Air blower with multiple sections of heat dissipation flow channels

Abstract

The utility model provides an air blower with multiple sections of heat dissipation flow channels, which comprises an air blower cylinder body, a first radial bearing, a stator and rotor assembly, an axial bearing and a second radial bearing, the first section is A1 * 3 + A2 * 2 + A3x + A4, and 5.4 < = A1 < = 6.1; a2 is greater than or equal to 11.3 and less than or equal to 12.7; a2 is greater than or equal to-5.5 and less than or equal to-6.5; 0.1 < = A2 < = 0.4; in the second part section, y is equal to B1 * 2 + B2x + B3, and B1 is greater than or equal to-0.1 and less than or equal to 1.2; b2 is greater than or equal to-2.1 and less than or equal to-0.4; the third section is as follows: y is equal to C1 < x > 3 + C2x < 2 > + C3x + C4, and C1 is greater than or equal to 18.1 and less than or equal to 20.5; c2 is not less than-33.5 and not more than-29.4; 12 < = C3 < = 13.9; 0 < = C4 < = 0.3. According to the air blower, the problems that an existing air blower is poor in heat dissipation performance and uneven in internal temperature distribution can be solved.

Description

Technical Field

[0001] The utility model relates to the technical field of blowers, in particular to a blower with multi-section heat dissipation channels. Background Art

[0002] When a magnetic levitation blower is operating, a large amount of heat is generated by the internal motor stator, rotor and bearings. When the temperatures of the motor stator, rotor and bearings are too high, the operating stability of the blower will decline. Therefore, it is necessary to dissipate heat inside the magnetic levitation blower. Existing magnetic levitation blowers use external water cooling, external air cooling or built-in cooling fans and other methods to dissipate heat from the blower. When using the external water cooling or air cooling heat dissipation method, the heat dissipation device occupies a large area and has high investment and maintenance costs. When using a built-in cooling fan for heat dissipation, the heat dissipation performance is extremely susceptible to the influence of the flow channel structure. The cooling air easily flows out from the flow channel with smaller air resistance, and the temperature of the cooling air gradually increases along the process, resulting in poor heat dissipation effect of the bearings located downstream of the flow channel and affecting the normal operation of the blower.

[0003] Due to the technical problems of poor heat dissipation performance, uneven temperature distribution inside the blower and large temperature difference existing in the magnetic levitation blower in the prior art, the utility model researches and designs a blower with multi-section heat dissipation channels. Summary of the Utility Model

[0004] Therefore, the technical problem to be solved by the utility model is to overcome the defects of poor heat dissipation performance, uneven temperature distribution inside the blower and large temperature difference existing in the blowers in the prior art, so as to provide a blower with multi-section heat dissipation channels.

[0005] To solve the above problems, the utility model provides a blower with multi-section heat dissipation channels, which includes:

[0006] A blower cylinder body, a first radial bearing, a stator-rotor assembly, an axial bearing and a second radial bearing. One axial end of the blower cylinder body has a gas inlet, and the blower cylinder body is also provided with a bearing air outlet, which is arranged at the other axial end of the blower cylinder body or on the side surface of the blower cylinder body relative to the gas inlet and close to the other axial end of the blower cylinder body.

[0007] The first radial bearing, the stator-rotor assembly, the axial bearing and the second radial bearing are all arranged inside the blower cylinder body. Along the direction of air flow and along the axis of the blower, the first radial bearing, the stator-rotor assembly, the axial bearing and the second radial bearing are arranged at intervals in sequence.

[0008] The axial end face of the first radial bearing facing the stator-rotor assembly is the first interface, and the axial end face of the axial bearing facing the stator-rotor assembly is the second interface; along the axis direction of the blower, the partial section between the gas inlet and the first interface is the first partial section, the partial section between the first interface and the second interface is the second partial section, and the partial section between the second interface and the radial section where the bearing air outlet is located is the third partial section;

[0009] In the radial section, for the first partial section: the central axis of the blower is the x-axis, the radial section of the gas inlet is the first reference plane at x = 0, and the direction from the first reference plane to the first radial bearing is the positive direction of the x-axis. In the radial section at the abscissa X on the x-axis, the total flow area of the gas passage is Y, x = X / X max , y = Y / Y max , and there is a curve relationship between x and y in the first partial section: y = A1x 3 + A2x 2 + A3x + A4, where 5.4 ≤ A1 ≤ 6.1; -11.3 ≤ A2 ≤ -12.7;

[0010] -5.5 ≤ A2 ≤ -6.5; 0.1 ≤ A2 ≤ 0.4, X max is the maximum value of X in the first partial section, Y max is the maximum value of Y in the first partial section;

[0011] For the second partial section: the central axis of the blower is the x-axis, the first interface is the second reference plane at x = 0, and the direction from the second reference plane to the axial bearing is the positive direction of the x-axis. In the radial section at the abscissa X on the x-axis, the total flow area of the gas passage is Y, x = X / X max , y = Y / Y max , and there is a curve relationship between x and y in the second partial section: y = B1x 2 + B2x + B3, where -0.1 ≤ B1 ≤ 1.2; -2.1 ≤ B2 ≤ -0.4; 0.5 ≤ B3 ≤ 1, X max is the maximum value of X in the second partial section, Y max is the maximum value of Y in the second partial section;

