CN109882425B - Axial force balance and sealing structure and high-power density centrifugal fan - Google Patents
Axial force balance and sealing structure and high-power density centrifugal fan Download PDFInfo
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- CN109882425B CN109882425B CN201910198690.9A CN201910198690A CN109882425B CN 109882425 B CN109882425 B CN 109882425B CN 201910198690 A CN201910198690 A CN 201910198690A CN 109882425 B CN109882425 B CN 109882425B
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Abstract
The invention discloses an axial force balance and sealing structure and a high-power density centrifugal fan. According to the axial force balancing and sealing structure, the axial force balancing disc and the sealing structure are integrally designed, so that the system structure is simplified, the mass attached to the output shaft is reduced, and the influence on the dynamic characteristic of the output shaft rotating at a high speed is small. In addition, a three-layer sealing structure is designed, and the sealing reliability is ensured. The pressure cavities on the two sides of the axial force balance disc are filled with pressure gas, so that axial vibration energy of the output shaft can be well absorbed, and the effect of improving the stability of the output shaft is achieved. And a thinner gas film also exists in the gap of the sealing structure, so that the radial vibration of the output shaft can be inhibited, the output shaft is ensured to have good dynamic characteristics, and the high-speed rotation is more stable.
Description
Technical Field
The invention relates to the technical field of centrifugal fans, in particular to an axial force balancing and sealing structure, and further relates to a high-power-density centrifugal fan adopting the axial force balancing and sealing structure.
Background
With the development of centrifugal fan devices toward high speed and high power density, higher requirements are placed on the sealing of centrifugal impellers and balancing devices of axial force. The axial force generated by the centrifugal impeller is small and is directly borne by the bearing, but for high-power high-speed centrifugal fan equipment, the axial force of the centrifugal impeller is large and possibly exceeds the bearing range of the bearing, so that an axial force balance disc is generally added on a shaft, and after the axial force is reduced, the residual axial force is borne by the bearing. However, the conventional axial force balancing device may cause a complicated structure of the rotor, and in addition, air passages for supplying pressure air are required to be provided on the left and right sides of the conventional axial force balancing device so as to form a pressure difference between the two sides of the balancing disk, so that a special air passage structure is required to be designed on the left and right sides of the balancing disk, which may cause a more complicated structure of the centrifugal fan. In addition, a sealing device is required to be designed to seal the centrifugal impeller, so that the structural complexity of the centrifugal fan is further increased.
Disclosure of Invention
The invention provides an axial force balancing and sealing structure and a high-power density centrifugal fan adopting the same, and aims to solve the technical problem that the axial force balancing device and the sealing device of the conventional high-power centrifugal fan are complex in structure.
According to one aspect of the present invention, there is provided an axial force balancing and sealing structure suitable for a high power density centrifugal fan, the high power density centrifugal fan comprising an output shaft, a volute, an impeller, a sliding bearing thrust disc, a sliding bearing and a high speed gear box, the volute is mounted on an outer box of the high speed gear box, the output shaft is mounted on an inner box of the high speed gear box through the sliding bearing, the impeller is mounted on the output shaft and located in the volute, the sliding bearing thrust disc is mounted on the output shaft,
the axial force balance and seal structure comprises an axial force balance disc for playing an axial seal effect, a first seal piece for playing the axial seal effect and a radial seal effect and a second seal piece for playing the axial seal effect, wherein the axial force balance disc is installed on an output shaft, the lower end of an impeller is abutted against the axial force balance disc, the first seal piece is installed on an inner box body of the high-speed gear box and sleeved on the periphery of a sliding bearing thrust disc, the second seal piece is installed on a volute transfer section of the volute, a non-contact labyrinth seal structure is adopted between the second seal piece and the impeller, between the axial force balance disc and the volute transfer section of the volute and between the first seal piece and the sliding bearing thrust disc, and a non-contact labyrinth seal structure is adopted between the second seal piece and the impeller, between the axial force balance disc and the volute transfer section of the volute, And a gap is reserved between the first sealing element and the thrust disc of the sliding bearing.
Further, one end, close to the impeller, of the first sealing element is an axial sealing end, one end, far away from the impeller, of the first sealing element is a radial sealing end, a gap between the axial sealing end of the first sealing element and the sliding bearing thrust disc is 0.18-0.22 mm, and a gap between the radial sealing end of the first sealing element and the sliding bearing thrust disc is 0.37-0.42 mm.
Further, the clearance between the second sealing element and the impeller is 0.22-0.28 mm.
