CN118881587A - Energy-saving non-frequency-converting speed-regulating centrifugal fan and control method thereof - Google Patents

Abstract

The invention discloses an energy-saving non-variable frequency speed regulation centrifugal fan and a control method thereof, and relates to the technical field of centrifugal pumps, comprising a driving motor, wherein one side of the driving motor is connected with a fan shell, and the fan shell is provided with an input port and an output port; the inner side of the fan shell is provided with a driving impeller, one side of the driving impeller is connected with an impeller shaft, one end of the impeller shaft away from the driving impeller is connected with a transmission mechanism, the output end of the driving motor is connected with a driving shaft, and the driving shaft is meshed with the transmission mechanism; the starting resistance of the driving motor is greatly reduced, the reverse impact force to the rotor inside the driving motor is also greatly reduced, when the driving impeller is blocked by foreign matters, the power between the driving shaft and the impeller shaft can be timely and automatically separated, the driving motor is prevented from being overheated and damaged, after the driving impeller discharges the foreign matters, the power between the driving shaft and the impeller shaft can be automatically recovered, and the working effect of the energy-saving non-variable frequency speed regulation centrifugal fan is ensured.

Description

Energy-saving non-frequency-converting speed-regulating centrifugal fan and control method thereof

Technical Field

The invention relates to the technical field of centrifugal pumps, and in particular to an energy-saving non-variable frequency speed regulating centrifugal fan and a control method thereof.

Background Art

Existing speed-regulating centrifugal fans, for example, a single-stage high-speed centrifugal fan speed regulating system and speed regulating method for desulfurization disclosed in Chinese patent publication number CN108412798A, and an outer rotor centrifugal fan using electromagnetic bearings disclosed in Chinese patent publication number CN104481899A. When such centrifugal fans are working, when the blades inside the fan are stuck by foreign objects, the motor connected to the fan will also be stuck. When the motor is stuck, the inside will heat up, causing the motor to be easily damaged.

Summary of the invention

In order to overcome the above-mentioned technical problems, the purpose of the present invention is to provide an energy-saving non-variable frequency speed regulation centrifugal fan and a control method thereof, so as to solve the problem in the prior art that when the blades inside the fan are stuck by foreign objects, the motor connected to the fan will also be stuck, and the input electrical energy of the motor will be directly converted into thermal energy, causing the inside of the motor to heat up quickly, resulting in the problem that the motor is easily burned out.

The purpose of the present invention can be achieved through the following technical solutions:

The first aspect of the present invention is to provide an energy-saving non-variable frequency speed regulating centrifugal fan, including a driving motor, one side of the driving motor is connected to a fan casing, an input port and an output port are provided on the fan casing, a driving impeller is arranged on the inner side of the fan casing, one side of the driving impeller is connected to an impeller shaft, an end of the impeller shaft away from the driving impeller is connected to a transmission mechanism, the output end of the driving motor is connected to a driving shaft, and the driving shaft is meshed with the transmission mechanism.

As a further solution of the present invention: the driving impeller comprises a rotating disk, and a plurality of impeller blades are fixedly connected to a side of the rotating disk away from the impeller shaft.

As a further solution of the present invention: a centrifugal track is provided on one side of the rotating disk away from the impeller blades, a centrifugal slider is provided inside the centrifugal track, one end of the centrifugal track is connected to an annular channel, and the other end of the centrifugal track is connected to a connecting hole.

As a further solution of the present invention: a pressure track is provided on the side of the rotating disk away from the impeller blades, one end of the pressure track is connected to the annular channel, and the centrifugal track and the pressure track are evenly arranged on the side of the rotating disk.

As a further solution of the present invention: a hydraulic cavity is provided on the inner side of the impeller shaft, one end of the pressure track away from the annular channel is connected to the hydraulic cavity, and the hydraulic cavity is filled with hydraulic oil.

As a further solution of the present invention: a control shaft is inserted into the inner side of the hydraulic cavity.

As a further solution of the present invention: the end face of the driving shaft is fixedly connected with a friction shaft and an active tooth, a friction groove is provided at one end of the control shaft close to the friction shaft, and an antimony block and a sliding extrusion block are arranged inside the control shaft near the friction groove.

As a further solution of the present invention: the transmission mechanism includes a mechanism body, a side of the mechanism body is fixedly connected with a driving tooth, and a side of the impeller shaft is provided with a shaft tooth groove matching the driving tooth.

As a further solution of the present invention: a sliding groove and a through groove are provided on the inner side of the mechanism body, a driven tooth matching the sliding groove is provided on the inner side of the sliding groove, the driven tooth matches the driving tooth, and one end of the control shaft is fixedly connected to the end face of the driven tooth.

