Flange end cover type motor capable of being directly connected with speed reducer

Abstract

The invention discloses a flange end cover type motor capable of being directly connected with a speed reducer. The flange end cover type motor comprises a motor rotor shaft, an air cooling rear end cover, a front end cover and a wind scooper, the wind scooper coaxially covers the rear side of the air cooling rear end cover, and a centrifugal wind bin is formed in the inner side of the wind scooper. The front end of the motor rotor shaft is a rotor shaft output end, and the rear end of the motor rotor shaft extends into the centrifugal air bin in which a conical surface centrifugal impeller is arranged; the front end of the front end cover is integrally provided with an extended neck tube, and at least a labyrinth type axial surface oil seal, a framework oil seal and a ball bearing are sequentially and coaxially arranged between the inner ring of the extended neck tube and the outer wall of the motor rotor shaft from outside to inside; the thermal failure of the labyrinth type axial surface oil seal of the inner ring of the front end cover, the framework oil seal and the inner ring of the ball bearing can be effectively avoided.

Description

Technical Field

[0001] The invention belongs to the field of motors. Background Art

[0002] In industrial transmission systems, the coordinated operation of motors and reducers is the core link to achieve power transmission and torque amplification. They are widely used in automation equipment, robots, conveying systems and various low-speed and heavy-load scenarios. However, the traditional connection method between motors and reducers usually adopts couplings or flange transition structures, such as Figure 1 As shown in the figure above, the space occupied is large: the transition structure increases the overall volume, which is not conducive to the compact design of the equipment; therefore, in scenarios where space is limited, it is necessary to design a structure in which the motor and the reducer are directly connected.

[0003] In general industrial motors, the rear end cover can directly receive the high-speed cooling airflow from the tail core wind chamber, and there is no obvious cooling problem. However, the front end cover is far away from the conical centrifugal impeller, and the inner ring cannot directly receive the cooling air generated by the centrifugal impeller. As a result, the friction heat generated by the labyrinth shaft oil seal, skeleton oil seal, and inner ring of the bearing on the inner ring of the front end cover and the surface of the motor rotor shaft is easily accumulated and cannot be effectively discharged, which makes it easy to cause high-temperature damage and loss of sealing performance.

[0004] In addition, the direct connection between the motor and the reducer will have a certain impact on the coaxiality, so the outer peripheral surface of the front of the motor rotor shaft and the labyrinth shaft oil seal, skeleton oil seal and the inner ring of the ball bearing are more likely to generate friction heat. Summary of the Invention

[0005] Purpose of the invention: In order to overcome the deficiencies in the prior art, the present invention provides a flange end cover type motor that can be directly connected to a reducer, which can effectively avoid thermal failure of the labyrinth axial surface oil seal, skeleton oil seal and inner ring of the ball bearing on the inner ring of the front end cover.

[0006] Technical solution: To achieve the above-mentioned purpose, the present invention provides a flange end cover type motor that can be directly connected to a reducer, comprising a motor rotor shaft, an air-cooled rear end cover, a front end cover and an air guide cover;

[0007] The air guide cover is coaxially arranged at the rear side of the air-cooled rear end cover, and a centrifugal air bin is formed inside the air guide cover;

[0008] The front end of the motor rotor shaft is the rotor shaft output end, and the rear end extends to the centrifugal wind chamber, in which there is a conical centrifugal impeller;

[0009] An extended neck tube is integrally provided at the front end of the front end cover, and a labyrinth-type shaft oil seal, a skeleton oil seal and a ball bearing are coaxially installed between the inner ring of the extended neck tube and the outer wall of the motor rotor shaft from the outside to the inside.

[0010] A shaft shoulder end face is provided on a section of the motor rotor shaft outside the labyrinth type shaft oil seal, and a circle of pulse breathing holes equidistantly distributed in a circumferential array is provided on the shaft shoulder end face.

[0011] The front end cover is coaxially connected to the flange through the front end of the extended neck tube. The output end of the rotor shaft is coaxially connected to the input shaft of the reducer through a keyway. At the same time, the flange at the front end of the front end cover is coaxially locked on the input end flange of the reducer through flange bolts.