Furthermore, an annular sealing groove is formed in the end face, close to the volute adapter section, of the axial force balancing disc, and the gap between the axial force balancing disc and the volute adapter section is 0.18-0.23 mm.
Further, a first lubricating layer is arranged at a gap between the axial force balance disc and the volute adapting section, a second lubricating layer is arranged at a gap between the axial sealing end of the first sealing element and the sliding bearing thrust disc, and a third lubricating layer is arranged at a gap between the radial sealing end of the first sealing element and the sliding bearing thrust disc.
Furthermore, the first lubricating layer, the second lubricating layer and the third lubricating layer are formed by spraying soft solid lubricants.
Further, the soft solid lubricant is molybdenum disulfide.
Further, the axial force balance disc is machined by forged aluminum.
Further, the high speed gearbox employs helical teeth for torque transmission.
The invention also provides a high power density centrifugal fan which comprises the axial force balancing and sealing structure.
The invention has the following beneficial effects:
according to the axial force balancing and sealing structure, the axial force balancing disc and the sealing structure are integrally designed, the axial force balancing and sealing structure is integrated, the system structure is simplified, the mass attached to the output shaft is reduced, and the influence on the dynamic characteristic of the output shaft rotating at high speed is small. In addition, a three-layer sealing structure is designed, and the sealing reliability is ensured. And the pressure cavities at the two sides of the axial force balance disc are filled with pressure gas and can be used as an axial additional damper of the output shaft, so that the axial vibration energy of the output shaft can be well absorbed, and the effect of improving the stability of the output shaft is achieved. And moreover, a thin gas film also exists in the gap of the sealing structure, the sealing structure can also play a role of a radial damper, the radial vibration of the output shaft can be inhibited, the output shaft is ensured to have good dynamic characteristics, the high-speed rotation is more stable, and even if the rotating speed of the impeller reaches above 40000r/min, the whole rotor system can still keep a highly stable running state.
In addition, the high-density power centrifugal fan has the advantages.
In addition to the objects, features and advantages described above, other objects, features and advantages of the present invention are also provided. The present invention will be described in further detail below with reference to the drawings.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
fig. 1 is a schematic structural view of a high power density centrifugal fan according to a preferred embodiment of the present invention.
Fig. 2 is a schematic structural view of a high power density centrifugal fan according to another angle in the preferred embodiment of the present invention.
FIG. 3 is a schematic cross-sectional view of the high speed gearbox of FIG. 1 in accordance with a preferred embodiment of the present invention.
Fig. 4 is a schematic view of the axial force balancing and sealing structure of fig. 3 in accordance with a preferred embodiment of the present invention.
Fig. 5 is a schematic block diagram of a centrifugal fan control system according to another embodiment of the present invention.
Illustration of the drawings:
1. a base; 2. a high speed gear box; 3. a volute impeller assembly; 4. a cabinet body; 5. an oil radiator; 6. an atmospheric valve; 7. a muffler assembly; 8. an oil-gas separation assembly; 9. a three-phase asynchronous motor; 10. an air outlet pipe; 11. an oil filter; 20. an inner box body; 21. an output shaft; 22. an input shaft; 23. inputting a bull gear; 24. an intermediate gear; 25. an intermediate gear shaft; 26. a gear pump; 27. an oil inlet pipe; 28. a sliding bearing; 29. a self-aligning bearing; 210. an oil tank; 211. a cylindrical roller bearing; 212. a deep groove ball bearing; 213. an outer case; 31. a volute; 32. an impeller; 33. an impeller lock nut; 34. an axial force balance disc; 35. a second seal member; 36. a first seal member; 37. a first cavity; 38. a second cavity; 39. a sliding bearing thrust disc; 341. a first lubricant layer; 342. a third lubricant layer; 343. a second lubricant layer; 41. and an air inlet.
Detailed Description
The embodiments of the invention will be described in detail below with reference to the accompanying drawings, but the invention can be embodied in many different forms, which are defined and covered by the following description.