The second aspect of the present invention is to provide a control method for an energy-saving non-variable frequency speed regulating centrifugal fan, comprising the following steps:

S1: Install a pressure sensor and a flow sensor on the inner side of the protective shell, and collect pressure data and flow data of the fluid inside the protective shell through the pressure sensor and the flow sensor;

S2: Generate a change curve of pressure data and flow data of the fluid inside the protective shell based on the change of the speed of the driving motor;

S3: The pressure sensor and flow sensor collect the pressure data and flow data of the fluid inside the protective shell in real time;

S4: Based on the real-time collected pressure data and flow data of the fluid inside the protective shell and the change curve, the speed data of the driving motor is automatically generated;

S5: Controlling the speed of the drive motor based on the automatically generated speed data of the drive motor.

Beneficial effects of the present invention:

In the present invention, by providing a driving shaft, an impeller shaft and a transmission mechanism, when the driving motor is just turned on, the high-speed rotating active teeth will squeeze the driven teeth, causing the driven teeth to move toward the inner end of the sliding groove. Since one end of the control shaft is fixedly connected to the end face of the driven teeth, the moving driven teeth will drive the control shaft to move synchronously, so that the driven teeth will not mesh with the active teeth, and the power of the driving shaft will not be transmitted to the main body of the mechanism, so that the starting resistance of the driving motor is greatly reduced, and the counter-impact force on the rotor inside the driving motor is also greatly reduced. When the driving impeller is stuck by foreign matter, the power between the driving shaft and the impeller shaft can be automatically separated in time to prevent the driving motor from being overheated and damaged. After the driving impeller expels the foreign matter, the power between the driving shaft and the impeller shaft can be automatically restored to ensure the working effect of the energy-saving non-variable frequency speed regulation centrifugal fan.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention will be further described below in conjunction with the accompanying drawings.

FIG1 is a schematic structural diagram of an energy-saving non-variable speed regulating centrifugal fan according to the present invention;

FIG2 is a side view of the energy-saving non-variable speed regulating centrifugal fan of the present invention;

3 is a schematic diagram of the internal structure of the energy-saving non-variable speed regulating centrifugal fan of the present invention;

FIG4 is a schematic diagram of the structure of the driving impeller in the present invention;

FIG5 is a front view of the driving impeller of the present invention;

FIG6 is a schematic diagram of the structure of the rotating disk of the present invention;

FIG7 is a cross-sectional view of the rotating disk of the present invention;

FIG8 is a schematic structural diagram of the transmission mechanism of the present invention;

FIG9 is a partial cross-sectional view of the control shaft of the present invention;

10 is a schematic diagram of the structure of the transmission mechanism and the drive shaft of the present invention;

11 is a schematic diagram of the structure of the transmission mechanism of the present invention;

FIG. 12 is a schematic diagram of the structure of the driven tooth in the present invention.

In the figure: 1. driving motor; 11. driving shaft; 12. friction shaft; 13. driving tooth; 14. friction head; 141. positioning surface; 2. protective shell; 3. fan shell; 31. driving impeller; 311. rotating disk; 312. impeller blade; 313. centrifugal track; 314. centrifugal slider; 315. annular channel; 316. pressure track; 317. connecting hole; 318. hydraulic chamber; 319. sealing disk; 32. impeller shaft; 321. shaft tooth groove; 33. transmission mechanism; 331. mechanism body; 332. driving tooth; 333. sliding groove; 334. through groove; 34. control shaft; 341. antimony block; 342. extrusion block; 35. driven tooth; 4. input port; 5. output port.

DETAILED DESCRIPTION

The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

Example 1

As shown in Figures 1 to 12, the present invention discloses an energy-saving non-variable frequency speed-regulating centrifugal fan, including a driving motor 1, a fan casing 3 is connected to one side of the driving motor 1, an input port 4 and an output port 5 are provided on the fan casing 3, the input port 4 is used to connect the input pipeline of the fluid, and the output port 5 is used to connect the output pipeline of the fluid. When the energy-saving non-variable frequency speed-regulating centrifugal fan is working, the fan casing 3 can suck the fluid from the input pipeline and the input port 4, and then discharge it from the output port 5 and the output pipeline, so as to realize the conveying function of the fluid. A driving impeller 31 is arranged on the inner side of the fan casing 3, and an impeller shaft 32 is connected to one side of the driving impeller 31, and an end of the impeller shaft 32 away from the driving impeller 31 is connected to There is a transmission mechanism 33, and the output end of the driving motor 1 is connected to the driving shaft 11, and the driving shaft 11 is meshed with the transmission mechanism 33. When in use, the driving motor 1 is turned on, and the power of the driving motor 1 can be transmitted to the transmission mechanism 33 through the driving shaft 11, and the transmission mechanism 33 then transmits the power to the driving impeller 31 through the impeller shaft 32, so as to realize the high-speed rotation of the driving impeller 31. The high-speed rotating driving impeller 31 will cause the fluid entering the fan casing 3 to generate centrifugal force, as shown in Figures 1 and 2, and the fluid generating the centrifugal force will enter the output port 5, and finally be discharged from the output pipe, while the high-speed rotating driving impeller 31 can continuously inhale the fluid through the input port 4, so as to ensure that the fluid is continuously transported.

