A through cooling device for an axial flux rotary machine

Abstract

The application discloses a through cooling device for an axial flux rotating machine, and relates to the technical field of rotating machine cooling, comprising a machine shell, a stator, a rotor, a centrifugal supercharging structure, a low-pressure cavity, a high-pressure cavity and a central flow-through structure. The central flow-through structure is internally provided with a central flow-through structure, and an axial flow-through channel thereof is the only fluid communication path between the low-pressure cavity and the high-pressure cavity. The application can realize global series cooling, the cooling medium flows through the stator, the bearing and the rotor in sequence, and cooling blind areas are eliminated. The stator end flow guide groove ensures uniform distribution of the medium and avoids local hot spots. The application utilizes negative pressure generated by self-rotation for driving, utilizes negative pressure formed by the centrifugal force of the rotor to suck the medium, and realizes self-circulation. The application has natural self-adaptive heat dissipation, the heat dissipation capacity is positively correlated with the rotating speed, the greater the load, the stronger the heat dissipation, and no sensor or active control is needed. The structure in the application can be applied to liquid cooling or air cooling.

Description

Technical Field

[0001] This invention relates to the field of rotating machinery cooling technology, specifically a through-type cooling device for axial flux rotating machinery. Background Technology

[0002] Axial flux rotating machinery (usually referring to axial flux motors or disc motors) is a type of motor where the magnetic flux direction is parallel to the shaft and the stator and rotor have a disc-shaped structure. During operation, axial flux rotating machinery experiences three main heat sources: copper and iron losses generated by the stator windings and core; high-speed frictional heat generated by the running of the support bearings; and eddy current and hysteresis losses generated by the rotor permanent magnets. All three heat sources require continuous and effective cooling.

[0003] Existing cooling solutions have many drawbacks: 1. System redundancy and dependence on external equipment: Traditional liquid cooling requires an external booster pump station, and air cooling requires an external cooling fan or independent cooling impeller. Some solutions are equipped with closed-loop regulation using temperature sensors, which not only increases the size and energy consumption of the whole machine, but also increases the number of failure points, and greatly increases the complexity of the system. 2. Incomplete cooling coverage and blind spots: Most cooling solutions only target the stator or rotor, generally neglecting bearing heat dissipation. Long-term operation of the equipment is prone to failure due to bearing overheating. 3. Uncontrolled flow path and medium bypass backflow: The existing self-circulating structure only relies on simple pressure difference to push the medium and does not utilize the internal negative pressure suction mechanism; the medium in the high-pressure area formed on the outer circumference of the rotor impeller will directly flow back to the low-pressure area through the axial air gap (as well as bearing gap, shaft end gap, etc.), forming a short-circuit circulation, and cannot flow through all heat sources completely along the preset path.

[0004] 4. Fixed flow path and lack of high and low pressure chamber coordination: The flow path of the existing self-circulating cooling structure is mostly fixed, but it does not cooperate with the sealing interval structure to form high and low pressure chamber partitions. It is impossible to establish a stable pressure gradient to guide the orderly flow of the medium, and it is also impossible to effectively block the bypass backflow, resulting in a single cooling path and incomplete coverage. Summary of the Invention

[0005] The purpose of this invention is to provide a through-type cooling device for axial flux rotating machinery to solve the problems mentioned in the background art.

[0006] To solve the above-mentioned technical problems, the present invention provides the following technical solution: a through-type cooling device for axial flux rotating machinery, comprising a housing, at least one stator and at least one rotor, wherein the stator is fixedly disposed inside the housing, and the rotor is rotatably disposed inside the housing, and the stator and rotor are arranged opposite each other along the axial direction; the outer wall of the rotor is provided with a centrifugal pressurization structure, a low-pressure chamber is provided inside the housing outside the stator, a high-pressure chamber is provided inside the housing outside the rotor, the low-pressure chamber and the high-pressure chamber are connected through a central flow passage structure, an inlet pipe is provided on the outer wall of the housing outside the low-pressure chamber, and an outlet pipe is provided on the outer wall of the housing outside the high-pressure chamber.

