Sensor detection device of compressor and compressor

Abstract

The invention discloses a sensor detection device of a compressor and the compressor. The sensor detection device comprises a mounting seat, a detection ring, a speed detection probe, an axial displacement detection probe and a radial displacement detection probe. The mounting seat and the detection ring are arranged at an interval along the axial direction of the detection ring; the mounting seat is provided with a first inner circumferential surface, a speed probe mounting hole is formed in the first inner circumferential surface, the speed detection probe is arranged in the speed probe mounting hole, a radial probe mounting hole is formed in the inner circumferential surface of the detection ring, and the radial displacement detection probe is arranged in the radial probe mounting hole; at least one of the sides, facing each other, of the mounting base and the detection ring is provided with an axial probe mounting hole. The radial displacement detection probe is arranged on the detection ring, and the speed detection probe is arranged on the mounting seat, so that the thickness of the detection ring can be reduced, the occupied size of the rotor can be reduced, the rotor can be manufactured to be shorter, and the dominant frequency of the rotor can be improved.

Description

Technical Field

[0001] The present invention relates to the technical field of air compression, and in particular to a sensor detection device for a compressor and a compressor. Background Art

[0002] This section merely provides background information related to the present disclosure and is not necessarily prior art.

[0003] Magnetic levitation centrifugal compressors are widely used in the industrial sector, primarily in high-speed rotating machinery such as magnetic levitation centrifugal refrigeration compressors, magnetic levitation air compressors, and magnetic levitation blowers. A common feature of magnetic levitation centrifugal compressors is that they are supported by bearings and utilize magnetic bearings to suspend the rotor. The displacement sensor is the component that identifies the suspension position and provides position feedback. Currently, two mounting components are installed within the compressor: the axial displacement detection probe, the radial displacement detection probe, and the speed detection probe are all integrated into the same mounting component and arranged along the rotor's axial direction. The other mounting component is equipped with an axial displacement detection probe, resulting in a relatively thick mounting component. This leaves insufficient space for internal components such as the stator and bearings that support the rotor, necessitating an increase in the axial dimension of the compressor casing. This increase in casing size increases the spacing between the two sets of bearings supporting the rotor, further increasing the rotor's axial dimension. Both mounting components are annular and can only be inserted from the shaft end, making assembly inconvenient. This increases the difficulty of rotor commissioning when the rotor is in magnetic levitation, impacting its operational stability. Summary of the Invention

[0004] The purpose of the present invention is to at least solve the problem that the thickness of the mounting member will increase the length of the rotor. This purpose is achieved by the following technical solutions:

[0005] A first aspect of the present invention provides a sensor detection device for a compressor, comprising:

[0006] A mounting seat and a detection ring, wherein the mounting seat and the detection ring are spaced apart along the axial direction of the detection ring, and the mounting seat has a first inner circumferential surface; and

[0007] A speed detection probe, an axial displacement detection probe and a radial displacement detection probe; the first inner circumference is provided with a speed probe mounting hole, a speed detection probe is provided in the speed probe mounting hole, the inner circumference of the detection ring is provided with a radial probe mounting hole, a radial displacement detection probe is provided in the radial probe mounting hole, at least one of the sides facing each other of the mounting seat and the detection ring is provided with an axial probe mounting hole, an axial displacement detection probe is provided in the axial probe mounting hole, the speed detection probe is used to detect the rotational speed of the compressor rotor, the axial displacement detection probe is used to detect the axial displacement of the rotor, and the radial displacement detection probe is used to detect the radial displacement of the rotor.

[0008] According to the sensor detection device of the compressor of the present invention, by arranging the axial displacement detection probe on at least one of the detection ring and the mounting seat, and arranging the radial displacement detection probe on the detection ring, and arranging the speed detection probe on the mounting seat, the thickness of the detection ring can be reduced, thereby reducing the size occupied by the rotor, thereby making the rotor shorter, which is beneficial to increasing the main frequency of the rotor.

[0009] In addition, the sensor detection device according to the present invention may also have the following additional technical features:

[0010] In some embodiments of the present invention, the mounting seat is a fan-shaped structure extending along the circumferential direction of the detection ring.

[0011] In some embodiments of the present invention, the central angle of the fan-shaped structure is less than or equal to 180°.

[0012] In some embodiments of the present invention, the fan-shaped structure includes a first fan-shaped segment and a second fan-shaped segment, the first fan-shaped segment is rotatably connected to the second fan-shaped segment around a first axis, the first axis is parallel to the axis of the detection ring, the first fan-shaped segment has a partial first inner circumferential surface, the second fan-shaped segment has a partial first inner circumferential surface, and the partial first inner circumferential surface of the first fan-shaped segment and the partial first inner circumferential surface of the second fan-shaped segment are respectively provided with velocity probe mounting holes.

[0013] In some embodiments of the present invention, along the circumferential direction of the detection ring, the distance between the velocity probe mounting hole of the first sector segment and the first axis is L1, and the distance between the velocity probe mounting hole of the second sector segment and the first axis is L2, L1=L2.

[0014] In some embodiments of the present invention, along the extension direction of the first axis, a first through hole is provided on one side of the first sector segment, and a second through hole is provided on one side of the second sector segment. The first through hole and the second through hole are configured to be connected to the compressor through fasteners.

[0015] In some embodiments of the present invention, the first through hole is an elongated slot hole extending in a circumferential direction of the first axis; and / or the second through hole is an elongated slot hole extending along the first axis.

[0016] In some embodiments of the present invention, there are multiple speed probe mounting holes, and the multiple speed detection probes are spaced apart along the circumferential direction of the detection ring. A speed detection probe is provided in each speed probe mounting hole.

[0017] In some embodiments of the present invention, there are two speed detection probes. Along the circumferential direction of the detection ring, the interval angle between the two speed detection probes is A, and the value range of A is 30°-90°.

[0018] In some embodiments of the present invention, an axial probe mounting hole is provided on the side of the mounting seat facing the detection ring, and the axial displacement detection probe and the speed detection probe arranged on the mounting seat are spaced apart along the circumferential direction of the detection ring.

[0019] In some embodiments of the present invention, there are at least three radial probe mounting holes, all of which are spaced apart along the circumferential direction of the detection ring, and a radial displacement detection probe is provided in each radial probe mounting hole.

[0020] In some embodiments of the present invention, the number of the radial probe mounting holes is four, and the four radial probe mounting holes are arranged at equal intervals along the circumferential direction of the detection ring.

[0021] In some embodiments of the present invention, an axial probe mounting hole is provided on the side of the detection ring facing the mounting seat, and the axial displacement detection probe and the radial displacement detection probe arranged on the detection ring are spaced apart along the circumferential direction of the detection ring.

[0022] A second aspect of the present invention provides a compressor, comprising a rotor and a sensor detection device for the compressor of the first aspect, wherein the rotor comprises a rotor shaft, wherein the outer peripheral surface of the rotor shaft is connected to a target disk, wherein a mounting seat is provided on one side of the target disk along the axial direction of the rotor shaft, and a detection ring is provided on the other side of the target disk, and the detection ring is sleeved on the target disk, and the diameter of the portion of the rotor shaft located within the detection ring is smaller than the inner diameter of the detection ring, the orthographic projection of the axial displacement detection probe along the axial direction of the rotor shaft is located on the target disk, and the detection end of the axial displacement detection probe is arranged toward the target disk, and the detection end of the radial displacement detection probe is arranged toward the rotor shaft, and the rotor shaft is configured to rotate relative to the mounting seat and the detection ring.