As shown in fig. 1 and 2, a preferred embodiment of the present invention provides a high power density centrifugal fan, which includes a base 1, a high-speed gear box 2, a volute impeller assembly 3, a cabinet 4, an oil radiator 5, an air release valve 6, a noise elimination assembly 7, an oil-gas separation assembly 8, a three-phase asynchronous motor 9, an air outlet pipe 10, and an oil filter 11, wherein the cabinet 4 is mounted on the base 1, the base 1 plays a supporting role, the cabinet 4 plays a safety protection role, the high-speed gear box 2, the volute impeller assembly 3, the oil radiator 5, the air release valve 6, the three-phase asynchronous motor 9, the air outlet pipe 10, and the oil filter 11 are all mounted inside the cabinet 4, and the noise elimination assembly 7 and the oil-gas separation assembly 8 are partially located inside the cabinet 4. The cabinet body 4 comprises two installation areas, the three-phase asynchronous motor 9 is located in one installation area, the high-speed gear box 2, the volute impeller assembly 3, the cabinet body 4, the oil radiator 5, the emptying valve 6, the noise elimination assembly 7, the oil-gas separation assembly 8, the three-phase asynchronous motor 9, the gas outlet pipeline 10 and the oil filter 11 are located in the other installation area, and installation and maintenance of all the assemblies are facilitated. The high-speed gear box 2 is installed on the bottom surface of the cabinet body 4, the volute impeller assembly 3 is installed on the high-speed gear box 2, the power output gear shaft of the three-phase asynchronous motor 9 is connected with the high-speed gear box 2, the high-speed gear box 2 transmits the rotation torque of the three-phase asynchronous motor 9 to the impeller of the volute impeller assembly 3, the volute impeller assembly 3 is connected with the gas outlet pipeline 10, and the impeller of the volute impeller assembly 3 is driven by the three-phase asynchronous motor 9 to rotate at a high speed to output high-pressure gas and output the high-pressure gas to the outside through the gas outlet. The three-phase asynchronous motor 9 adopts a three-phase permanent magnet synchronous motor, so that the power loss of the motor during operation can be reduced, and the operation efficiency of the motor is improved. It can be understood that the flow channel design of the volute and the impeller in the volute impeller assembly 3 adopts a three-dimensional flow design theory, so that the operating efficiency of the centrifugal fan is greatly improved, the use cost of the centrifugal fan in long-term operation is reduced, and the energy-saving and consumption-reducing effects are obvious. It can be understood that a plurality of supporting feet are provided on the base 1 to stably support on the ground, or the bottom of the base 1 is provided with a roller capable of positioning to facilitate movement.
The high-speed gearbox 2 is integrated with a transmission system and a lubricating system, and an oil tank 210 of the lubricating system is used as a supporting structure of the transmission system, so that the structural size of the centrifugal fan is greatly reduced, and the power density of the centrifugal fan is greatly improved. Lubricating oil in the oil tank 210 circulates to transmission system through the pipeline to gear and bearing among the transmission system lubricate, and lubricated oil return flows to oil tank 210 earlier, and rethread fluid filter 11 carries out filtration treatment, then carries out the heat exchange through oil liquid radiator 5, has reduced the temperature of lubricating oil, and during the lubricating oil after the cooling reentered transmission system, thereby realized the cyclic utilization of lubricating oil. As shown in fig. 2, the cabinet 4 is provided with an air inlet 41 on the side wall close to the oil radiator 5, and the airflow enters the cabinet 4 through the air inlet 41 on the cabinet 4 and exchanges heat with the oil radiator 5 to cool the lubricated return oil, and then enters the diversion basin of the volute impeller assembly 3 and is discharged from the air outlet pipeline 10 after being accelerated by the centrifugal impeller. It will also be appreciated that, preferably, the air inlet 41 is provided with a filtering assembly (not shown) for filtering the air entering the cabinet 4 to remove particulate impurities in the air, thereby ensuring the cleanliness of the air.
The air release valve 6 is communicated with the air outlet pipeline 10, the noise elimination assembly 7 is installed above the air release valve 6, and the noise elimination assembly 7 is used for reducing pneumatic noise generated when the air release valve 6 works, so that noise pollution is greatly reduced. The silencing component 7 adopts a medium-frequency and high-frequency combined silencer, so that the noise reduction effect is better. Preferably, the cabinet body 4 is integrally wrapped with silencing cotton to prevent noise generated by the centrifugal fan during operation from leaking, so that noise pollution is further reduced.
Oil-gas separation subassembly 8 communicates through pipeline and lubricating system's oil tank 210, because the lubricating oil in the oil tank 210 has certain temperature, lubricating oil can produce the evaporation, and the gas that is mingled with oil gas passes through oil-gas separation subassembly 8 back, and gaseous exhaust hole from oil-gas separation subassembly 8 is discharged, and the lubricating oil after the separation flows back to in the oil tank 210 through the pipeline, and the hookup location of pipeline and oil tank 210 is located above the inside liquid level of oil tank 210. And, the oil tank 210 carries out the circulation of gas through oil-gas separation subassembly 8 with the external world, has reduced the inside atmospheric pressure of oil tank 210, when lubricating oil is pumped out from oil tank 210 and is lubricated bearing and gear of transmission system, can realize spraying lubricating oil at bearing and gear department high pressure, has not only reduced the operating power of pump, energy saving and consumption reduction, and lubricated effect is better moreover.