As shown in Figures 5 and 6, the driving impeller 31 includes a rotating disk 311, and a plurality of impeller blades 312 are fixedly connected to the side of the rotating disk 311 away from the impeller shaft 32. It should be noted that the plurality of impeller blades 312 are evenly fixed on one side of the rotating disk 311, and the impeller blades 312 are formed in an arc shape. Taking Figure 5 as an example, the impeller blades 312 in Figure 5 will rotate counterclockwise at high speed when working, and the arc-shaped impeller blades 312 help the fluid to be discharged from the gap cavity between the impeller blades 312 into the output port 5.

As shown in Figure 6, a centrifugal track 313 is provided on the side of the rotating disk 311 away from the impeller blade 312, and a centrifugal slider 314 is provided on the inner side of the centrifugal track 313. One end of the centrifugal track 313 is connected to an annular channel 315, and the other end of the centrifugal track 313 is connected to a connecting hole 317. It should be noted that the centrifugal slider 314 matches the centrifugal track 313. When the rotating disk 311 rotates at a high speed, the centrifugal slider 314 in the centrifugal track 313 will inevitably be affected by the centrifugal force. Since the other end of the centrifugal track 313 is connected to the connecting hole 317, the fluid inside the fan casing 3 can enter the centrifugal track 313 through the connecting hole 317, and will act on one end of the centrifugal slider 314. The centrifugal slider 314 will be affected by the pressure and centrifugal force of the fluid at the same time, and move toward one end of the annular channel 315 in the centrifugal track 313.

As shown in FIG6 , a pressure track 316 is provided on one side of the rotating disk 311 away from the impeller blade 312, one end of the pressure track 316 is connected to the annular channel 315, and the centrifugal track 313 and the pressure track 316 are evenly arranged on the side of the rotating disk 311. It should be noted that since one end of the pressure track 316 is connected to the annular channel 315 and one end of the centrifugal track 313 is connected to the annular channel 315, the pressure track 316 is connected to the centrifugal track 313 through the annular channel 315. Taking FIG6 as an example, the pressure track 316 and the centrifugal track 313 are connected. There are three groups of 13, so that the angle between the pressure track 316 and the centrifugal track 313 is sixty degrees, and they are evenly opened on the side of the rotating disk 311. In this way, when the rotating disk 311 rotates at a high speed, the pressure track 316 and the centrifugal track 313 will evenly bear the centrifugal force, ensuring that the rotating disk 311 will not generate a deflection force during the high-speed rotation, making the rotation of the rotating disk 311 more stable. The outer side of the rotating disk 311 is sealed with a sealing disk 319, and the sealing disk 319 is used to seal the centrifugal track 313, the annular channel 315 and the pressure track 316.

It should also be noted that the pressure rails 316 and the centrifugal rails 313 are interconnected through the annular channel 315 , so that a communicating vessel is formed between multiple groups of pressure rails 316 and centrifugal rails 313 .

As shown in FIGS. 5, 6 and 7, a hydraulic chamber 318 is provided on the inner side of the impeller shaft 32, and one end of the pressure track 316 away from the annular channel 315 is connected to the hydraulic chamber 318, and the hydraulic chamber 318 is filled with hydraulic oil. It should be noted that when the rotating disk 311 rotates at a high speed, the centrifugal slider 314 in the centrifugal track 313 is subjected to the centrifugal force. Since the other end of the centrifugal track 313 is connected with a connecting hole 317, the fluid inside the fan housing 3 can enter the centrifugal track 313 through the connecting hole 317, so that It will act on one end of the centrifugal slider 314, and the centrifugal slider 314 will be simultaneously subjected to the pressure and centrifugal force of the fluid, and move toward one end of the annular channel 315 in the centrifugal track 313, while the hydraulic chamber 318, the pressure track 316 and the annular channel 315 are all filled with hydraulic oil. In this way, when the centrifugal slider 314 moves toward one end of the annular channel 315, the centrifugal slider 314 will squeeze the hydraulic oil in the pressure track 316, thereby increasing the hydraulic oil pressure in the hydraulic chamber 318, the pressure track 316 and the annular channel 315.

