H-1. The stator H-9 is arranged between the inner wall of the housing H-1 and the rotor H-8, and is fixedly connected to the inner wall of the housing H-1.

[0380] Both ends of the rotor H-8 are provided with radial bearings H-3 and bearing supports H-2. One end of the rotor H-8 is provided with a thrust bearing H-4 and a thrust bearing fixing plate H-5, and the radial bearing H-3 is axially limited by the thrust bearing fixing plate H-5.

[0381] In some embodiments, the compressor includes a thrust plate H-6 and a diffuser H-7. The diffuser H-7 is disposed at the end of the housing H-1. The thrust plate H-6 is fixed to the rotor H-8, and thrust bearings H-4 are disposed on opposite sides of the thrust plate H-6, wherein the thrust bearing H-4 on one side is fixed to the thrust bearing fixing plate H-5, and the thrust bearing H-4 on the other side is fixed to the diffuser H-7. Further, the radial bearing H-3 and the thrust bearing H-4 are gas bearings. Further, the radial bearing H-3 and the thrust bearing H-4 are dynamic pressure gas bearings.

[0382] Rotating machinery supported by hydrodynamic gas bearings has extremely high requirements for the coaxiality of the radial bearings H-3 on both sides of the rotor H-8. If the coaxiality is poor, the bearing performance will be reduced, and in severe cases, the rotor will not be able to float.

[0383] The bearing support H-2 provided by the present invention adopts a dual positioning method of pins and stoppers in terms of positioning. The stoppers can ensure the coaxiality of the bearing after assembly, and then the pins can be used for precise positioning. The pins can be arranged horizontally or vertically. The stoppers and pins are used to complete the final positioning to ensure the micron-level coaxiality of the two radial bearings H-3.

[0384] The bearing support H-2 provided in the present invention has a plurality of (for example, four) vent holes H-25 that allow the bearing support H-2 to communicate with each other on the left and right sides ( Fig.30 The left and right sides of the figure are as follows: the side where the thrust bearing H-4 is located is the left side, and the side where the radial bearing H-3 is located is the right side, ensuring that the operating back pressures of the thrust bearing H-4 and the radial bearing H-3 are the same and stable.

[0385] For example, for a centrifugal refrigeration compressor, the vent hole H-25 can also ensure that the back pressure of the thrust bearing H-4 and the radial bearing H-3 is always equal to the pressure in the compressor motor cavity. The stable and identical bearing back pressure can improve the stability of the bearing rotor system.

[0386] In summary, the bearing support H-2 provided by the present invention has high structural strength and long service life; it adopts double positioning of stopper and pin, and the bearing assembly accuracy is high; the inside and outside of the bearing support H-2 are connected through the vent hole H-25, which improves the stability of the bearing rotor system.

[0387] Bearing support structure modification example 2

[0388] Combination Figure 34 to Figure 37The present invention provides a bearing support assembly, which in an illustrative embodiment includes a fixing plate I-51 and a bearing support seat I-52. The bearing support seat I-52 is provided with a through hole I-522 for mounting a radial bearing I-8; the fixing plate I-51 is detachably mounted on one end of the bearing support seat I-52 along the axial direction, and the side of the fixing plate I-51 away from the bearing support seat I-52 is used to mount a thrust bearing. The fixing plate I-51 can be mounted on the bearing support seat I-52 by fasteners.

[0389] like Fig.36 As shown, since the through hole I-522 of the bearing support I-52 is used to install the radial bearing I-8, and the end face A is used to install the fixing plate I-51, the installation verticality of the fixing plate I-51 relative to the axis will be affected, thereby affecting the verticality of the thrust bearing and the radial bearing. The fixing plate I-51 and the bearing support I-52 in this embodiment adopt a split structure, which is conducive to ensuring the verticality relationship between the through hole I-522 and the end face A during processing; and when two radial bearings I-8 are provided, it is also conducive to ensuring the coaxiality of the two bearing supports I-52 corresponding to the through holes I-522, thereby ensuring the coaxiality of the two radial bearings I-8. Therefore, the assembly accuracy of the bearing can be improved by ensuring the processing accuracy, so as to improve the stability of the bearing rotor system; and it can also improve the qualified rate of parts processing and reduce processing costs.

[0390] like Fig.34 As shown, the fixing plate 1-51 is also used to limit the displacement of the radial bearing 1-8 in the axial direction away from the bearing support 1-52. Therefore, the fixing plate 1-51 can not only install the first thrust bearing 1-10', but also axially limit the radial bearing 1-8, which can make the structure of the bearing support assembly more compact, and is conducive to ensuring the parallelism of the mounting surface of the first thrust bearing 1-10' and the axial limiting surface of the radial bearing 1-8 through the processing parallelism of both sides of the fixing plate 1-51, thereby improving the installation accuracy of the first thrust bearing 1-10' and the radial bearing 1-8.

[0391] like Fig.35 As shown, a positioning ring I-511 is provided at one end of the fixed plate I-51 facing the bearing support I-52, and an annular first groove I-521 is provided on the bearing support I-52. The positioning ring I-511 is embedded in the first groove I-521 to radially position the fixed plate I-51, and there is a gap between the fixed plate I-51 and the main shaft I-1. Moreover, the inner wall I-512 of the positioning ring I-511 cooperates with the outer wall of a partial length section of the radial bearing I-8, and is used to support a partial length section of the radial bearing I-8, and at the same time plays an axial thrust role for the radial bearing I-8. In order to achieve axial thrust, the hole on the fixed plate I-51 that cooperates with the radial bearing I-8 is set along a partial thickness of the fixed plate I-51, and a thrust platform is left at the end away from the bearing support I-52.

[0392] Combination Fig.35 and Fig.37 The bearing support assembly of the present invention also includes a shell I-6, a first end of the bearing support I-52 is connected to the fixed plate I-51, and a second end is connected to the shell I-6. Since the outer diameter of the thrust bearing is smaller than the inner diameter of the shell I-6, correspondingly, the outer profile of the cross-section of the bearing support I-52 gradually increases from the first end to the second end.

[0393] To lose weight, Fig.35 As shown, a weight reducing groove I-524 may also be provided on the side of the bearing support I-52 away from the thrust bearing. For example, the weight reducing groove I-524 may be provided in a ring shape, with an inner wall parallel to the axis and an outer wall consistent with the outer contour of the bearing support I-52.

[0394] This V-shaped bearing support I-52 adopts a structure with a gradually changing cross-sectional area, which can improve the overall structural strength of the bearing support I-52, evenly distribute the force at various locations, optimize the load-bearing capacity, and the outer wall is an inclined surface, which is easy to realize through casting, and has a draft angle when casting through a mold.

[0395] Furthermore, if Fig.35 As shown, the bearing support 1-52 is provided with a vent hole 1-526, which is used to make the working environment of the radial bearing 1-8 consistent with the first thrust bearing 1-10', for example, to make the working back pressure and temperature of the radial bearing 1-8 consistent with the first thrust bearing 1-10'. Refrigerant for cooling the motor enters and exits the motor cavity. When the compressor operates normally, the overall motor cavity pressure and temperature are stable, and the thrust bearing and the radial bearing work in the same environment as the motor cavity, that is, to ensure gas circulation, and the back pressure is relatively stable. If the back pressure fluctuates too much, it will cause the bearing gas film to fluctuate, affecting the bearing performance.

[0396] like Fig.36 As shown, an operating hole I-523 is provided in the radial direction on the bearing support I-52, so that a vibration sensor or a temperature sensor can be installed on the outer wall of the radial bearing I-8 through the operating hole I-523 to monitor the working state of the radial bearing I-8. The hole section of the operating hole I-523 along the radial outer side can be used as a bypass hole to ensure that the thrust bearing and the radial bearing I-8 and the motor cavity have the same pressure and temperature, and the hole section of the operating hole I-523 along the radial inner side plays a role in dissipating heat for the radial bearing I-8.

[0397] In some embodiments, in combination Fig.36 and Fig.37As shown, the second end of the bearing support I-52 is provided with a flange I-525, and a stopper I-527 is provided at the outer end of the flange I-525. The bearing support I-52 is installed in the housing I-6 through the flange I-525 and fixed by fasteners. At the same time, the bearing support I-52 relies on the stopper I-527 for radial positioning and relies on the end of the flange I-525 for axial positioning.

[0398] The stopper I-527 is used to first reposition the connection between the bearing support I-52 and the housing I-6, and can preliminarily position the installation position relationship between the bearing support I-52 and the housing I-6. Further, the bearing support assembly also includes a pin, and a pin hole I-528 is provided on the flange I-525 of the bearing support I-52. The pin can penetrate the pin hole I-528 and the pin hole on the housing I-6 to perform a second repositioning of the connection between the bearing support I-52 and the housing I-6, so as to accurately position the installation position relationship between the bearing support I-52 and the housing I-6. The pin can be set axially or radially.

[0399] This embodiment can accurately ensure the installation accuracy of the bearing support I-52 in the housing I-6 by adopting double positioning, thereby improving the position accuracy between the radial bearing I-8 and the thrust bearing.

[0400] like Fig.36 and Fig.37 As shown, the bearing support I-52 is arranged in the shell I-6, and the through hole I-522 of the bearing support I-52 and the end face A for installing the fixing plate I-51 are configured to be processed to a preset size when the bearing support I-52 and the shell I-6 are assembled into a combination.

[0401] This embodiment is processed in a state where the bearing support I-52 and the housing I-6 are positioned and formed into an assembly. The installation accuracy of the bearing can be ensured by the processing accuracy of the assembly, and the verticality of the through hole I-522 and the end face A can be ensured by one-time positioning and clamping.

[0402] Furthermore, if Fig.37 As shown, two bearing supports I-52 are axially spaced apart in the shell I-6 for supporting two different positions of the main shaft I-1, and the through holes I-522 of the two bearing supports I-52 are configured to be processed to a preset size when the two bearing supports I-52 and the shell I-6 are assembled into a combination.

[0403] This embodiment processes the two bearing supports I-52 and the housing I-6 while positioning and forming an assembly, so that the two through holes I-522 can be processed in sequence from one side of the assembly, and the size and coaxiality of the two through holes I-522 can be ensured by one-time positioning and clamping.