As shown in fig. 1 and 3, the high-speed gearbox 2 further includes an inner box 20, an outer box 213, an output gear shaft 21, an input shaft 22, an input large gear 23, an intermediate gear 24, an intermediate gear shaft 25, a gear pump 26, an oil inlet pipe 27, a sliding bearing 28, a self-aligning bearing 29, a cylindrical roller bearing 211 and a deep groove ball bearing 212, the inner box 20 is located inside the outer box 213, the input large gear 23, the intermediate gear 24, the intermediate gear shaft 25, the sliding bearing 28, the self-aligning bearing 29, the cylindrical roller bearing 211 and the deep groove ball bearing 212 are all located in the inner box 20, the output gear shaft 21 and the input shaft 22 are both mounted on the inner box 20 and extend out of the outer box 213, the gear pump 26 is mounted on the outer box 213 and extends into the inner box 20, one end of the oil inlet pipe 27 is communicated with the oil filter 11, and one end of the, The cylindrical roller bearing 211, the deep groove ball bearing 212, the transmission contact surfaces of the input large gear 23 and the intermediate gear shaft 25 and the transmission contact surfaces of the intermediate gear 24 and the output gear shaft 21 are positioned, so that lubricating oil is sprayed at the positions under high pressure, the lubricated return oil is directly introduced into the oil tank 210, the outer box body 213 plays a role in sealing and protecting, and the inner part of the inner box body 20 is used as a lubricating cavity and mainly plays a role in sealing. It can be understood that one end of the oil inlet pipe 27 is connected with the oil inlet of the inner case 20 and extends to the sliding bearing 28, the self-aligning bearing 29, the cylindrical roller bearing 211, the deep groove ball bearing 212, the transmission contact surfaces of the input large gear 23 and the intermediate gear shaft 25, and the transmission contact surfaces of the intermediate gear 24 and the output gear shaft 21 through the internal pipe of the inner case 20 to lubricate the above positions. The gear pump 26 is used for pumping high-pressure lubricating oil into the transmission system and pumping the lubricated return oil out of the oil tank 210, an oil inlet of the gear pump 26 is communicated with the oil tank 210, an oil outlet of the gear pump 26 is communicated with the oil filter 11, the lubricating oil in the oil tank 210 is pumped out through the gear pump 26 under high pressure, then is filtered by the oil filter 11 and then is subjected to heat exchange with the oil radiator 5 to cool the lubricating oil, and the cooled lubricating oil is communicated to the transmission system through the oil inlet pipe 27 to lubricate the transmission system. The input shaft 22, the input large gear 23, the intermediate gear 24, the intermediate gear shaft 25, the gear pump 26, the sliding bearing 28, the self-aligning bearing 29, the cylindrical roller bearing 211 and the deep groove ball bearing 212 form a transmission system of the high-speed gearbox 2, and the gear pump 26, the oil inlet pipe 27, the oil tank 210, the oil radiator 5 and the oil filter 11 form a lubricating system. The sliding bearing 28 adopts a high-performance tilting pad sliding bearing, which can allow a certain degree of misalignment of the rotating shaft and has better transmission reliability. The volute impeller assembly 3 is mounted on the outer casing 213. The input shaft 22 is connected with a motor shaft of the three-phase asynchronous motor 9 through an elastic pin coupling, and the misalignment of the rotating shaft to a certain degree is allowed. The input gearwheel 23 is mounted on the input shaft 22 and rotates synchronously with the input shaft 22, the input gearwheel 23 is in tooth fit with an intermediate gear shaft 25 for torque transmission, the intermediate gear 24 is fixedly mounted on the intermediate gear shaft 25 and rotates synchronously with the intermediate gear shaft 25, and the intermediate gear 24 is in tooth fit with the output gear shaft 21 for torque transmission to the output gear shaft 21. It is understood that both ends of the output gear shaft 21 are respectively mounted on the inner case 20 through a sliding bearing 28, both ends of the intermediate gear shaft 25 are respectively mounted on the inner case 20 through a cylindrical roller bearing 211 and a self-aligning bearing 29, and specifically, one end of the intermediate gear shaft 25 near the bottom of the inner case 20 is mounted on the inner case 20 through a self-aligning bearing 29, and one end of the intermediate gear shaft 25 near the top of the inner case 20 is mounted on the inner case 20 through a cylindrical roller bearing 211. Both ends of the input shaft 22 are respectively mounted on the inner case 20 through a deep groove ball bearing 212. In addition, the gear pump 26 is fixedly connected with the input shaft 22, the input shaft 22 can directly transmit torque to the gear pump 26, the gear pump 26 is communicated with the oil inlet pipe 27, and when