A rotating machine

Abstract

This utility model provides a rotating machine, comprising: a rotating shaft, a cylinder, an impeller, a collector, a motor rotor, a motor stator, and an aluminum sleeve. The inlet flow area of ​​the collector is S. An air gap exists between the motor rotor and the motor stator, forming a first channel allowing airflow. Gas through holes are provided on the aluminum sleeve along its axial direction, penetrating both ends, forming a second channel allowing airflow. The total area of ​​the air gap within the cross-section of the rotating shaft is S. q The total area of ​​the gas passage is S lt And satisfy the relation 1.5≤S q / S lt ≤3, 1.2≤(S) q +S lt ) / S≤1.5. According to this utility model, without changing the impeller speed, a larger overall air volume can be output, reducing the temperature of the motor and the front radial rotor, thereby reducing the overall temperature of the machine; effectively solving the problem that the existing magnetic levitation blower structure has poor air cooling effect, resulting in high temperature of the internal components of the blower and affecting the service life of the motor.

Description

Technical Field

[0001] This utility model relates to the field of magnetic levitation blower technology, specifically to a rotating machine. Background Technology

[0002] During operation, the blades of a maglev blower increase the pressure, velocity, and temperature of the gas, converting kinetic energy into pressure energy to draw in and compress air. Simultaneously, the motor of the maglev blower generates considerable heat during operation, which can negatively impact its lifespan, thus requiring heat dissipation. Current maglev blowers employ air cooling. These blowers utilize a series-connected single-channel structure, where the cooling air absorbs heat as it passes through the axial stator windings, causing the cooling air temperature to rise. This results in poor cooling of the motor and the front radial rotor.

[0003] Because existing magnetic levitation blower structures suffer from poor air-cooling performance, resulting in high temperatures in internal components and affecting motor lifespan, this invention designs a rotating machine. Utility Model Content

[0004] Therefore, the technical problem to be solved by this utility model is to overcome the defects of the existing magnetic levitation blower structure, which has poor air cooling heat dissipation effect, resulting in high temperature of the internal components of the blower and affecting the service life of the motor, thereby providing a rotating machine.

[0005] To solve the above problems, this utility model provides a rotating machine, which includes:

[0006] The device comprises a rotating shaft, a cylindrical body, an impeller, a collector, a motor rotor, a motor stator, and an aluminum sleeve. The rotating shaft, the motor rotor, the motor stator, and the aluminum sleeve are all disposed within the cylindrical body. The impeller is arranged at one axial end of the rotating shaft, i.e., at one axial end of the cylindrical body. The collector is disposed at the inlet of the impeller. The collector is the first airflow inlet of the cylindrical body. The inlet flow area of ​​the collector is S, so that airflow can be drawn in from the collector through the impeller and enter the cylindrical body.

[0007] The motor rotor is located on the inner circumference of the motor stator, and the outer circumference of the motor stator is fixed to the cylindrical body by the aluminum sleeve. An air gap exists between the motor rotor and the motor stator, forming a first channel allowing airflow. Gas through-holes are provided on the aluminum sleeve, extending through both ends along its axial direction, forming a second channel allowing airflow. Within the cross-section of the rotating shaft, the total area of ​​the air gap is S. q The total area of ​​the gas through-holes is S. lt And satisfy the relation 1.5≤S q / S lt ≤3, 1.2≤(S)q +S lt ) / S≤1.5.

[0008] In some implementations...

[0009] Within the projection plane of the axial end face of the aluminum sleeve, the outer diameter of the aluminum sleeve is R. lt The gas passage is a circular hole, and the distance between the center of the gas passage and the central axis of the aluminum sleeve is 0.9R. lt

[0010] ~0.95R lt The radius of the gas through hole is r, and there are multiple gas through holes. The multiple gas through holes are distributed at intervals in the circumferential direction of the aluminum sleeve, and the number of gas through holes n is 16-20.

[0011] In some implementations...

[0012] The gas passage of the aluminum sleeve is also provided with fins. One end of the fin is connected to the inner peripheral wall of the gas passage, and the other end extends toward the central axis of the gas passage to form a free end.

[0013] In some implementations...

[0014] Within the projected plane of the axial end face of the aluminum sleeve, the radial height of the fin is h, and the diameter of the gas passage is D. lt And satisfy the relationship: 0.16 <h / D lt <0.3; there are multiple fins, and the multiple fins are distributed at intervals in both the circumferential and axial directions of the gas passage.