[0012] When the flange of the front end cover and the input end flange of the reducer are locked, a cavity connected to the outside world is formed in the center between the flange of the front end cover and the input end flange of the reducer. The cavity is connected to each pulse breathing hole, and the cavity is connected to the outside world through several oblique through holes on the flange.

[0013] The outer conical surface of the conical centrifugal impeller is provided with centrifugal blades, and the inner ring of the conical centrifugal impeller is coaxially connected to a sleeve. The sleeve contains a pressure air chamber. The pressure air chamber is sealed with a flexible diaphragm at one end close to the motor rotor shaft. The outer contour of the flexible diaphragm is sealed and connected to the inner contour of the sleeve. When the pressure in the pressure air chamber changes alternately, the flexible diaphragm will fluctuate alternately.

[0014] Taking the root profile of the conical centrifugal impeller as the boundary, the sleeve is divided into sleeve section a and sleeve section b, wherein sleeve section a is closer to the motor rotor shaft;

[0015] The outer ring of the end of the sleeve section a is provided with an external thread; the tail end of the motor rotor shaft is provided with an internal threaded hole coaxially; the external thread is threadedly matched with the internal threaded hole, and when the external thread and the internal threaded hole are threadedly matched and tightened, a columnar pressure transmission cavity is formed between the bottom surface of the internal threaded hole and the flexible diaphragm;

[0016] A plurality of pulse air guide channels are distributed in a circumferential array in the rotor shaft of the motor close to the circumferential surface of the rotor shaft. The pulse air guide channels extend along the axis of the motor rotor shaft. The front ends of the plurality of pulse air guide channels are respectively connected to the plurality of pulse breathing holes, and the rear ends of the plurality of pulse air guide channels are all connected to the columnar pressure transmission cavity.

[0017] A hole-blocking column is coaxially provided at the inner axis of the rear end wall of the air guide cover, and a semi-cylindrical air distribution valve core is coaxially provided at the end of the hole-blocking column. The outer circumferential surface of the semi-cylindrical air distribution valve core is on the same circumferential surface as the outer circumferential surface of the hole-blocking column. The integral structure formed by the hole-blocking column and the semi-cylindrical air distribution valve core coaxially extends into the pressure air chamber, and the outer circumferential surface of the integral structure formed by the hole-blocking column and the semi-cylindrical air distribution valve core is gap-matched with the inner wall surface of the pressure air chamber.

[0018] A pressure-matching hole a is vertically hollowed out on section a of the sleeve, and a pressure-matching hole b is vertically hollowed out on section b of the sleeve; during the rotation of the sleeve along the axis, the outer arc surface of the semi-cylindrical gas distribution valve core periodically and alternately blocks the pressure-matching hole a and the pressure-matching hole b.

[0019] From the axial perspective of the sleeve, the pressure-matching hole a and the pressure-matching hole b are centrally symmetrical relative to the axis of the sleeve.

[0020] When the motor is running, the wind load torque on the conical centrifugal impeller causes the external thread and the internal thread hole to tighten.

[0021] The inner diameter of the pulse air guide channel ranges from 0.8mm to 1mm; the clearance range between the outer peripheral surface of the integrated structure formed by the plugging column and the semi-cylindrical air distribution valve core and the inner wall surface of the pressure air chamber is: 0.02-0.1mm.

[0022] A plurality of air inlet mesh holes are hollowed out on the rear end wall of the air guide cover.