[0023] In some embodiments of the present invention, a characteristic structure for being recognized by a speed detection probe is formed on the outer circumferential surface of the rotor shaft, and the characteristic structure includes a groove or a protrusion. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Various other advantages and benefits will become apparent to those skilled in the art upon reading the detailed description of the preferred embodiment below. The accompanying drawings are for illustration purposes only and are not to be considered as limiting the present invention. The same reference numerals are used throughout the accompanying drawings to denote the same components. In the accompanying drawings:

[0025] Figure 1 The schematic diagram schematically shows the structural relationship between the sensor detection device and the rotor shaft;

[0026] Figure 2 for Figure 1 AA section view;

[0027] Figure 3 for Figure 1BB cross-sectional view;

[0028] Figure 4 Schematically showing a partial structural diagram of a rotor of a compressor according to some embodiments of the present invention;

[0029] Figure 5 Schematically shows an axonometric view of an embodiment of a mounting base;

[0030] Figure 6 Schematically shows a structural diagram of an embodiment of a mounting base;

[0031] Figure 7 、 Figures 9-12 sectional views of different embodiments of the compressor of the present invention passing through the axis of the rotor;

[0032] Figure 8 for Figure 7 A local enlarged view at location I;

[0033] Figure 13 A cross-sectional view of a support member of some embodiments of the compressor of the present invention passing through the axis of the rotor;

[0034] Figure 14 and Figure 15 for Figure 13 AA cross-sectional views of different embodiments;

[0035] Figure 16 This is an axonometric view of a support member of a compressor according to an embodiment of the present invention.

[0036] The reference numerals are as follows:

[0037] 95. Compressor;

[0038] 951, bearing assembly;

[0039] 9511, support member; 95111, first magnetic pole portion; 95112, protective bearing mounting portion; 951121, bearing mounting hole; 95113, cooling channel; 95114, cooling medium inlet; 95115, cooling medium outlet;

[0040] 95116, sealing portion; 951161, first protrusion; 951162, first sealing tooth; 95117, air duct;

[0041] 9512, magnetic pole plate; 95121, second magnetic pole portion; 95122, protective bearing; 951221, first shaft mounting hole;

[0042] 952, thrust plate; 9521, second shaft mounting hole;

[0043] 953, gas compression assembly; 9531, impeller; 95311, second protrusion; 95312, second sealing tooth; 9532, rotor; 95321, rotor shaft; 953211, first shaft segment; 953212, second shaft segment; 95322, characteristic structure; 9533, spacer; 9534, shaft sleeve;

[0044] 954, casing assembly; 9541, casing; 9542, volute; 95421, suction chamber; 95422, compressed air duct;

[0045] 955, axial bearing winding;

[0046] 956. Sensor detection device;

[0047] 9561, mounting seat; 95611, velocity probe mounting hole; 95612, axial probe mounting hole; 9562, detection ring; 95621, radial probe mounting hole; 9564, first sector; 95641, first through hole; 9565, second sector; 95651, second through hole;

[0048] 95631, speed detection probe; 95632, axial displacement detection probe; 95633, radial displacement detection probe;

[0049] 957, target plate;

[0050] 958, radial magnetic bearing; 9581, bearing seat;

[0051] 959, stator;

[0052] X first axis. DETAILED DESCRIPTION

[0053] Exemplary embodiments of the present disclosure will be described in more detail below with reference to the accompanying drawings. Although exemplary embodiments of the present disclosure are shown in the accompanying drawings, it should be understood that the present disclosure can be implemented in various forms and should not be limited by the embodiments described herein. Rather, these embodiments are provided to enable a more thorough understanding of the present disclosure and to fully convey the scope of the present disclosure to those skilled in the art.

[0054] It should be understood that the terms used herein are for the purpose of describing specific example embodiments only and are not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms "one", "an" and "said" as used herein may also be meant to include plural forms. The terms "comprise", "include", "contain" and "have" are inclusive and therefore specify the presence of stated features, steps, operations, elements and / or parts, but do not exclude the presence or addition of one or more other features, steps, operations, elements, parts, and / or combinations thereof. The method steps, processes, and operations described herein are not to be construed as necessarily requiring them to be performed in the specific order described or illustrated, unless the order of execution is clearly indicated. It should also be understood that additional or alternative steps may be used.

[0055] Although the terms first, second, third, etc. can be used in the text to describe multiple elements, components, regions, layers and / or sections, these elements, components, regions, layers and / or sections should not be limited by these terms. These terms can only be used to distinguish an element, component, region, layer or section from another region, layer or section. Unless the context clearly indicates otherwise, terms such as "first", "second" and other numerical terms do not imply order or sequence when used in the text. Therefore, the first element, component, region, layer or section discussed below can be referred to as the second element, component, region, layer or section without departing from the teaching of the example embodiments.

[0056] For ease of description, spatially relative terms may be used herein to describe the relationship of one element or feature relative to another element or feature as shown in the figures, such as "inside," "outside," "inside," "outside," "below," "beneath," "above," and the like. Such spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is flipped, an element described as "below" or "below" another element or feature would then be oriented as "above" or "above" another element or feature. Thus, the example term "below" can include both above and below orientations. The device may be otherwise oriented (rotated 90 degrees or in other orientations) and the spatially relative descriptors used herein are interpreted accordingly.

[0057] According to the embodiment of the present invention, please refer to Figure 1-Figure 3A sensor detection device 956 for a compressor is proposed, comprising a mounting seat 9561, a detection ring 9562, a speed detection probe 95631, an axial displacement detection probe 95632, and a radial displacement detection probe 95633. Mounting seat 9561 and detection ring 9562 are spaced apart along the axial direction of detection ring 9562, and mounting seat 9561 has a first inner circumferential surface. A speed probe mounting hole 95611 is provided on the first inner circumference, and a speed detection probe 95631 is provided in the speed probe mounting hole 95611. A radial probe mounting hole 95621 is provided on the inner circumference of the detection ring 9562, and a radial displacement detection probe 95633 is provided in the radial probe mounting hole 95621. At least one of the sides facing each other of the mounting seat 9561 and the detection ring 9562 is provided with an axial probe mounting hole 95612, and an axial displacement detection probe 95632 is provided in the axial probe mounting hole 95612. The speed detection probe 95631 is used to detect the rotational speed of the compressor rotor 9532, the axial displacement detection probe 95632 is used to detect the axial displacement of the rotor 9532, and the radial displacement detection probe 95633 is used to detect the radial displacement of the rotor 9532.

[0058] The mounting seat 9561 may be a ring-shaped structure, or a plate-shaped or fan-shaped structure.

[0059] The radial displacement detection probe 95633 can be fixed in the radial probe mounting hole 95621 by bonding, clamping or threaded connection.

[0060] The axial displacement detection probe 95632 can be fixed in the axial probe mounting hole 95612 by bonding, clamping or threaded connection.

[0061] The speed detection probe 95631 can be fixed in the speed probe mounting hole 95611 by bonding, clamping or threading.

[0062] At least one axial probe mounting hole 95612 may be provided on the side of the mounting seat 9561 facing the detection ring 9562, or the axial probe mounting hole 95612 may not be provided.