[0015] In some implementations...

[0016] The end of the collector furthest from the impeller is the gas inlet of the blower. The flow channel radius of the collector at this gas inlet is R. The cylinder body has a cylindrical structure with an inner diameter of R. t R and R t The relationship between them satisfies: 0.18 ≤ R t / R≤0.24.

[0017] In some implementations...

[0018] A comb-tooth disk is provided at the axial end of the cylinder away from the impeller. The comb-tooth disk is located on the outer periphery of the rotating shaft and is fixed. A gap exists between the radial inner circumference of the comb-tooth disk and the rotating shaft to form an auxiliary air inlet for air intake into the cylinder. The radius of the radial inner circumference of the comb-tooth disk is R. x R t With R xThe relationship between them satisfies: 0.22 ≤ R x / R t ≤0.24.

[0019] In some implementations...

[0020] The comb tooth disk has comb teeth protruding from its inner peripheral wall toward the rotating shaft. The free ends of the comb teeth do not contact the rotating shaft, and there are multiple comb teeth that are spaced apart along the circumferential and / or axial direction of the comb tooth disk.

[0021] In some implementations...

[0022] It also includes an axial bearing disposed inside the cylinder. The axial bearing includes a first axial stator, a second axial stator, and a thrust disk. The thrust disk is located between the first axial stator and the second axial stator. A gas channel is provided on the thrust disk through its two axial ends. One axial end of the gas channel is opposite to the radial inner circumference of the first axial stator, and the other axial end of the gas channel is opposite to the radial inner circumference of the second axial stator. A heat dissipation channel is also provided on the thrust disk, extending to its outer circumference. One end of the heat dissipation channel is connected to the gas channel, and the other end extends to the outer circumference of the thrust disk. A heat dissipation outlet is provided on the cylinder, which is opposite to and connected to the heat dissipation channel, so that gas entering the cylinder from the collector is discharged from the cylinder through the gas channel, the heat dissipation channel, and the heat dissipation outlet. Gas entering the cylinder from the comb plate is also discharged from the cylinder through the gas channel, the heat dissipation channel, and the heat dissipation outlet.

[0023] In some implementations...

[0024] The flow area of ​​the heat dissipation outlet is S. z The flow area of ​​the auxiliary air intake is S. x And there are S and S z and S x The relationship between them is: 0.62≤(S+S) x ) / S z ≤0.78.

[0025] In some implementations...

[0026] In the projection plane of the longitudinal plane passing through the central axis of the rotating shaft, the position of the axial end face of the collector away from the impeller is defined as position 0. The total axial length of the rotating machinery is L. The position of the comb disc is position L. The distance between the motor stator and the position defined as 0 along the axial direction of the rotating shaft is 1 / 4L to 1 / 2L. The distance between the axial bearing and the position defined as 0 along the axial direction of the rotating shaft is 1 / 2L to 1 / 3L.

[0027] The rotating machinery provided by this utility model has the following beneficial effects:

[0028] This invention utilizes the air gap between the motor rotor and stator as a primary airflow channel to cool the rotor and stator. Furthermore, gas passages on the aluminum sleeve surrounding the stator create a second airflow channel, effectively increasing the cooling area for the aluminum sleeve and stator, thus improving the stator's heat dissipation performance. Compared to existing magnetic levitation blowers that only use the air gap as a cooling channel, this invention directs a portion of the gas flow between the rotor and stator (with a margin) to the stator (aluminum sleeve), increasing the airflow to the stator and improving heat dissipation for both the stator and aluminum sleeve. Moreover, the relationship between the first and second channels and the inlet flow area—1.5 ≤ Sq / Slt ≤ 3, 1.2 ≤ (Sq + Slt) / S ≤ 1.5—further ensures uniform airflow distribution between the two channels, improving the heat exchange efficiency between the stator, rotor, and aluminum sleeve, and increasing the overall motor cooling rate. (See also...) Figure 5 As shown, without changing the impeller speed, the overall system can output a large air volume, reducing the temperature of the motor and the front radial rotor, thereby reducing the overall temperature of the machine. This effectively solves the problem in existing magnetic levitation blower structures where poor air cooling results in high temperatures of internal components, affecting the lifespan of the motor. Attached Figure Description

[0029] Figure 1 This is a three-dimensional structural diagram of the rotating machinery (magnetic levitation blower) of this utility model;

[0030] Figure 2 This is an internal structural diagram of the rotating machinery (magnetic levitation blower) of this utility model;

[0031] Figure 3 This is a schematic diagram of the structure of the aluminum sleeve in the rotating machinery of this utility model;

[0032] Figure 4 This is a schematic diagram of the structure of the comb disc in the rotating machinery of this utility model;

[0033] Figure 5The temperature reduction of the motor in this utility model is related to (S) q +S lt The relationship curve of ) / S.