[0023] Beneficial effect: There is always a significant air pressure difference between the outer end of the pressure-matching hole a and the outer end of the pressure-matching hole b in the present invention; when the conical centrifugal impeller and the sleeve rotate at high speed, the pressure-matching hole a and the pressure-matching hole b are periodically and alternately connected to the pressure air chamber at high frequency, thereby causing the air pressure in the pressure air chamber to undergo periodic high-frequency transformation, and the flexible diaphragm follows the back-and-forth pulse fluctuation; in the process of the back-and-forth pulse fluctuation of the flexible diaphragm, the volume and pressure of the columnar pressure transmission cavity are periodically and frequently fluctuated, and the periodic high-frequency pulse fluctuation of the pressure is transmitted to the pulse breathing holes through the pulse air guide channels, thereby finally causing the pulse breathing holes to perform High-frequency pulse breathing; during the process of high-frequency pulse breathing through the pulse breathing hole, the external air is sucked into the front section of the pulse air guide channel from the pulse breathing hole and then exhaled quickly in the form of pulses, so that the heat near the outer peripheral surface of the motor rotor shaft where the labyrinth oil seal, skeleton oil seal and ball bearing are located in the front of the motor rotor shaft can be quickly exchanged with the outside world under the action of high-frequency breathing, thereby achieving efficient heat dissipation of the outer peripheral surface of the motor rotor shaft where the labyrinth oil seal, skeleton oil seal and ball bearing are located; avoiding thermal failure of the inner ring of the labyrinth oil seal, skeleton oil seal and ball bearing. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 There is a difference between the connection between the motor and the reducer with a transition structure and without a transition structure;

[0025] Figure 2 This is the overall schematic diagram of the motor;

[0026] Figure 3 for Figure 2 An enlarged partial schematic diagram at the mark 8;

[0027] Figure 4It is the overall schematic diagram of the front end cover;

[0028] Figure 5 This is a schematic diagram after the stator, rotor and housing are hidden;

[0029] Figure 6 for Figure 5 Cross-sectional view of

[0030] Figure 7 for Figure 6 A magnified diagram of the tail. DETAILED DESCRIPTION

[0031] The present invention will be further described below with reference to the accompanying drawings.

[0032] As attached Figures 1 to 7 A flange end cover type motor that can be directly connected to a reducer is shown in FIG. Figure 2 , including a motor rotor shaft 16, a permanent magnet rotor 15, a stator coil 14, a heat dissipation housing 13, an air-cooled rear end cover 50, a front end cover 5 and an air guide cover 9;

[0033] The permanent magnet rotor 15 is coaxially fixed to the outside of the motor rotor shaft 16, and the stator coil 14 is fixed to the inner wall of the heat dissipation housing 13. The outer wall of the heat dissipation housing 13 is provided with a plurality of heat dissipation fins 100 parallel to the axial direction in a circumferential array: the front end cover 5 and the air-cooled rear end cover 50 are coaxially encapsulated and locked to the front and rear ends of the heat dissipation housing 13 respectively through locking members; the air guide cover 9 is coaxially provided on the rear side of the air-cooled rear end cover 50 and is locked by a circle of bolt locking members; a centrifugal wind bin 11 is formed on the inside of the air guide cover 9, and a circle of air outlets 12 connected to the centrifugal wind bin 11 are formed between the inner ring of the front end of the air guide cover 9 and the outer ring of the rear end of the heat dissipation housing 13. The air blown out of the air outlet 12 is blown along the heat dissipation housing 1 3 is blown toward each heat dissipation fin 100 in a direction parallel to the axis of the motor; the front and rear parts of the motor rotor shaft 16 are respectively coaxially rotated with the inner ring of the front cover 5 and the inner ring of the air-cooled rear cover 50 through bearings 30; the front end of the motor rotor shaft 16 is the rotor shaft output end 3, and the rear end extends to the centrifugal air bin 11, and the centrifugal air bin 11 is coaxially provided with a conical centrifugal impeller 10, which is coaxially fixedly installed at the tail of the motor rotor shaft 16; the front end of the front cover 5 is integrally provided with an extended neck tube 5b, and between the inner ring of the extended neck tube 5b and the outer wall of the motor rotor shaft 16, at least a labyrinth shaft oil seal 28, a skeleton oil seal 29 and a ball bearing 30 are coaxially installed from the outside to the inside.