[0063] At least one axial probe mounting hole 95612 may be provided on the side of the detection ring 9562 facing the mounting seat 9561 , or the axial probe mounting hole 95612 may not be provided.

[0064] The mounting seat 9561 and the detection ring 9562 may further be provided with at least one axial probe mounting hole 95612 on the side facing each other.

[0065] According to the sensor detection device 956 of the compressor of the present invention, the axial probe mounting hole 95612 is set on at least one of the detection ring 9562 and the mounting seat 9561, and the radial displacement detection probe 95633 is set on the detection ring 9562, and the speed detection probe 95631 is set on the mounting seat 9561. This can reduce the space occupied by the speed detection probe 95631 on the detection ring 9562 along the axial direction of the detection ring 9562, thereby reducing the thickness of the detection ring 9562 and the size of the shaft section of the rotor 9532 corresponding to the detection ring 9562, which is beneficial to improving the main frequency of the rotor 9532.

[0066] In some embodiments of the present invention, please refer to Figure 1-Figure 3 The mounting seat 9561 is a fan-shaped structure extending along the circumferential direction of the detection ring 9562.

[0067] The central angle of the fan-shaped structure can be greater than 180° or less than or equal to 180°. When the central angle of the fan-shaped structure is greater than 180°, the size of the notch formed at both ends of the first inner circumferential surface along its own circumference is greater than or equal to the diameter of the corresponding shaft segment of the rotor shaft 95321, so as to facilitate the installation of the fan-shaped structure from one side of the rotor shaft 95321. During installation, the first inner circumferential surface can be kept concentric with the rotor shaft 95321.

[0068] Optionally, both the mounting seat 9561 and the detection ring 9562 can be fixed in the casing assembly of the compressor, specifically by screws or clamping. Taking the magnetic levitation compressor as an example, the mounting seat 9561 and the detection ring 9562 can be fixed on the bearing seat 9581 of the radial magnetic levitation bearing 958 in the compressor. Specifically, the mounting seat 9561 and the detection ring 9562 are respectively provided with connecting holes, and the connecting holes pass through the mounting seat 9561 and the detection ring 9562 along the axial direction of the detection ring 9562, respectively. The end of the screw passes through the respective connecting holes of the mounting seat 9561 and the detection ring 9562 and is threadedly connected to the bearing seat 9581, or the mounting seat 9561 and the detection ring 9562 are fixed to the connecting plate, and the connecting plate is fixed to the inner wall of the casing assembly or the bearing seat 9581.

[0069] The fan-shaped structure allows speed detection probe 95631 to be installed into speed probe mounting hole 95611 from one side of the first inner circumferential surface, facilitating installation. Furthermore, compared to the current method of using both mounting members in a circular ring structure, the fan-shaped mounting base 9561 allows installation from one radial side of rotor shaft 95321, improving assembly efficiency and allowing the first inner circumferential surface to be positioned close to rotor shaft 95321 while maintaining a certain distance for easier detection.

[0070] In some embodiments of the present invention, the central angle of the fan-shaped structure is less than or equal to 180°.

[0071] Thus, the mounting seat 9561 can be fixed to the compressor on one side of the radial direction of the rotor shaft 95321, which facilitates the assembly and disassembly of the mounting seat 9561. In addition, the inner peripheral surface of the fan-shaped structure is an open structure, which facilitates the installation of the speed detection probe 95631.

[0072] In some embodiments of the present invention, please refer to Figure 5 The fan-shaped structure includes a first fan-shaped segment 9564 and a second fan-shaped segment 9565. The first fan-shaped segment 9564 is rotatably connected to the second fan-shaped segment 9565 around a first axis X. The first axis X is parallel to the axis of the detection ring 9562. The first fan-shaped segment 9564 has a partial first inner circumferential surface, and the second fan-shaped segment 9565 has a partial first inner circumferential surface. The partial first inner circumferential surface of the first fan-shaped segment 9564 and the partial first inner circumferential surface of the second fan-shaped segment 9565 are respectively provided with a velocity probe mounting hole 95611.

[0073] Specifically, the first sector 9564 can be rotatably connected to the second sector 9565 via a hinge shaft. In other examples, the first sector 9564 can be rotatably connected to the second sector 9565 via bolts, and after adjustment, the tightening force of the bolts can be used to lock the two sectors together to maintain their relative position unchanged.

[0074] Thus, rotating the first segment 9564 relative to the second segment 9565 can change the positions of the two speed probe mounting holes 95611, and thus the positions of the two speed detection probes 95631, enabling detection of the rotational speed of rotors 9532 of different diameters. Furthermore, by rotating the first segment 9564, the fan-shaped structure can be installed from one side of the rotor shaft 95321. Rotating the first segment 9564 also maintains the two speed detection probes 95631 in the proper position, facilitating detection of the rotational speed of the rotor 9532.

[0075] In some embodiments of the present invention, please refer to Figure 6 Along the circumferential direction of the detection ring 9562, the distance between the velocity probe mounting hole 95611 of the first sector segment 9564 and the first axis X is L1, and the distance between the velocity probe mounting hole 95611 of the second sector segment 9565 and the first axis X is L2, L1=L2.

[0076] During installation, the first sector segment 9564 can be adjusted to a position with the first axis X as the center, and then the position of the second sector segment 9565 can be adjusted at a symmetrical angle for easy adjustment so that the different speed detection probes 95631 are all radially toward the rotor shaft 95321, reducing the installation deviation of the different speed detection probes 95631 to ensure the accuracy of the speed measurement of the rotor shaft 95321.

[0077] In some embodiments of the present invention, please refer to Figure 6 Along the extension direction of the first axis X, a first through hole 95641 is provided on one side of the first sector segment 9564, and a second through hole 95651 is provided on one side of the second sector segment 9565. The first through hole 95641 and the second through hole 95651 are configured to be connected to the compressor 95 through fasteners.

[0078] In some embodiments of the present invention, please refer to Figure 6 , the first through hole 95641 is a long slot hole extending along the circumferential direction of the first axis X; and / or, the second through hole 95651 is a long slot hole extending along the first axis X.

[0079] By setting the long slot hole, a fastener can be used to pass through the long slot hole to connect with the compressor. The fastener can be any combination of a screw stud and a nut or a combination of a screw and a nut.

[0080] In some embodiments of the present invention, when portions of the first inner circumferential surfaces of the first sector segment 9564 and the second sector segment 9565 are coaxial, along the circumferential direction of the first inner circumferential surface, the angle between the ends of the first sector segment 9564 and the second sector segment 9565 facing away from each other is less than or equal to 180 degrees, which can facilitate the installation of the mounting seat 9561.

[0081] In some embodiments of the present invention, along the axial direction of the detection ring 9562 , an axial probe mounting hole 95612 is provided on a side of either the first sector segment 9564 or the second sector segment 9565 facing the detection ring 9562 .

[0082] In some embodiments of the present invention, please refer to Figure 3 There are multiple speed probe mounting holes 95611, and multiple speed detection probes 95631 are arranged at intervals along the circumferential direction of the detection ring 9562. A speed detection probe 95631 is installed in each speed probe mounting hole 95611.

[0083] In this way, the measurement error of the rotational speed of the rotor 9532 can be reduced, which is beneficial to improving the measurement accuracy.

[0084] In some embodiments of the present invention, please refer to Figure 3 There are two speed detection probes 95631. Along the circumferential direction of the detection ring 9562, the interval angle between two adjacent speed detection probes 95631 is A, and the value range of A is 30°-90°.