[0404] Since the key parts on the bearing support I-52 are processed in one positioning and clamping process, the coaxiality of the two through holes I-522 and the verticality of the corresponding through hole I-522 of each bearing support I-52 and the end face A can be improved, thereby ensuring the coaxiality of the two radial bearings I-8 and the verticality of the thrust bearing, thereby improving the working stability of the rotor system. Through actual measurement, the coaxiality of the two radial bearings I-8 and the verticality of the radial bearing I-8 and the thrust bearing can be improved to within 5 microns.

[0405] The specific processing method of the bearing support assembly is described below. During processing, the two bearing supports I-52 are first repositioned through the stop I-527 to match the housing I-6, and then the flange I-525 is fixed to the housing I-6 through fasteners, and then fixed with pins. Subsequently, the housing I-6 and the two bearing supports I-52 are positioned on the processing equipment as an integral component, and the end faces A of the two bearing supports I-52 and the fixing plate I-51 are processed to ensure the verticality of the thrust bearing and the radial bearing I-8, and then the through holes I-522 of the two bearing supports I-52 are processed in sequence from one side to ensure the coaxiality of the two radial bearings I-8.

[0406] After the processing is completed, the bearing support I-52 is removed, and the radial bearing I-8 is installed into the through hole I-522 of the bearing support I-52 by heat-fitting, and then the fixing plate I-51 is installed on the first end of the bearing support I-52. Then, the bearing support I-52 with the fixing plate I-51 can be fixed on the housing I-6 together, and the bearing support I-52 can be positioned by the stop I-527 and the pin position determined during processing.

[0407] If each bearing adopts a hydrodynamic gas bearing, since the bearing itself has high machining accuracy and requires extremely high assembly position accuracy, if the assembly accuracy is reduced, the bearing performance will be reduced, and in severe cases, the rotor will not be able to float; when two or more hydrodynamic radial bearings are used, the coaxiality of the bearing is required to be at the micron level, and the verticality of all thrust surfaces relative to the center of the rotor is also required to be at the micron level. The method of the present invention can process the through holes I-522 and the end faces A of the two bearing supports I-52 in one positioning and clamping process, which can improve the machining accuracy and subsequent assembly accuracy.

[0408] Secondly, the present invention provides a processing method of the bearing support assembly based on the above embodiment, which, in some embodiments, includes:

[0409] Step I-101, assembling the bearing support I-52 and the housing I-6 into a combined body;

[0410] Step I-102, positioning and clamping the assembly on a processing device, which may be a machine tool, etc.;

[0411] Step I-103, the through hole I-522 of the bearing support I-52 and the end face A for mounting the fixing plate I-51 are processed to the preset size by one-time positioning and clamping.

[0412] This embodiment is processed in a state where the bearing support I-52 and the housing I-6 are positioned and formed into an assembly, so that the installation accuracy of the bearing can be ensured by the processing accuracy of the assembly. Moreover, through one-time positioning and clamping, a unified processing reference can be used to ensure the processing verticality of the through hole I-522 and the end face A, thereby ensuring the verticality of the radial bearing I-8 and the thrust bearing.

[0413] In some embodiments, two bearing supports I-52 are provided in the housing I-6 and are spaced apart along the axial direction. After the two bearing supports I-52 and the housing I-6 are assembled into a combination body through step I-101, the processing method further includes:

[0414] Step I-104, process the through holes I-522 of the two bearing supports I-52 to a preset size through one-time positioning and clamping.

[0415] There is no restriction on the execution order of step I-104 and step I-103. In actual processing, the two through holes I-522 and the end face A are finely processed in one positioning and clamping process according to the convenience of processing.

[0416] This embodiment processes the two bearing supports I-52 and the housing I-6 while positioning and forming an assembly, so that the installation accuracy of the bearings can be ensured by the machining accuracy of the assembly, and a unified machining reference can be used by one-time positioning and clamping, and the size and coaxiality of the two through holes I-522 can be ensured by one-time positioning and clamping.

[0417] In some embodiments, step I-104 processes the through holes I-522 of the two bearing supports I-52 to a preset size by one-time positioning and clamping, specifically including: processing the through holes I-522 of the two bearing supports I-52 to a preset size in sequence from one side of the shell I-6.

[0418] The through hole I-522 can be processed by boring. The processing tool processes the two through holes I-522 in sequence through axial feeding from one side of the shell I-6 to improve the processing efficiency and further improve the coaxiality of the two through holes I-522.

[0419] In some embodiments, a stopper I-527 is provided at one end of the bearing support I-52 connected to the housing I-6. Step I-101 of assembling the bearing support I-52 and the housing I-6 into a combined body specifically includes:

[0420] Step I-101A, matching the bearing support I-52 with the housing I-6 through the stopper I-527 for the first repositioning;

[0421] Step I-101B, fixing the bearing support I-52 and the housing I-6 by fasteners;

[0422] Step I-101C: After the flange is fixed to the housing I-6, pins are driven in for a second re-positioning.

[0423] In this embodiment, steps I-101 to I-103 are performed sequentially.

[0424] After the initial positioning through the stop I-527, the positional relationship between the bearing support I-52 and the housing I-6 is constrained by fasteners. On this basis, on the basis of the original pin hole I-528, pin holes are made on the bearing support I-52 and the housing I-6, and the pins are inserted into the pin holes. The pins can prevent the bearing support I-52 and the housing I-6 from changing positions due to large cutting forces during the processing process, and can also provide accurate positioning for the subsequent product assembly process. By adopting double positioning, the installation accuracy of the bearing support I-52 in the housing I-6 can be accurately guaranteed, thereby improving the position accuracy between the radial bearing I-8 and the thrust bearing.

[0425] Furthermore, after the processing is completed, the processing method further comprises:

[0426] Step I-105, disassemble the assembly formed by the bearing support I-52 and the housing I-6 so as to install the radial bearing I-8 while the bearing support I-52 and the housing I-6 are separated.

[0427] After the processing is completed, the bearing support I-52 is removed, and the radial bearing I-8 is installed into the through hole I-522 of the bearing support I-52 by heat installation, and then the fixing plate I-51 is installed at the first end of the bearing support I-52. The bearing support I-52 can be fixed on the housing I-6 by the pin position determined during processing. The bearing support I-52 ensures the assembly accuracy of the bearing through the stop I-527 and the pin double positioning method to improve the stability of the bearing rotor system.

[0428] Finally, the present invention also provides a compressor, including the bearing support assembly of the above embodiment. For example, the compressor is a centrifugal compressor. Alternatively, the compressor can also be a centrifugal refrigeration compressor or a screw refrigeration compressor.

[0429] The working principle of the centrifugal compressor is as follows: during the operation of the compressor, the main shaft I-1 rotates at a high speed, the gas is accelerated through the left impeller I-2 and enters the diffuser I-3, the gas is compressed and pressurized through the diffuser I-3 and then enters the first volute, the exhaust channel on the first volute guides the compressed gas to enter the right impeller I-2, and then enters the right diffuser I-3 after the centrifugal action of the right impeller I-2, the gas enters the second volute after the second stage of compression, and is discharged from the compressor through the exhaust channel on the second volute.

[0430] like Fig.34 As shown, the centrifugal compressor of the present invention also includes: a main shaft I-1, a diffuser I-3, a thrust plate I-4 and a second thrust bearing I-10. The thrust plate I-4 is configured to be rotatable together with the main shaft I-1 and is axially located between the diffuser I-3 and the fixed plate I-51. The first thrust bearing I-10' is arranged at one end of the fixed plate I-51 away from the bearing support I-52, and the second thrust bearing I-10 is arranged at one end of the diffuser I-3 away from the diffuser surface. Specifically, the thrust plate I-4 has a thrust portion I-41. The left and right surfaces of the thrust portion I-41 form working surfaces with the thrust bearings on both sides, which can withstand bidirectional axial forces and ensure the stable and reliable operation of the compressor during full-operation operation and reversal.

[0431] Furthermore, the thrust plate I-4 may also include a connecting portion I-42, the thrust plate I-4 is connected to the thrust portion I-41, and is sleeved on the main shaft I-1. The bottom of the second groove I-31 is provided with a through hole, and the connecting portion I-42 is embedded in the through hole. The connecting portion I-42 can be interference fit with the main shaft I-1 so that the thrust plate I-4 can rotate with the main shaft I-1. The diffuser I-3 and the fixed plate I-51 are fixedly arranged, and there is a gap between them and the main shaft I-1. For example, the thrust plate I-4 can be a cylindrical stepped structure.

[0432] For example, the first thrust bearing 1-10', the second thrust bearing 1-10 and / or the radial bearing 1-8 may be a static pressure or dynamic pressure gas thrust bearing, or may also be a magnetic bearing.

[0433] by Fig.34 For example, since there is a gap between the thrust bearing and the thrust plate I-4, the gas will form a pressurized gas film in this gap to play a thrust and lubrication role. Since the thrust bearing itself is in the compressor cavity, the gas comes from the cavity environment. During the rotation of the rotor, the gas can be brought into the gap to form a dynamic pressure gas thrust bearing.

[0434] In the centrifugal compressor of this embodiment, the thrust plate can cooperate with the thrust bearings on both sides to withstand axial forces in the left and right directions to ensure the stability of the compressor during full-operation and reverse operation. The operating condition of the compressor refers to the evaporation temperature and condensation temperature of the system where the compressor is located. The full operating condition means that the compressor works within a certain evaporation temperature range and condensation temperature range. When the compressor stops, since the exhaust pressure is higher than the suction pressure, a reverse situation will occur after the stop.

[0435] Furthermore, there are gaps between both sides of the thrust plate 1-4 and the first thrust bearing 1-10' and the second thrust bearing 1-10, and the gaps on both sides are defined by the diffuser 1-3 and the fixing plate 1-51 abutting against each other.

[0436] For example, the first thrust bearing 1-10', the second thrust bearing 1-10 and / or the radial bearing 1-8 may be a static pressure or dynamic pressure gas thrust bearing, or may also be a magnetic bearing.