[0034] In this solution, since the air-cooled rear end cover 50 can directly receive the high-speed cooling airflow in the centrifugal air silo 11, there is no obvious cooling problem; and the extended neck tube 5b of the front end cover 5 is far away from the conical centrifugal impeller 10, and the inner ring of the extended neck tube 5b cannot directly receive the cooling air generated by the conical centrifugal impeller 10, which leads to the problem that the friction heat generated by the labyrinth axial surface oil seal 28, the skeleton oil seal 29 and the inner ring of the ball bearing 30 and the surface of the motor rotor shaft 16 is easily accumulated and cannot be effectively discharged, and then it is easy to cause high-temperature damage and loss of sealing performance. In addition, the coaxiality will be affected to a certain extent during the direct connection with the reducer. Therefore, the outer peripheral surface of the front of the motor rotor shaft 16 and the labyrinth axial surface oil seal 28, the skeleton oil seal 29 and the inner ring of the ball bearing 30 are more likely to generate friction heat; for this reason, the following structure is designed:

[0035] like Figures 3 to 7 As shown, in this solution, a section of the motor rotor shaft 16 outside the labyrinth oil seal 28 has a circle of shaft shoulder end face 17, as shown in FIG. Figure 3 A circle of pulse breathing holes 18a equidistantly distributed in a circular array is provided on the shoulder end face 17 .

[0036] like Figure 6 and 7 The outer conical surface of the conical centrifugal impeller 10 is provided with centrifugal blades 27, and the inner ring of the conical centrifugal impeller 10 is coaxially connected to a sleeve 20. The sleeve 20 contains a pressure air chamber 26, and the pressure air chamber 26 is sealed with a flexible diaphragm 40 at one end close to the motor rotor shaft 16. The outer contour of the flexible diaphragm 40 is sealed and connected to the inner contour of the sleeve 20. The flexible diaphragm 40 can be an elastic material, such as a relaxed elastic silicone diaphragm. When the pressure in the pressure air chamber 26 changes alternately, the flexible diaphragm 40 will fluctuate alternately; with the root contour of the conical centrifugal impeller 10 as the boundary, the sleeve 20 is divided into a sleeve a section 20a and a sleeve b section 20b, wherein the sleeve a section 20a is closer to the motor rotor shaft 16.

[0037] The outer ring of the end of the sleeve section a 20a is provided with an external thread 22; the tail end of the motor rotor shaft 16 is coaxially provided with an internal threaded hole 27; the external thread 22 is threadedly engaged with the internal threaded hole 27 and is reinforced with anti-loosening thread glue or other anti-loosening devices. To prevent falling off, when the motor is running, the wind load torque applied to the conical centrifugal impeller 10 causes the external thread 22 and the internal threaded hole 27 to tend to tighten; when the external thread 22 and the internal threaded hole 27 are threadedly engaged and tightened, a columnar pressure transmission cavity 41 is formed between the bottom surface of the internal threaded hole 27 and the flexible diaphragm 40;

[0038] A number of pulse air guide channels 18 are distributed in a circular array close to the rotor shaft circumference 16a inside the motor rotor shaft 16. The pulse air guide channels 18 extend along the axial direction of the motor rotor shaft 16. The front ends of the pulse air guide channels 18 are respectively connected to a number of pulse breathing holes 18a, and the rear ends of the pulse air guide channels 18 are all connected to the columnar pressure transmission cavity 41; the inner diameter of the pulse air guide channel 18 is very small, and the inner diameter range of the pulse air guide channel 18 is 0.8mm to 1.5mm, which is adaptively designed according to actual conditions; a number of air inlet mesh holes 50 are hollowed out on the tail end wall 23 of the air guide cover 9.

[0039] A hole-blocking column 24 is coaxially provided at the inner axis of the tail end wall 23 of the air guide cover 9, and a semi-cylindrical air distribution valve core 25 is coaxially provided at the end of the hole-blocking column 24. The outer peripheral surface of the semi-cylindrical air distribution valve core 25 is on the same circumferential surface as the outer peripheral surface of the hole-blocking column 24; the integrated structure formed by the hole-blocking column 24 and the semi-cylindrical air distribution valve core 25 coaxially extends into the pressure air chamber 26, and the outer peripheral surface of the integrated structure formed by the hole-blocking column 24 and the semi-cylindrical air distribution valve core 25 is gap-matched with the inner wall surface of the pressure air chamber 26, and the gap range is: 0.02-0.18mm. This gap allows relative rotation without sliding friction while achieving a relatively airtight degree (relative to the pressure distribution hole a 42 and the pressure distribution hole b 43 mentioned later).