[0085] Compared with the case where three or more speed detection probes 95631 are used, the use of the speed detection probes 95631 can be saved while ensuring the measurement accuracy, thereby reducing the cost.

[0086] In some embodiments of the present invention, please refer to Figure 1 and Figure 3 An axial probe mounting hole 95612 is provided on the side of the mounting seat 9561 facing the detection ring 9562. Along the circumferential direction of the detection ring 9562, the axial displacement detection probe 95632 and the speed detection probe 95631 arranged on the mounting seat 9561 are spaced apart.

[0087] In this way, the possibility of mutual interference during the detection process can be reduced, thereby improving the reliability of the detection.

[0088] In some embodiments of the present invention, please refer to Figure 2 The number of radial probe mounting holes 95621 is at least three, and all radial probe mounting holes 95621 are arranged at intervals along the circumferential direction of the detection ring 9562. A radial displacement detection probe 95633 is provided in each radial probe mounting hole 95621.

[0089] When the rotor 9532 undergoes radial displacement, the radial displacement detection probes 95633 at different positions can synchronously collect displacement data, significantly suppressing single-point measurement errors. Compared with single-probe or dual-probe solutions, they can capture the dynamic eccentric displacement of the rotor 9532 in real time to improve displacement detection accuracy.

[0090] In some embodiments of the present invention, please refer to Figure 2 The number of radial probe mounting holes 95621 is four, and the four radial probe mounting holes 95621 are arranged at equal intervals along the circumferential direction of the detection ring 9562.

[0091] With this arrangement, linear measurement of the radial displacement of the rotor 9532 can be achieved, that is, by measuring the displacement of the rotor 9532 in two mutually perpendicular radial directions, all-round detection of the radial direction of the rotor 9532 can be achieved without the need for conversion, making control simpler.

[0092] In some embodiments of the present invention, please refer to Figure 2 An axial probe mounting hole 95612 is provided on the side of the detection ring 9562 facing the mounting seat 9561. Along the circumferential direction of the detection ring 9562, the axial displacement detection probe 95632 and the radial displacement detection probe 95633 arranged on the detection ring 9562 are spaced apart.

[0093] The axial probe mounting hole 95612 will not occupy too much of the axial dimension of the detection ring 9562, so that the axial dimension of the detection ring 9562 can be made smaller, thereby reducing the axial dimension of the detection ring 9562 occupied by the rotor 9532, which is beneficial to improving the main frequency of the rotor 9532.

[0094] According to the embodiment of the present invention, please refer to Figure 7 A compressor is proposed, including a rotor 9532 and a sensor detection device 956 for the compressor according to the above embodiment. The rotor 9532 includes a rotor shaft 95321. A target disk 957 is connected to the outer circumferential surface of the rotor shaft 95321. A mounting seat 9561 is provided on one side of the target disk 957 along the axial direction of the rotor shaft 95321, and a detection ring 9562 is provided on the other side of the target disk 957. The detection ring 9562 is sleeved on the target disk 957. The diameter of the portion of the rotor shaft 95321 located within the detection ring 9562 is smaller than the inner diameter of the detection ring 9562. The orthographic projection of the axial displacement detection probe 95632 along the axial direction of the rotor shaft 95321 is located on the target disk 957. The detection end of the axial displacement detection probe 95632 is arranged toward the target disk 957, and the detection end of the radial displacement detection probe 95633 is arranged toward the rotor shaft 95321. The rotor shaft 95321 is configured to rotate relative to the mounting seat 9561 and the detection ring 9562.

[0095] Optionally, the compressor further includes a stator, a radial magnetic bearing 958, and a casing assembly. The casing assembly has a receiving cavity, the stator is mounted within the receiving cavity, the radial magnetic bearing 958 is located within the receiving cavity, the sensor detection device 956 is located between the radial magnetic bearing 958 and the stator, the radial magnetic bearing 958 includes a radial bearing seat 9581, the radial bearing seat 9581 is connected to the casing assembly, and the mounting seat 9561 and the detection ring 9562 are respectively detachably connected to the radial bearing seat 9581. The connection between the radial bearing seat 9581 and the casing assembly includes, but is not limited to, welding or screw connection.

[0096] The target plate 957 can be a separate component or can be integrally formed with the rotor 9532. When the target plate 957 is a separate component, the target plate 957 is in driving connection with the rotor shaft 95321. Specifically, the target plate 957 can be fixed by an interference fit or by a set screw. For example, the target plate 957 has a threaded hole that is threadedly connected to the set screw. The end of the set screw abuts against the rotor shaft 95321 to limit the target plate 957 along the axial and circumferential directions of the rotor shaft 95321.

[0097] By optimizing the structure of the sensor detection device 956 , the distance between the radial magnetic bearing 958 and the stator can be shortened, making the structure more compact, which is beneficial to shortening the length of the rotor 9532 and increasing the main frequency of the rotor 9532 .

[0098] In some embodiments of the present invention, please refer to Figure 4 The outer peripheral surface of the rotor shaft 95321 is formed with a characteristic structure 95322 for being identified by the speed detection probe 95631, and the characteristic structure 95322 includes a groove or a protrusion.

[0099] During the rotation of the rotor 9532 , the speed sensor generates an identification signal through the characteristic structure every time the rotor 9532 rotates one circle, so that the rotation speed of the rotor 9532 can be detected based on the frequency of the identification signal.

[0100] In another example, the characteristic structure may also be provided on the target disk 957 . Along the radial direction of the target disk 957 , the characteristic structure and the axial displacement detection probe 95632 are staggered to avoid interference with the axial displacement detection probe 95632 in detecting the axial displacement.

[0101] The characteristic structure is set to facilitate the speed sensor to generate a signal during the rotation of the rotor 9532 to detect the rotation speed of the rotor 9532.

[0102] In some embodiments of the present invention, please refer to Figure 7 、 Figures 9-12 The compressor 95 further includes a bearing assembly 951, a thrust plate 952, and a gas compression assembly 953. The bearing assembly 951 includes a support member 9511, a magnetic pole plate 9512, and a protective bearing 95122. The support member 9511 includes a first magnetic pole portion 95111, a protective bearing mounting portion 95112, and a sealing portion 95116. The first magnetic pole portion 95111 and the sealing portion 95116 are disposed opposite each other along the axial direction of the protective bearing 95122. The protective bearing 95122 is mounted on the protective bearing mounting portion 95112. The first magnetic pole portion 95111 is opposite to and connected to the magnetic pole plate 9512. At least two of the first magnetic pole portion 95111, the protective bearing mounting portion 95112, and the sealing portion 95116 are integrally formed. Gas compression assembly 953 includes an impeller 9531, which is located on the side of support member 9511 facing away from magnetic pole plate 9512. The back of impeller 9531 faces and rotates in a sealed manner with seal 95116. A radial magnetic bearing 958 is located between magnetic pole plate 9512 and sensor detection device 956.

[0103] Mounting seat 9561 and detection ring 9562 can be fixed to bearing seat 9581 of radial magnetic bearing 958 in the compressor. Optionally, mounting seat 9561 can be arranged on the side of detection ring 9562 facing away from radial magnetic bearing 958, or mounting seat 9561 can be arranged on the side of detection ring 9562 facing radial magnetic bearing 958.