[0012] For the third partial section: the central axis of the blower is the x-axis, the second interface is the third reference plane at x = 0, and the direction from the third reference plane to the second radial bearing is the positive direction of the x-axis. In the radial section at the abscissa X on the x-axis, the total flow area of the gas passage is Y, x = X / X max , y = Y / Y max, and there is a third part where x and y satisfy a curve relationship within the segment: y = C1x 3 + C2x 2 + C3x + C4, where 18.1 ≤ C1 ≤ 20.5; -33.5 ≤ C2 ≤ -29.4; 12 ≤ C3 ≤ 13.9; 0 ≤ C4 ≤ 0.3, X max is the maximum value of X within the third part segment, and Y max is the maximum value of Y within the third part segment.

[0013] In some embodiments,

[0014] The total axial length of the blower cylinder is L, the outer radius of the blower cylinder is R1, and the total outer surface area of the blower cylinder is A t ;

[0015] The flow cross-sectional area of the gas inlet is A j , and there is a relationship between A j and A t as follows: 0.0045 ≤ A j / A t ≤ 0.01.

[0016] In some embodiments,

[0017] The stator-rotor assembly includes a motor rotor and a motor stator. A first heat dissipation air duct is provided on the motor stator, and a second heat dissipation air duct for air flow is provided on the blower cylinder. After the cooling air passes through the air gap between the motor stator and rotor, it is divided into two paths. One path flows out from the first heat dissipation air duct on the motor stator, and one path passes through the axial bearing and the second radial bearing and then flows out from the second heat dissipation air duct. The minimum flow cross-sectional area of the first heat dissipation air duct is A1, and the minimum flow cross-sectional area of the second heat dissipation air duct is A2. The relationship between A1 and A2 is: 1 ≤ A1 / A2 ≤ 13, and the relationship between Aj and A2 is: 0.8 ≤ Aj / A2 ≤ 0.94.

[0018] In some embodiments,

[0019] A first ventilation hole is axially penetrated through the motor stator to form the first heat dissipation air duct. The total area of multiple first ventilation holes is A4, and the relationship between A4 and A2 is 1.5 ≤ A4 / A2 ≤ 3.

[0020] In some embodiments,

[0021] There is a first gap between the motor stator and the motor rotor. The axial bearing includes a front axial bearing, a rear axial bearing and a thrust disc. The front axial bearing, the thrust disc and the rear axial bearing are arranged in sequence along the axial direction. The thrust disc is located between the front axial bearing and the rear axial bearing. The first radial bearing has a second gap along the axial direction. The rear axial bearing has a third gap. The front axial bearing has a fourth gap. The second radial bearing has a fourth gap. The ranges of the first gap, the second gap, the third gap and the fourth gap are all within 0.002R1 to 0.01R1.

[0022] In some embodiments,

[0023] On the blower cylinder body, there is a motor air outlet disposed opposite to and communicating with the heat dissipation air duct one of the motor stator in the radial direction. The motor air outlet penetrates through the inner and outer walls of the blower cylinder body. After the air flow passes through the channel between the motor stator and the motor rotor, a part of it passes through the heat dissipation air duct one and is discharged from the motor air outlet.

[0024] In some embodiments,

[0025] There are multiple bearing air outlets, and the multiple bearing air outlets are spaced apart on the outer peripheral surface of the blower cylinder body. The total area of the multiple bearing air outlets is A o1 , and there are also multiple motor air outlets. The multiple motor air outlets are spaced apart in the circumferential direction of the blower cylinder body. The total area of the multiple motor air outlets is A o2 , A o1 The relationship with A t is: 0.03 ≤ A o1 / A t ≤ 0.08, A o1 The relationship with A o2 is 0.9 ≤ A o1 / A o2 ≤ 1.1.

[0026] In some embodiments,

[0027] Inside the blower cylinder body, and between the first radial bearing and the gas inlet, there is also a flow guiding structure. The flow guiding structure is a circular disc-shaped structure, and there are multiple second ventilation holes axially penetrating through it. The total area of the multiple second ventilation holes is A3, and the relationship between A3 and A2 is: 1.5 ≤ A3 / A2 ≤ 3.

[0028] In some embodiments,

[0029] It further includes a rotating shaft and a cooling impeller. At least part of the structure of the rotating shaft is disposed inside the blower cylinder, and the first radial bearing, the stator-rotor assembly, the axial bearing, and the second radial bearing are all sleeved on the outer periphery of the rotating shaft. The cooling impeller is disposed at an axial end of the rotating shaft facing the gas inlet so as to rotate integrally with the rotating shaft, and the cooling impeller is located between the gas inlet and the guiding structure.