the gear pump 26 is driven by the input shaft 22 to rotate, lubricating oil is pumped from the oil tank 21 through the oil inlet pipe 27 and is introduced into the inner box body 20, so that the sliding bearing 28, the self-aligning bearing 29, the cylindrical roller bearing 211, the deep groove ball bearing 212, the transmission contact surfaces of the input large gear 23 and the intermediate gear shaft 25 and the transmission contact surfaces of the intermediate gear 24 and the output gear shaft 21 are lubricated. The high-speed gearbox 2 adopts a high-speed transmission system with a large transmission ratio, the working speed of the impeller 32 can be increased to above 40000r/min, the maximum linear speed can reach above 400m/s, and the power density of the fan is greatly improved. Moreover, the gear pump 26 is directly connected with the input shaft 22 of the transmission system, so that the system structure is simplified, the gear pump 26 is driven to work by the rotation of the input shaft 22, and the power density of the centrifugal fan is improved. In addition, the high-speed gearbox 2 integrates the traditional system and the lubricating system, and the oil tank 210 of the lubricating system is used as a supporting seat of the transmission system, so that the system structure is simplified, and the power density of the centrifugal fan is improved.
As shown in fig. 3 and 4, the volute impeller assembly 3 adopts an axial force balancing and sealing structure integrated design, the volute impeller assembly 3 includes a volute 31, an impeller 32, an impeller lock nut 33, an axial force balancing disc 34, a second sealing member 35, a first sealing member 36 and a sliding bearing thrust disc 39, the impeller 32 is fixedly mounted on the output gear shaft 21 of the transmission system and locked by the impeller lock nut 33 so as to rotate synchronously with the output gear shaft 21, the volute 31 is fixedly mounted on the outer casing 213, the volute 31 is fixedly connected with the impeller 32, the impeller 32 is located inside the volute 31, the volute 31 is communicated with the gas outlet pipeline 10, the impeller 32 rotates at a high speed with the output gear shaft 21 of the transmission system so as to accelerate gas, and the generated high-pressure gas flows to the gas outlet pipeline 10 through the volute 31. The plain bearing thrust disk 39 is fixedly mounted on the output gear shaft 21 and is disposed adjacent to the plain bearing 28 for transmitting axial forces to the plain bearing 28 to be received by the plain bearing 28, it being understood that the plain bearing thrust disk 39 is disposed only on a side adjacent to the impeller 32. The first sealing element 36 is installed on the inner box body 20 and sleeved on the periphery of the sliding bearing thrust disc 39, and the first sealing element 36 can play roles of axial sealing and radial sealing. Specifically, one end of the first sealing element 36 close to the impeller 32 is an axial sealing end, one end of the first sealing element 36 far away from the impeller 32 is a radial sealing end, a non-contact labyrinth sealing structure is adopted between the first sealing element 36 and the sliding bearing thrust disc 39, an axial gap between the first sealing element 36 and the sliding bearing thrust disc 39 is 0.18 mm-0.22 mm, preferably 0.2mm, and a radial gap between the first sealing element 36 and the sliding bearing thrust disc 39 is 0.37 mm-0.42 mm, preferably 0.4 mm. It will be understood that the axial clearance refers to the clearance between the axial sealing end of the first seal 36 and the plain bearing thrust disc 39, and the radial clearance refers to the clearance between the radial sealing end of the first seal 36 and the plain bearing thrust disc 39. The non-contact labyrinth seal structure is adopted between the first sealing element 36 and the sliding bearing thrust disc 39, so that the oil and gas sealing effect can be effectively realized, and when the axial gap and the radial gap are controlled within the range, a thin gas film can be formed in the non-contact labyrinth seal structure, the radial damper can be realized, the radial vibration of the output gear shaft 21 can be restrained, and the stable output gear shaft 21 can be realized. An airflow cavity of the impeller 32 is formed among the impeller 32, the volute adapter section 311, the first sealing element 36 and the output gear shaft 21, and the airflow cavity and the lubrication cavity can be separated by the first sealing element 36, so that the excessive pressure in the inner box body 20 caused by compressed gas entering the lubrication cavity is avoided, and meanwhile, lubricating oil is prevented from entering the airflow cavity of the impeller 32 to destroy the gas cleanliness. The second sealing element 35 is fixedly installed on the volute adapter section 311, a non-contact labyrinth sealing structure is designed between the second sealing element 35 and the impeller 32, the second sealing element 35 can play a role in axial sealing, a gap