[0007] Furthermore, the centrifugal pressurization structure is a drive impeller integrated on the rotor or a liquid-throwing channel located on the outermost periphery of the rotor and extending along the outer periphery of the rotor.

[0008] Furthermore, the central flow passage structure is located at the center of the stator and rotor shafts; the central flow passage structure includes a first hollow shaft and a second hollow shaft, the first hollow shaft is horizontally fixed inside the bearing at the center of the stator shaft, the outer wall of the second hollow shaft is sleeved at the center of the rotor shaft, the second hollow shaft is fixedly connected to the inner wall of the first hollow shaft, and an axial flow passage is opened on the inner side of the second hollow shaft, the low-pressure chamber and the high-pressure chamber are connected through the axial flow passage.

[0009] Furthermore, the stator core back sandwich and winding gap are both provided with impregnation channels.

[0010] Furthermore, it also includes a sealing interval structure, which includes a backflow sealing structure and a blocking sealing structure. The backflow sealing structure is located at at least one end of the stator outer wall and is located between the low-pressure chamber and the high-pressure chamber.

[0011] Furthermore, the reflux sealing structure includes a first sealing structure and a second sealing structure. The first sealing structure is disposed between the outer wall of the stator and the inner wall of the housing; the second sealing structure is disposed at the interface between the inner side of the rotor and the outer wall of the central flow structure.

[0012] Furthermore, the blocking sealing structure includes a third sealing structure and a fourth sealing structure. The third sealing structure is located at the interface between the outer shaft end of the rotor and the housing, and the fourth sealing structure is located at the point where the power interface extends out of the housing.

[0013] Furthermore, it also includes a preset throttling gap, which is located between the low-pressure chamber and the high-pressure chamber, and the preset throttling gap is located at least once between the rotor and the central flow structure or between the rotor and the housing.

[0014] Furthermore, the inner wall of the housing is provided with a flow guide groove on the low-pressure chamber side, and the flow guide groove is radial, annular, or a channel formed by interspersed ribs.

[0015] Furthermore, the number and arrangement of the stator and rotor are any one of the following: single stator and single rotor, single rotor and double stator, or single stator and double rotor.

[0016] Compared with the prior art, the beneficial effects achieved by the present invention are: 1. This invention comprises a casing, stator, rotor, centrifugal pressurization structure, low-pressure chamber, high-pressure chamber, and central flow structure. The stator and rotor are arranged axially opposite each other to form an axial air gap, with at least one such gap. The central flow structure is internally located, and its axial flow channel is the only fluid connection path between the low-pressure chamber and the high-pressure chamber. A series-connected cooling main channel is formed by sequentially connecting the stator fluid channel, bearing cooling area, and axial flow channel inside the low-pressure chamber, and the rotor fluid channel inside the high-pressure chamber, creating a unidirectional cooling path without bypass. When the rotor rotates, the centrifugal pressurization structure throws the medium in the high-pressure chamber on the rotor side outwards, and the central flow structure reduces the pressure in the low-pressure chamber on the stator side, thus creating a negative pressure at the inlet pipe. Driven by the pressure difference, the cooling medium flows from the low-pressure chamber to the high-pressure chamber. The medium flows unidirectionally along the main cooling channel in a series, while the bearings are cooled by the medium flowing through the central flow structure. This invention achieves full-area series cooling: the cooling medium flows sequentially through the stator, bearings, and rotor, eliminating cooling blind spots; the stator end guide groove ensures uniform medium distribution and avoids local hot spots; this invention utilizes its own rotation to generate negative pressure drive: no external pump station or independent heat dissipation impeller is needed, the negative pressure formed by the rotor's centrifugal force draws in the medium, achieving self-circulation; this invention has natural adaptive heat dissipation: the heat dissipation capacity is positively correlated with the rotational speed, the greater the load, the stronger the heat dissipation, without the need for sensors or active control; this invention uses multiple seals to block bypasses: progressive seals are set in potential backflow paths such as the axial air gap and the rotor inner wall gap to ensure that the medium flows strictly unidirectionally along the preset series flow channel; the architecture of this invention can be applied to liquid cooling or air cooling.