[0437] by Fig.34 For example, since there is a gap between the thrust bearing and the thrust plate I-4, the gas will form a pressurized gas film in this gap to play a thrust and lubrication role. Since the thrust bearing itself is in the compressor cavity, the gas comes from the cavity environment. During the rotation of the rotor, the gas can be brought into the gap to form a dynamic pressure gas thrust bearing.

[0438] By abutting against each other and performing combined limiting, the position of the thrust plate I-4 and the gap between the thrust bearings on both sides are limited, thereby accurately ensuring the thrust bearing gap, reducing the difficulty of assembly, improving assembly efficiency and assembly accuracy, and ensuring the working performance of the thrust bearing, thereby improving the operating stability of the compressor.

[0439] Furthermore, the thrust plate I-4 may also include a connecting portion I-42, the thrust plate I-4 is connected to the thrust portion I-41, and is sleeved on the main shaft I-1. The bottom of the second groove I-31 is provided with a through hole, and the connecting portion I-42 is embedded in the through hole. The connecting portion I-42 can be interference fit with the main shaft I-1 so that the thrust plate I-4 can rotate with the main shaft I-1. The diffuser I-3 and the fixed plate I-51 are fixedly arranged, and there is a gap between them and the main shaft I-1. For example, the thrust plate I-4 can be a cylindrical stepped structure.

[0440] Further, still refer to Fig.34 A second groove I-31 is provided at one end of the diffuser I-3 away from the diffuser surface, a first thrust bearing I-10' is provided at the bottom of the second groove I-52 along the axial direction, a fixing plate I-51 is fixed to the diffuser I-3, and a thrust portion I-41 of the thrust plate I-4 is located in the second groove I-31.

[0441] Since the bearing support I-52 needs to be fixed on the shell I-6 of the compressor, its own position is fixed, so the fixing plate I-51 can be axially positioned. In addition, the diffuser I-3 is also fixed on the shell I-6, and the diffuser I-3 and the fixing plate I-51 are abutted against each other, so that the clearance of the thrust bearings on both sides can be accurately guaranteed by the axial depth of the second groove I-31, which can improve the assembly accuracy, reduce the assembly difficulty, improve the assembly efficiency, and at the same time ensure the performance of the thrust bearing, prevent the thrust bearing performance from being reduced or even failed due to inaccurate clearance control, thereby improving the operating stability of the compressor.

[0442] like Fig.34 As shown, the depth of the second groove I-31 includes: the thickness of the thrust portion I-41, the thickness of the thrust bearings on both sides, and the gap between the thrust bearings on both sides. Therefore, in order to ensure the gap between the thrust bearings on both sides, the gap can be controlled by increasing the depth of the second groove I-31, the thickness of the thrust portion I-41, and the thickness of the thrust bearings on both sides. The specific method is: according to the gap range that the thrust bearing needs to achieve, the thickness tolerance range of the thrust portion I-41, and the thickness tolerance range of the thrust bearing, the design depth and tolerance range of the second groove I-31 are reversed. Therefore, the thrust bearing gap can be ensured by improving the machining accuracy of the depth of the second groove I-31, which can improve the assembly accuracy, reduce the assembly difficulty, and thus improve the assembly efficiency.

[0443] In some embodiments, the first thrust bearing 1-10' is directly fixed to the bottom of the second groove 1-31. This structure integrates the diffuser 1-3 and the thrust bearing fixing plate into one part, and the bottom of the second groove 1-31 can be used as the fixing plate in the second thrust bearing 1-10, without the need to set up an additional thrust bearing fixing plate, which can further reduce the axial size of the bearing support assembly and make the structure more compact.

[0444] In a specific structure, reference Fig.34 The first thrust bearing I-10' is fixed to the fixing plate I-51 by fasteners, the second thrust bearing I-10 is fixed to the diffuser I-3 by fasteners, the fixing plate I-51 and the diffuser I-3 are fixed by fasteners, and the outer periphery of the diffuser I-3 is provided with a positioning stop to facilitate positioning and installation with the shell I-6.

[0445] Bearing support structure modification example 3

[0446] See also Figures 38 to 40 The embodiment of the present invention provides a compressor, including a bearing support J-1, a radial bearing J-2, a main shaft J-4 and a thrust bearing J-3. The bearing support J-1 includes a first through hole J-11, and the radial bearing J-2 is installed in the first through hole J-11. The main shaft J-4 is installed on the radial bearing J-2 and the thrust bearing J-3 at the same time; the thrust bearing J-3 abuts against the side of the bearing support J-1.

[0447] The side surface of the bearing support J-1 serves as the mounting surface J-17 of the thrust bearing J-3, thereby realizing the installation and positioning of the thrust bearing J-3. The radial bearing J-2 is also directly mounted on the bearing support J-1. The bearing support J-1 simultaneously positions the thrust bearing J-3 and the radial bearing J-2. When machining parts, the verticality of the mounting surface J-17 is easier to ensure.

[0448] In some embodiments, the thrust bearing J-3 has no support, and the thrust bearing J-3 is in the form of a thin sheet. One side of the thrust bearing J-3 directly abuts against the side of the bearing support J-1, and the other side thereof directly abuts against the thrust plate J-6. No other bearing, positioning or mounting structure is provided between the thrust bearing J-3 and the mounting surface J-17. The radial bearing J-2 includes a base and a bearing body fixed to the inner wall of the through hole of the base, and the bearing body is a cylindrical thin sheet. The base is used to realize the installation of the radial bearing J-2.

[0449] Since the radial force of the rotating machinery is basically equal to the rotor gravity, the radial load is relatively small, and the radial strength requirement of the bearing support J-1 is not high, and the bearing support J-1 can easily meet the radial strength requirement. The axial load is larger than the radial load, and the axial load is transmitted to the bearing support J-1 through the thrust bearing J-3.

[0450] In the above technical solution, the bearing support J-1 itself integrates two functions, which respectively support the radial bearing J-2 and position and fix the thrust bearing J-3. The machining accuracy of the bearing support J-1 is achieved, so that the thrust bearing J-3 meets the micron-level verticality requirement when installed. In addition, the bearing support J-1 simultaneously positions the radial bearing J-2 and the thrust bearing J-3. Since there is no need to set a thrust bearing fixing plate, the thickness occupied by the thrust bearing fixing plate is reduced. Furthermore, the two radial bearings J-2 support the main shaft J-4; the thrust bearing J-3 bears the axial force and axially positions the main shaft J-4. The above structure also shortens the length of the main shaft J-4, reduces the size of the entire compressor, and reduces the weight.

[0451] See also Fig.38 A positioning step surface J-12 is provided in the first through hole J-11, and the end surface of the radial bearing J-2 abuts against the positioning step surface J-12.

[0452] See also Fig.38 and Fig.39The bearing support J-1 and the radial bearing J-2 are interference fit, and the radial bearing J-2 is axially limited by the positioning step surface J-12. The positioning step surface J-12 is specifically a step surface, and one end of the radial bearing J-2 abuts against the positioning step surface J-12 to realize the positioning of the radial bearing J-2 on the bearing support J-1, and no other positioning components are required, which simplifies the system structure and makes the compressor structure more compact.

[0453] See also Fig.38 and Fig.40 In some embodiments, a thrust plate J-6 is installed on the side of the thrust bearing J-3 away from the bearing support J-1. The thrust bearing J-3 is in direct contact with the thrust plate J-6.

[0454] See also Fig.38 In some embodiments, the bearing support J-1 is provided with a second through hole J-13, and the second through hole J-13 is used to connect the cavity J-18 where the thrust bearing J-3 is located with the first through hole J-11 where the radial bearing J-2 is located, so that the radial bearing J-2 and the thrust bearing J-3 have the same working environment.

[0455] The working environment refers to temperature and pressure, specifically making the working environment of the thrust bearing J-3 and the radial bearing J-2 the same as the motor cavity.

[0456] The central axis of the second through hole J-13 is perpendicular to the central axis of the first through hole J-11, or forms an angle therebetween. The second through hole J-13, for example, is a plurality of holes with different diameters.

[0457] In some embodiments, the number of the second through holes J- 13 is 2 to 14, such as 2, 4, 8, or 12.

[0458] In the above technical solution, 2 to 12 second through holes J-13 connecting the left and right channels are evenly arranged on the bearing support J-1, so that the radial bearing J-2 and the thrust bearing J-3 have the same working environment. The refrigerant for cooling the motor flows in and out of the motor cavity. When the compressor operates normally, the overall motor cavity pressure and temperature are stable. The thrust bearing J-3 and the radial bearing J-2 have the same working environment as the motor cavity, which ensures that the gas is circulated and the back pressure is relatively stable, reducing the fluctuation of the bearing gas film and optimizing the bearing performance.

[0459] See also Fig.40 and Fig.41 In some embodiments, the second through holes J-13 are evenly arranged relative to the circumferential direction of the bearing support J-1.

[0460] See also Fig.40 and Fig.41In some embodiments, the outer edge size of the side of the bearing support J-1 facing the thrust bearing J-3 is smaller than the outer edge size of the side of the bearing support J-1 facing away from the thrust bearing J-3. Fig.40 Taking the direction shown as an example, the outer edge size of the right side of the bearing support J-1 is large, and the outer edge size of the left side is small. This structure makes the bearing support J-1 easy to install in the compressor.

[0461] See also Fig.40 and Fig.41 In some embodiments, the outer edge size of the bearing support J-1 is generally gradual, and an annular boss is provided at the wide end of the bearing support J-1, and the boss is provided with a mounting hole J-15, through which the bearing support J-1 is positioned when it is installed on the cylinder J-5. The mounting hole J-15 is, for example, a pin hole.

[0462] The above technical solution adopts an integrated bearing support, which has high structural strength and is easy to cast. The bearing support J-1 adopts a V-shaped structure, which effectively realizes the transmission of axial force to the motor cylinder J-5, and improves the strength and service life of the bearing support J-1;

[0463] See also Fig.40 In some embodiments, the bearing support J-1 is provided with a stop J-14 for positioning with the compressor cylinder J-5.