[0034] The reference numerals in the attached figures are as follows:

[0035] 1. Cylinder; 2. Collector; 3. Impeller; 4. Shaft; 5. Aluminum sleeve; 6. Motor stator; 7. Motor rotor; 8. Thrust disc; 9. Coil; 10. Front radial rotor; 11. Rear radial rotor; 12. Front radial stator; 13. Rear radial stator; 14. First axial stator; 15. Second axial stator; 16. Heat dissipation outlet; 17. Comb toothed disc; 18. Gas through hole; 19. Gas passage. Detailed Implementation

[0036] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present utility model or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of the present utility model without creative effort are within the scope of protection of the present utility model.

[0037] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0038] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0039] In the description of this utility model, it should be understood that the directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this utility model. The directional terms "inner" and "outer" refer to the inner and outer contours of each component itself.

[0040] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0041] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this utility model.

[0042] like Figure 1-5 As shown, this utility model provides a rotating machine (preferably a magnetic levitation blower), which includes:

[0043] The assembly includes a rotating shaft 4, a cylindrical body 1, an impeller 3, a collector 2, a motor rotor 7, a motor stator 6, and an aluminum sleeve 5. The rotating shaft 4, the motor rotor 7, the motor stator 6, and the aluminum sleeve 5 are all disposed in the cylindrical body 1. The impeller 3 is arranged at one axial end of the rotating shaft 4, that is, at one axial end of the cylindrical body 1. The collector 2 is disposed at the inlet of the impeller 3. The collector 2 is the first airflow inlet of the cylindrical body 1. The inlet flow area of ​​the collector 2 is S, so that airflow can be drawn in from the collector 2 through the impeller 3 and enter the cylindrical body 1.

[0044] The motor rotor 7 is located on the inner circumference of the motor stator 6, and the outer circumference of the motor stator 6 is fixed to the cylinder 1 by the aluminum sleeve 5. An air gap exists between the motor rotor 7 and the motor stator 6, forming a first channel allowing airflow. Gas through holes 18 are provided on the aluminum sleeve 5, extending through both ends along its axial direction, forming a second channel allowing airflow. Within the cross-section of the rotating shaft 4, the total area of ​​the air gap is S. q The total area of ​​the gas through-hole 18 is S lt And satisfy the relation 1.5≤S q / S lt ≤3, 1.2≤S q +S lt / S≤1.5.

[0045] This invention utilizes the air gap between the motor rotor and stator as a primary airflow channel to cool the rotor and stator. Furthermore, gas passages on the aluminum sleeve surrounding the stator create a second airflow channel, effectively increasing the cooling area for the aluminum sleeve and stator, thus improving the stator's heat dissipation performance. Compared to existing magnetic levitation blowers that only use the air gap as a cooling channel, this invention directs a portion of the gas flow between the rotor and stator (with a margin) to the stator (aluminum sleeve), increasing the airflow to the stator and improving heat dissipation for both the stator and aluminum sleeve. Moreover, the relationship between the first and second channels and the inlet flow area—1.5 ≤ Sq / Slt ≤ 3, 1.2 ≤ (Sq + Slt) / S ≤ 1.5—further ensures uniform airflow distribution between the two channels, improving the heat exchange efficiency between the stator, rotor, and aluminum sleeve, and increasing the overall motor cooling rate. (See also...) Figure 5 As shown, without changing the impeller speed, the overall system can output a large air volume, reducing the temperature of the motor and the front radial rotor, thereby reducing the overall temperature of the machine. This effectively solves the problem in existing magnetic levitation blower structures where poor air cooling results in high temperatures of internal components, affecting the lifespan of the motor.

[0046] In some implementations...