[0017] 2. This invention uses a sealed partition structure to divide the inner cavity of the housing into a low-pressure chamber on the stator side and a high-pressure chamber on the rotor side, which are connected only by an axial through-hole in the central flow structure. When the rotor rotates, its centrifugal pressurization structure throws the medium in the high-pressure chamber on the rotor side outward, increasing the pressure inside the chamber. At the same time, a low-pressure area is formed in the central region due to the ejection of the medium, and the pressure in the low-pressure chamber on the stator side is further reduced by the central flow structure, establishing a stable pressure gradient. The cooling medium is drawn in from the inlet pipe on the outside of the housing under negative pressure suction, flows sequentially through the stator, bearings, central flow structure, and high-pressure chamber on the rotor side along the series main flow channel, and then is discharged. After being cooled by an external heat exchanger, the medium circulates. A preset throttling gap serves as a substitute for a sealing interval structure. Instead of setting an independent sealing interval structure, a preset micro-gap set along the circumference or axial direction between the rotor and the central flow structure or between the rotor and the casing is used as the inlet channel and dynamic sealing structure for the cooling medium. The size of this gap is determined according to the properties of the cooling medium, the design flow rate, the rotor operating speed, and the allowable pressure drop, so that when the rotor rotates, the cooling medium enters the high-pressure chamber on the rotor side in a metered manner through the gap under the action of pressure difference. At the same time, the fluid resistance generated by the gap inhibits the reverse flow of the medium through the gap. Attached Figure Description

[0018] The accompanying drawings are provided to further illustrate the invention and form part of the specification. They are used in conjunction with embodiments of the invention to explain the invention and do not constitute a limitation thereof. In the drawings: Figure 1 This is a schematic diagram of the device structure of the single stator and single rotor of the present invention; Figure 2 This is the present invention. Figure 1 Another structural diagram; Figure 3 This is the present invention. Figure 1 Side view of the medium-low pressure chamber; Figure 4 This is a schematic diagram of the device structure of the single rotor dual stator of the present invention; Figure 5 This is the present invention. Figure 4 Another structural diagram; Figure 6 This is the present invention. Figure 4 Schematic diagram of a single rotor double stator; Figure 7 This is a schematic diagram of the device structure of the single stator and dual rotor of the present invention; Figure 8 This is the present invention. Figure 7 A schematic diagram of the structure of a single stator with dual rotors; Figure 9 This is the present invention. Figure 7 Schematic diagram of the middle stator; Figure 10 This is the present invention. Figure 7 Schematic diagram of the second hollow shaft in the middle; In the diagram: 1. Housing; 101. Low-pressure chamber; 102. High-pressure chamber; 103. Inlet pipe; 104. Outlet pipe; 105. Guide groove; 2. Stator; 201. Immersion channel; 202. Bearing; 3. Rotor; 4. Centrifugal pressurization structure; 5. Central flow structure; 501. First hollow shaft; 502. Second hollow shaft; 503. Axial flow channel; 6. First sealing structure; 7. Second sealing structure. Detailed Implementation

[0019] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0020] Example 1

[0021] Please see Figures 1-10 This invention provides a technical solution: a through-type cooling device for axial flux rotating machinery, comprising a housing 1, at least one stator 2, and at least one rotor 3. The stator 2 is fixedly disposed inside the housing 1, and the rotor 3 is rotatably disposed inside the housing 1. The stator 2 and rotor 3 are arranged opposite each other along the axial direction. A centrifugal pressurization structure 4 is provided on the outer wall of the rotor 3. A low-pressure chamber 101 is provided inside the housing 1 outside the stator 2, and a high-pressure chamber 102 is provided inside the housing 1 outside the rotor 3. The low-pressure chamber 101 and the high-pressure chamber 102 are connected by a central flow passage structure 5. An inlet pipe 103 is provided on the outer wall of the housing 1 outside the low-pressure chamber 101, and an outlet pipe 104 is provided on the outer wall of the housing 1 outside the high-pressure chamber 102. The centrifugal pressurization structure 4... The impeller is integrated on the rotor or a liquid-throwing channel is located on the outermost periphery of the rotor 3 and extends along the outer periphery of the rotor 3; the central flow structure 5 is located at the axis of the stator 2 and the rotor 3; the central flow structure 5 includes a first hollow shaft 501 and a second hollow shaft 502, the first hollow shaft 501 is horizontally fixed inside the bearing 202 at the axis of the stator 2, the outer wall of the second hollow shaft 502 is sleeved at the axis of the rotor 3, the second hollow shaft 502 is fixedly connected to the inner wall of the first hollow shaft 501, and an axial flow channel 503 is opened on the inner side of the second hollow shaft 502, the low-pressure chamber 101 and the high-pressure chamber 102 are connected through the axial flow channel 503; the back sandwich of the iron core of the stator 2 and the winding gap are both provided with wetting channels 201.