[0464] Specifically, on the side of the boss away from the bearing support J-1, the bearing support J-1 is also provided with a stopper J-14, and the bearing support J-1 is positioned relative to the compressor cylinder J-5 through the stopper J-14.

[0465] In the above technical solution, the bearing support J-1 adopts the dual positioning of the mounting hole J-15 and the stopper J-14. The stopper J-14 ensures the coaxiality of the bearing after assembly, and then the pin is passed through the mounting hole J-15 for precise positioning. The above structure meets the coaxiality requirement of the two radial bearings J-2 at both ends of the main shaft J-4 to reach the micron level, making the performance of the radial bearing J-2 reliable and allowing the rotor to work normally.

[0466] In some embodiments, the bearing support J-1 is provided with a weight-reducing hole J-16 to achieve lightweighting of the compressor.

[0467] The shape of the weight-reducing hole J-16 matches the shape of the bearing support J-1. The weight-reducing hole J-16 is annular. From the cross-sectional view, the contour lines of the weight-reducing holes J-16 located on each side of the central axis of the bearing support J-1 are also roughly trumpet-shaped. The weight-reducing holes J-16 of the above structure make the wall thickness of the bearing support J-1 roughly uniform. The middle of the bearing support J-1 is hollowed out into a V shape to ensure that the wall thickness of the casting is relatively uniform, which reduces the deadweight of the support and facilitates casting.

[0468] Diffuser structure modification example

[0469] See also Figure 42 to Figure 45 In some embodiments, the present disclosure provides a compressor, including an impeller K-1, a thrust bearing K-2, and a diffuser K-3. A side surface K-31 of the diffuser K-3 abuts against the impeller K-1, and an axial inner recess K-32 is provided on the other side, and the bottom surface of the axial inner recess K-32 abuts against the thrust bearing K-2. A thrust plate K-7 is provided on the other side of the thrust bearing K-2.

[0470] The diffuser K-3 mentioned above integrates the function of the thrust bearing fixing plate. The bottom surface of the axial inner concave portion K-32 of the diffuser K-3 directly abuts against the thrust bearing K-2, which plays a positioning role for the thrust bearing K-2. The thrust bearing K-2 is directly locked by screws to bear the axial force of the rotor. The bottom surface of the axial inner concave portion K-32 of the diffuser K-3 serves as the fixing surface of the thrust bearing K-2. The fixing surface has high verticality accuracy, so that the air film on the mating surface of the thrust plate K-7 and the thrust bearing K-2 is uniform, and the thrust bearing K-2 is uniformly stressed, which reduces the wear of the thrust bearing K-2 and extends the service life of the thrust bearing K-2.

[0471] The compressor provided by the above technical solution reduces the number of parts and improves quality control due to the adoption of the diffuser K-3 with the above structure; while meeting the functional requirements, the thickness of the thrust bearing fixing plate is reduced, thereby reducing the rotor length, which not only improves the stiffness of the rotor and increases the critical speed of the bending mode of the bearing-rotor system, but also reduces the weight of the rotor and reduces the bearing load, thereby improving the stability of the bearing-rotor system.

[0472] In some embodiments, a seal K-4 is provided on the inner wall of the through hole of the diffuser K-3.

[0473] The diffuser K-3 converts the velocity energy of the medium at the outlet of the impeller K-1 into pressure energy. The inner wall of the through hole of the diffuser K-3 is provided with a seal K-4, which cooperates with the rotor to form a shaft seal to prevent the exhaust gas of the impeller K-1 from entering the motor cavity.

[0474] In some embodiments, seal K-4 includes sealing comb teeth.

[0475] In some embodiments, the diffuser K-3 and the seal K-4 are integrated. This structure integrates the seal K-4, the thrust bearing fixing plate and the existing diffuser into one part, with a high degree of integration, reducing the number of parts and improving quality control; the length of this part is reduced while meeting functional requirements, thereby reducing the length of the rotor, which not only improves the stiffness of the rotor and the critical speed of the bending mode of the bearing rotor system, but also reduces the weight of the rotor and reduces the bearing load, and the two together improve the stability of the bearing rotor system.

[0476] In some embodiments, the compressor further includes a cylinder K-5, which is connected to the diffuser K-3 and is positioned by a positioning stop K-33 of the diffuser K-3.

[0477] During assembly, first fix the thrust bearing K-2 on the diffuser K-3 by screws, then position the diffuser K-3 on the motor cylinder K-5 by the stopper, and then use pins to accurately position it. The above structure realizes the accurate positioning and assembly of the diffuser and the cylinder K-5.

[0478] The coaxiality of the diffuser K-3 shaft seal part and the verticality of the thrust bearing K-2 fixing surface are both ensured on one part, which not only reduces the difficulty of processing and assembly, but also greatly reduces the cumulative dimensional tolerance and form and position errors of processing and assembly.

[0479] Moreover, compared with multiple parts, one part has only one assembly reference, which improves assembly accuracy and efficiency. Due to the high coaxiality accuracy of the comb seal, the chance of wear between the comb seal and the rotor during operation is reduced, the increase in the sealing gap is reduced, the increase in leakage loss is reduced, and the energy efficiency of the compressor is improved.

[0480] In some embodiments, the diffuser K-3 is cast. The diffuser K-3 and the seal K-4 are integrally cast, which improves production efficiency.

[0481] In some embodiments, a main shaft K-6 is installed in the through hole of the diffuser K-3, and the material of the diffuser K-3 is softer than that of the main shaft K-6.

[0482] During operation, when wear occurs, the diffuser K-3 is worn, and the main shaft K-6 is not worn or is less worn. The above structure plays a role in protecting the main shaft K-6.

[0483] In some embodiments, the thickness of the diffuser K-3 is less than 14 mm. The thickness of the diffuser K-3 is significantly reduced compared to the total thickness of the thrust bearing fixing plate of the existing diffuser K-3, thereby achieving lightweighting of the compressor.

[0484] Diffuser, thrust plate and related matching structure modification example 1

[0485] refer to Fig.46 In some embodiments, the present disclosure provides a centrifugal compressor. In order to make those skilled in the art more clearly understand the improvements of the present invention, first combine Fig.46 The overall structure of the centrifugal compressor will be described.

[0486] like Fig.46As shown, taking a two-stage centrifugal compressor as an example, it includes a first volute L-61, a second volute L-63 and an intermediate casing L-62. The first volute L-61 and the second volute L-63 are respectively arranged at the two ends of the intermediate casing L-62 in the axial direction, together forming a compressor casing L-6. The main shaft L-1 is arranged at the center of the compressor casing, and an impeller L-2 is respectively arranged at the two ends of the main shaft L-1. A diffuser L-3 is arranged at the inner end of the impeller L-2. When the impeller L-2 rotates at a high speed, the gas rotates with it. Under the action of centrifugal force, the gas is thrown into the rear diffuser L-3 for expansion, and the velocity energy of the medium at the outlet of the impeller L-2 is converted into pressure energy. The gas with increased pressure is discharged from the volute.

[0487] In order to support the main shaft L-1, radial bearings L-8 are provided at both ends of the main shaft L-1, and the radial bearings L-8 are supported by bearing supports L-52, and the bearing supports L-52 are connected to the intermediate housing L-62. A stator assembly L-7 is provided between the main shaft L-1 and the intermediate housing L-62. Since the impeller L-2 generates axial force during operation, a thrust bearing is provided at one end of the main shaft L-1 to balance the axial force generated by the impeller L-2.

[0488] The working principle of this compressor is as follows: during the operation of the compressor, the main shaft L-1 rotates at high speed, and the gas enters the diffuser L-3 through the impeller L-2 on the left. After the first stage of compression, the gas enters the first volute L-61. The exhaust channel on the first volute L-61 guides the compressed gas to enter the right impeller L-2. After the centrifugal action of the right impeller L-2, it enters the right diffuser L-3. After the second stage of compression, the gas enters the second volute L-63 and is discharged from the compressor through the exhaust channel on the second volute L-63.

[0489] Next, the bearing support assembly in the centrifugal compressor will be described in detail. In some embodiments, Fig.47 As shown, the centrifugal compressor includes: a main shaft L-1, an impeller L-2, a diffuser L-3, a thrust plate L-4 and a support assembly L-5.

[0490] Among them, a magnetic steel L-13 may be provided in the middle of the main shaft L-1, the diffuser L-3 is fixed on the housing L-6, and a first thrust bearing L-10 is provided at one end of the diffuser L-3 away from the diffuser surface, and the diffuser surface is the end surface close to the impeller L-2. The support assembly L-5 is provided at one end of the diffuser L-3 away from the diffuser surface, one end of which is fixed to the housing L-6 of the compressor, and the other end is against the end surface of the diffuser L-3, and a second thrust bearing L-10' is provided on the side of the support assembly L-5 facing the diffuser L-3. The thrust plate L-4 is configured to rotate with the main shaft L-1, and the thrust plate L-4 has a thrust portion L-41, for example, a disc-shaped structure, and the gaps between the two sides of the thrust portion L-41 and the first thrust bearing L-10 and the second thrust bearing L-10' are limited by the diffuser L-3 and the support assembly L-5 abutting against each other. The left and right sides of the thrust part L-41 form working surfaces with the thrust bearings on both sides, which can withstand bidirectional axial forces and ensure the stable and reliable operation of the compressor under full working conditions and during reverse rotation.

[0491] For example, the first thrust bearing L-10 and the second thrust bearing L-10' may be static pressure or dynamic pressure gas thrust bearings, or may also be magnetic suspension bearings.

[0492] by Fig.47 For example, since there is a gap between the thrust bearing and the thrust plate L-4, the gas will form a pressurized gas film in this gap to play a thrust and lubrication role. Since the thrust bearing itself is in the compressor cavity, the gas comes from the cavity environment. During the rotation of the rotor, the gas can be brought into the gap to form a dynamic pressure gas thrust bearing.

[0493] In the centrifugal compressor of this embodiment, the thrust plate can cooperate with the thrust bearings on both sides to withstand axial forces in the left and right directions to ensure the stability of the compressor during full-operation and reverse operation. The operating condition of the compressor refers to the evaporation temperature and condensation temperature of the system where the compressor is located. The full operating condition means that the compressor works within a certain evaporation temperature range and condensation temperature range. When the compressor stops, since the exhaust pressure is higher than the suction pressure, a reverse situation will occur after the stop.