[0030] The blower with multiple-section heat dissipation channels provided by the present utility model has the following beneficial effects:

[0031] By adopting the structural form of arranging multiple-section heat dissipation channels inside the blower in the present utility model, especially the first partial section mainly for cooling the first radial bearing between the gas outlet and the first radial bearing, the second partial section mainly for cooling the stator-rotor assembly, and the third partial section mainly for cooling the axial bearing and the second radial bearing, and setting the axial position X and the total gas passage area Y of the three different partial sections to satisfy y = A1x 3 + A2x 2 + A3x + A4, where 5.4 ≤ A1 ≤ 6.1; -11.3 ≤ A2 ≤ -12.7; -5.5 ≤ A2 ≤ -6.5; 0.1 ≤ A2 ≤ 0.4, y = B1x 2 + B2x + B3, where -0.1 ≤ B1 ≤ 1.2; -2.1 ≤ B2 ≤ -0.4; 0.5 ≤ B3 ≤ 1, and y = C1x 3 + C2x 2 + C3x + C4, where 200654 ≤ C1 ≤ 226238; 18.1 ≤ C1 ≤ 20.5; -33.5 ≤ C2 ≤ -29.4; 12 ≤ C3 ≤ 13.9; 0 ≤ C4 ≤ 0.3, it is possible to effectively design a more reasonable gas flow channel inside the blower, form a new type of blower, reasonably arrange the cross-sectional area of the air duct, make the air volume distribution of the bearings and the stator-rotor of the motor more reasonable, give full play to the cooling effect of the gas on each component of the blower, improve the heat exchange efficiency, reduce the temperature of the bearing parts and the stator and rotor of the motor inside the blower, achieve the purpose of enhancing the operation reliability of the blower, play the role of reducing the temperature difference inside the blower and making the temperature field distribution more uniform, solve the problems of poor heat dissipation performance of the existing blower, uneven temperature distribution inside the blower, and large temperature difference, and ensure the stable operation of the blower. In addition, through the design of at least 3 internal channels as described above, the present utility model can also reduce the pressure loss of the gas inside the blower. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] Figure 1 is the external shape structure diagram of the blower with multiple-section heat dissipation channels of the present utility model;

[0033] Figure 2 is a longitudinal sectional view of the blower with multi-section heat dissipation channels of the present utility model;

[0034] Figure 3 is a heat dissipation simulation temperature field diagram of the blower with multi-section heat dissipation channels of the present utility model;

[0035] Figure 4 is a three-dimensional structure diagram of the flow guiding structure inside the blower of the present utility model;

[0036] Figure 5 is a three-dimensional structure diagram of the motor stator of the present utility model (heat dissipation air duct one);

[0037] Figure 6 is a three-dimensional structure diagram of the front axial bearing of the present utility model;

[0038] Figure 7 is a three-dimensional structure diagram of the blower cylinder of the present utility model (heat dissipation air duct two).

[0039] The reference numerals are shown as:

[0040] 1. Heat dissipation impeller collector; 2. Motor air outlet; 3. Bearing air outlet; 4. Heat dissipation impeller; 5. First radial bearing; 6. Flow guiding structure; 61. Second ventilation hole; 200. Stator-rotor assembly; 7. Motor rotor; 8. Motor stator; 300. Axial bearing; 9. Rear axial bearing; 10. Front axial bearing; 11. Second radial bearing; 12. Blower cylinder; 13. Heat dissipation air duct two; 14. Heat dissipation air duct one; 15. Rotating shaft; 100. Gas inlet. Specific embodiments

[0041] Next, the technical solutions in the embodiments of the present utility model will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present utility model. Obviously, the described embodiments are only a part of the embodiments of the present utility model, rather than all the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and in no way limits the present utility model and its application or use. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative efforts belong to the scope of protection of the present utility model.

[0042] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless otherwise clearly specified in the context, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "include" and / or "comprise" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0043] Unless otherwise specifically stated, the relative arrangements of components and steps, numerical expressions, and numerical values set forth in these embodiments do not limit the scope of the present utility model. At the same time, it should be understood that for the convenience of description, the dimensions of the various parts shown in the drawings are not drawn according to the actual proportional relationship. Technologies, methods, and devices known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, the said technologies, methods, and devices should be regarded as part of the authorization specification. In all the examples shown and discussed here, any specific value should be construed as merely exemplary and not as a limitation. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that like reference numerals and letters denote like items in the following drawings, and thus, once an item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

[0044] In the description of the present utility model, it should be understood that the orientation or positional relationships indicated by orientation terms such as "front, rear, upper, lower, left, right", "lateral, vertical, perpendicular, horizontal", and "top, bottom", etc. are generally based on the orientation or positional relationships shown in the drawings, and are only for the convenience of describing the present utility model and simplifying the description. Without contrary description, these orientation terms do not indicate and imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and thus cannot be construed as limiting the protection scope of the present utility model; the orientation terms "inside, outside" refer to the inside and outside relative to the contour of each component itself.

[0045] For the convenience of description, spatial relative terms such as "above...", "over...", "on the upper surface of...", "above-mentioned", etc. can be used here to describe the spatial positional relationships of a device or feature shown in the drawings with other devices or features. It should be understood that the spatial relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the drawings. For example, if the device in the drawing is inverted, the device described as "above other devices or structures" or "over other devices or structures" will then be positioned "below other devices or structures" or "under other devices or structures". Thus, the exemplary term "above..." can include both the orientations of "above..." and "below...". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and corresponding interpretations should be made for the spatial relative descriptions used here.