[0022] In one embodiment, a sealing gap structure is further included, the sealing gap structure comprising a backflow sealing structure and a blocking sealing structure. The backflow sealing structure is disposed at at least one end of the outer wall of the stator 2, and is disposed between the low-pressure chamber 101 and the high-pressure chamber 102. The backflow sealing structure comprises a first sealing structure 6 and a second sealing structure 7. The first sealing structure 6 is disposed between the outer wall of the stator 2 and the inner wall of the housing 1. The second sealing structure 7 is disposed at the interface between the inner side of the rotor 3 and the outer wall of the central flow structure 5. The blocking sealing structure comprises a third sealing structure and a fourth sealing structure. The third sealing structure is disposed at the interface between the outer shaft end of the rotor 3 and the housing 1, and the fourth sealing structure is disposed at the point where the power interface exits the housing 1. A sealing gap structure is provided at at least one end of the stator 2. (e.g., annular sealing plate), dividing the inner cavity into a stator-side low-pressure chamber 101 and a rotor-side high-pressure chamber 102. This structure integrates a sealing element mounting base and a bearing mounting base; the bearing is mounted on the sealing interval structure, located near the central flow channel, and dissipates heat through the flowing medium; multiple backflow blocking seals: First layer: located at the axial air gap interface between the low-pressure chamber and the high-pressure chamber (labyrinth, brush, magnetohydrodynamic, or gap seal), blocking the medium from flowing back through the air gap bypass - this is the most critical seal; Second layer: located at the interface between the inner side of the rotor and the outer wall of the central flow structure (interference fit or integrated), blocking the medium from flowing back through the gap between the inner wall of the rotor and the shaft; Third layer (preferred): located at the interface between the outer shaft end of the rotor and the housing; Fourth layer (preferred): located at the point where the power interface exits the housing.

[0023] In one embodiment, the inner wall of the housing 1 is provided with a guide groove 105 on one side of the low-pressure chamber 101. The guide groove 105 is radial, annular, or a channel formed by interspersed ribs. After the cooling medium enters the low-pressure chamber 101 on the stator side from the inlet pipe 103, it is evenly distributed and guided to each winding area of ​​the stator 2 through the guide groove 105 to eliminate dead flow angles and cooling blind spots.

[0024] In one embodiment, the number and arrangement of the stator 2 and rotor 3 are any one of single stator single rotor, single rotor double stator, and single stator double rotor. The cooling design in this invention is applicable to any combination of single stator single rotor, single rotor double stator, and single stator double rotor. It should be noted that when a single stator double rotor combination is used, the structure is slightly different (e.g., Figures 7-10 As shown), firstly, the inner wall of the low-pressure chamber 101 no longer has the guide groove 105. Secondly, the outer wall of the second hollow shaft 502 in the central flow structure 5 has several holes and slots arranged in a ring (the bearing 202 is arranged at both ends of the stator, and the center position of the stator is not blocked by the bearing 202, so the bearing 202 will not block the above-mentioned holes and slots). These are used to allow the cooling medium entering the low-pressure chamber 101 to enter the second hollow shaft 502 from this point, and then move to the high-pressure chamber 102.