As shown in FIG7 , the control shaft 34 is inserted into the inner side of the hydraulic chamber 318. When the hydraulic oil pressure inside the hydraulic chamber 318, the pressure track 316 and the annular channel 315 increases, the pressure of the hydraulic oil will directly act on the end face of the control shaft 34, so that the control shaft 34 is affected by the hydraulic oil pressure.

As shown in Figures 8 and 9, the end face of the driving shaft 11 is fixedly connected with the friction shaft 12 and the active tooth 13, and a friction groove is provided at one end of the control shaft 34 close to the friction shaft 12. An antimony block 341 and a sliding extrusion block 342 are provided inside the control shaft 34 near the friction groove. It should be noted that the end of the friction shaft 12 away from the driving shaft 11 is slidably connected with a friction head 14, and the friction head 14 cooperates with the friction groove at one end of the control shaft 34. The end side of the friction head 14 contacts the inner wall of the friction groove, and the diameter of the sliding part of the friction head 14 is smaller than the diameter of the friction groove, so as to ensure that the friction head 14 can rotate freely in the friction groove. In addition, it should be noted that a limiting rib is provided on the inner side of the friction shaft 12 to limit the radial position of the friction head 14, so as to ensure that when the friction shaft 12 rotates at a high speed, the friction head 14 can be driven to rotate synchronously at a high speed, and the axial position of the friction head 14 is not affected.

As shown in Figures 6 and 10, the transmission mechanism 33 includes a mechanism body 331, and the side of the mechanism body 331 is fixedly connected with a driving tooth 332. The side of the impeller shaft 32 is provided with a shaft tooth groove 321 that matches the driving tooth 332. It should be noted that during the transmission of the mechanism body 331, the driving tooth 332 on the side of the mechanism body 331 will be stuck in the shaft tooth groove 321. When the mechanism body 331 rotates at a high speed, the mechanism body 331 will drive the impeller shaft 32 to rotate synchronously at a high speed through the cooperation between the driving tooth 332 and the shaft tooth groove 321.

As shown in Figures 8, 10, 11 and 12, a sliding groove 333 and a through groove 334 are provided on the inner side of the mechanism body 331, and a driven tooth 35 matching the sliding groove 333 is provided on the inner side of the sliding groove 333. The driven tooth 35 matches the driving tooth 13, and one end of the control shaft 34 is fixedly connected to the end face of the driven tooth 35. It should be noted that since the driven tooth 35 matches the driving tooth 13, the rotating drive shaft 11 will drive the mechanism body 331 to rotate through the cooperation of the driven tooth 35 and the driving tooth 13, thereby realizing the transmission of power of the drive motor 1.

When the energy-saving non-variable frequency speed regulating centrifugal fan is used, it is divided into a starting process of the energy-saving non-variable frequency speed regulating centrifugal fan, a stalling process of the driving impeller 31 due to an external force, and an automatic recovery process of the driving impeller 31, which are specifically as follows:

Energy-saving non-variable frequency speed regulating centrifugal fan starting process: as shown in Figures 1 to 12, first, the drive motor 1 needs to be turned on. When the drive motor 1 receives the connection of the external power supply, the drive motor 1 will convert the electrical energy into kinetic energy, and the output end of the drive motor 1 will cause the drive shaft 11 to rotate at a high speed. At this time, since the driving impeller 31 is in a stopped state, the centrifugal slider 314 will not be affected by the centrifugal force. Therefore, when the drive shaft 11 drives the active tooth 13 to rotate at a high speed, the high-speed rotating active tooth 13 will squeeze the driven tooth 35, so that the driven tooth 35 moves toward the inner end of the sliding groove 333. Since one end of the control shaft 34 is fixedly connected to the end face of the driven tooth 35, the moving driven tooth 35 will drive the control shaft 34 to move synchronously, so that the driven tooth 35 will not mesh with the active tooth 13, and the power of the drive shaft 11 will not be transmitted to the mechanism body 331, so that the starting resistance of the drive motor 1 is greatly reduced, and the counter-impact force on the rotor inside the drive motor 1 will also be greatly reduced, and the friction shaft 12 on the drive shaft 11 will pass through the through groove 3 34 cooperates with the friction groove on the end face of the control shaft 34. Since the drive shaft 11 and the friction shaft 12 are fixedly connected, the drive shaft 11 will drive the friction shaft 12 to rotate at a high speed. In addition, it should be noted that a symmetrical limit block needs to be set on the side of the control shaft 34, and a limit groove matching the limit block is provided on the side wall of the hydraulic chamber 318 to limit the radial position of the control shaft 34 to prevent the control shaft 34 from rotating. When the friction shaft 12 rotates at a high speed, the friction shaft 12 will drive the friction head 14 to make the friction head 14 high The friction head 14 rotates at high speed and generates heat by friction with the groove wall of the friction groove, so that the temperature of the control shaft 34 increases. The antimony block 341 arranged inside the control shaft 34 expands when heated. The expanded volume of the antimony block 341 acts on the inner end of the extrusion block 342, so that the extrusion block 342 moves into the friction groove and is finally squeezed on the side of the friction shaft 12, so that the friction force between the friction shaft 12 and the extrusion block 342 is greatly increased, so that the friction shaft 12, the friction head 14 and the control shaft 34 are locked. The friction shaft 12 and the friction head 14 will drive the control shaft 34 to rotate, the rotating control shaft 34 will drive the impeller shaft 32 to rotate, and the rotating impeller shaft 32 will drive the driving impeller 31 to rotate. When the driving impeller 31 rotates, the centrifugal slider 314 in the centrifugal track 313 will naturally generate centrifugal force. The centrifugal slider 314 will be simultaneously affected by the pressure and centrifugal force of the fluid and move toward one end of the annular channel 315 in the centrifugal track 313. The hydraulic chamber 318, the pressure track 316 and the annular channel 317 are connected to the hydraulic chamber 318. 15 is filled with hydraulic oil. When the centrifugal slider 314 moves toward one end of the annular channel 315, the centrifugal slider 314 squeezes the hydraulic oil in the pressure rail 316, increasing the hydraulic oil pressure in the hydraulic chamber 318, the pressure rail 316 and the annular channel 315. The pressure of the hydraulic oil directly acts on the end face of the control shaft 34, so that the control shaft 34 is affected by the hydraulic oil pressure, and the control shaft 34 moves in the hydraulic chamber 318, squeezing the driven gear 35. As shown in FIG. 10, in the friction head 1 4 is provided with three groups of positioning surfaces 141, and the three groups of positioning surfaces 141 correspond to the positions of the three groups of active teeth 13 one by one. The number of the extrusion blocks 342 provided inside the control shaft 34 is also three groups, and they match the three groups of positioning surfaces 141. In addition, it should be noted that the positions of the three groups of extrusion blocks 342 are just staggered with the three groups of convex teeth on the driven teeth 35, so that when the extrusion blocks 342 act on the positioning surfaces 141, it can be ensured that the driven teeth 35 are just matched with the active teeth 13, so that when the control shaft 34 drives the driven teeth When the tooth 35 moves, the driven tooth 35 will just mesh with the active tooth 13. When the friction head 14 and the control shaft 34 rotate synchronously, no frictional heat will be generated between the friction head 14 and the control shaft 34. A protective shell 2 is nested outside the impeller shaft 32. A coolant can be set between the protective shell 2 and the impeller shaft 32 to reduce the temperature of the impeller shaft 32. In this way, the antimony block 341 will shrink and the extrusion block 342 will be out of contact. However, at this time, the driven tooth 35 is meshed with the active tooth 13, so it does not affect the rotation of the driving impeller 31.

The stalling process of the driving impeller 31 under the action of external force: as shown in Figures 1 to 12, during the operation of the driving impeller 31, if an emergency occurs, such as foreign matter entering the fan casing 3, the high-speed rotating driving impeller 31 is stuck, causing the driving impeller 31 to stall, that is, the rotation speed of the driving impeller 31 is suddenly reduced. For ordinary centrifugal pumps, since the connection between the driving motor 1 and the driving impeller 31 is fixed, when the rotation speed of the driving impeller 31 is suddenly reduced, it will inevitably cause the rotation speed of the driving motor 1 to suddenly decrease. In this way, the electrical energy in the driving motor 1 cannot be converted into kinetic energy, but will be quickly converted into heat energy, causing the internal temperature of the driving motor 1 to rise rapidly, which may easily cause the driving motor 1 to malfunction and be damaged. However, when the rotation speed of the driving impeller 31 of the energy-saving non-variable frequency speed regulating centrifugal fan of the present invention is suddenly reduced, , the centrifugal force of the centrifugal slider 314 will be reduced, that is, the force of the centrifugal slider 314 on the hydraulic oil in the pressure track 316 will be reduced. At this time, when the driving shaft 11 drives the active tooth 13 to rotate, the active tooth 13 will squeeze the driven tooth 35, so that the driven tooth 35 moves toward the inner end of the sliding groove 333. Since one end of the control shaft 34 is fixedly connected to the end face of the driven tooth 35, the moving driven tooth 35 will drive the control shaft 34 to move synchronously, so that the driven tooth 35 will not mesh with the active tooth 13, and the power of the driving shaft 11 will not be transmitted to the mechanism body 331. In this way, the stuck driving impeller 31 will not affect the operation of the driving motor 1, and the driving motor 1 can drive the driving shaft 11 to continue to rotate at a high speed, ensuring that the electrical energy inside the driving motor 1 is converted into kinetic energy in time and not converted into heat energy.