[0046] In addition, it should be noted that the use of words such as "first", "second", etc. to limit components is only for the convenience of distinguishing the corresponding components. Without additional statement, the above words have no special meaning, and thus cannot be construed as limiting the protection scope of the present utility model.

[0047] As shown Figure 1-7 in the figure, the present utility model provides a blower (preferably a magnetic levitation blower) with multiple-section heat dissipation channels, which includes:

[0048] a blower cylinder body 12, a first radial bearing 5, a stator-rotor assembly 200, an axial bearing 300 and a second radial bearing 11. One axial end of the blower cylinder body 12 has a gas inlet 100. The blower cylinder body 12 is also provided with a bearing air outlet 3, and the bearing air outlet 3 is arranged at the other axial end of the blower cylinder body 12 or on the side surface of the blower cylinder body 12 relative to the gas inlet 100 and close to the other axial end of the blower cylinder body 12.

[0049] The first radial bearing 5, the stator-rotor assembly 200, the axial bearing 300 and the second radial bearing 11 are all arranged inside the blower cylinder body 12. Along the direction of air flow and along the axis of the blower, the first radial bearing 5, the stator-rotor assembly 200, the axial bearing 300 and the second radial bearing 11 are arranged at intervals in sequence.

[0050] The axial end face of the first radial bearing 5 facing the stator-rotor assembly 200 is a first interface, and the axial end face of the axial bearing 300 facing the stator-rotor assembly 200 is a second interface; along the axis direction of the blower, the partial section between the gas inlet 100 and the first interface is a first partial section, the partial section between the first interface and the second interface is a second partial section, and the partial section between the second interface and the radial section where the bearing air outlet 3 is located is a third partial section;

[0051] In the radial section, for the first partial section: the central axis of the blower is the x-axis, the radial section of the gas inlet 100 is the first reference plane at x = 0, and the direction from the first reference plane to the first radial bearing 5 is the positive direction of the x-axis. In the radial section at the abscissa X on the x-axis, the total flow area of the gas channel is Y, x = X / X max , y = Y / Y max , and there is a curve relationship between x and y in the first partial section: y = A1x 3 + A2x 2 + A3x + A4, where 5.4 ≤ A1 ≤ 6.1; -11.3 ≤ A2 ≤ -12.7; -5.5 ≤ A2 ≤ -6.5; 0.1 ≤ A2 ≤ 0.4, X max is the maximum value of X in the first partial section, and Y max is the maximum value of Y in the first partial section;

[0052] Second part segment: The central axis of the blower is the x-axis. Taking the first interface as the second reference plane where x = 0, and taking the direction from the second reference plane to the axial bearing 300 as the positive direction of the x-axis. In the radial cross-section at the abscissa X on the x-axis, the total flow area of the gas passage is Y, x = X / X max , y = Y / Y max , and in the second part segment, the relationship between x and y satisfies the curve: y = B1x 2 + B2x + B3, where -0.1 ≤ B1 ≤ 1.2; -2.1 ≤ B2 ≤ -0.4; 0.5 ≤ B3 ≤ 1, X max is the maximum value of X in the second part segment, Y max is the maximum value of Y in the second part segment;

[0053] Third part segment: The central axis of the blower is the x-axis. Taking the second interface as the third reference plane where x = 0, and taking the direction from the third reference plane to the second radial bearing 11 as the positive direction of the x-axis. In the radial cross-section at the abscissa X on the x-axis, the total flow area of the gas passage is Y, x = X / X max , y = Y / Y max , and in the third part segment, the relationship between x and y satisfies the curve: y = C1x 3 + C2x 2 + C3x + C4, where 18.1 ≤ C1 ≤ 20.5; -33.5 ≤ C2 ≤ -29.4; 12 ≤ C3 ≤ 13.9; 0 ≤ C4 ≤ 0.3, X max is the maximum value of X in the third part segment, Y max is the maximum value of Y in the third part segment.

[0054] In the present utility model, by adopting the structural form of arranging multiple heat dissipation flow channels inside the blower, especially the first part segment mainly for cooling the first radial bearing between the gas outlet and the first radial bearing, the second part segment mainly for cooling the stator-rotor assembly, and the third part segment mainly for cooling the axial bearing and the second radial bearing, and for the three different part segments, setting the relationship between the axial position X and the total flow area Y of the gas passage to satisfy y = A1x 3 + A2x 2 + A3x + A4, where 5.4 ≤ A1 ≤ 6.1; -11.3 ≤ A2 ≤ -12.7; -5.5 ≤ A2 ≤ -6.5; 0.1 ≤ A2 ≤ 0.4, y = B1x 2 + B2x + B3, where -0.1 ≤ B1 ≤ 1.2; -2.1 ≤ B2 ≤ -0.4; 0.5 ≤ B3 ≤ 1, and y = C1x 3 + C2x 2+ C3x + C4, where 18.1 ≤ C1 ≤ 20.5; -33.5 ≤ C2 ≤ -29.4; 12 ≤ C3 ≤ 13.9; 0 ≤ C4 ≤ 0.3, which can effectively design a more reasonable internal gas flow path of the blower, form a new type of blower, reasonably arrange the cross-sectional area of the air duct, make the air volume distribution of the bearing and the stator and rotor of the motor more reasonable, can give full play to the cooling effect of the gas on each component of the blower, improve the heat exchange efficiency, reduce the temperature of the internal bearing parts of the blower and the stator and rotor of the motor, and achieve the purpose of enhancing the operation reliability of the blower, play the role of reducing the internal temperature difference of the blower and making the temperature field distribution more uniform, solve the problem that the existing blower has poor heat dissipation performance, resulting in uneven internal temperature distribution and large temperature difference of the blower, and ensure the stable operation of the blower. In addition, through the design of at least the above 3 internal channels, the present invention can also reduce the pressure loss of the gas inside the blower.