[0104] At least two of the first magnetic pole portion 95111, the protective bearing mounting portion 95112 and the sealing portion 95116 are integrally formed, including: any two of the first magnetic pole portion 95111, the protective bearing mounting portion 95112 and the sealing portion 95116 can be integrally formed, or the three can be integrally formed. Figure 7The structure in which the first magnetic pole portion 95111, the protective bearing mounting portion 95112 and the sealing portion 95116 in the compressor 95 are integrally formed is shown as an example. Figure 10 The structure of the first magnetic pole portion 95111 and the protective bearing mounting portion 95112 in the compressor 95 is shown as an integral part. The sealing portion 95116 is a separate part, and the sealing portion 95116 can be connected to the protective bearing mounting portion 95112 by screws or welding. Figure 11 It is exemplarily shown that the first magnetic pole portion 95111 in the compressor 95 is a separate part, and the protective bearing mounting portion 95112 and the sealing portion 95116 are integrally formed. The first magnetic pole portion 95111 can be connected to the protective bearing mounting portion 95112 by screws or welding. Figure 12 The structure of the first magnetic pole portion 95111 and the sealing portion 95116 in the compressor 95 is shown as an integral part. The protective bearing mounting portion 95112 can be connected to the first magnetic pole portion 95111 by screw connection or welding.

[0105] The magnetic pole plate 9512 and the support member 9511 are made of magnetic conductive materials, which can be, but are not limited to, magnetic conductive materials such as iron-cobalt alloy, neodymium iron boron or low carbon steel.

[0106] By integrally molding at least two of the first magnetic pole portion 95111, the protective bearing mounting portion 95112, and the sealing portion 95116, the at least two integrally molded parts can share a portion, eliminating the trouble of connecting them by screws, thereby reducing the dimension from the magnetic pole plate 9512 to the sealing portion 95116 along the length direction of the rotor shaft 95321, and further reducing the dimension from the impeller 9531 to the magnetic pole plate 9512 along the length direction of the rotor shaft 95321. The impeller 9531 is connected to the end of the rotor shaft 95321. After the dimension from the impeller 9531 to the magnetic pole plate 9512 is reduced, the dimension from the end of the rotor shaft 95321 to the magnetic pole plate 9512 along the axial direction of the rotor shaft 95321 can also be reduced. On the premise that the position of the other end of the rotor shaft 95321 remains unchanged, the dimension of the rotor shaft 95321 in the axial direction is shortened, thereby improving the natural frequency of the rotor shaft 95321. In addition, the first magnetic pole portion 95111 constitutes a part of the axial magnetic levitation bearing of the second magnetic pole portion 95121. When the first magnetic pole portion 95111 and the protective bearing mounting portion 95112 are integrally formed, the concentricity of the protective bearing 95122 and the axial magnetic levitation bearing can be improved. Moreover, the integrally formed structure can reduce the number of parts, which is conducive to assembly and disassembly.

[0107] In some embodiments of the present invention, please refer to Figure 7The protective bearing mounting portion 95112 has a bearing mounting hole 951121. The protective bearing 95122 is located within the bearing mounting hole 951121 and engages with the inner circumference of the bearing mounting hole 951121. The protective bearing 95122 has a first shaft mounting hole 951221. One end of the rotor shaft 95321 passes through the first shaft mounting hole 951221 and is fixedly connected to the impeller 9531.

[0108] The fit between the protective bearing 95122 and the bearing mounting hole 951121 can be a transition fit or an interference fit to ensure the concentricity of the protective bearing 95122 and the bearing mounting hole 951121.

[0109] The protective bearing 95122 can protect the rotor 9532 and the stator 959 in the event of a sudden power outage, thereby preventing the rotor 9532 from colliding with the stator 959 in the event of a sudden power outage during the suspended operation, and thus supporting the rotor 9532.

[0110] In some embodiments of the present invention, please refer to Figure 7 The magnetic pole plate 9512 has a second magnetic pole portion 95121, which is spaced apart from and opposite to the first magnetic pole portion 95111 along the axial direction of the protective bearing 95122. The gas compression assembly 953 also includes a thrust plate 952, which is fixedly mounted on the rotor shaft 95321. The thrust plate 952 is located between the first magnetic pole portion 95111 and the second magnetic pole portion 95121 and is movable relative to the support member 9511 along the axial direction of the protective bearing 95122. The first magnetic pole portion 95111 and the second magnetic pole portion 95121 are respectively configured to adjust the position of the thrust plate 952 through magnetic force. The thrust plate 952 has a second shaft mounting hole 9521, and the rotor shaft 95321 passes through the second shaft mounting hole 9521 and is fixedly connected to the thrust plate 952.

[0111] The rotor shaft 95321 can be fixedly connected to the thrust plate 952 by interference fit or threaded connection.

[0112] In compressor 95, rotor shaft 95321 is also supported by two sets of radial magnetic bearings. These two sets of radial magnetic bearings, combined with the circumferential permanent magnets of rotor 9532, magnetically pull rotor 9532 upward, levitating it. Compressor 95 also includes a housing assembly 954 and two sets of radial magnetic bearings. Housing assembly 954 defines an internal accommodating chamber, within which bearing assembly 951, thrust plate 952, and gas compression assembly 953 are located. Within the accommodating chamber is also located a stator 959, which rotates in conjunction with rotor 9532. Rotor 9532 rotates under the influence of the magnetic field of stator 959, operating in the same manner as an electric motor and will not be further described here.

[0113] Please refer to Figure 7 The casing assembly 954 includes a casing 9541 and a volute 9542. At least one end of the casing 9541 is connected to the volute 9542. The volute 9542 has an intake chamber 95421 and a compressed air duct 95422. The intake chamber 95421 and the compressed air duct 95422 are communicated. An air inlet is provided at one end of the intake chamber 95421 along the axial direction of the rotor shaft 95321. The impeller 9531 is arranged in the intake chamber 95421 and is located on the intake side of the compressed air duct 95422. The exhaust port of the impeller 9531 is communicated with the intake side of the compressed air duct 95422. The gas compressed by the impeller 9531 enters the channel of the volute 9542 and is discharged through the volute 9542. To reduce gas leakage into the housing cavity of casing 9541, a seal 95116 is required to engage with the wheel back of impeller 9531 in a rotating seal to reduce gas leakage and maintain the stability of the pressure output of compressor 95. Casing assembly 954 has a housing cavity, and the bearing assembly and thrust plate are both located within the housing cavity.

[0114] To reduce resistance to rotor 9532's rotation and minimize wear on the bearings supporting it, two sets of radial magnetic bearings are mounted on rotor 9532, spaced apart along the axial direction of rotor 9532. The magnetic fields generated by the radial magnetic bearings interact with the permanent magnets in rotor 9532, levitating rotor 9532. Rotor 9532 is then rotated by stator 959, achieving its suspended rotation. Rotor 9532 may experience axial movement during rotation, which can cause wear and tear on rotor 9532.

[0115] The support member 9511 can be connected to the housing assembly 954, specifically to any one of the housing 9541 and the volute 9542. Optionally, the connection method between the support member 9511 and the housing assembly 954 includes but is not limited to screw connection, welding or riveting.