[0047] Within the projection plane of the axial end face of the aluminum sleeve 5, the outer diameter of the aluminum sleeve 5 is R. lt The gas through-hole 18 is a circular hole, and the distance between the center of the gas through-hole 18 and the central axis of the aluminum sleeve 5 is 0.9R. lt ~0.95R lt The radius of the gas through hole 18 is r, and there are multiple gas through holes 18. The multiple gas through holes 18 are distributed at intervals in the circumferential direction of the aluminum sleeve 5, and the number of gas through holes 18 n is 16-20.

[0048] This is a further preferred structural form of the aluminum sleeve portion and the gas through hole of this utility model, by setting the center of the gas through hole at 0.9R. lt ~0.95R lt The gas passage is positioned so that it is located at the flange of the aluminum sleeve, which effectively reduces the length of the gas passage and ensures the smooth flow of the second channel, thus ensuring effective heat dissipation and cooling of the aluminum sleeve and stator. The gas passage of this invention has multiple holes, which can increase the gas flow area and further improve the heat dissipation performance of the aluminum sleeve and motor stator.

[0049] In some implementations...

[0050] The gas passage 18 of the aluminum sleeve 5 is also provided with fins. One end of the fin is connected to the inner peripheral wall of the gas passage 18, and the other end extends toward the central axis of the gas passage 18 and forms a free end.

[0051] By incorporating fins within the gas passage through the aforementioned preferred structural form, this invention increases the contact area between the gas and the fins as the gas flows through the passage, thereby increasing the surface area of ​​the internal flow channel of the aluminum sleeve and optimizing the heat transfer path, significantly improving heat dissipation efficiency while also achieving lightweight and cost control.

[0052] In some implementations...

[0053] Within the projection plane of the axial end face of the aluminum sleeve 5, the radial height of the fin is h, and the diameter of the gas through-hole 18 is D. lt And satisfy the relationship: 0.16 <h / D lt <0.3; there are multiple fins, and the multiple fins are distributed at intervals in both the circumferential and axial directions of the gas passage 18.

[0054] This invention also utilizes the aforementioned fin height h and gas passage diameter D lt The relationship between them is satisfied: 0.16 <h / D lt <0.3, which can further optimize the heat transfer path of the gas flow and further improve the cooling and heat dissipation efficiency between the gas and the fins and aluminum sleeve (stator); by setting multiple fins, the multiple fins can be distributed along the circumferential and / or axial directions, which can further increase the heat exchange contact area with the gas and further improve the cooling and heat dissipation performance of the aluminum sleeve and stator, as well as the motor.

[0055] In some implementations...

[0056] The end of the collector 2 furthest from the impeller 3 is the gas inlet of the blower, and the flow channel radius of the collector 2 at this gas inlet is R. The cylinder 1 has a cylindrical structure with an inner diameter of R.t R and R t The relationship between them satisfies: 0.18 ≤ R t / R≤0.24.

[0057] This utility model also utilizes the above-mentioned collector channel inlet radius R and the inner diameter R of the cylinder. t The relationship between them is: 0.18 ≤ R t With a / R≤0.24, the blower cylinder and collector can form the optimal fit size, which can minimize wind resistance, increase air volume, ensure uniform airflow distribution, avoid local turbulence or dead zones, and further improve heat exchange efficiency.

[0058] In some implementations...

[0059] A comb-tooth disk 17 is provided at the other axial end of the cylinder 1 away from the impeller 3. The comb-tooth disk 17 is located on the outer periphery of the rotating shaft 4. The comb-tooth disk 17 is fixed, and there is a gap between the radial inner periphery of the comb-tooth disk 17 and the rotating shaft 4 to form an auxiliary air inlet for air intake into the cylinder 1. The radius of the radial inner periphery of the comb-tooth disk 17 is R. x R t With R x The relationship between them satisfies: 0.22 ≤ R x / R t ≤0.24.

[0060] This invention also improves the air intake volume into the cylinder by using a comb-tooth disc structure at the other end of the cylinder's axial direction, which forms an auxiliary air intake port with a gap between it and the rotating shaft. This enhances the heat dissipation performance of the magnetic levitation blower. Furthermore, the radial inner circumference radius R of the comb-tooth disc is also increased. x With the inner diameter R of the cylinder t The relationship between them is set to satisfy: 0.22≤R x / R t ≤0.24, which can further ensure that the airflow leaking from the blower impeller can enter the blower evenly; secondly, it can ensure that the axial force is not too large.