[0025] Working principle of the invention: Refer to the instruction manual appendix Figures 1-10 The present invention comprises a housing 1, a stator 2, a rotor 3, a centrifugal pressurization structure 4, a low-pressure chamber 101, a high-pressure chamber 102, and a central flow passage structure 5. The stator 2 and rotor 3 are arranged opposite each other along the axial direction to form an axial air gap, and there is at least one such gap. The central flow structure 5 has a central flow structure (hollow support shaft, central flow cavity or shaftless docking channel) inside, and its axial flow channel 503 is the only fluid communication path between the low-pressure chamber 101 and the high-pressure chamber 102. The series-through cooling main channel is as follows: the stator 2 fluid channel (immersion channel 201, located inside the low-pressure chamber 101), the bearing 202 cooling area, the axial flow channel 503, and the rotor fluid channel (surrounding the back of the permanent magnet, located inside the high-pressure chamber 102) are connected in series to form a unidirectional cooling path without bypass. The cooling medium flows from the low-pressure chamber 101 to the high-pressure chamber 102 under the pressure difference, and the bearing 202 is cooled by the medium flowing through the central flow structure 5. Each stator-side low-pressure chamber 101 contains a stator fluid flow channel, and each rotor-side high-pressure chamber 102 contains a rotor fluid flow channel. The bearing 202 is mounted on the sealed spacer structure and located near the central flow channel. The stator fluid flow channel, bearing cooling zone, axial flow channel of the central flow structure, and rotor fluid flow channel are connected in series to form a series through-type cooling main channel. The cooling medium flows through the stator 2, bearing 202, and rotor 3 in the main channel to form a full-area series cooling. When the rotor 3 rotates, the centrifugal pressurization structure 4 throws the medium in the high-pressure chamber 102 on the rotor side outward and reduces the pressure in the low-pressure chamber 101 on the stator side through the central flow structure 5, thereby forming a negative pressure at the inlet pipe 103, drawing the cooling medium into the equipment, and flowing unidirectionally along the series through-type cooling main channel. This invention enables full-area series cooling: the cooling medium flows sequentially through the stator 2, bearing 202, and rotor 3, eliminating cooling blind spots; the stator end guide groove 105 ensures uniform medium distribution and avoids local hot spots; this invention utilizes its own rotation to generate negative pressure drive: no external pump station or independent heat dissipation impeller is needed, the negative pressure formed by the centrifugal force of the rotor 3 draws in the medium, achieving self-circulation; this invention has natural adaptive heat dissipation: the heat dissipation capacity is positively correlated with the rotational speed, the greater the load, the stronger the heat dissipation, without the need for sensors or active control; this invention uses multiple seals to block bypasses: progressive seals are set in potential backflow paths such as the axial air gap (most critical) and the rotor inner wall gap to ensure that the medium flows strictly in one direction along the preset series flow channel; the architecture of this invention can be applied to liquid cooling or air cooling: the same core structural principle can be adapted to different media, only requiring adjustment of the flow channel cross-section, impeller parameters, and sealing form; The flow passage structure in this invention is diverse: the central flow passage structure can adopt a hollow support shaft, a central flow passage cavity, or a shaftless docking channel to adapt to different installation requirements; Centrifugal negative pressure suction and liquid inlet structure: When the rotor 3 rotates, the centrifugal pressurization structure 4 throws the medium in the high-pressure chamber 102 on the rotor side outward, so that high pressure is formed in the chamber and low pressure is formed in the central area. The pressure in the low-pressure chamber 101 on the stator side is reduced through the central flow structure 5, thereby forming negative pressure at the inlet pipe 103. The end face of the casing 1 outside the low-pressure chamber 101 is provided with a central hole as an inlet, and the outer side of the central hole is connected to the external inlet pipe 103. The centrifugal negative pressure formed in the equipment cavity draws the external cooling medium into the low-pressure chamber 101 on the stator side through the external inlet pipe 103 and the inlet, and then completes the whole-area circulation cooling along