[0055] The present invention provides a high heat dissipation performance blower with a parallel heat dissipation flow path. The internal structure of the blower is complex. Only the main components are provided here. For a relatively simplified blower, it mainly includes a blower cylinder body and a heat dissipation impeller. The heat dissipation gas outlets are distributed on the blower cylinder body. The inside of the blower cylinder body mainly includes a stator core, a rotating shaft, a motor rotor, a thrust disk, and a coil, and adopts a heat dissipation gas channel with one-way inlet and two-way outlet. By normalizing the areas and corresponding positions of each part, the present invention can obtain the following relationships: The first part satisfies the curve relationship: y = A1x 3 + A2x 2 + A3x + A4 (5.4 ≤ A1 ≤ 6.1; -11.3 ≤ A2 ≤ -12.7; -5.5 ≤ A2 ≤ -6.5; 0.1 ≤ A2 ≤ 0.4). The cross-sectional area of the gas channel first decreases and then increases with the change of position. The decreasing part accelerates the heat dissipation gas, and the increasing part enables the gas to pass smoothly. The decreasing part accelerates the heat dissipation gas, and the changing cross-sectional size can enhance the air flow disturbance and improve the heat exchange performance, reaching the second part; The second part satisfies the curve relationship: y = B1x 2 + B2x + B3 (-0.1 ≤ B1 ≤ 1.2; -2.1 ≤ B2 ≤ -0.4; 0.5 ≤ B3 ≤ 1). The cross-sectional area of the gas channel gradually increases from the air gap between the stator and rotor of the motor through the first heat dissipation air duct to the air outlet of the motor, aiming to reduce the flow resistance of the cooling air; The third part satisfies the curve relationship: y = C1x 3 + C2x 2+C3x + C4 (18.1 ≤ C1 ≤ 20.5; -33.5 ≤ C2 ≤ -29.4; 12 ≤ C3 ≤ 13.9; 0 ≤ C4 ≤ 0.3). The gas passage sequentially passes through the rear axial bearing 9, the front axial bearing 10, the front radial bearing (the second radial bearing 11), and the second heat dissipation air duct 13 from the electronic stator-rotor air gap to the bearing air outlet 3. The area first increases and then decreases. The increasing part enables the smooth passage of the gas, and the decreasing part accelerates the heat dissipation gas. Moreover, the changing cross-sectional size can enhance the air flow disturbance, improve the heat transfer performance, and achieve the enhanced heat transfer effect on the rear axial bearing, the front axial bearing, and the front radial bearing.

[0056] The technical solution of the present utility model has been verified by CFD numerical calculation. Refer to Figure 5 the CFD numerical calculation result diagram of the internal temperature field of the blower in

[0057] In some embodiments,

[0058] The total axial length of the blower cylinder 12 is L, the outer radius of the blower cylinder 12 is R1, and the total outer surface area of the blower cylinder 12 is A t ;

[0059] The flow cross-sectional area of the gas inlet 100 is A j , and there is a relationship between A j and A t as follows: 0.0045 ≤ A j / A t ≤ 0.01.

[0060] In the present utility model, by setting the heat dissipation gas inlet at the top end of the motor, i.e., one axial end of the rotating shaft, and the relationship between the heat dissipation gas inlet area A j and A t satisfies: 0.0045 ≤ A j / A t ≤ 0.01, it can not only increase the flow rate of the heat exchange air flow, but also avoid causing large losses, prevent the impeller from not functioning due to too small a heat dissipation gas inlet area, resulting in too small a gas flow rate entering the blower interior, and at the same time prevent the gas flow velocity from slowing down and causing large losses when the heat dissipation gas inlet area is too large.

[0061] In some embodiments,

[0062] The stator-rotor assembly 200 includes a motor rotor 7 and a motor stator 8. A first heat dissipation air duct 14 is provided on the motor stator 8, and a second heat dissipation air duct 13 for air flow is provided on the blower cylinder 12. After the cooling air passes through the air gap between the motor stator and rotor, it is divided into two paths. One path flows out from the first heat dissipation air duct 14 on the motor stator 8, and the other path passes through the axial bearing 300 and the second radial bearing 11 and then flows out from the second heat dissipation air duct 13. The minimum flow cross-sectional area of the first heat dissipation air duct 14 is A1, and the minimum flow cross-sectional area of the second heat dissipation air duct 13 is A2. The relationship between A1 and A2 is: 1 ≤ A1 / A2 ≤ 13, and the relationship between Aj and A2 is: 0.8 ≤ Aj / A2 ≤ 0.94.