Automatic recovery process of the driving impeller 31: as shown in Figures 1 to 12, when the foreign matter entering the fan casing 3 is transported to the output port 5 by the driving impeller 31, it will not affect the continued rotation of the driving impeller 31. At this time, the driving shaft 11 will drive the friction shaft 12 to rotate at a high speed. In addition, it should be noted that symmetrical limit blocks need to be set on the side of the control shaft 34, and limit grooves matching the limit blocks are opened on the side walls of the hydraulic chamber 318 to limit the radial position of the control shaft 34 to prevent the control shaft 34 from rotating. When the friction shaft 12 rotates at a high speed, the friction shaft 12 will drive the friction head 14 to rotate at a high speed. The high-speed rotating friction head 14 and the groove wall of the friction groove will generate heat by friction, so that the temperature of the control shaft 34 increases, and the antimony block 341 set inside the control shaft 34 will The expanded volume of the antimony block 341 will act on the inner end of the extrusion block 342, causing the extrusion block 342 to move into the friction groove and finally squeeze on the side of the friction shaft 12, so that the friction force between the friction shaft 12 and the extrusion block 342 is greatly increased, ensuring that the friction shaft 12, the friction head 14 and the control shaft 34 are locked, so that the friction shaft 12 and the friction head 14 will drive the control shaft 34 to rotate, and the rotating control shaft 34 will drive the impeller shaft 32 to rotate, and the rotating impeller shaft 32 will drive the driving impeller 31 to rotate. When the driving impeller 31 rotates, it will naturally cause the centrifugal slider 314 in the centrifugal track 313 to generate centrifugal force. The centrifugal slider 314 will be simultaneously subjected to the pressure and centrifugal force of the fluid and move toward one end of the annular channel 315 in the centrifugal track 313, while the hydraulic chamber 31 8. The interior of the pressure track 316 and the annular channel 315 are filled with hydraulic oil. In this way, when the centrifugal slider 314 moves toward one end of the annular channel 315, the centrifugal slider 314 will squeeze the hydraulic oil inside the pressure track 316, so that the hydraulic oil pressure inside the hydraulic chamber 318, the pressure track 316 and the annular channel 315 increases. The pressure of the hydraulic oil will directly act on the end surface of the control shaft 34, so that the control shaft 34 is affected by the hydraulic oil pressure, and the control shaft 34 will move in the hydraulic chamber 318 to squeeze the driven teeth 35. As shown in FIG. 10, three groups of positioning surfaces 141 are provided on the side of the friction head 14. The three groups of positioning surfaces 141 correspond to the positions of the three groups of driving teeth 13 one by one. The number of the extrusion blocks 342 provided inside the control shaft 34 is also three, and they match the three groups of positioning surfaces 141. In addition, it should be noted that the positions of the three groups of extrusion blocks 342 are just staggered with the three groups of convex teeth on the driven teeth 35, so that when the extrusion block 342 acts on the positioning surface 141, it can be ensured that the driven teeth 35 are just matched with the active teeth 13, so that when the control shaft 34 drives the driven teeth 35 to move, the driven teeth 35 will just mesh with the active teeth 13, and when the friction head 14 and the control shaft 34 rotate synchronously, there will be no frictional heat between the friction head 14 and the control shaft 34. A protective shell 2 is nested outside the impeller shaft 32, and a coolant can be arranged between the protective shell 2 and the impeller shaft 32 to reduce the temperature of the impeller shaft 32, so that the antimony block 341 will shrink and the extrusion block 342 will be out of contact, but at this time the driven teeth 35 are meshed with the active teeth 13, so it does not affect the rotation of the driving impeller 31.