[0116] Therefore, the position of the thrust disk 952 needs to be adjusted via the first magnetic pole portion 95111 and the second magnetic pole portion 95121 to change the axial position of the rotor 9532 so that the rotor 9532 does not interfere with the rotor 9532 in the suspended state. The bearing assembly 951 also includes an axial bearing winding 955, which is located between the first magnetic pole portion 95111 and the second magnetic pole portion 95121 and is disposed on the outer circumference of the thrust disk 952. The axial bearing winding 955 generates magnetic force, which is then guided by the magnetic pole plate 9512 and the support member 9511. The first magnetic pole portion 95111 and the second magnetic pole portion 95121 generate magnetic force, causing the thrust disk 952 to generate a force along the axial direction of the rotor 9532, thereby changing the position of the thrust disk 952 to adjust the position of the rotor shaft 95321 in the axial direction. The first magnetic pole portion 95111, the second magnetic pole portion 95121 and the axial bearing winding 955 form an axial magnetic levitation bearing (thrust magnetic levitation bearing), which has the same working principle as the axial magnetic levitation in the prior art and will not be repeated here.

[0117] In some embodiments of the present invention, please refer to Figure 8 The sealing portion 95116 includes multiple circles of first protrusions 951161, which are coaxially arranged with the protective bearing 95122 and spaced apart radially along the rotor shaft 95321. The back of the impeller 9531 is provided with multiple circles of second protrusions 95311, which are coaxially arranged with the rotor shaft 95321 and spaced apart radially along the rotor shaft 95321. At least one circle of second protrusions 95311 is provided between two adjacent circles of first protrusions 951161.

[0118] The profile of the cross section of the first protrusion 951161 and the second protrusion 95311 passing through the axis of the protective bearing 95122 can be, but is not limited to, a rectangle, an arc, a triangle, an ellipse, etc., and can also be other irregular shapes.

[0119] In one example, multiple circles of first protrusions 951161 are flush with one end facing away from the magnetic pole plate 9512, and multiple circles of second protrusions 95311 are flush with one end facing the magnetic pole plate 9512, which can reduce the size of the sealing portion 95116 along the axial direction of the rotor shaft 95321. In another example, along the radial direction of the rotor shaft 95321 from the inside to the outside, the size of the multiple circles of first protrusions 951161 from the end facing away from the magnetic pole plate 9512 to the end of the magnetic pole plate 9512 along the axial direction of the rotor shaft 95321 gradually decreases, and the size of the multiple second protrusions 95311 from the end facing the magnetic pole plate 9512 to the end of the magnetic pole plate 9512 along the axial direction of the rotor shaft 95321 gradually increases; or, along the radial direction of the rotor shaft 95321 from the inside to the outside, the size of the multiple circles of first protrusions 951161 from the end facing away from the magnetic pole plate 9512 to the end of the magnetic pole plate 9512 along the axial direction of the rotor shaft 95321 gradually increases, and the size of the multiple second protrusions 95311 from the end facing the magnetic pole plate 9512 to the end of the magnetic pole plate 9512 along the axial direction of the rotor shaft 95321 gradually decreases, which can also form a labyrinth seal to reduce gas leakage.

[0120] The first protrusion 951161 and the second protrusion 95311 cooperate to form a labyrinth seal, extending the path for gas to pass through. When the gas passes through the mating surface between the first protrusion 951161 and the second protrusion 95311, the pressure loss will hinder the passage of the gas, thereby reducing gas leakage.

[0121] In some embodiments of the present invention, please refer to Figure 8 , the multiple circles of first protrusions 951161 are arranged flush with one end away from the magnetic pole plate 9512; and / or, the multiple circles of second protrusions 95311 are arranged flush with one end toward the magnetic pole plate 9512.

[0122] Thus, the size of the sealing portion 95116 along the axial direction of the rotor shaft 95321 can be reduced, making the structure compact, which is conducive to reducing the length of the rotor shaft 95321.

[0123] In some embodiments of the present invention, please refer to Figure 8 The sealing portion 95116 also includes multiple circles of first sealing teeth 951162, which are coaxially arranged with the protective bearing 95122. Along the radial direction of the rotor shaft 95321, the multiple circles of first sealing teeth 951162 are arranged at intervals, and at least one circle of first sealing teeth 951162 is formed at the end of the first protrusion 951161 away from the magnetic pole plate 9512.

[0124] Optionally, in a half-section of the first sealing tooth 951162 passing through the axis of the rotor shaft 95321, the radial dimension of the half-section decreases from the root to the end away from the root, from the root to the connection end of the first sealing tooth 951162. For example, the outer contour of the half-section can be trapezoidal or hemispherical, or can be a structure constructed of any of a spline curve, a straight line, or an arc.

[0125] In other examples, the first sealing teeth 951162 may also be rectangular.

[0126] Therefore, when the gas passes through the first sealing teeth 951162, the gas is disturbed, causing a pressure drop in the gas, thereby significantly reducing the leakage.

[0127] In some embodiments of the present invention, please refer to Figure 8 The first sealing teeth 951162 formed on the first protrusion 951161 are multiple circles, and the first sealing teeth 951162 are inclined outward along the radial direction of the rotor shaft 95321.

[0128] Among the multiple first sealing teeth 951162 forming the same circle of first protrusions 951161, a circle of grooves is formed between two adjacent circles of first sealing teeth 951162. The width of the grooves in the radial direction of the first sealing teeth 951162 gradually increases from the bottom of the grooves to the notch of the grooves. In a half-section of the first sealing teeth 951162 passing through the axis of the rotor shaft 95321, the radial dimension of the half-section of the first sealing teeth 951162 decreases from the root to the end away from the root.

[0129] The first sealing tooth 951162 is tilted outward in the radial direction of the rotor shaft 95321, which means that the end of the first sealing tooth 951162 away from its root is offset relative to its root in the radial direction of the rotor shaft 95321, that is, the first sealing tooth 951162 can be an inclined tooth structure.

[0130] By tilting the first sealing teeth 951162 in multiple turns, a tortuous airflow channel is formed, which prevents the high-pressure side gas from leaking to the low-pressure side. Specifically, when the high-pressure gas passes through the sealing portion 95116, it must pass through the gap between the first protrusion 951161 and the second protrusion 95311 in sequence. Because the first sealing teeth 951162 are radially spaced and tilted outward, the direction of gas flow is forced to change. Every time the gas passes through the gap between the first sealing teeth 951162, the pressure drop occurs due to the throttling effect. After passing through multiple turns of the first sealing teeth 951162, the leakage amount is greatly attenuated. In addition, when the impeller 9531 rotates, an air film is formed in the tiny gap between the back of the impeller 9531 and the sealing first sealing teeth 951162. The first sealing teeth 951162 can reduce the disturbance of the rotating airflow on the sealing gap, avoiding fluctuations in the leakage amount caused by unstable airflow in the gap.

[0131] In some embodiments of the present invention, please refer to Figure 8 The back of the impeller 9531 is provided with multiple circles of second sealing teeth 95312, which are coaxially arranged with the rotor shaft 95321. Along the radial direction of the rotor shaft 95321, the multiple circles of second sealing teeth 95312 are arranged at intervals, and at least one circle of second sealing teeth 95312 is formed on one end of the second protrusion 95311 facing the magnetic pole plate 9512.

[0132] Optionally, in a half-section of the second sealing tooth 95312 passing through the axis of the rotor shaft 95321, the radial dimension of the half-section decreases from the root to the end away from the root, from the root to the connection end of the first sealing tooth 951162. For example, the outer contour of the half-section can be trapezoidal or hemispherical, or can be a structure constructed of any of a spline curve, a straight line, or an arc.