between the second sealing element 35 and the impeller 32 is 0.22-0.28 mm, a throttling sealing function can be effectively played, a primary sealing effect is good, in addition, the relative linear velocity between the second sealing element 35 and the impeller 32 is the largest, if the output gear shaft 21 deforms during high-speed rotation, the abrasion is the most serious, therefore, the gap is controlled to be 0.22-0.28 mm, preferably 0.25mm, a good sealing effect can be ensured, and the second sealing element 35 and the impeller 32 can be prevented from being abraded due to the deformation of the output gear shaft 21. The axial force balance disc 34 is installed on the output gear shaft 21, the lower end of the impeller 32 abuts against the axial force balance disc 34, the axial force balance disc 34 can also play a role in axial sealing, specifically, a labyrinth seal structure is also adopted between the axial force balance disc 34 and the volute transition section 311, specifically, an annular seal groove is formed in the end face, close to the volute transition section 311, of the axial force balance disc 34, the gap between the axial force balance disc 34 and the volute transition section 311 is 0.18-0.23 mm, preferably 0.2mm, and the sealing capacity is further improved. Because the working rotating speed of the impeller 32 can reach above 40000r/min, the axial force generated by the high-speed rotation of the impeller 32 is large, and if the axial force is completely born by the sliding bearing 28, the axial force may exceed the bearing range of the sliding bearing 28, so that the high-speed rotation instability of the output gear shaft 21 is caused, and even the whole high-speed gear box 2 is damaged.
The axial force balance disc 34 of the present invention divides the airflow cavity of the impeller 32 into a first cavity 37 and a second cavity 38, high-pressure gas generated by the high-speed rotation of the impeller 32 leaks into the first cavity 37 through a gap between the second seal 35 and the impeller 32, energy loss of the high-pressure gas occurs due to the throttling action of the gap between the second seal 35 and the impeller 32, the gas pressure is reduced, gas in the first cavity 37 also leaks into the second cavity 38 from a seal gap on the axial force balance disc 34, the gas pressure in the second cavity 38 is lower than that in the first cavity 37 due to energy loss, a certain pressure difference exists between the first cavity 37 and the second cavity 38, so that an axial force is generated on both sides of the axial force balance disc 34, and the axial force generated by the pressure difference between the two cavities can counteract a part of the axial force generated by the high-speed rotation of the impeller 32, the remaining axial force is then received by the sliding bearing 28, improving the stability of the output gear shaft 21 when rotating at high speed. It can be understood that the sliding bearing 28 adopts a high-performance tilting pad sliding bearing, and the bearing effect is better, and the bearing can bear larger axial force and radial force.
It can be understood that the axial force balance disk 34 is made of forged aluminum, so that the mass is greatly reduced on the premise of ensuring the strength of the parts, and the influence on the dynamic characteristics of the output gear shaft 21 can be reduced. The input large gear 23 and the intermediate gear 24 are helical gears, and correspondingly, the teeth of the intermediate gear shaft 25 and the output gear shaft 21 are also helical gears, and the direction of the axial force generated when torque is transmitted by the tooth-tooth engagement is also opposite to the direction of the axial force generated by the high-speed rotation of the impeller 32, and thus, a force for balancing the axial force can be also exerted.
It can be understood that, as a preferable mode, a first lubricating layer 341 is further provided at the gap between the axial force balancing disk 34 and the volute adapter section 311, a second lubricating layer 343 is provided at the gap between the axial sealing end of the first sealing member 36 and the sliding bearing thrust disk 39, a third lubricating layer 342 is provided at the gap between the radial sealing end of the first sealing member 36 and the sliding bearing thrust disk 39, and the first lubricating layer 341, the second lubricating layer 343 and the third lubricating layer 342 are sprayed by a soft solid lubricant. Because the centrifugal fan with high power density needs to stride over the first-order critical rotating speed when running at high speed, the output gear shaft 21 adopts a cantilever type supporting design, and the output gear shaft 21 can generate bending deformation when the first-order critical rotating speed is exceeded, the gap of the non-contact labyrinth seal structure adopted by the invention is small, and the abrasion of the seal structure can be generated. It is understood that molybdenum disulfide is preferably used as the soft solid lubricant.