the series main channel. There are two ways to implement a centrifugal pressurization structure: Option A: The rotor 3 integrates a drive impeller, located in the high-pressure chamber 102 on the rotor side. The blade shape, outlet angle, and diameter of the impeller are customized according to the type of cooling medium and the required flow rate. Option B: A liquid-throwing channel is provided on the outermost periphery of rotor 3, which is connected to the high-pressure chamber 102 on the rotor side; after the cooling medium enters the high-pressure chamber 102 on the rotor side through the central flow structure, it flows from the inside to the outside along the liquid-throwing channel under the action of centrifugal force and is thrown out at high speed from the liquid-throwing port on the outer periphery of the rotor, forming a driving effect; the cross-sectional shape, spiral angle and length of the liquid-throwing channel are adjusted according to the heat dissipation requirements. This invention uses a sealed partition structure to divide the inner cavity of the housing 1 into a stator-side low-pressure chamber 101 and a rotor-side high-pressure chamber 102, which are connected only by an axial through-hole in the central flow structure 5. When the rotor 3 rotates, the centrifugal pressurization structure 4 on it throws the medium in the rotor-side high-pressure chamber 102 outward, increasing the pressure inside the chamber. At the same time, the central region forms a low pressure due to the medium being thrown out, and the pressure in the stator-side low-pressure chamber 101 is further reduced through the central flow structure 5, establishing a stable pressure gradient. The cooling medium is drawn in from the inlet pipe 103 outside the housing 1 under negative pressure suction, flows sequentially through the stator 2, bearing 202, central flow structure 5, and rotor-side high-pressure chamber 102 along the series main channel, and then is discharged, cooled by an external heat exchanger, and then circulated. Naturally adaptive: The higher the rotation speed, the greater the centrifugal force, the stronger the negative pressure suction, the flow rate increases automatically, and the heat dissipation capacity increases with the load, without the need for any sensors or active control. In this invention, the negative pressure generated by the centrifugal force of the rotor 3 itself eliminates the need for sensors; this invention features a unique series main channel, high and low pressure chamber partitions, and multiple seals to block all bypass gaps (especially axial air gaps); this invention enables full-coverage sequential cooling of the stator → bearing → rotor (full-domain series cooling); this invention is naturally positively correlated with rotational speed; in this invention, the central flow structure 5, in conjunction with the sealing interval structure, forms a unique channel between the high and low pressure chambers, establishing a stable pressure gradient, and can be configured in various forms (hollow support shaft, central flow chamber, shaftless docking channel); in this invention, the cooling medium is introduced into the low-pressure chamber 101 through the inlet pipe 103 on the outside of the casing, utilizing centrifugal negative pressure to drive full-domain series cooling, with multiple seals blocking bypasses; This invention utilizes the centrifugal force generated by the rotation of rotor 3 to actively divide the inner cavity of housing 1 into a low-pressure chamber 101 and a high-pressure chamber 102, and draws cooling medium from the outside of housing 1 through centrifugal negative pressure, so that the cooling medium flows in series through stator 2, bearing 202 and rotor 3 in sequence, to achieve full-coverage sequential cooling of the three major heat sources - that is, full-domain series cooling. In this invention, the centrifugal negative pressure generated by the rotation of the rotor 3 itself is used to draw in the cooling medium through the inlet pipe 103 on the outside of the casing 1, and the cooling medium flows in series through the stator 2, bearing 202 and rotor 3 in sequence, so as to realize the axial flux motor, generator, liquid cooling pump and centrifugal fan and other equipment with full coverage of the three heat sources for self-circulating heat dissipation. Regarding the conductive cooling medium: When water or other conductive liquids are used as the cooling medium, the surface of the stator 2 winding must have a waterproof insulation layer to prevent leakage and short circuit; this invention does not limit the specific insulation implementation method, and any insulation measures that enable the winding to operate safely in a conductive liquid can be used in conjunction with the cooling architecture of this invention.