[0061] In some implementations...

[0062] The comb tooth disk 17 has comb teeth protruding from its inner peripheral wall toward the rotating shaft 4. The free ends of the comb teeth do not contact the rotating shaft 4. There are multiple comb teeth, which are distributed at intervals along the circumference and / or axial direction of the comb tooth disk 17.

[0063] This invention also utilizes the comb tooth structure on the inner circumference of the comb tooth disk to create resistance to the gas entering the cylinder through the auxiliary air inlet, and increases the flow contact area between the gas and the comb tooth disk, thereby improving the heat exchange performance of the comb tooth disk and other structures.

[0064] In some implementations...

[0065] It also includes an axial bearing, which is disposed inside the cylinder 1. The axial bearing includes a first axial stator 14, a second axial stator 15, and a thrust disk 8. The thrust disk 8 is located between the first axial stator 14 and the second axial stator 15. A gas channel 19 is provided on the thrust disk 8 through its two axial end faces. One axial end of the gas channel 19 is opposite to the radial inner circumference of the first axial stator 14, and the other axial end of the gas channel 19 is opposite to the radial inner circumference of the second axial stator 15. The thrust disk 8 is also provided with... The cylinder 1 has a heat dissipation channel extending to its outer circumference. One end of the heat dissipation channel is connected to the gas channel 19, and the other end extends to the outer circumference of the thrust plate 8. The cylinder 1 is provided with a heat dissipation outlet 16, which is opposite to and connected to the heat dissipation channel, so that the gas entering the cylinder from the collector 2 is discharged from the cylinder 1 through the gas channel 19, the heat dissipation channel, and the heat dissipation outlet 16. The gas entering the cylinder from the comb plate 17 is also discharged from the cylinder 1 through the gas channel 19, the heat dissipation channel, and the heat dissipation outlet 16.

[0066] This is a further preferred structural form of the present invention, namely, a magnetic levitation axial bearing structure set inside the cylinder. The gas channel set on the thrust plate can guide the gas from the left and right sides of the thrust plate after cooling the motor and bearing into the interior of the thrust plate, and then guide the gas out of the thrust plate through the heat dissipation channel inside the thrust plate, and then guide the gas out of the heat dissipation outlet on the cylinder to the outside of the cylinder. Therefore, it can ensure that the gas continuously enters the interior of the cylinder from the air inlets at both ends of the cylinder, further improving the cooling efficiency of the motor and bearing inside the magnetic levitation blower.

[0067] In some implementations...

[0068] The flow area of ​​the heat dissipation outlet 16 is S. z The flow area of ​​the auxiliary air intake is S. x And there are S and S z and S x The relationship between them is: 0.62≤(S+S) x ) / S z ≤0.78.

[0069] This invention sets the heat dissipation outlet area and the flow area of ​​the air inlets at both ends to satisfy the above relationship: 0.62≤(S+S). x ) / S zWith a value of ≤0.78, it can balance the flow velocity and pressure loss on both sides, avoid turbulence and local high temperature, ensure uniform airflow distribution through area matching, maximize heat exchange, optimize design to reduce energy loss, and improve overall heat dissipation performance.

[0070] In some implementations...

[0071] In the projection plane of the longitudinal plane passing through the central axis of the rotating shaft 4, the position of the axial end face of the collector 2 away from the impeller 3 is defined as position 0, the total axial length of the magnetic levitation blower is L, the setting position of the comb plate 17 is position L, the distance between the motor stator 6 and the position defined as 0 along the axial direction of the rotating shaft 4 is 1 / 4L to 1 / 2L, and the distance between the axial bearing and the position defined as 0 along the axial direction of the rotating shaft 4 is 1 / 2L to 1 / 3L.

[0072] By optimizing the axial arrangement of the comb plate, motor stator, and axial bearing, this invention can optimize the distribution of airflow entering from both sides, ensuring uniform and effective heat dissipation for the motor and axial bearing, and further improving the cooling performance of the motor and axial bearing.