The axial force balance disc 34 and the sealing structure are integrally designed, and the axial force balance and the sealing structure are integrated, so that the system structure is simplified, the mass attached to the output gear shaft 21 is reduced, and the influence on the dynamic characteristic of the output gear shaft 21 rotating at high speed is small. In addition, a three-layer sealing structure is designed, and the sealing reliability is ensured. In addition, pressure chambers are designed on two sides of the axial force balance disk 34, the axial force generated by the pressure difference between the two pressure chambers can counteract a part of the axial force generated by the high-speed rotation of the impeller 32, and the cavities on two sides of the axial force balance disk 34 are filled with pressure gas and can be used as an axial additional damper of the output gear shaft 21, so that the axial vibration energy of the output gear shaft 21 can be well absorbed, and the effect of improving the stability of the output gear shaft 21 is achieved. In addition, a thin gas film also exists in the gap of the sealing structure, the gap can also play a role of a radial damper, the radial vibration of the output gear shaft 21 can be inhibited, the output gear shaft 21 is ensured to have good dynamic characteristics, the high-speed rotation is more stable, and even if the rotating speed of the impeller 32 reaches above 40000r/min, the whole rotor system can still keep a highly stable operation state.
It can be understood that, as shown in fig. 5, another embodiment of the present invention further provides a centrifugal fan control system for intelligently controlling the centrifugal fan as described above, the centrifugal fan control system includes a detection unit 100, a controller 200, and a wireless transmission module 300, the detection unit 100 and the wireless transmission module 300 are both connected to the controller 200, and the controller 200 is further connected to the blow valve 6 and the frequency converter of the three-phase asynchronous motor 9, respectively. The detection unit 100 is used for detecting data such as oil pressure, oil temperature, bearing temperature and vibration intensity in the high-speed gearbox 2, the detection unit 100 is also used for detecting data such as air volume and air pressure of the volute impeller assembly 3, the detection unit 100 transmits a detection result to the controller 200, and the controller 200 can control the opening degree of the vent valve 6 and/or the working frequency of a frequency converter of the three-phase asynchronous motor 9 according to the detection result of the detection unit 100. The wireless transmission module 300 can wirelessly transmit the data detected by the detection unit 100 to the cloud server, can remotely monitor the operation state of the centrifugal fan, and can pre-judge the operation state of the centrifugal fan through an expert system to realize the functions of early warning and remote fault diagnosis of the centrifugal fan. In addition, the centrifugal fan is further provided with a data interface (not shown), the data interface is connected with the controller 200, the centrifugal fan is directly connected with the central control platform through the data interface, so that remote start and shutdown are realized, meanwhile, an intelligent start mode is met, only the required air volume is remotely set on the central control platform, the central control platform can calculate the working frequency of the frequency converter of the three-phase asynchronous motor 9 and/or the opening degree of the vent valve 6 and transmit control parameters to the controller 200, and the controller 200 controls the working state of the three-phase asynchronous motor 9 and/or the vent valve 6 according to the control parameters. It can be understood that the controller 200 is a PLC, the detection unit 100 includes one or more of a lubricant pressure sensor, a lubricant temperature sensor, a bearing temperature sensor, a vibration sensor, and a wind gauge, and the wireless transmission module 300 is at least one of a 2G module, a 3G module, a GSM module, a 4G module, a 5G module, a Wifi module, and a wireless serial module.
The centrifugal fan control system can adjust the working state of the centrifugal fan according to the requirements of users, thereby realizing intelligent control, ensuring that the centrifugal fan operates in a high-efficiency and stable state and improving the reliability of the centrifugal fan. In addition, the remote power-on and power-off and intelligent power-on can be realized by connecting the central control platform; by transmitting the detection data to the cloud server, the running state of the centrifugal fan can be pre-judged through the expert system, and fault alarming and remote fault diagnosis of the centrifugal fan are achieved. The centrifugal fan control system provides a set of precise aeration scheme for a sewage treatment plant, greatly reduces the energy consumption of the water plant, and achieves the aims of energy conservation and consumption reduction.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. An axial force balance and sealing structure is suitable for a high-power-density centrifugal fan, the high-power-density centrifugal fan comprises an output shaft (21), a volute (31), an impeller (32), a sliding bearing thrust disc (39), a sliding bearing (28) and a high-speed gear box (2), the volute (31) is arranged on an outer box body (213) of the high-speed gear box (2), the output shaft (21) is arranged on an inner box body (20) of the high-speed gear box (2) through the sliding bearing (28), the impeller (32) is arranged on the output shaft (21) and is positioned in the volute (31), the sliding bearing thrust disc (39) is arranged on the output shaft (21) and is close to the sliding bearing (28),
the axial force balance and seal structure comprises an axial force balance disc (34) for playing an axial seal role, a first seal member (36) for playing an axial seal role and a radial seal role and a second seal member (35) for playing an axial seal role, wherein the axial force balance disc (34) is installed on an output shaft (21) and the lower end of an impeller (32) is abutted against the axial force balance disc (34), the first seal member (36) is installed on an inner box body (20) of the high-speed gear box (2) and sleeved on the periphery of a sliding bearing thrust disc (39), the second seal member (35) is installed on a volute transfer section (311) of a volute (31), a non-contact tooth labyrinth seal structure is adopted between the second seal member (35) and the impeller (32), between the axial force balance disc (34) and the volute transfer section (311) of the volute (31), and between the first seal member (36) and the sliding bearing thrust disc (39) And clearances are reserved between the second sealing element (35) and the impeller (32), between the axial force balance disc (34) and a volute adapter section (311) of the volute (31), and between the first sealing element (36) and a sliding bearing thrust disc (39).