[0026] Example 2

[0027] The difference between this invention and Embodiment 1 is that a preset throttling gap is used instead of a sealing interval structure. This preset throttling gap is located between the low-pressure chamber 101 and the high-pressure chamber 102, and is located at least once between the rotor 3 and the central flow-through structure 5 or between the rotor 3 and the housing 1. The annular sealing plate at the outer end of the stator 2 is eliminated, and the fit clearance between the central flow-through structure 5 and the inner hole of the rotor 3 is designed as a preset micro-gap. The size of this gap is determined based on parameters such as the properties of the cooling medium, design flow rate, rotational speed, and allowable pressure drop. When the rotor 3 rotates, the cooling medium, under the action of pressure difference, quantitatively enters the high-pressure chamber 102 on the rotor side through this gap, and the gap flow resistance suppresses reverse backflow. This embodiment is simplified. The structure retains the liquid inlet function of the central hole of the shell, and can also be used for parallel water pipe installation; the preset throttling gap serves as a substitute for the sealing interval structure, so an independent sealing interval structure is not required. Instead, a preset micro gap set along the circumference or axial direction between the rotor 3 and the central flow structure 5 or between the rotor 3 and the housing 1 is used as the liquid inlet channel and dynamic sealing structure for the cooling medium; the size of the gap is determined according to the properties of the cooling medium, the design flow rate, the operating speed of the rotor 3, and the allowable pressure drop and other operating parameters, so that when the rotor 3 rotates, the cooling medium enters the high-pressure chamber 102 on the rotor side through the gap under the action of pressure difference, while the fluid resistance generated by the gap inhibits the reverse flow of the medium through the gap.

[0028] Example 3 (Liquid-cooled motor, built-in impeller, liquid inlet through the central hole of the housing) The system features a single rotor and dual stators, with an annular sealing plate separating the cavities and a hollow support shaft connecting them. The rotor 3 integrates a drive impeller (Scheme A). The outer end face of the casing 1 of the low-pressure chamber 101 has a central hole connected to an external inlet pipe 103. Centrifugal negative pressure draws external coolant into the stator-side low-pressure chamber 101 through the central hole, then evenly distributes it to the winding areas of each stator 2 via the stator end face guide groove 105. The coolant flows sequentially through the bearing area, the central through-hole, and the rotor-side high-pressure chamber 102 (after centrifugal pressurization by the impeller, it is thrown towards the back of the permanent magnet), finally exiting through the drain pipe 104 outside the high-pressure chamber 102. After cooling by an external heat exchanger, the coolant circulates. Multiple seals block bypasses (especially the first seal blocks axial air gap backflow). Higher speeds result in greater flow rates, with adaptive heat dissipation.

[0029] Example 4 (Liquid-cooled motor, external liquid slinging channel) Scheme B centrifugal pressurization structure (rotor peripheral liquid throwing channel) is adopted; the coolant is drawn into the low-pressure chamber 101 through the central hole of the housing, and after the stator 2 is uniformly cooled by the guide groove 105 on the end face of the stator 2, it flows through the bearing area and the central through hole in sequence, and enters the central low-pressure area of ​​the high-pressure chamber 102 on the rotor side. Then, under the action of centrifugal force, it is thrown outward through the liquid throwing channel, while cooling the back side of the rotor permanent magnet, and finally discharged from the liquid throwing port.

[0030] Example 5 (Air-cooled axial flux centrifugal fan) The medium is air, and the central hole of the casing serves as the air inlet. The rotor 3 is integrated with the impeller. After the air is drawn in, it flows sequentially through the low-pressure chamber 101 on the stator side (which cools the stator 2 uniformly through the guide groove 105), the bearing area, the central through hole, and the high-pressure chamber 102 on the rotor side (which cools the rotor 3), thus simultaneously achieving fan compression and motor heat dissipation.

[0031] Example 6 (Axial Flux Generator) The structure is the same as in Embodiment 3. The external prime mover drives the rotor 3, the stator 2 generates electricity, the cooling system is the same, and the electrical energy is output through the sealed lead wire.

[0032] Example 7 (Axial Flux Liquid Cooling Pump) The pump has a single stator and a single rotor. The pump impeller is installed at the end of the rotor 3. The pumped liquid (such as water, coolant, etc.) enters from the pump inlet. A portion of it is drawn into the equipment as a cooling medium through the central hole of the casing. After being evenly distributed and cooled by the guide groove 105, it flows into the main pumping channel. The liquid simultaneously undertakes the functions of pumping and cooling. When used as a liquid-cooled pump, the water pipes of the inlet and outlet structures can be installed in parallel: the inlet pipe and the outlet pipe are arranged parallel to each other on the same side or opposite side of the pump body, without the need for vertical turns or large-angle bends. The pipeline extends in a straight line, which greatly saves installation space and reduces the local resistance loss caused by fluid turning, thereby improving pumping efficiency. When the pumped liquid is a conductive medium such as water, the stator winding is treated with waterproof insulation.