[0040] A pressure-matching hole a 42 with a diameter greater than 10 mm is vertically hollowed out on the sleeve section a 20a, and a pressure-matching hole b 43 with a diameter greater than 10 mm is vertically hollowed out on the sleeve section b 20b; from the axial perspective of the sleeve 20, the pressure-matching hole a 42 and the pressure-matching hole b 43 are centrally symmetrical relative to the axis of the sleeve 20; during the rotation of the sleeve 20 along the axis, the outer arc surface of the semi-cylindrical gas distribution valve core 25 periodically and alternately blocks the pressure-matching hole a 42 and the pressure-matching hole b 43.

[0041] Core working principle:

[0042] When the motor is working normally, it rotates at a speed of about 20pr / s, so that the conical centrifugal impeller 10 rotates at a high speed of 20pr / s;

[0043] In this solution, when the conical centrifugal impeller 10 rotates at high speed, the air pressure on the outer conical surface with blades will be significantly higher than the air pressure on the inner conical surface without blades. This phenomenon is mainly determined by the following three physical mechanisms:

[0044] 1. When the blades rotate at high speed with the conical centrifugal impeller 10, the gas on the outer conical surface of the conical centrifugal impeller 10 is pushed by the blades 27, and the molecular density increases. According to the ideal gas state equation (PV=nRT), when the gas volume is limited, the density increases, resulting in a corresponding increase in pressure. The blades directly work on the airflow, converting its kinetic energy into pressure energy; the airflow on the pressure surface of the blades is squeezed, and the static pressure increases;

[0045] 2. The air on one side of the conical surface of the conical centrifugal impeller 10 generates a vortex due to airflow separation, and the static pressure decreases; this pressure difference forms a pressure gradient, driving the gas to flow from the blade side to the bladeless side;

[0046] 3. The tip of the blade-following conical centrifugal impeller 10 guides the airflow to concentrate and diffuse outward along the conical surface; the constraint of the outer conical surface of the blade-following conical centrifugal impeller 10 causes the airflow to form a slight compression zone in the area near the center on one side of the outer conical surface, while the airflow on the inner conical surface of the bladeless side is not actively compressed.

[0047] Therefore, the air pressure distribution of the conical centrifugal impeller 10 is essentially the superposition result of the centrifugal supercharging effect of the rotating machinery and the active work of the blades; the working surface of the blades generates high pressure by directly compressing the gas and guiding the centrifugal motion, while the air pressure on the bladeless side is always low due to the lack of active compression mechanism, the existence of flow separation and low-pressure tail flow.

[0048] In this solution, the outer end of the pressure-matching hole a 42 is connected to the relatively low-pressure air on the side of the inner conical surface of the conical centrifugal impeller 10 without blades, while the outer end of the pressure-matching hole b 43 is connected to the relatively high-pressure air on the side of the outer conical surface of the conical centrifugal impeller 10 with blades; therefore, there is always a significant air pressure difference between the outer end of the pressure-matching hole a 42 and the outer end of the pressure-matching hole b 43.

[0049] When the conical centrifugal impeller 10 and the sleeve 20 rotate at high speed, since the integrated structure formed by the blocking column 24 and the semi-cylindrical air distribution valve core 25 is stationary, the outer arc surface of the semi-cylindrical air distribution valve core 25 periodically and alternately blocks the pressure distribution hole a 42 and the pressure distribution hole b 43, thereby causing the pressure distribution hole a 42 and the pressure distribution hole b 43 to be periodically and alternately connected to the pressure air chamber 26 at a high frequency, thereby causing the air pressure in the pressure air chamber 26 to change periodically at a high frequency, thereby causing the flexible diaphragm 40 to follow the back and forth pulse fluctuations; the fluctuation frequency is about 20 times per second.