[0063] It can not only reduce the residual gas inside the blower, reduce the internal pressure loss, but also improve the heat dissipation and cooling effect. That is, it can effectively avoid the situation that the too small outlet area of the heat dissipation gas will cause the gas accumulation inside the blower and result in too large internal pressure loss. It can also prevent the adverse effect that the too large outlet area of the heat dissipation gas will cause the heat dissipation gas to escape before fully playing the cooling role. It makes the air volume distribution more reasonable and improves the heat dissipation and resistance performance of the flow channel.

[0064] In some embodiments,

[0065] A first ventilation hole is axially penetrated through the motor stator 8 to form the first heat dissipation air duct 14. The total area of multiple first ventilation holes is A4. The relationship between A4 and A2 is 1.5 ≤ A4 / A2 ≤ 3. It can enable the heat dissipation gas to conduct convective heat transfer through the wall surface of the ventilation hole, be used to cool the stator core and coil, and at the same time discharge the heat dissipation gas.

[0066] In some embodiments,

[0067] There is a first gap between the motor stator 8 and the motor rotor 7. The axial bearing 300 includes a front axial bearing 10, a rear axial bearing 9 and a thrust disc. The front axial bearing 10, the thrust disc and the rear axial bearing 9 are arranged in sequence along the axial direction. The thrust disc is located between the front axial bearing 10 and the rear axial bearing 9. The first radial bearing 5 has a second gap along the axial direction, the rear axial bearing 9 has a third gap, the front axial bearing 10 has a fourth gap, and the second radial bearing 11 has a fourth gap. The ranges of the first gap, the second gap, the third gap and the fourth gap are all within 0.002R1 to 0.01R1. It can form appropriate sizes of the motor stator-rotor gap and bearing gap. On the premise of ensuring the motor efficiency and the magnetic bearing support force, it can make the gap have good flow resistance performance, enable a certain flow rate of heat dissipation gas to flow through and take away the heat dissipated by the bearing and the motor, and reduce the temperature at the bearing and the motor.

[0068] In some embodiments,

[0069] On the blower cylinder body 12, a motor air outlet 2 is provided opposite to and communicating with the first heat dissipation air duct 14 of the motor stator 8 in the radial direction. The motor air outlet 2 penetrates the inner and outer walls of the blower cylinder body 12. After the air flow passes through the channel between the motor stator 8 and the motor rotor 7, a part of the air flow passes through the first heat dissipation air duct 14 and is discharged from the motor air outlet 2.

[0070] This is the preferred air path structure and flow pattern of the present utility model, that is, after passing through the air gap between the stator and the rotor, it is divided into two paths. One path further cools the stator and the coil through the first heat dissipation air duct of the motor stator, and the other path flows through the axial bearing and the front radial bearing to cool them, which can further improve the cooling and heat dissipation performance.

[0071] In some embodiments,

[0072] There are a plurality of bearing air outlets 3, and the plurality of bearing air outlets 3 are spaced apart on the outer peripheral surface of the blower cylinder body 12. The total area of the plurality of bearing air outlets 3 is A o1 There are also a plurality of motor air outlets 2, and the plurality of motor air outlets 2 are spaced apart in the circumferential direction of the blower cylinder body 12. The total area of the plurality of motor air outlets 2 is A o2 A o1 The relationship between A t and A o1 / A t is: 0.03 ≤ A o1 / A o2 ≤ 0.08, and the relationship between A o1 / A o2 is 0.9 ≤ A

[0073] This can ensure the smooth flow of air, avoid the situation that the outlet area is too large and occupies space, prevent the situation that the outlet cross-sectional area is too small and hinders the air flow, and prevent the situation that the outlet cross-sectional area is too large and is not conducive to layout and occupies space.

[0074] In some embodiments,

[0075] A flow guide structure 6 is provided within the blower barrel 12 and between the first radial bearing 5 and the gas inlet 100. The flow guide structure 6 is a circular disc-shaped structure having a plurality of second ventilation holes 61 (preferably 8 to 24) extending therethrough in the axial direction. The total area of the plurality of second ventilation holes 61 is A3, and the relationship between A3 and A2 is: 1.5≤A3 / A2≤3. The flow guide structure can be used to guide the direction of the airflow, so that the airflow discharged from the heat dissipation impeller changes from radial flow to axial flow. After the gas flows through the ventilation holes, the rectification effect of the ventilation holes can reduce the degree of gas flow turbulence. By providing a larger total cross-sectional area of the ventilation holes, the pressure loss of the gas flow is reduced. When the gas flows in the ventilation holes, it can also undergo convective heat exchange through the surface of the ventilation holes, which is beneficial to the heat dissipation of the rear radial bearing of the blower.

[0076] In some embodiments,

[0077] It also includes a rotating shaft 15 and a heat dissipation impeller 4, at least part of the structure of the rotating shaft 15 is arranged in the blower barrel 12, and the first radial bearing 5, the stator and rotor assembly 200, the axial bearing 300 and the second radial bearing 11 are all sleeved on the outer periphery of the rotating shaft 15; the heat dissipation impeller 4 is arranged at one axial end of the rotating shaft 15 facing the gas inlet 100 so that it can rotate integrally with the rotating shaft 15, and the heat dissipation impeller 4 is located between the gas inlet 100 and the guide structure 6.