[0033] Finally, it should be noted that the above descriptions are merely preferred embodiments of the present invention and are not intended to limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments or make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A through-type cooling device for axial flux rotating machinery, comprising a housing (1), at least one stator (2) and at least one rotor (3), characterized in that: The stator (2) is fixed inside the housing (1), and the rotor (3) is rotatably disposed inside the housing (1). The stator (2) and the rotor (3) are arranged opposite each other along the axial direction. The outer wall of the rotor (3) is provided with a centrifugal pressurization structure (4). The housing (1) is provided with a low-pressure chamber (101) outside the stator (2) and a high-pressure chamber (102) outside the rotor (3). The low-pressure chamber (101) and the high-pressure chamber (102) are connected through a central flow passage structure (5). The outer wall of the housing (1) is provided with an inlet pipe (103) outside the low-pressure chamber (101) and an outlet pipe (104) outside the high-pressure chamber (102).

2. A through-type cooling device for axial flux rotating machinery according to claim 1, characterized in that: The centrifugal booster structure (4) is a drive impeller integrated on the rotor or a liquid-throwing channel located on the outermost periphery of the rotor (3) and extending along the outer periphery of the rotor (3).

3. A through-type cooling device for axial flux rotating machinery according to claim 1, characterized in that: The central flow structure (5) is located at the center of the stator (2) and the rotor (3); the central flow structure (5) includes a first hollow shaft (501) and a second hollow shaft (502). The first hollow shaft (501) is horizontally fixed inside the bearing (202) at the center of the stator (2). The outer wall of the second hollow shaft (502) is fitted at the center of the rotor (3). The second hollow shaft (502) is fixedly connected to the inner wall of the first hollow shaft (501). An axial flow channel (503) is opened on the inner side of the second hollow shaft (502). The low-pressure chamber (101) and the high-pressure chamber (102) are connected through the axial flow channel (503).

4. A through-type cooling device for axial flux rotating machinery according to claim 1, characterized in that: The stator (2) has a wetting channel (201) in the back layer of the core and the winding gap.

5. A through-type cooling device for axial flux rotating machinery according to claim 1, characterized in that: It also includes a sealing interval structure, which includes a backflow sealing structure and a blocking sealing structure. The backflow sealing structure is located at at least one end of the outer wall of the stator (2) and is located between the low-pressure chamber (101) and the high-pressure chamber (102).

6. A through-type cooling device for axial flux rotating machinery according to claim 5, characterized in that: The backflow sealing structure includes a first sealing structure (6) and a second sealing structure (7). The first sealing structure (6) is located between the outer wall of the stator (2) and the inner wall of the housing (1). The second sealing structure (7) is located at the interface between the inner side of the rotor (3) and the outer wall of the central flow structure (5).

7. A through-type cooling device for axial flux rotating machinery according to claim 5, characterized in that: The blocking sealing structure includes a third sealing structure and a fourth sealing structure. The third sealing structure is located at the interface between the outer shaft end of the rotor (3) and the housing (1), and the fourth sealing structure is located at the point where the power interface passes through the housing (1).

8. A through-type cooling device for axial flux rotating machinery according to claim 1, characterized in that: It also includes a preset throttling gap, which is located between the low-pressure chamber (101) and the high-pressure chamber (102), and the preset throttling gap is located at least once between the rotor (3) and the central flow structure (5) or between the rotor (3) and the housing (1).

9. A through-type cooling device for axial flux rotating machinery according to claim 1, characterized in that: The inner wall of the housing (1) is provided with a guide groove (105) on one side of the low-pressure chamber (101). The guide groove (105) is radial, annular or formed by ribs.

10. A through-type cooling device for axial flux rotating machinery according to claim 1, characterized in that: The number and layout of the stator (2) and rotor (3) are any one of the following: single stator and single rotor, single rotor and double stator, or single stator and double rotor.

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