[0494] Moreover, since the diffuser L-3 and the support assembly L-5 need to be fixed on the compressor casing L-6, their own positions are fixed. The support assembly L-5 and the diffuser L-3 are abutted against each other for combined limiting, which limits the position of the thrust plate L-4 and the gap between the thrust bearings on both sides. In this way, the thrust bearing gap can be accurately guaranteed, the assembly difficulty can be reduced, the assembly efficiency and assembly accuracy can be improved, and the working performance of the thrust bearing can be guaranteed, thereby improving the operating stability of the compressor.

[0495] like Fig.47As shown, a first groove L-31 is provided at one end of the diffuser L-3 away from the diffuser surface, and a first thrust bearing L-10 is provided at the bottom of the first groove L-31 along the axial direction. The thrust portion L-41 is located in the first groove L-31, and there is a gap between both sides of the thrust portion L-41 and the first thrust bearing L-10 and the second thrust bearing L-10'.

[0496] Since the diffuser L-3 and the support assembly L-5 are against each other, the axial depth of the first groove L-31 can accurately ensure the clearance of the thrust bearings on both sides, which can improve the assembly accuracy, reduce the difficulty of assembly, and improve the assembly efficiency. At the same time, it can also ensure the performance of the thrust bearing and prevent the thrust bearing performance from being reduced or even failing due to inaccurate clearance control, thereby improving the operating stability of the compressor.

[0497] like Fig.47 As shown, the depth of the first groove L-31 includes: the thickness of the thrust portion L-41, the thickness of the thrust bearings on both sides, and the gap between the thrust bearings on both sides. Therefore, in order to ensure the gap between the thrust bearings on both sides, the gap can be controlled by increasing the depth of the first groove L-31, the thickness of the thrust portion L-41, and the thickness of the thrust bearings on both sides. The specific method is: according to the gap range that the thrust bearing needs to achieve, the thickness tolerance range of the thrust portion L-41, and the thickness tolerance range of the thrust bearing, the design depth and tolerance range of the first groove L-31 are reversed. Therefore, the thrust bearing gap can be ensured by improving the machining accuracy of the depth of the first groove L-31, which can improve the assembly accuracy, reduce the assembly difficulty, and thus improve the assembly efficiency.

[0498] In some embodiments, Fig.47 and Fig.48 As shown, the centrifugal compressor also includes a housing L-6 and a radial bearing L-8, which is used to bear the radial force of the rotor, mainly from the gravity of the rotor itself. For example, the radial bearing L-8 can be a static pressure or dynamic pressure gas radial bearing, or it can also be a magnetic suspension bearing.

[0499] The support assembly L-5 includes a fixed plate L-51 and a bearing support L-52. The fixed plate L-51 is against the diffuser L-3, and the second thrust bearing L-10' is arranged on the fixed plate L-51 on the side facing the diffuser L-3; the bearing support L-52 is arranged on the side of the fixed plate L-51 away from the diffuser L-3, and the first end of the bearing support L-52 is connected to the fixed plate L-51, and the second end is connected to the housing L-6, and is used to support the main shaft L-1 through the radial bearing L-8.

[0500] The support assembly L-5 in this embodiment adopts a split structure. The second thrust bearing L-10' is installed through the fixing plate L-51, and the radial bearing L-8 is installed on the bearing support L-52. This is beneficial to improve the installation position accuracy of the radial bearing L-8 and the thrust bearing at both ends of the main shaft L-1, including the coaxiality of the two radial bearings L-8 and the verticality of the thrust bearing, which can improve the working stability of the rotor system.

[0501] Specifically, Fig.50 As shown, this can be achieved in the following manner. A flange L-52L-5 is provided at the second end of the bearing support L-52, and a stopper L-52L-7 is provided at the outer end of the flange L-52L-5. The bearing support L-52 is installed in the intermediate housing L-62 through the flange L-52L-5 and fixed by fasteners. At the same time, the bearing support L-52 is radially positioned by the stopper L-52L-7.

[0502] During processing, the two bearing supports L-52 are first repositioned through the stop L-52L-7 to match with the intermediate housing L-62, and then the flange L-52L-5 is fixed to the intermediate housing L-62 by fasteners, and then fixed by pins. Subsequently, the intermediate housing L-62 and the two bearing supports L-52 are positioned on the processing equipment as an integral component, and the end faces of the two bearing supports L-52 matching with the fixing plate L-51 are processed to ensure the verticality of the thrust bearing and the radial bearing L-8, and then the mounting holes L-52 of the two bearing supports L-52 are processed in sequence from one side to ensure the coaxiality of the two radial bearings L-8.

[0503] After the processing is completed, the bearing support L-52 is removed, and the radial bearing L-8 is installed into the mounting hole L-52 of the bearing support L-52 by heat-fitting, and then the fixing plate L-51 is installed at the first end of the bearing support L-52. The bearing support L-52 can be fixedly installed on the housing L-6 by the pin position determined during processing.

[0504] Since all key positioning parts are processed in one clamping process, the coaxiality of the two radial bearings L-8 and the verticality of the thrust bearing can be guaranteed, thereby improving the working stability of the rotor system.

[0505] like Fig.48 As shown, the fixing plate L-51 is also used to limit the axial displacement of the radial bearing L-8 toward the diffuser L-3 side. Therefore, the fixing plate L-51 can not only install the second thrust bearing L-10', but also axially limit the radial bearing L-8, which can make the structure of the bearing support assembly more compact and facilitate the parallelism of the mounting surface of the second thrust bearing L-10' and the axial limiting surface of the radial bearing L-8 through the processing parallelism on both sides of the fixing plate L-51, thereby improving the installation accuracy of the thrust bearing and the radial bearing L-8.

[0506] Furthermore, a positioning ring L-51 is provided at one end of the fixing plate L-51 facing the bearing support L-52, and an annular second groove L-52 is provided on the bearing support L-52. The positioning ring L-51 is embedded in the second groove L-52 to radially position the fixing plate L-51, and there is a gap between the fixing plate L-51 and the main shaft L-1. Moreover, the inner wall of the positioning ring L-51 matches the outer wall of a partial length section of the radial bearing L-8, and is used to support a partial length section of the radial bearing L-8, and at the same time, it plays an axial thrust role for the radial bearing L-8.

[0507] In a specific structure, such as Fig.47 As shown, the first thrust bearing L-10 is fixed to the diffuser L-3 by the fastener L-32, and the second thrust bearing L-10' is fixed to the fixing plate L-51 by the fastener L-32. The fixing plate L-51 and the diffuser L-3 are abutted against each other. The outer periphery of the diffuser L-3 is provided with a positioning stop L-33 so as to position and install it with the shell L-6.

[0508] In some embodiments, Fig.49 As shown, the fixing plate L-51 and the bearing support L-52 form an integrated structure. The support assembly L-5 adopts an integrated structure to simplify the structure, reduce the difficulty of assembly, and easily ensure the verticality of the radial bearing L-8 and the thrust bearing through the processing accuracy of the support assembly L-5.

[0509] In some embodiments, not shown in the figure, the centrifugal compressor also includes a housing L-6 and a radial bearing L-8, wherein the support assembly L-5 includes a bearing support L-52, the first end of the bearing support L-52 abuts against the diffuser L-3, and the second end is connected to the housing L-6, and the second thrust bearing L-10' is arranged on the side of the bearing support L-52 facing the diffuser L-3, and the bearing support L-52 is also used to support the main shaft L-1 through the radial bearing L-8. When machining the mounting hole L-52, a thrust stop is reserved for the bearing support L-52 to axially limit the radial bearing L-8.

[0510] and Fig.49 Compared with the illustrated embodiment, the fixing plate L-51 is omitted, which can further reduce the axial dimension of the bearing support assembly, simplify the structure, reduce the difficulty of assembly, and easily ensure the verticality of the radial bearing L-8 and the thrust bearing through the processing accuracy of the support assembly L-5.

[0511] like Fig.48 and Fig.49As shown, the centrifugal compressor also includes a housing L-6 and a radial bearing L-8, and the support assembly L-5 includes a bearing support L-52. The first end of the bearing support L-52 abuts against the diffuser L-3, and the second end is connected to the housing L-6, and is used to support the main shaft L-1 through the radial bearing L-8. Since the outer diameter of the thrust bearing is smaller than the inner diameter of the housing L-6, the outer profile of the cross section of the bearing support L-52 gradually increases from the first end to the second end. In order to reduce weight, as shown in FIG. Fig.50 As shown, a weight reducing groove L-52L-4 can also be set on the side of the bearing support L-52 away from the thrust bearing. For example, the weight reducing groove L-52L-4 is set in a ring shape, the inner wall is parallel to the axis, and the outer wall is consistent with the outer contour shape of the bearing support L-52.

[0512] This V-shaped bearing support L-52 adopts a structure with a gradually changing cross-sectional area, which can improve the overall structural strength of the bearing support L-52, evenly distribute the force at various locations, optimize the load-bearing capacity, and the outer wall is an inclined surface, which is easy to realize through casting, and has a draft angle when casting through a mold.

[0513] Furthermore, if Fig.50 As shown, the bearing support L-52 is provided with a vent hole L-52L-6, which is used to make the working environment of the radial bearing L-8 consistent with the first thrust bearing L-10 and the second thrust bearing L-10', for example, to make the working back pressure of the radial bearing L-8 consistent with the first thrust bearing L-10 and the second thrust bearing L-10'. Refrigerant for cooling the motor enters and exits the motor cavity. When the compressor operates normally, the overall motor cavity pressure and temperature are stable, and the thrust bearing and the radial bearing work in the same environment as the motor cavity, that is, to ensure gas circulation, and the back pressure is relatively stable. If the back pressure fluctuates too much, it will cause the bearing gas film to fluctuate, affecting the bearing performance.