[0078] When the blower of the present invention is running, the heat dissipation impeller 4 rotates and draws external air into the blower. The cooling air flows along the flow channel in sequence through the gap between the guide structure 6, the first radial bearing 5, the motor rotor 7 and the motor stator 8, and then is divided into two paths. One path passes through the heat dissipation air duct 14 to further cool the motor stator 8 and the motor rotor 7, and then flows out from the motor air outlet 2. At the same time, the other path passes through the heat dissipation air duct 2 13 to cool the rear axial bearing 9, the front axial bearing 10 and the front radial bearing (the first radial bearing 5), and then flows out from the bearing air outlet 3.

[0079] In some embodiments,

[0080] The outer radius of the blower barrel 12 is R k The total area of the outer surface of the blower cylinder 12 is A k The inner radius of the blower cylinder 12 is R kn , when the blower cylinder inner radius is different in different blower parts, in order to ensure the overall strength of the blower, the outer radius R of the blower cylinder 12 is k The inner radius R of the blower cylinder 12 kn Satisfy between: 1.05≤R k / R kn ≤1.1.

[0081] The blower cylinder of the present utility model has a certain thickness. The housing with this thickness can play a role in protecting the internal components of the blower. The thickness of the blower cylinder varies along the axial direction of the blower. Here, the thickness is the ratio of the inner and outer diameters at the thinnest part of the blower housing, which can improve the strength of the blower. If the thickness is too thin, it may lead to insufficient strength in some parts of the blower.

[0082] The above are only the preferred embodiments of the present utility model and are not intended to limit the present utility model. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present utility model shall be included within the protection scope of the present utility model. The above is only the preferred implementation manner of the present utility model. It should be noted that for those of ordinary skill in the art in this technical field, without departing from the technical principle of the present utility model, several improvements and variations can be made, as well as the mutual combination of embodiments. These improvements and variations should also be regarded as within the protection scope of the present utility model.

Claims

1. A blower with multi-section heat dissipation channels, characterized in that: Comprising: A blower cylinder body (12), a first radial bearing (5), a stator-rotor assembly (200), an axial bearing (300) and a second radial bearing (11). One axial end of the blower cylinder body (12) has a gas inlet (100). The blower cylinder body (12) is further provided with a bearing air outlet (3), and the bearing air outlet (3) is arranged at the other axial end of the blower cylinder body (12) or on the side surface of the blower cylinder body (12) that is closer to the other axial end of the blower cylinder body (12) relative to the gas inlet (100). The first radial bearing (5), the stator-rotor assembly (200), the axial bearing (300) and the second radial bearing (11) are all arranged inside the blower cylinder body (12). Along the direction of air flow and along the axis of the blower, the first radial bearing (5), the stator-rotor assembly (200), the axial bearing (300) and the second radial bearing (11) are arranged at intervals in sequence. The axial end face of the first radial bearing (5) facing the stator-rotor assembly (200) is a first interface, and the axial end face of the axial bearing (300) facing the stator-rotor assembly (200) is a second interface; along the axis direction of the blower, the partial section between the gas inlet (100) and the first interface is a first partial section, the partial section between the first interface and the second interface is a second partial section, and the partial section between the second interface and the radial section where the bearing air outlet (3) is located is a third partial section. In the radial section, for the first partial section: the central axis of the blower is the x-axis, the radial section of the gas inlet (100) is the first reference plane at x = 0, and the direction from the first reference plane to the first radial bearing (5) is the positive direction of the x-axis. In the radial section at the abscissa X on the x-axis, the total flow area of the gas passage is Y, x = X / X max , y = Y / Y max , and in the first partial section, there is a curve relationship between x and y: y = A1x 3 + A2x 2 + A3x + A4, where 5.4 ≤ A1 ≤ 6.1; -11.3 ≤ A2 ≤ -12.7; -5.5 ≤ A2 ≤ -6.5; 0.1 ≤ A2 ≤ 0.4, X max is the maximum value of X in the first partial section, Y max is the maximum value of Y in the first partial section; Second part segment: The central axis of the blower is the x-axis. The second reference plane where x = 0 is the first interface plane, and the positive direction of the x-axis is the direction from the second reference plane to the axial bearing (300). In the radial cross-section at the abscissa X on the x-axis, the total flow area of the gas passage is Y, x = X / X max , y = Y / Y max , and there is a curve relationship between x and y in the second part segment: y = B1x 2 + B2x + B3, where -0.1 ≤ B1 ≤ 1.2; -2.1 ≤ B2 ≤ -0.4; 0.5 ≤ B3 ≤ 1, X max is the maximum value of X in the second part segment, Y max is the maximum value of Y in the second part segment; Third part segment: The central axis of the blower is the x-axis. The third reference plane with the second interface at x = 0, and the positive direction of the x-axis is the direction from the third reference plane to the second radial bearing (11). In the radial cross-section at the abscissa X on the x-axis, the total flow area of the gas passage is Y, x = X / X max , y = Y / Y max , and there is a curve relationship between x and y in the third part segment: y = C1x 3 + C2x 2 + C3x + C4, where 18.1 ≤ C1 ≤ 20.5; -33.5 ≤ C2 ≤ -29.4; 12 ≤ C3 ≤ 13.9; 0 ≤ C4 ≤ 0.3, X max is the maximum value of X in the third part segment, Y max is the maximum value of Y in the third part segment.