[0050] During the back-and-forth pulse fluctuation of the flexible diaphragm 40, the volume and pressure of the columnar pressure transmission cavity 41 fluctuate periodically at high frequency. The periodic high-frequency pulse fluctuation of the pressure is transmitted to the pulse breathing holes 18a through the pulse air guide channels 18, thereby ultimately causing the pulse breathing holes 18a to perform high-frequency pulse breathing.

[0051] During the high-frequency pulse breathing of the pulse breathing hole 18a, the external air is sucked into the front section of the pulse air guide channel 18 from the pulse breathing hole 18a and then exhaled quickly in the form of pulses, so that the heat near the outer peripheral surface of the motor rotor shaft 16 where the labyrinth oil seal 28, the skeleton oil seal 29 and the ball bearing 30 are located in the front of the motor rotor shaft 16 is quickly exchanged with the outside world under the action of high-frequency breathing, thereby achieving efficient heat dissipation of the outer peripheral surface of the motor rotor shaft 16 where the labyrinth oil seal 28, the skeleton oil seal 29 and the ball bearing 30 are located; and avoiding thermal failure of the inner ring of the labyrinth oil seal 28, the skeleton oil seal 29 and the ball bearing 30.

[0052] The motor of this solution can be used alone when not matched with the reducer 4, and the pulse breathing hole 18a is directly connected to the outside world to directly achieve the best heat dissipation performance.

[0053] like Figure 2 、 3 4. When the motor of this solution is required to be directly connected to the input end of reducer 4, the following necessary structures are designed:

[0054] The front end cover 5 is coaxially connected to the flange 5c through the front end of the extended neck tube 5b. The rotor shaft output end 3 is coaxially connected to the input shaft of the reducer 4 through a keyway. At the same time, the flange 5c at the front end of the front end cover 5 is coaxially locked to the input end flange of the reducer 4 through flange bolts. When the flange 5c of the front end cover 5 and the input end flange of the reducer 4 are locked, a cavity connected to the outside world is formed in the center between the flange 5c of the front end cover 5 and the input end flange of the reducer 4. The cavity is connected to each pulse breathing hole 18a, and the cavity is connected to the outside world through a number of oblique through holes 19 on the flange 5c.

[0055] The above are only preferred embodiments of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present invention. These improvements and modifications should also be regarded as the scope of protection of the present invention.

Claims

1. A flanged end cover motor that can be directly connected to a reducer, characterized in that: It comprises a motor rotor shaft (16), an air-cooled rear end cover (50), a front end cover (5) and an air guide cover (9); The air guide cover (9) is coaxially arranged on the rear side of the air-cooled rear end cover (50), and a centrifugal air silo (11) is formed inside the air guide cover (9); The front end of the motor rotor shaft (16) is the rotor shaft output end (3), and the rear end extends into the centrifugal wind silo (11), wherein a conical centrifugal impeller (10) is arranged in the centrifugal wind silo (11); The front end of the front end cover (5) is integrally provided with an extended neck tube (5b), and between the inner ring of the extended neck tube (5b) and the outer wall of the motor rotor shaft (16), at least a labyrinth-type axial surface oil seal (28), a skeleton oil seal (29) and a ball bearing (30) are coaxially installed from the outside to the inside; A shaft shoulder end face (17) is provided on a section of the motor rotor shaft (16) outside a labyrinth-type shaft oil seal (28). The shaft shoulder end face (17) is provided with a circle of pulse breathing holes (18a) distributed in a circumferential array at equal intervals.

2. A flange-end-cover motor capable of being directly connected to a reducer according to claim 1, characterized in that: The front end cover (5) is coaxially connected to a flange (5c) through the front end of the extended neck tube (5b); the rotor shaft output end (3) is coaxially and synchronously connected to the input shaft of the reducer (4) through a keyway, and the flange (5c) at the front end of the front end cover (5) is coaxially locked to the input end flange of the reducer (4) through flange bolts.

3. A flange-end-cover motor capable of being directly connected to a reducer according to claim 2, characterized in that: When the flange (5c) of the front end cover (5) and the input end flange of the reducer (4) are locked, a cavity communicating with the outside world is formed in the center between the flange (5c) of the front end cover (5) and the input end flange of the reducer (4). The cavity is connected to each pulse breathing hole (18a), and the cavity is connected to the outside world through a plurality of oblique through holes (19) on the flange (5c).