[0073] This invention provides a novel air-cooled heat dissipation channel for a magnetic levitation blower. The blower's internal structure mainly includes a blower cylinder and a cooling impeller. The blower cylinder has motor heat dissipation outlets and bearing heat dissipation outlets. The blower internally includes comb teeth, a thrust plate, an axial stator, an aluminum sleeve, a stator core, a shaft, a motor rotor, coils, front / rear radial rotors, and front / rear radial stators. It adopts a series-connected single-channel design, adds a leakage air inlet (auxiliary air inlet) on the blower side, and removes the bearing heat dissipation outlets. Its advantages are: fully utilizing air cooling, achieving a larger overall air volume output without changing the impeller speed, reducing the temperature at the thrust plate location, and thus lowering the overall machine temperature, resulting in better performance and application value for the blower.

[0074] This utility model's blower has two inlets: a cooling impeller inlet and a comb tooth leakage inlet (auxiliary air inlet). Air is mainly drawn in through the cooling impeller inlet, while some air easily leaks into the blower at the comb tooth. Air flows through the collector, enters through the cooling inlet, and then enters the blower through the stator channel. Air enters through the motor gap channel and the aluminum sleeve, cooling the blower and motor, carrying away heat. Air entering through the motor gap channel flows through the motor rotor and shaft, with some flowing into the thrust plate cooling channel to further reduce the temperature at the axial stator and rotor. Air entering through the aluminum sleeve carries away heat from the stator core and finally exits through the bearing cooling outlet above the thrust plate. Air entering through the leakage inlet enters the blower and flows directly into the front radial stator-rotor gap, effectively reducing the temperature there. It then flows through the thrust plate and axial stator plate, further reducing the temperature at the axial stator and rotor, and finally exits through the bearing cooling outlet.

[0075] This invention relates to a magnetic levitation blower cooling channel. Based on a parallel multi-channel design, it increases the leakage air intake on the blower side, modifies the parallel channel area, effectively reduces the temperature at the motor rotor, and places the bearing cooling outlet above the thrust plate, further improving cooling at the front radial rotor, lowering the overall machine temperature, and increasing the overall energy efficiency ratio. The new air-cooled cooling channel adds an exhaust at the thrust plate location, using it as a bearing-side outlet; increases the leakage on the blower side; and modifies the shape of the aluminum sleeve to increase the contact area with the airflow. Without changing the impeller speed, it can output a larger air volume, reducing the temperature of the motor and the front radial rotor, thus achieving the goal of lowering the overall machine temperature.

[0076] This utility model can solve the following technical problems:

[0077] 1. In the existing magnetic levitation blower structure, there are problems such as high flow resistance, poor air cooling effect, high temperature of internal components of the blower, and impaired motor life.

[0078] 2. In existing magnetic levitation blowers, the temperature of the motor and the front radial rotor is relatively high, which can easily lead to an increase in the temperature of the displacement sensor and affect the operation of the blower.

[0079] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this utility model should be included within the protection scope of this utility model. The above description is only a preferred embodiment of this utility model. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of this utility model, and these improvements and modifications should also be considered within the protection scope of this utility model.

Claims

1. A rotary machine characterized by: include: The rotating shaft (4), the cylinder (1), the impeller (3), the collector (2), the motor rotor (7), the motor stator (6), and the aluminum sleeve (5) are all located in the cylinder (1). The impeller (3) is arranged at one axial end of the rotating shaft (4), that is, at one axial end of the cylinder (1). The collector (2) is provided at the inlet of the impeller (3). The collector (2) is the first airflow inlet of the cylinder (1). The inlet flow area of ​​the collector (2) is S, so that airflow can be drawn in from the collector (2) through the impeller (3) and enter the cylinder (1). The motor rotor (7) is located on the inner circumference of the motor stator (6), and the outer circumference of the motor stator (6) is fixed to the cylinder (1) by the aluminum sleeve (5). There is an air gap between the motor rotor (7) and the motor stator (6), forming a first channel that allows airflow. The aluminum sleeve (5) is provided with gas through holes (18) extending through both ends along its axial direction, forming a second channel that allows airflow. In the cross-section of the rotating shaft (4), the total area of ​​the air gap is S. q The total area of ​​the gas through-hole (18) is S. lt And satisfy the relation 1.5≤S q / S lt ≤3, 1.2≤(S) q +S lt ) / S≤1.

5.