2. The blower with multi-section heat dissipation channels according to claim 1, characterized in that: The total axial length of the blower cylinder (12) is L, the outer radius of the blower cylinder (12) is R1, and the total outer surface area of the blower cylinder (12) is A t ; The flow cross-sectional area of the gas inlet (100) is A j , and there is A j and A t The relationship between them is: 0.0045 ≤ A j / A t ≤ 0.

01.

3. The blower with multi-section heat dissipation channels according to claim 2, characterized in that: The stator-rotor assembly (200) includes a motor rotor (7) and a motor stator (8). The motor stator (8) is provided with a first heat dissipation air duct (14), and the blower cylinder body (12) is provided with a second heat dissipation air duct (13) for air flow. After the cooling air passes through the air gap between the motor stator and the motor rotor, it is divided into two paths. One path flows out from the first heat dissipation air duct (14) on the motor stator (8), and the other path passes through the axial bearing (300) and the second radial bearing (11) and then flows out from the second heat dissipation air duct (13). The minimum flow cross-sectional area of the first heat dissipation air duct (14) is A1, and the minimum flow cross-sectional area of the second heat dissipation air duct (13) is A2. The relationship between A1 and A2 is: 1≤A1 / A2≤13, and the relationship between Aj and A2 is: 0.8≤Aj / A2≤0.

94.

4. The blower with multi-section heat dissipation channels according to claim 3, characterized in that: The motor stator (8) is axially penetrated with first ventilation holes to form the first heat dissipation air duct (14). The total area of a plurality of first ventilation holes is A4, and the relationship between A4 and A2 is 1.5≤A4 / A2≤3.

5. The blower with multi-section heat dissipation channels according to claim 3, characterized in that: There is a first gap between the motor stator (8) and the motor rotor (7). The axial bearing (300) includes a front axial bearing (10), a rear axial bearing (9) and a thrust disc. The front axial bearing (10), the thrust disc and the rear axial bearing (9) are arranged in sequence along the axial direction and are connected in sequence. The thrust disc is located between the front axial bearing (10) and the rear axial bearing (9). The first radial bearing (5) has a second gap along the axial direction. The rear axial bearing (9) has a third gap. The front axial bearing (10) has a fourth gap. The second radial bearing (11) has a fourth gap. The ranges of the first gap, the second gap, the third gap and the fourth gap are all within 0.002R1 to 0.01R1.

6. The blower with multi-segment heat dissipation channels according to claim 3, characterized in that: An air outlet of the motor (2) is arranged on the blower cylinder body (12) in a radial direction opposite to and communicating with the first heat dissipation air duct (14) of the motor stator (8). The air outlet of the motor (2) penetrates through the inner and outer walls of the blower cylinder body (12). After the air flow passes through the channel between the motor stator (8) and the motor rotor (7), a part of the air flow passes through the first heat dissipation air duct (14) and is discharged from the air outlet of the motor (2).

7. The blower with multi-segment heat dissipation channels according to claim 6, characterized in that: The bearing air outlets (3) are multiple, and the multiple bearing air outlets (3) are spaced apart on the outer peripheral surface of the blower cylinder (12). The total area of the multiple bearing air outlets (3) is A o1 , and the motor air outlets (2) are also multiple. The multiple motor air outlets (2) are spaced apart along the circumferential direction of the blower cylinder (12). The total area of the multiple motor air outlets (2) is A o2 , A o1 and the relationship between A t and A o1 is: 0.03 ≤ A t / A o1 ≤ 0.08, and the relationship between A o2 and A o1 is 0.9 ≤ A o2 ≤ 1.

1.

8. The blower with multi-segment heat dissipation channels according to claim 3, characterized in that: A flow guiding structure (6) is further arranged in the blower cylinder body (12) and between the first radial bearing (5) and the gas inlet (100). The flow guiding structure (6) is in a circular disc shape, and a plurality of second ventilation holes (61) are axially penetrated thereon. The total area of the plurality of second ventilation holes (61) is A3, and the relationship between A3 and A2 is: 1.5 ≤ A3 / A2 ≤ 3.

9. The blower with multi-segment heat dissipation channels according to claim 8, characterized in that: It further includes a rotating shaft (15) and a heat dissipation impeller (4). At least part of the structure of the rotating shaft (15) is arranged in the blower cylinder body (12), and the first radial bearing (5), the stator-rotor assembly (200), the axial bearing (300) and the second radial bearing (11) are all sleeved on the outer periphery of the rotating shaft (15). The heat dissipation impeller (4) is arranged at an axial end of the rotating shaft (15) facing the gas inlet (100) so as to be able to rotate integrally with the rotating shaft (15). The heat dissipation impeller (4) is located between the gas inlet (100) and the flow guiding structure (6).

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