4. The flange end cover type motor capable of being directly connected to a reducer according to claim 1, characterized in that: The outer conical surface of the conical centrifugal impeller (10) is provided with centrifugal blades (27), the inner ring of the conical centrifugal impeller (10) is coaxially connected to a sleeve (20), the sleeve (20) contains a pressure chamber (26), and a flexible diaphragm (40) is sealed at one end of the pressure chamber (26) close to the motor rotor shaft (16), the outer contour of the flexible diaphragm (40) is sealed and connected to the inner contour of the sleeve (20), and when the pressure in the pressure chamber (26) changes alternately, the flexible diaphragm (40) will fluctuate alternately; The sleeve (20) is divided into a sleeve a section (20a) and a sleeve b section (20b) with the root profile of the conical centrifugal impeller (10) as the boundary, wherein the sleeve a section (20a) is closer to the motor rotor shaft (16); The outer ring of the end of the sleeve section a (20a) is provided with an external thread (22); the tail end of the motor rotor shaft (16) is coaxially provided with an internal threaded hole (27); the external thread (22) and the internal threaded hole (27) are threadedly matched, and when the external thread (22) and the internal threaded hole (27) are threadedly matched and tightened, a columnar pressure transmission cavity (41) is formed between the bottom surface of the internal threaded hole (27) and the flexible diaphragm (40); A plurality of pulse air guide channels (18) are distributed in a circumferential array in the motor rotor shaft (16) close to the rotor shaft circumference (16a), the pulse air guide channels (18) extend along the axis of the motor rotor shaft (16), the front ends of the plurality of pulse air guide channels (18) are respectively connected to the plurality of pulse breathing holes (18a), and the rear ends of the plurality of pulse air guide channels (18) are all connected to the columnar pressure transmission cavity (41); A hole-blocking column (24) is coaxially provided at the inner side axis of the tail end wall (23) of the air guide cover (9), and a semi-cylindrical gas distribution valve core (25) is coaxially provided at the end of the hole-blocking column (24). The outer peripheral surface of the semi-cylindrical gas distribution valve core (25) and the outer peripheral surface of the hole-blocking column (24) are on the same circumferential surface; the integral structure formed by the hole-blocking column (24) and the semi-cylindrical gas distribution valve core (25) coaxially extends into the pressure air chamber (26), and the outer peripheral surface of the integral structure formed by the hole-blocking column (24) and the semi-cylindrical gas distribution valve core (25) is clearance-matched with the inner wall surface of the pressure air chamber (26); A pressure-matching hole a (42) is vertically hollowed out on the sleeve section a (20a), and a pressure-matching hole b (43) is vertically hollowed out on the sleeve section b (20b); during the sleeve (20) rotating along the axis, the outer arc surface of the semi-cylindrical gas distribution valve core (25) periodically and alternately blocks the pressure-matching hole a (42) and the pressure-matching hole b (43).

5. The flange end cover type motor capable of being directly connected to a reducer according to claim 4, characterized in that: From an axial perspective of the sleeve (20), the pressure-matching hole a (42) and the pressure-matching hole b (43) are centrally symmetrical relative to the axis of the sleeve (20).

6. The flange-end-cover type motor capable of being directly connected to a reducer according to claim 4, characterized in that: When the motor is running, the wind load torque applied to the conical centrifugal impeller (10) causes the external thread (22) and the internal thread hole (27) to be tightened.

7. A flange-end-cover type motor capable of being directly connected to a reducer according to claim 6, characterized in that: The inner diameter of the pulse air guide channel (18) ranges from 0.8 mm to 1 mm; the clearance between the outer peripheral surface of the integral structure formed by the hole blocking column (24) and the semi-cylindrical air distribution valve core (25) and the inner wall surface of the pressure air chamber (26) ranges from 0.02 to 0.1 mm.

8. The flange-end-cover motor capable of being directly connected to a reducer according to claim 7, characterized in that: A plurality of air inlet mesh holes (50) are hollowed out on the rear end wall (23) of the air guide cover (9).

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