2. The rotating machinery according to claim 1, characterized in that: Within the projection plane of the axial end face of the aluminum sleeve (5), the outer diameter of the aluminum sleeve (5) is R. lt The gas through-hole (18) is a circular hole, and the distance between the center of the gas through-hole (18) and the central axis of the aluminum sleeve (5) is 0.9R. lt ~0.95R lt The radius of the gas through hole (18) is r, and there are multiple gas through holes (18). The multiple gas through holes (18) are distributed at intervals in the circumferential direction of the aluminum sleeve (5), and the number of gas through holes (18) n is 16-20.

3. The rotating machinery according to claim 1, characterized in that: The gas through hole (18) of the aluminum sleeve (5) is also provided with fins. One end of the fin is connected to the inner peripheral wall of the gas through hole (18), and the other end extends toward the central axis of the gas through hole (18) to form a free end.

4. The rotating machinery according to claim 3, characterized in that: In a projection plane of an axial end surface of the aluminum jacket (5), a radial height of the fin is h, and a diameter of the gas passage hole (18) is D lt , and the relationship 0.16 < h / D is satisfied lt <0.3; the fins are a plurality of, and the plurality of fins are spaced apart in both a circumferential direction and an axial direction of the gas passage hole (18).

5. The rotating machinery according to claim 1, characterized in that: The end of the collector (2) furthest from the impeller (3) is the gas inlet of the blower. The flow channel radius of the collector (2) at this gas inlet is R. The cylinder (1) has a cylindrical structure with an inner diameter of R. t R and R t The relationship between them satisfies: 0.18 ≤ R t / R≤0.

24.

6. The rotating machinery according to claim 5, characterized in that: A comb plate (17) is provided at the other axial end of the cylinder (1) away from the impeller (3). The comb plate (17) is located on the outer periphery of the rotating shaft (4). The comb plate (17) is fixed, and there is a gap between the radial inner periphery of the comb plate (17) and the rotating shaft (4) to form an auxiliary air inlet for air intake into the cylinder (1). The radius of the radial inner periphery of the comb plate (17) is R. x R t With R x The relationship between them satisfies: 0.22 ≤ R x / R t ≤0.

24.

7. The rotating machinery according to claim 6, characterized in that: The comb tooth disk (17) has comb teeth protruding from its inner peripheral wall toward the rotating shaft (4). The free ends of the comb teeth do not contact the rotating shaft (4), and there are multiple comb teeth, which are distributed at intervals along the circumference and / or axial direction of the comb tooth disk (17).

8. The rotating machinery according to claim 6, characterized in that: It also includes an axial bearing, which is disposed inside the cylinder (1). The axial bearing includes a first axial stator (14), a second axial stator (15), and a thrust disk (8). The thrust disk (8) is located between the first axial stator (14) and the second axial stator (15). A gas channel (19) is provided on the thrust disk (8) through its two axial ends. One axial end of the gas channel (19) is opposite to the space of the radial inner circumference of the first axial stator (14), and the other axial end of the gas channel (19) is opposite to the space of the radial inner circumference of the second axial stator (15). The thrust disk (8) is also provided with A heat dissipation channel extends through its outer circumference. One end of the heat dissipation channel is connected to the gas channel (19), and the other end extends through the outer circumference of the thrust plate (8). A heat dissipation outlet (16) is provided on the cylinder (1). The heat dissipation outlet (16) is opposite to and connected to the heat dissipation channel, so that the gas entering the cylinder from the collector (2) is discharged from the cylinder (1) through the gas channel (19), the heat dissipation channel, and the heat dissipation outlet (16). The gas entering the cylinder (1) from the comb plate (17) is also discharged from the cylinder (1) through the gas channel (19), the heat dissipation channel, and the heat dissipation outlet (16).

9. The rotating machinery according to claim 8, characterized in that: The flow area of ​​the heat dissipation outlet (16) is S. z The flow area of ​​the auxiliary air intake is S. x And there are S and S z and S x The relationship between them is: 0.62 ≤ (S + S) x ) / S z ≤0.

78.

10. The rotating machinery according to claim 8, characterized in that: In the projection plane of the longitudinal plane passing through the central axis of the rotating shaft (4), the position of the axial end face of the collector (2) away from the impeller (3) is defined as position 0, the total axial length of the rotating machinery is L, the setting position of the comb disc (17) is position L, the distance between the motor stator (6) and the position defined as 0 along the axial direction of the rotating shaft (4) is 1 / 4L to 1 / 2L, and the distance between the axial bearing and the position defined as 0 along the axial direction of the rotating shaft (4) is 1 / 2L to 1 / 3L.

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