[0514] like Fig.48 As shown, an operating hole L-52 is provided in the radial direction on the bearing support L-52, so that a vibration sensor or a temperature sensor can be installed on the outer wall of the radial bearing L-8 through the operating hole L-52 to monitor the working state of the radial bearing L-8. The hole section of the operating hole L-52 along the radial outer side can be used as a bypass hole to ensure that the thrust bearing and the radial bearing L-8 and the motor cavity have the same pressure and temperature, and the hole section of the operating hole L-52 along the radial inner side plays a role in dissipating heat for the radial bearing L-8.

[0515] In some embodiments, Fig.48As shown, the first thrust bearing L-10 is directly fixed to the bottom of the first groove L-31 of the diffuser L-3. For example, the first thrust bearing L-10 adopts a hydrodynamic thrust bearing, which is a thin sheet structure, and the hydrodynamic thrust bearing can be directly fixed to the bottom of the first groove L-31. This structure integrates the diffuser L-3 and the thrust bearing fixing plate into one part, and the bottom of the first groove L-31 can be used as the fixing plate of the first thrust bearing L-10. There is no need to set up an additional thrust bearing fixing plate, which can further reduce the axial size of the bearing support assembly and make the structure more compact.

[0516] In some embodiments, Fig.46 As shown, the centrifugal compressor also includes an impeller L-2 and a locking component L-9. A cavity L-11 is provided in the main shaft L-1 and a shaft core L-12 is provided at the center. The end of the shaft core L-12 extends out of the end of the main shaft L-1. The impeller L-2 is sleeved on the outer end of the shaft core L-12, and the impeller L-2 is locked on the shaft core L-12 by the locking component L-9, and the impeller L-2 is located on the outside of the diffuser L-3.

[0517] This embodiment allows the impeller L-2 to be detachably arranged relative to the main shaft L-1, which can reduce the difficulty of disassembling and assembling the impeller, simplify the assembly process and required equipment of the impeller, and improve the assembly efficiency and the operability of disassembly and maintenance. Moreover, this installation method can not only prevent the main shaft or impeller from deforming, but also ensure the installation strength of the impeller, avoid stress concentration, and thus improve the compression capacity of the compressor. In addition, by setting a cavity on the main shaft, the weight of the main shaft can be reduced to increase the critical speed of the rotor, further improving the ultimate working capacity of the compressor.

[0518] Still refer to Fig.46 The shaft core L-12 is directly formed when processing the cavity L-11, so that the shaft core L-12 and the rest of the main shaft L-1 are processed into one piece, and the shaft core L-12 does not need to be installed in the cavity of the main shaft L-1, which can further reduce the difficulty of assembly, increase the connection strength between the shaft core L-12 and the main shaft L-1, and ensure the position accuracy of the shaft core L-12, effectively solve the problem of the front end of the rotor beating, reduce the length of the cantilever end, and thus improve the working stability and reliability of the compressor. For example, the cavity L-11 can be an annular groove, or a plurality of holes symmetrical with respect to the center of the axis.

[0519] like Fig.48As shown, the thrust plate L-4 also includes a connecting portion L-42, which is connected to the thrust portion L-41 and sleeved on the main shaft L-1. A through hole L-34 is provided at the bottom of the first groove L-31, and the connecting portion L-42 is embedded in the through hole L-34. The connecting portion L-42 can be interference fit with the main shaft L-1 so that the thrust plate L-4 can rotate with the main shaft L-1. The diffuser L-3 and the fixed plate L-51 are fixedly arranged, and there is a gap between them and the main shaft L-1. For example, the thrust plate L-4 can be a cylindrical stepped structure.

[0520] like Fig.51 As shown, the centrifugal compressor also includes an impeller L-2 disposed at the end of the main shaft L-1, and the impeller L-2 is located outside the diffuser L-3. The side wall of the through hole L-34 is provided with a first axial comb-tooth sealing structure L-35, which forms a shaft seal with the thrust plate L-4, and can reduce the refrigerant from entering the motor cavity through the gap between the diffuser L-3 and the thrust plate L-4 along with the impeller exhaust. And / or the end of the impeller L-2 facing the diffuser L-3 is provided with a radial comb-tooth sealing structure L-21, which can reduce the refrigerant from flowing toward the periphery along the gap between the impeller L-2 and the diffuser L-3. And / or the impeller L-2 has an embedded portion L-22 embedded in the diffuser L-3, for example, the embedded portion L-22 can be a slender strip structure extending in the axial direction, and the embedded portion L-22 is provided with a second axial comb-tooth sealing structure L-23 on the radial inner side along the length direction, so as to reduce the refrigerant from flowing toward the periphery along the gap between the impeller L-2 and the diffuser L-3.

[0521] Specifically, the inclined surface of the comb teeth is inclined from the high-pressure side to the low-pressure side, and the top end of the comb teeth may be trapezoidal.

[0522] This embodiment can reduce the refrigerant leakage between the impeller L-2 and the diffuser L-3, and between the diffuser L-3 and the thrust plate L-4. It can not only ensure the clearance required for the operation of the main shaft L-1 and the impeller L-2, but also prevent the refrigerant leakage caused by excessive clearance, effectively solve the compressor sealing problem, and help improve the energy efficiency of the compressor.

[0523] Moreover, this structure integrates the diffuser L-3, thrust bearing fixing plate and shaft seal into one part, which can simplify the installation structure, make the structure more compact, and improve assembly efficiency. Fig.47As shown, the outer periphery of the diffuser L-3 is provided with a positioning stop L-33 so as to be positioned and installed with the housing L-6, and then precisely positioned with the pins. As a result, the coaxiality of the shaft seal part on the diffuser and the verticality of the fixed surface of the thrust bearing are both guaranteed on one part, which not only reduces the difficulty of processing, but also greatly reduces the cumulative assembly error. The shaft seal requiring high coaxiality and the thrust bearing requiring high verticality share the positioning stop L-33 and the pin for positioning, unifying the assembly benchmark, reducing the difficulty of assembly, and improving the assembly accuracy, which can not only improve the verticality of the fixed surface of the thrust bearing to ensure the working performance of the thrust bearing, but also improve the coaxiality of the first axial comb tooth seal structure L-35 to prevent the comb teeth from being worn and affecting the sealing performance.

[0524] In terms of material selection, the material of the diffuser L-3 is lower in hardness than the thrust plate L-4. Generally, the diffuser L-3 can be made of aluminum, and the thrust plate can be made of L-45 steel or L-40Cr, etc. In this way, if the first axial comb seal structure L-35 on the diffuser L-3 wears against the main shaft L-1, the comb will wear first to prevent the main shaft L-1 from wearing.

[0525] Still refer to Fig.51 The first axial comb-tooth sealing structure L-35, the radial comb-tooth sealing structure L-21 and the second axial comb-tooth sealing structure L-23 are arranged at the same time, and the radial comb-tooth sealing structure L-21 is located between the first axial comb-tooth sealing structure L-35 and the second axial comb-tooth sealing structure L-23 in the radial direction. This arrangement can make the airflow form a circuitous flow path, optimize the airflow deceleration and pressure reduction effect, and improve the sealing performance.

[0526] Specifically, a boss is provided at one end of the impeller L-2 facing the diffuser L-3, and the boss extends into the groove of the diffuser L-3. A radial comb tooth sealing structure L-21 is provided at the end of the boss so as to further extend the gas flow path while achieving radial sealing, optimize the airflow deceleration and pressure reduction effect, and improve the sealing performance.

[0527] In addition, the present invention also provides an air conditioning device, including the centrifugal compressor of the above embodiment. The centrifugal compressor of the present invention can withstand axial forces in two directions, ensuring the stability of the compressor during full-operation and reverse operation; and can accurately ensure the assembly clearance of the thrust bearing, ensuring the performance of the thrust bearing, thereby improving the operating stability of the compressor. Both of these factors can improve the stability and reliability of the air conditioning device.

[0528] Diffuser, thrust plate and related matching structure modification example 2

[0529] refer to Fig.30 In some embodiments, the present disclosure provides a rotor assembly, including a housing H-1. A receiving cavity is formed in the housing H-1.

[0530] In some embodiments, the rotor assembly includes a shaft H-8, which is rotatably disposed in the receiving cavity of the housing H-1. The shaft H-8 is equivalent to the rotor of the compressor.

[0531] Furthermore, the rotating shaft H-8 is arranged along the central axis direction of the accommodating cavity in the shell H-1.

[0532] In some embodiments, the rotor assembly assembly uses a motor (but not limited thereto), and the housing of the motor and the housing H-1 of the rotor assembly assembly are the same housing.

[0533] In some embodiments, the motor includes a stator H-9, which is disposed between the inner wall of the housing H-1 and the rotating shaft H-8, and the stator H-9 is fixed to the inner wall of the housing H-1.

[0534] In some embodiments, the rotor assembly includes a thrust plate H-6, which is disposed in the housing H-1 and fixed to the end of the rotating shaft H-8; the thrust plate H-6 rotates with the rotating shaft H-8.

[0535] In some embodiments, the rotor assembly includes a first fixing member and a second fixing member, and the first fixing member and the second fixing member are respectively arranged on both sides of the thrust plate H-6. The first fixing member and the second fixing member do not rotate with the rotating shaft H-8 and the thrust plate H-6.

[0536] In some embodiments, the rotor assembly includes a first thrust bearing H-4, which is disposed between the thrust plate H-6 and the first fixing member, and the first thrust bearing H-4 is fixed to the first fixing member.

[0537] In some embodiments, the rotor assembly includes a second thrust bearing H-4, which is disposed between the thrust plate H-6 and the second fixing member, and the second thrust bearing H-4 is fixed to the second fixing member.

[0538] In some embodiments, thrust bearings are arranged on both sides of the thrust disk H-6. The thrust disk H-6 bears bidirectional axial force, which can improve the performance of the thrust bearing. The structure is simple to assemble and compact, and can minimize the rotor length, reduce the bearing load, increase the rotor stiffness, increase the bending mode critical speed, and improve the stability of the bearing rotor system.

[0539] In some embodiments, the first thrust bearing H-4 and the second thrust bearing H-4 include gas bearings. Further, the first thrust bearing H-4 and the second thrust bearing H-4 are hydrodynamic gas bearings.