[0133] In other examples, the second sealing teeth 95312 may also be rectangular.

[0134] By staggered arrangement of multiple circles of first protrusions 951161 and second protrusions 95311, and provision of multiple circles of first sealing teeth 951162 and multiple circles of second sealing teeth 95312, a complex return path is formed inside the sealing area, so that the gas must undergo multiple changes in direction and throttling resistance before it can leak out, thereby significantly increasing the sealing impedance and reducing the leakage rate.

[0135] In some embodiments of the present invention, please refer to Figure 8 The second sealing teeth 95312 formed on the second protrusion 95311 are multiple circles, and the second sealing teeth 95312 are inclined outward along the radial direction of the rotor shaft 95321.

[0136] Among the multiple second sealing teeth 95312 forming the same circle of first protrusions 951161, a circle of grooves is formed between two adjacent circles of second sealing teeth 95312. The width of the grooves gradually increases in the radial direction of the second sealing teeth 95312 from the bottom of the grooves to the notch of the grooves. In a half-section of the second sealing teeth 95312 passing through the axis of the rotor shaft 95321, the radial dimension of the half-section of the second sealing teeth 95312 decreases from the root to the end away from the root.

[0137] The second sealing teeth 95312 are tilted outwardly in the radial direction of the rotor shaft 95321, which means that the end of the second sealing teeth 95312 away from the root thereof is offset relative to the root thereof in the radial direction of the rotor shaft 95321, that is, the second sealing teeth 95312 may have an inclined tooth structure.

[0138] By tilting the second sealing teeth 95312 in multiple circles, a tortuous airflow channel is formed to prevent the high-pressure side gas from leaking to the low-pressure side. Specifically, when the high-pressure gas passes through the sealing portion 95116, it must pass through the gap between the first protrusion 951161 and the second protrusion 95311 in sequence. Since the second sealing teeth 95312 are radially spaced and tilted outward, the direction of gas flow is forced to change. Every time the gas passes through the gap between the second sealing teeth 95312, the pressure drop occurs due to the throttling effect. After passing through multiple circles of the second sealing teeth 95312, the leakage amount is greatly attenuated. In addition, when the impeller 9531 rotates, an air film is formed in the tiny gap between the back of the impeller 9531 and the sealed second sealing teeth 95312. The second sealing teeth 95312 can reduce the disturbance of the rotating airflow to the sealing gap, thereby avoiding fluctuations in leakage due to unstable airflow in the gap.

[0139] In some embodiments of the present invention, please refer to Figure 9 The support member 9511 has a cooling channel 95113 , and the cooling channel 95113 is provided with a cooling medium inlet 95114 and a cooling medium outlet 95115 .

[0140] In one example, see Figure 14 The cooling channel 95113 may include a circumferential channel surrounding the rotor shaft 95321. The circumferential channel is a channel that circumscribes the rotor shaft 95321. Specifically, the cooling medium inlet 95114 and the cooling medium outlet 95115 are located on opposite sides of the cooling channel 95113 along the radial direction of the rotor shaft 95321. That is, the cooling medium inlet 95114 and the cooling medium outlet 95115 face opposite directions and are generally spaced 180 degrees apart along the circumferential direction of the rotor shaft 95321.

[0141] In another example, see Figure 15 Cooling channel 95113 comprises an arcuate channel extending circumferentially along rotor shaft 95321. Cooling medium inlet 95114 communicates with one end of the arcuate channel, while cooling medium outlet 95115 communicates with both ends of the arcuate channel. A blocking portion is formed between the two ends of the arcuate channel to block the ends, forming a discontinuous channel along the circumferential direction of rotor shaft 95321.

[0142] In yet another example, the cooling channel 95113 may be a vortex flow channel extending along the circumferential direction of the rotor shaft 95321 .

[0143] Liquid medium or gas can be passed into the cooling channel 95113. The liquid medium can be, but is not limited to, water or oil.

[0144] At least two of the first magnetic pole portion 95111, the protective bearing mounting portion 95112 and the sealing portion 95116 are integrally formed, which can reduce the size between the magnetic pole plate 9512 and the sealing portion 95116 along the axial direction of the rotor shaft 95321, and reduce the transmission path of the cooling channel 95113, which is beneficial to improving the heat exchange efficiency between the cooling channel 95113 and the first magnetic pole portion 95111 and the second magnetic pole portion 95121, thereby better improving the temperature of the axial magnetic levitation bearing (thrust magnetic levitation bearing) when the compressor 95 is working.

[0145] In some embodiments of the present invention, please refer to Figure 16 The support member 9511 has an air duct 95117 extending along the radial direction of the protective bearing 95122. The air duct 95117 penetrates the inner circumferential surface of the support member 9511 and the outer circumferential surface of the support member 9511 along the radial direction of the protective bearing 95122. Along the axial direction of the protective bearing 95122, the air duct 95117 is spaced apart from or adjacent to the protective bearing 95122.

[0146] Optionally, the dimension of the air duct 95117 along the circumferential direction of the protective bearing 95122 is W, and the dimension W decreases from the outside to the inside in the radial direction of the support member 9511. In other embodiments, the dimension W along the radial direction of the support member 9511 from the outside to the inside can also be a constant value.

[0147] Housing assembly 954 is provided with an air inlet and an exhaust port, each connected to air duct 95117. These ports can be connected to circulating cooling systems to cool components such as protective bearing 95122, the axial magnetic bearing, and the rotor. A fan and heat exchanger can be connected to the cooling circuit. The exhaust gas is cooled by the heat exchanger and then passed through the fan to the air inlet via the cooling circuit, completing the cooling cycle.

[0148] By setting up the air duct 95117, the protective bearing 95122, the axial magnetic bearing, the rotor 9532 and other components can be cooled to prevent the compressor 95 from working unstably due to high temperature during operation.

[0149] In some embodiments of the present invention, there are multiple air ducts 95117 , and the multiple air ducts 95117 are arranged at intervals along the circumferential direction of the protective bearing 95122 .

[0150] Thereby, the cooling area can be increased to further improve the cooling effect.

[0151] In some embodiments of the present invention, please refer to Figure 13-15 , the cooling channel 95113 is arranged around the protective bearing 95122.

[0152] Optionally, the cooling channel 95113 can be a flat channel, that is, the size of the cooling channel 95113 along the axial direction of the rotor shaft 95321 is smaller than the size of the cooling channel 95113 along the radial direction of the rotor shaft 95321, so that the cooling area can be increased to improve the cooling effect.

[0153] Thus, the length of the cooling channel 95113 can be increased to improve the heat exchange effect between the cooling channel 95113 and the axial magnetic suspension bearing (thrust magnetic suspension bearing).

[0154] In some embodiments of the present invention, the impeller 9531 is interference fit with the rotor shaft 95321 so that there is a high degree of coaxiality between the impeller 9531 and the rotor shaft 95321. A through hole is provided at one end of the impeller 9531, and the impeller 9531 is threadedly connected to the end of the rotor shaft 95321 by a screw, and a portion of the screw is located in the through hole.