To sum up, through the provided drive shaft 11, impeller shaft 32 and transmission mechanism 33, when the drive motor 1 is just turned on, the high-speed rotating active tooth 13 will squeeze the driven tooth 35, so that the driven tooth 35 moves toward the inner end of the sliding groove 333. Since one end of the control shaft 34 is fixedly connected to the end face of the driven tooth 35, the moving driven tooth 35 will drive the control shaft 34 to move synchronously, so that the driven tooth 35 will not mesh with the active tooth 13, and the power of the drive shaft 11 will not be transmitted to the mechanism body 331, so that the starting resistance of the drive motor 1 is greatly reduced, and the counter-impact force on the rotor inside the drive motor 1 is also greatly reduced. When the drive impeller 31 is stuck by foreign matter, the power between the drive shaft 11 and the impeller shaft 32 can be automatically separated in time to prevent the drive motor 1 from overheating and damage. After the drive impeller 31 expels foreign matter, the power between the drive shaft 11 and the impeller shaft 32 can be automatically restored to ensure the working effect of the energy-saving non-variable frequency speed regulation centrifugal fan.

Example 2

The control method for an energy-saving non-variable frequency speed regulating centrifugal fan comprises the following steps:

S1: Install a pressure sensor and a flow sensor inside the protective shell 2, and collect pressure data and flow data of the fluid inside the protective shell 2 through the pressure sensor and the flow sensor.

It should be noted that the specifications and installation positions of the pressure sensor and the flow sensor are adaptively adjusted by technical personnel in this field according to the volume of the protective shell 2 and the inner driving impeller 31. The pressure sensor can directly collect the pressure data of the fluid inside the protective shell 2, and then convert the pressure data into an electrical signal and transmit it to the control module. The control module is loaded on the microprocessor, and the microprocessor can be installed on the drive motor 1. The drive motor 1 provides power to the microprocessor. The flow sensor directly collects the flow data of the fluid inside the protective shell 2, and then converts the flow data into an electrical signal and transmits it to the control module.

S2: Generate a change curve of the pressure data and flow data of the fluid inside the protective shell 2 based on the change in the rotation speed of the driving motor 1.

It should be noted that the speed variation range of the drive motor 1 is controlled by technicians in this field. For example, the speed level of the drive motor 1 can be divided into three stages: low speed, medium speed and high speed. The specific values of low speed, medium speed and high speed are adaptively adjusted by technicians in this field according to the specifications of the drive motor 1. Then, the drive motor 1 is turned on to make the drive motor 1 work at a low speed. The control module then collects the pressure data and flow data of the fluid inside the protective shell 2 through the pressure sensor and the flow sensor.

The drive motor 1 is turned on to operate at a medium speed, and the control module then collects pressure data and flow data of the fluid inside the protective shell 2 through a pressure sensor and a flow sensor.

The drive motor 1 is turned on to operate at a high speed, and the control module then collects pressure data and flow data of the fluid inside the protective shell 2 through a pressure sensor and a flow sensor.

Based on the three sets of pressure data and flow data, a computer is used to simulate the change curve of the pressure data and flow data. In order to make the change curve of the pressure data and flow data more accurate, the speed levels of the drive motor 1 can be divided into multiple groups, and then the corresponding number of groups of pressure data and flow data can be obtained, so as to improve the accuracy of the change curve of the pressure data and flow data.

S3: The pressure sensor and the flow sensor collect the pressure data and flow data of the fluid inside the protective shell 2 in real time.

It should be noted that, during the operation of the drive motor 1, the pressure sensor and the flow sensor collect pressure data and flow data of the fluid inside the protective shell 2 in real time, and then convert the collected pressure data and flow data into electrical signals and transmit them to the control module.

S4: Automatically generate the rotation speed data of the drive motor 1 based on the real-time collected pressure data and flow data of the fluid inside the protective shell 2 and the change curve.

It should be noted that after receiving the pressure data and flow data of the fluid inside the protective shell 2 collected in real time by the pressure sensor and the flow sensor, the control module automatically generates the speed data of the drive motor 1, that is, the speed value of the drive motor 1, based on the pre-generated flow data and the change curve of the pressure data and the flow data.

S5: Based on the automatically generated rotation speed data of the drive motor 1 , the rotation speed of the drive motor 1 is controlled.

It should be noted that the control module controls the speed of the drive motor 1 by controlling the voltage of the drive motor 1. When the voltage of the drive motor 1 increases, the magnetic flux inside the drive motor 1 increases, and the speed of the drive motor 1 also increases. When the voltage of the drive motor 1 decreases, the magnetic flux inside the drive motor 1 decreases, and the speed of the drive motor also decreases.