[0540] In some embodiments, the first thrust bearing H-4 and the second thrust bearing H-4 are thin-sheet structures.

[0541] In some embodiments, the first fixing member includes a diffuser H-7, and the diffuser H-7 is connected to the end of the housing H-1. The first thrust bearing H-4 is fixed to the diffuser H-7. The diffuser H-7 also serves as a thrust bearing fixing member. The diffuser H-7 is provided with an axial hole, and the rotating shaft H-8 passes through the axial hole provided on the diffuser H-7.

[0542] Furthermore, the first thrust bearing H-4 is fixed to the diffuser H-7 by screw locking.

[0543] In some embodiments, the cross section of the thrust plate H-6 is L-shaped, and includes a first portion and a second portion. The first portion is disposed in the gap between the inner wall of the shaft hole of the diffuser H-7 and the rotating shaft H-8. The second portion is disposed between the first thrust bearing H-4 and the second thrust bearing H-4.

[0544] In some embodiments, the axial hole of the diffuser H-7 includes a first axial hole and a second axial hole, the aperture of the first axial hole is smaller than the aperture of the second axial hole, the end of the rotating shaft H-8 and the first portion of the thrust plate H-6 are both located in the first axial hole, the first thrust bearing H-4 is located in the second axial hole and fixedly connected to the inner wall surface of the second axial hole, the second portion of the thrust plate H-6 is located in the second axial hole, and the second thrust bearing H-4 is located in the second axial hole.

[0545] The clearance of the thrust bearing is related to the thickness of the thrust plate H-6, the depth of the second shaft hole of the diffuser H-7 and the thrust bearing. The accuracy of these three factors can be improved to achieve the purpose of controlling the clearance.

[0546] In some embodiments, the depth of the second axial hole of the diffuser H-7 is inferred from the known thrust bearing clearance range, thrust plate thickness tolerance range, and thrust bearing thickness tolerance range, that is, the boss length tolerance range of the second axial hole is formed. The thrust bearing clearance is ensured by improving the machining accuracy of the boss length of the diffuser H-7 to prevent inaccurate clearance control from causing thrust bearing performance degradation or failure. At the same time, the assembly difficulty is reduced and the assembly efficiency and assembly accuracy are improved.

[0547] By improving the machining accuracy of the diffuser H-7, the thrust bearing clearance is accurately guaranteed to prevent bearing performance degradation or bearing failure caused by inappropriate thrust bearing clearance. At the same time, the structure is compact and the rotor length is minimized.

[0548] Furthermore, a shaft sealing structure is provided on the inner wall of the shaft hole of the diffuser H-7, and the shaft sealing structure is used to form a dynamic seal with the thrust plate H-6, and has a shaft sealing function, which can prevent external gas from entering the housing H-1. In the case where the diffuser H-7 is a first-stage diffuser, the shaft sealing structure is used to prevent the exhaust gas of the first-stage impeller from entering the housing H-1, that is, the motor cavity.

[0549] Optionally, the shaft sealing structure includes a comb teeth sealing structure.

[0550] In some embodiments, the diffuser H-7 has a shaft sealing function and a function of connecting the first thrust bearing H-4, that is, the shaft sealing structure and the fixing plate of the first thrust bearing H-4 are integrated on the diffuser H-7, and the structure is compact.

[0551] In some embodiments, the second fixing member includes a bearing support H-2, which is disposed in the housing H-1. The first end of the bearing support H-2 is fixedly connected to the second thrust bearing H-4, and the second end of the bearing support H-2 is connected to the inner wall of the housing H-1.

[0552] The first end and the second end of the bearing support H-2 are two opposite ends along the axial direction of the rotating shaft H-8.

[0553] In the above embodiment, the bearing support H-2 also serves as a fixing plate for the second thrust bearing H-4.

[0554] In other embodiments, the second fixing member includes a fixing plate H-5 and a bearing support H-2 disposed in the housing H-1.

[0555] The first end of the fixing plate H-5 is fixedly connected to the second thrust bearing H-4; the second end of the fixing plate H-5 is fixedly connected to the bearing support H-2.

[0556] The fixing plate H-5 is arranged between the second thrust bearing H-4 and the bearing support H-2.

[0557] The first end of the bearing support H-2 is fixedly connected to the second end of the fixing plate H-5; the second end of the bearing support H-2 is connected to the inner wall of the housing H-1.

[0558] The first end and the second end of the bearing support H-2 are two opposite ends.

[0559] In the above embodiment, the bearing support H-2 and the fixing plate H-5 are arranged separately.

[0560] In some embodiments, the fixing plate H-5 is provided with a mating portion, which extends outward and is used to cooperate with the bearing hole H-21 provided on the first end of the bearing support H-2.

[0561] Furthermore, the bearing hole H-21 arranged in the bearing support H-2 includes a first hole and a second hole, the first hole is close to the first end of the bearing support H-2 relative to the second hole, the hole diameter of the first hole is larger than the hole diameter of the second hole, and the radial bearing H-3 is arranged in the bearing hole H-21, and the gap between the radial bearing H-3 and the first hole is used to accommodate the mating part arranged on the fixing plate H-5.

[0562] A first thrust bearing H-4 is arranged on one side of the thrust plate H-6, and a second thrust bearing H-4 is arranged on the other side of the thrust plate H-6. The first thrust bearing H-4 is fixed on the diffuser H-7. The second thrust bearing H-4 is fixed on the fixing plate H-5.

[0563] Furthermore, the first thrust bearing H-4 is fixed to the diffuser H-7 by screws, the second thrust bearing H-4 is fixed to the fixing plate H-5 by screws, and the fixing plate H-5 is fixed to the bearing support H-2 by screws.

[0564] Furthermore, the inner wall of the housing H-1 extends toward the center axis of the housing H-1 to form a mounting portion, and the mounting portion is used to be fixedly connected to the second end of the bearing support H-2.

[0565] In some embodiments, Fig.33 As shown, the radial dimension of the second end of the bearing support H-2 is greater than the radial dimension of the first end of the bearing support H-2.

[0566] Along the direction from the first end to the second end of the bearing support H-2, the radial dimension of at least a portion between the first end and the second end of the bearing support H-2 gradually increases.

[0567] The inventors found that the radial force borne by the bearing support H-2 is basically equal to the gravity of the rotor, and the radial load is relatively small, so the radial strength requirement of the bearing support H-2 is not high. However, when the bearing support H-2 bears radial load and axial load at the same time, the bearing support H-2 also needs to have a certain structural strength to withstand the radial load and axial load. Therefore, the radial dimension of at least part of the bearing support H-2 provided by the present invention gradually increases, which can meet the radial strength requirement, and the gradual increase in the radial dimension can improve the structural strength of the bearing support H-2.

[0568] In the related art, the radial dimensions of the entire bearing support H-2 are set to be consistent by increasing the wall thickness and additionally providing reinforcing ribs, thereby increasing the structural strength of the bearing support H-2, which results in increased equipment weight and increased costs.

[0569] The inventors also found that the axial load on the bearing support H-2 is greater than the radial load, and the axial load is transmitted to the bearing support H-2 through the thrust bearing and the thrust bearing fixing plate. Therefore, the first end of the bearing support H-2 provided by the present invention cooperates with the thrust bearing fixing plate and the thrust bearing, and the radial dimension of the first end of the bearing support H-2 is smaller than the radial dimension of the second end of the bearing support H-2 connected to the housing H-1, and along the direction from the first end to the second end of the bearing support H-2, the radial dimension of at least part of the bearing support H-2 gradually increases, which can well transmit the axial force to the housing H-1 of the rotor assembly component motor, thereby improving the strength and service life of the bearing support H-2.

[0570] In some embodiments, along the direction from the first end to the second end of the bearing support H-2, the radial dimension of the middle part of the bearing support H-2 between the first end and the second end gradually increases. The bearing support structure can not only meet the strength requirements, but also reliably deliver power.

[0571] In some embodiments, the bearing support H-2 is V-shaped, has high structural strength, and is easy to cast, which can ensure high-precision assembly of the hydrodynamic bearing and improve the stability of the bearing rotor system.

[0572] In some embodiments, the radial dimension of the first end of the bearing support H-2 is smaller than the radial dimension of the second end of the bearing support H-2.

[0573] In some embodiments, Fig.33 As shown, the bearing support H-2 includes a bearing hole H-21, and the bearing hole H-21 is used to install the bearing.

[0574] In some embodiments, the bearing support H-2 includes an annular groove H-22, which is arranged around the bearing hole H-21.

[0575] Optionally, the cross-section of the annular groove H-22 is V-shaped, which is compatible with the V-shaped structure of the bearing support H-2.

[0576] The bearing support H-2 is hollowed out around the bearing hole H-21 to form a V-shaped annular groove H-22 to ensure that the wall thickness of the casting is relatively uniform, which reduces the deadweight of the support and facilitates casting.

[0577] In some embodiments, the inner wall of the housing H-1 is provided with a mounting portion extending toward the center of the housing H-1 for connecting with the second end of the bearing support H-2.

[0578] In some embodiments, the second end of the bearing support H-2 includes a limiting portion H-23, and the limiting portion H-23 abuts against the inner side of the mounting portion.

[0579] The second end of the bearing support H-2 also includes a connecting portion H-24, which extends outward relative to the limiting portion H-23 and is used to connect with the mounting portion.

[0580] A stop is formed between the limiting portion H-23 and the connecting portion H-24 for cooperating with the mounting portion for positioning.

[0581] Furthermore, the connection portion H-24 is connected to the mounting portion provided on the inner wall of the housing H-1 through a pin, and the bearing support H-2 is positioned together by the pin and the provided mounting stop, thereby ensuring high-precision assembly of the bearing.

[0582] In some embodiments, the connecting portion H-24 is annular and arranged along the circumference of the limiting portion H-23.

[0583] In some embodiments, the bearing support H-2 includes a bearing hole H-21, and the bearing hole H-21 is used to install the bearing.