[0155] In some embodiments of the present invention, please refer to Figure 7 and Figure 8 The rotor shaft 95321 includes a first shaft segment 953211 and a second shaft segment 953212. A first shoulder is formed between the first and second shaft segments 953211 and 953212. The diameter of the first shaft segment 953211 is larger than that of the second shaft segment 953212. The protective bearing 95122 has a clearance fit with the first shaft segment 953211. The impeller 9531 has an interference fit with the second shaft segment 953212. The impeller 9531 can abut the first shoulder, or a spacer 9533 can be provided between the impeller 9531 and the first shoulder. The impeller 9531 abuts the spacer 9533, which abuts the first shoulder and has a clearance fit with the rotor shaft 95321. The spacer 9533 facilitates adjustment of the clearance between the inner ring of the protective bearing 95122 and the spacer 9533 along the axial direction of the protective bearing 95122.

[0156] In some embodiments of the present invention, please refer to Figure 7 and Figure 8Compressor 95 also includes a sleeve 9534, which is located between thrust plate 952 and impeller 9531. The outer circumference of sleeve 9534 has a clearance fit with the inner ring of protective bearing 95122, while the inner circumference of sleeve 9534 has an interference fit or transition fit with rotor shaft 95321. One end of sleeve 9534 abuts thrust plate 952, while the other end abuts impeller 9531. Spacer 9533 abuts sleeve 9534. Along the axial direction of rotor shaft 95321, the dimension between sleeve 9534 and thrust plate 952 is greater than the dimension of protective bearing 95122, allowing axial movement between thrust plate 952 and rotor shaft 95321. In other embodiments, the sleeve 9534 may not be provided, and the inner ring of the protective bearing 95122 is clearance-fitted with the first shaft segment 953211. The interference force between the thrust plate 952 and the first shaft segment 953211 is utilized to enable the thrust plate 952 and the rotor shaft 95321 to move axially together through the axial magnetic bearing.

[0157] In some embodiments of the present invention, the thrust disk 952 has a first abutment portion, which abuts against one end of the sleeve 9534. Along the radial direction of the rotor shaft 95321, the first abutment portion is spaced apart from the outer ring of the protective bearing 95122. Along the axial direction of the rotor shaft 95321, the end of the protective bearing 95122 facing the thrust disk 952 is spaced apart from the first abutment portion.

[0158] The above description is merely a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any changes or substitutions that can be easily conceived by a person skilled in the art within the technical scope disclosed in the present invention should be included in the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be based on the scope of protection of the claims.

Claims

1. A sensor detection device for a compressor, characterized in that: include: A mounting seat and a detection ring, wherein the mounting seat and the detection ring are spaced apart along the axial direction of the detection ring, and the mounting seat has a first inner circumferential surface; as well as A speed detection probe, an axial displacement detection probe and a radial displacement detection probe; the first inner circumference is provided with a speed probe mounting hole, the speed detection probe is installed in the speed probe mounting hole, the inner circumference of the detection ring is provided with a radial probe mounting hole, the radial displacement detection probe is installed in the radial probe mounting hole, at least one of the sides facing each other of the mounting seat and the detection ring is provided with an axial probe mounting hole, the axial displacement detection probe is installed in the axial probe mounting hole, the speed detection probe is used to detect the rotational speed of the compressor rotor, the axial displacement detection probe is used to detect the axial displacement of the rotor, and the radial displacement detection probe is used to detect the radial displacement of the rotor.

2. The sensor detection device for a compressor according to claim 1, characterized in that: The mounting seat is a fan-shaped structure extending along the circumferential direction of the detection ring.

3. The sensor detection device for a compressor according to claim 2, characterized in that: The central angle of the fan-shaped structure is less than or equal to 180°.

4. The sensor detection device for a compressor according to claim 2, characterized in that: The fan-shaped structure includes a first fan-shaped segment and a second fan-shaped segment. The first fan-shaped segment is rotatably connected to the second fan-shaped segment around a first axis. The first axis is parallel to the axis of the detection ring. The first fan-shaped segment has a portion of the first inner circumferential surface. The second fan-shaped segment has a portion of the first inner circumferential surface. The velocity probe mounting hole is respectively provided on the portion of the first inner circumferential surface of the first fan-shaped segment and the portion of the first inner circumferential surface of the second fan-shaped segment.

5. The sensor detection device for a compressor according to claim 4, characterized in that: Along the circumferential direction of the detection ring, the distance between the velocity probe mounting hole of the first sector segment and the first axis is L1, and the distance between the velocity probe mounting hole of the second sector segment and the first axis is L2, where L1=L2.

6. The sensor detection device for a compressor according to claim 4, characterized in that: Along the extension direction of the first axis, a first through hole is provided on one side of the first sector segment, and a second through hole is provided on one side of the second sector segment. The first through hole and the second through hole are configured to be connected to the compressor via fasteners.

7. The sensor detection device according to claim 6, characterized in that: The first through hole is a long slot hole extending along the circumferential direction of the first axis; and / or the second through hole is a long slot hole extending along the first axis.

8. The sensor detection device for a compressor according to any one of claims 1 to 7, characterized in that: There are multiple speed probe mounting holes, and the multiple speed detection probes are arranged at intervals along the circumferential direction of the detection ring. Each speed probe mounting hole is equipped with a speed detection probe.

9. The sensor detection device for a compressor according to claim 8, characterized in that: There are two speed detection probes. Along the circumferential direction of the detection ring, the interval angle between the two speed detection probes is A, and the value range of A is 30°-90°.

10. The sensor detection device for a compressor according to claim 8, characterized in that: An axial probe mounting hole is provided on a side of the mounting seat facing the detection ring. Along the circumferential direction of the detection ring, the axial displacement detection probe and the speed detection probe arranged on the mounting seat are spaced apart.

11. The sensor detection device for a compressor according to any one of claims 1 to 7, characterized in that: The number of the radial probe mounting holes is at least three, all of the radial probe mounting holes are arranged at intervals along the circumferential direction of the detection ring, and each of the radial probe mounting holes is provided with a radial displacement detection probe.

12. The sensor detection device for a compressor according to claim 11, characterized in that: The number of the radial probe mounting holes is four, and the four radial probe mounting holes are arranged at equal intervals along the circumferential direction of the detection ring.

13. The sensor detection device for a compressor according to claim 11, characterized in that: An axial probe mounting hole is provided on a side of the detection ring facing the mounting seat. Along the circumferential direction of the detection ring, the axial displacement detection probe and the radial displacement detection probe arranged on the detection ring are spaced apart.

14. A compressor, characterized in that: A sensor detection device comprising a rotor and a compressor according to any one of claims 1 to 13, wherein the rotor comprises a rotor shaft, the outer circumferential surface of the rotor shaft is connected to a target disk, the mounting seat is provided on one side of the target disk along the axial direction of the rotor shaft, the detection ring is provided on the other side of the target disk, and the detection ring is sleeved on the target disk, the diameter of the portion of the rotor shaft located within the detection ring is smaller than the inner diameter of the detection ring, the orthographic projection of the axial displacement detection probe along the axial direction of the rotor shaft is located on the target disk, the detection end of the axial displacement detection probe is arranged toward the target disk, the detection end of the radial displacement detection probe is arranged toward the rotor shaft, and the rotor shaft is configured to rotate relative to the mounting seat and the detection ring.

15. The compressor according to claim 14, characterized in that A characteristic structure for being recognized by the speed detection probe is formed on the outer circumferential surface of the rotor shaft, and the characteristic structure includes a groove or a protrusion.

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