2. The axial force balancing and sealing structure of claim 1,
one end, close to the impeller (32), of the first sealing element (36) is an axial sealing end, one end, far away from the impeller (32), of the first sealing element (36) is a radial sealing end, a gap between the axial sealing end of the first sealing element (36) and the sliding bearing thrust disc (39) is 0.18-0.22 mm, and a gap between the radial sealing end of the first sealing element (36) and the sliding bearing thrust disc (39) is 0.37-0.42 mm.
3. The axial force balancing and sealing structure of claim 1,
the clearance between the second sealing element (35) and the impeller (32) is 0.22-0.28 mm.
4. The axial force balancing and sealing structure of claim 1,
an annular sealing groove is formed in the end face, close to the volute transition section (311), of the axial force balancing disc (34), and the gap between the axial force balancing disc (34) and the volute transition section (311) is 0.18-0.23 mm.
5. The axial force balancing and sealing structure according to claim 2,
a first lubricating layer (341) is arranged at a gap between the axial force balance disc (34) and the volute adapter section (311), a second lubricating layer (343) is arranged at a gap between the axial sealing end of the first sealing element (36) and the sliding bearing thrust disc (39), and a third lubricating layer (342) is arranged at a gap between the radial sealing end of the first sealing element (36) and the sliding bearing thrust disc (39).
6. The axial force balancing and sealing structure according to claim 5,
the first lubricating layer (341), the second lubricating layer (343) and the third lubricating layer (342) are formed by spraying soft solid lubricants.
7. The axial force balancing and sealing structure according to claim 6,
the soft solid lubricant is molybdenum disulfide.
8. The axial force balancing and sealing structure of claim 1,
the axial force balance disc (34) is machined from forged aluminum.
9. The axial force balancing and sealing structure of claim 1,
the high-speed gear box (2) adopts helical teeth to transmit torque.
10. A high power density centrifugal fan is characterized in that,
the high power density centrifugal fan comprises the axial force balancing and sealing structure as claimed in any one of claims 1 to 9.
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| CN111120364A (en) * | 2019-12-27 | 2020-05-08 | 湖南泛航智能装备有限公司 | High-speed centrifugal compressor |
| CN113285558B (en) | 2021-04-22 | 2022-04-29 | 东南大学 | Bias magnetic field adjustable force balance type stator permanent magnet motor magnetic bearing |
| CN116447166A (en) * | 2023-04-19 | 2023-07-18 | 烟台东德实业有限公司 | Axial force balancing method for impeller of air compressor |
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| US6309174B1 (en) * | 1997-02-28 | 2001-10-30 | Fluid Equipment Development Company, Llc | Thrust bearing for multistage centrifugal pumps |
| CN104019051A (en) * | 2014-04-29 | 2014-09-03 | 北京化工大学 | Adjustable balance disk seal of centrifugal compressor |
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| KR20130074543A (en) * | 2011-12-26 | 2013-07-04 | 삼성전기주식회사 | Spindle motor |
| CN109253165A (en) * | 2018-11-15 | 2019-01-22 | 哈尔滨广瀚动力技术发展有限公司 | A kind of dish type thrust bearing with Self-balancing |
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Patent Citations (4)
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| US6309174B1 (en) * | 1997-02-28 | 2001-10-30 | Fluid Equipment Development Company, Llc | Thrust bearing for multistage centrifugal pumps |
| US9461520B2 (en) * | 2003-02-10 | 2016-10-04 | Ebara International Corporation | Cryogenic liquid rotary machinery |
| CN104019051A (en) * | 2014-04-29 | 2014-09-03 | 北京化工大学 | Adjustable balance disk seal of centrifugal compressor |
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