[0584] In some embodiments, the bearing support H-2 includes a vent hole H-25, which is arranged along the radial direction of the bearing support H-2, the first end of the vent hole H-25 is connected to the bearing hole H-21, and the second end of the vent hole H-25 is connected to the outside of the bearing support H-2.

[0585] In some embodiments, the rotor assembly includes a radial bearing H-3, which is disposed at the end of the rotating shaft H-8 and is located in the bearing hole H-21 of the bearing support H-2.

[0586] In other embodiments, the rotor assembly includes a radial bearing H-3, which is disposed at the end of the rotating shaft H-8 and is located in the bearing hole H-21 of the bearing support H-2. The radial bearing H-3 and the second thrust bearing H-4 are respectively located on both sides of the fixing plate H-5.

[0587] In some embodiments, the radial bearing H-3 is arranged in the bearing hole H-21 of the bearing support H-2 by shrink fitting.

[0588] In some embodiments, the radial bearing H-3 comprises a gas bearing. Further, the radial bearing H-3 comprises a hydrodynamic gas bearing.

[0589] In some embodiments, the thrust plate H-6 is disposed at the first end of the rotating shaft H-8.

[0590] In some embodiments, a radial bearing H-3 and a bearing support H-2 cooperating with the radial bearing H-3 are provided at the second end of the rotating shaft H-8.

[0591] In some embodiments, the first end of the rotating shaft H-8 is provided with a thrust plate H-6, a first thrust bearing H-4, a second thrust bearing H-4, a radial bearing H-3, a bearing support H-2 and other structures, and the second end of the rotating shaft H-8 is provided with a radial bearing H-3 and a bearing support H-2. The first end and the second end of the rotating shaft H-8 are in an asymmetric assembly form. This assembly form can minimize the length and weight of the rotating shaft H-8 while ensuring bidirectional load-bearing, reduce the radial bearing load, increase the rotor stiffness, and increase the critical speed of the rotor bending mode; and it is convenient for gap adjustment, and can ensure the coaxiality of the two radial bearings H-3 and the verticality of the thrust bearing with high precision, thereby improving assembly efficiency and assembly accuracy.

[0592] If a symmetrical assembly method is adopted: on the one hand, the difficulty of assembly is increased, and the length and weight of the entire rotor are also increased; on the other hand, since the thrust bearing clearance is very small, if a symmetrical structure is used, it will be very difficult to adjust the clearance.

[0593] In some embodiments, radial bearings H-3 are arranged at both ends of the rotating shaft H-8 to bear radial force, and thrust bearings are arranged on both sides of the thrust plate H-6 to bear bidirectional axial force. This structure is simple to assemble and compact, and can minimize the rotor length, reduce the bearing load, increase the rotor stiffness, increase the critical speed of the bending mode, and improve the stability of the bearing rotor system.

[0594] In some embodiments, bearing supports H-2 are provided at both ends of the rotating shaft H-8. The two bearing supports H-2 are bored with bearing holes H-21 by a matching boring method, which can well ensure the coaxiality of the two bearing holes H-21 and the verticality of the matching surface of the fixing part.

[0595] Furthermore, the radial bearing H-3 is interference fit with the bearing hole H-21 of the bearing support H-2. This method can better reduce the assembly error and ensure the coaxiality of the two bearing holes H-21. The coaxiality of the radial bearing hole H-21 is jointly ensured by machining and shrink-fit assembly processes.

[0596] In addition, the verticality of the thrust surfaces on both sides of the thrust plate H-6 can also be well guaranteed by machining, so that the accuracy of coaxiality and verticality can be guaranteed, preventing the bearing performance from being reduced due to low accuracy. In severe cases, the bearing fails and the rotor cannot float.

[0597] Some embodiments provide a compressor comprising the rotor assembly in the above embodiments.

[0598] In some embodiments, the motor housing of the compressor and the housing H-1 of the rotor assembly are the same housing.

[0599] In some embodiments, the compressor comprises a centrifugal compressor.

[0600] The assembly form of the H-8 end of the rotating shaft in the above compressor: 1) can reduce the bearing load, improve the rotor stiffness, increase the bending mode critical speed, and improve the stability of the bearing-rotor system; 2) high precision ensures the coaxiality of the two radial bearings and the verticality of the thrust bearing, and improves the assembly efficiency and assembly accuracy; 3) high precision ensures the clearance of the bidirectional thrust bearing, and prevents the thrust bearing performance from being reduced or even failing due to inaccurate clearance control.

[0601] The assembly form of the H-8 end of the inner rotating shaft of the above-mentioned compressor has a compact structure, which can reduce the rotor length and bearing load, and improve the rotor stiffness and bending mode critical speed.

[0602] The present invention can improve the coaxiality of the radial bearing and the verticality of the thrust surface through machining and assembly processes, thereby improving assembly efficiency and assembly accuracy.

[0603] The present invention controls the machining accuracy of the diffuser H-7 to accurately ensure the thrust bearing clearance, thereby preventing inaccurate clearance control from causing thrust bearing performance degradation or failure.

[0604] The above-mentioned embodiments of the compressor and compressor internal components or assembly structures are applicable to various refrigerant circulation systems and refrigeration equipment. Therefore, the present disclosure also provides a refrigerant circulation system including any embodiment of the above-mentioned compressor and compressor internal components or assembly structures, and a refrigeration equipment including any embodiment of the above-mentioned compressor and compressor internal components or assembly structures.

[0605] So far, various embodiments of the present disclosure have been described in detail. In order to avoid obscuring the concept of the present disclosure, some details known in the art are not described. Based on the above description, those skilled in the art can fully understand how to implement the technical solution disclosed here.

[0606] Although some specific embodiments of the present disclosure have been described in detail by way of examples, it should be understood by those skilled in the art that the above examples are for illustration only and are not intended to limit the scope of the present disclosure. It should be understood by those skilled in the art that the above embodiments may be modified or some technical features may be replaced by equivalents without departing from the scope and spirit of the present disclosure. The scope of the present disclosure is defined by the appended claims.

Claims

1. A compressor, characterized in that: include: A housing and a motor drive system; the motor drive system comprises a compressor rotor and a motor stator, the housing has a motor accommodating chamber and a compression chamber, the motor stator is fixedly arranged in the motor accommodating chamber and has a rotor mounting hole, and the compressor rotor is rotatably arranged in the housing; The motor stator is provided with a reflux flow hole extending along the axial direction of the compressor rotor, and part of the fluid in the motor accommodating cavity flows from one end of the motor stator to the other end of the motor stator through the reflux flow hole; The compressor rotor comprises: a motor rotor, located in the motor accommodating cavity and penetrating the rotor mounting hole, having a hollow portion and a vent hole, wherein the vent hole is connected to both the hollow portion and the motor accommodating cavity; and The compression unit rotating part is located in the compression chamber, fixedly connected to the end of the motor rotor and forms an air intake passage communicating with the hollow part with the motor rotor, and the fluid in the compression chamber enters the hollow part through the air intake passage and enters the motor accommodating chamber through the air vent; Wherein, an axial notch for cooperating with the rotating part of the compression unit is provided at the end of the motor rotor, a first leakage groove recessed radially outward is provided on the side wall of the axial notch, and the intake passage includes the first leakage groove; and / or The end surface of the compression unit rotating part cooperates with the end surface of the motor rotor, the end surface of the compression unit rotating part is provided with a second leakage groove, and the intake passage includes the second leakage groove; and / or The end surface of the rotating part of the compression unit cooperates with the end surface of the motor rotor, the end surface of the motor rotor is provided with a third leakage groove, and the intake passage includes the third leakage groove.

2. The compressor according to claim 1, characterized in that The reflux hole comprises: a return air hole, located above the compressor rotor, for circulating gas; and / or, The liquid return hole is located below the compressor rotor and is used for circulating liquid.

3. The compressor according to claim 1, characterized in that Also included is a compression system comprising a volute having at least two volute profiles in different angular ranges.

4. The compressor according to claim 3, characterized in that The at least two volute profiles include a first volute profile and a second volute profile distributed along the airflow direction inside the volute, and a parting interface between the first volute profile and the second volute profile is 80º~100º relative to a direction perpendicularly pointing from the center of the volute to the airflow outlet of the volute.

5. The compressor according to claim 4, characterized in that The first volute profile is D-shaped, trapezoidal or elliptical, and the second volute profile is a circle with an angle greater than 180°.

6. The compressor according to claim 1, characterized in that The compressor rotor comprises: a motor rotor, which is located in the motor accommodating cavity and penetrates the rotor mounting hole, and has a hollow portion and a vent hole, wherein the vent hole is connected to both the hollow portion and the motor accommodating cavity; the motor rotor comprises: permanent magnet; A first end shaft segment, fixedly disposed at a first end of the permanent magnet; and The second end shaft segment is fixedly disposed on the second end of the permanent magnet.

7. The compressor according to claim 1, characterized in that The compressor is a centrifugal compressor, and the rotating part of the compression unit is an impeller.

8. The compressor according to claim 1, characterized in that A gas bearing is also included, and the compressor rotor is rotatably supported in the housing through the gas bearing.

9. The compressor according to claim 6, characterized in that The first end shaft segment includes a first axial hole and a plurality of first through holes connecting the first axial hole and the motor accommodating cavity, the hollow portion includes the first axial hole, and the vent hole includes the first through hole; and / or, The second end shaft segment includes a second axial hole and a plurality of second through holes connecting the second axial hole and the motor accommodating cavity, the hollow portion includes the second axial hole, and the vent hole includes the second through holes.

10. The compressor according to claim 1, characterized in that The housing is provided with: a cooling fluid inlet; a spiral groove, disposed on the inner wall of the housing, and forming a spiral cooling channel with the outer peripheral surface of the motor stator, wherein a first end of the spiral cooling channel is communicated with the cooling fluid inlet, and a second end of the spiral cooling channel is communicated with the motor accommodating cavity at one end of the motor stator; and The cooling fluid outlet is communicated with the motor accommodating cavity at the other end of the motor stator.

11. A refrigerant circulation system, characterized in that: A compressor comprising the compressor according to any one of claims 1 to 10.

12. A refrigeration device, characterized in that: A compressor comprising the compressor according to any one of claims 1 to 10.

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