The above is a detailed description of an embodiment of the present invention, but the content is only a preferred embodiment of the present invention and cannot be considered to limit the scope of implementation of the present invention. All equivalent changes and improvements made within the scope of the present invention should still fall within the scope of the patent coverage of the present invention.

Claims (10)

1. The energy-saving non-variable frequency speed regulation centrifugal fan is characterized by comprising a driving motor (1), wherein one side of the driving motor (1) is connected with a fan shell (3), and an input port (4) and an output port (5) are formed in the fan shell (3);

The fan is characterized in that a driving impeller (31) is arranged on the inner side of the fan shell (3), one side of the driving impeller (31) is connected with an impeller shaft (32), one end, away from the driving impeller (31), of the impeller shaft (32) is connected with a transmission mechanism (33), the output end of the driving motor (1) is connected with a driving shaft (11), and the driving shaft (11) is meshed with the transmission mechanism (33).

2. The energy-saving non-variable frequency speed-regulating centrifugal fan according to claim 1, wherein the driving impeller (31) comprises a rotating disc (311), and a plurality of impeller blades (312) are fixedly connected to one side of the rotating disc (311) away from the impeller shaft (32).

3. The energy-saving non-variable frequency speed regulation centrifugal fan according to claim 2, wherein a centrifugal track (313) is arranged on one side, far away from the impeller blades (312), of the rotating disc (311), a centrifugal slider (314) is arranged on the inner side of the centrifugal track (313), one end of the centrifugal track (313) is connected with an annular channel (315), and the other end of the centrifugal track (313) is connected with a communication hole (317).

4. The energy-saving non-variable frequency speed regulation centrifugal fan according to claim 3, wherein a pressure rail (316) is arranged on one side of the rotating disc (311) far away from the impeller blades (312), one end of the pressure rail (316) is connected with the annular channel (315), and the centrifugal rail (313) and the pressure rail (316) are uniformly arranged on the side face of the rotating disc (311) at intervals.

5. The energy-saving non-variable frequency speed regulation centrifugal fan according to claim 4, wherein a hydraulic cavity (318) is formed in the inner side of the impeller shaft (32), one end, away from the annular channel (315), of the pressure rail (316) is communicated with the hydraulic cavity (318), and the hydraulic cavity (318) is filled with hydraulic oil.

6. The energy-saving non-variable frequency speed regulating centrifugal fan according to claim 5, wherein a control shaft (34) is inserted into the inner side of the hydraulic cavity (318).

7. The energy-saving non-variable frequency speed regulation centrifugal fan according to claim 6, wherein the end face of the driving shaft (11) is fixedly connected with a friction shaft (12) and driving teeth (13), a friction groove is formed in one end, close to the friction shaft (12), of the control shaft (34), and antimony regulus (341) and a sliding extrusion block (342) are arranged in the position, close to the friction groove, of the control shaft (34).

8. The energy-saving non-variable frequency speed-regulating centrifugal fan according to claim 7, wherein the transmission mechanism (33) comprises a mechanism main body (331), a driving tooth (332) is fixedly connected to the side surface of the mechanism main body (331), and a shaft tooth slot (321) matched with the driving tooth (332) is formed in the side surface of the impeller shaft (32).

9. The energy-saving non-variable frequency speed regulation centrifugal fan according to claim 8, wherein a sliding groove (333) and a penetrating groove (334) are formed in the inner side of the mechanism main body (331), driven teeth (35) matched with the sliding groove (333) are arranged in the inner side of the sliding groove (333), the driven teeth (35) are matched with the driving teeth (13), and one end of the control shaft (34) is fixedly connected with the end face of the driven teeth (35).

10. The control method for the energy-saving non-variable frequency speed regulation centrifugal fan as claimed in any one of claims 1 to 9, which is characterized by comprising the following steps:

S1: installing a pressure sensor and a flow sensor on the inner side of the protective shell (2), and collecting pressure data and flow data of fluid on the inner side of the protective shell (2) through the pressure sensor and the flow sensor;

S2: generating a change curve of pressure data and flow data of fluid inside the protective shell (2) based on the change of the rotating speed of the driving motor (1);

S3: the pressure sensor and the flow sensor collect pressure data and flow data of fluid inside the protective shell (2) in real time;

S4: automatically generating rotating speed data of the driving motor (1) based on pressure data and flow data of fluid inside the protective shell (2) and a change curve acquired in real time;

s5: the rotational speed of the drive motor (1) is controlled based on the automatically generated rotational speed data of the drive motor (1).