CN118008841A - Centrifugal air compressor and supercharging system - Google Patents
Centrifugal air compressor and supercharging system Download PDFInfo
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- CN118008841A CN118008841A CN202410216871.0A CN202410216871A CN118008841A CN 118008841 A CN118008841 A CN 118008841A CN 202410216871 A CN202410216871 A CN 202410216871A CN 118008841 A CN118008841 A CN 118008841A
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Abstract
The application discloses a centrifugal air compressor and a supercharging system, wherein the air compressor comprises a rotor dynamic balance assembly, a bearing seat assembly, an air inlet cap cover, an air inlet machine brake assembly, a diffuser machine brake assembly and an exhaust volute; the bearing seat assembly and the air inlet cap cover are respectively positioned at two ends of the rotor dynamic balance assembly, and the air inlet machine brake assembly, the diffuser machine brake assembly and the exhaust volute are respectively connected to the outside of the rotor dynamic balance assembly. The rotor dynamic balance assembly is used for enabling the air inlet machine brake assembly to suck air and apply work to the air flow through rotary motion, and enabling the air flow to enter the diffuser machine brake assembly; the diffuser gate assembly is used for carrying out speed reduction and diffusion on the air flow to obtain pressurized air; and the exhaust volute is used for collecting the pressurized gas. Through the rotational speed adjustment of rotor dynamic balance subassembly, can adjust gas flow in real time to can adjust the atmospheric pressure ratio of output in real time, and then promote air compressor's high-pressure air conversion efficiency.
Description
Technical Field
The application relates to the technical field of air compressors, in particular to a centrifugal air compressor and a supercharging system.
Background
The acoustic agglomeration technology can increase the collision and condensation efficiency of particles, has short low-frequency sound wave length and long transmission distance, is suitable for the ground emission of sound wave equipment and long-distance transmission to cloud cover, and has great application potential in the fields of artificial precipitation, artificial defogging and aerosol pollution treatment.
At present, the performance of low-frequency strong sound wave equipment mainly depends on the high-pressure air conversion efficiency of an air compressor, and when the air pressure of the existing air compressor is improved, the existing air compressor is limited by the structure and the working principle due to the lack of a component for adjusting the air flow, and the output air pressure is relatively low, so that the high-pressure air conversion efficiency of the existing air compressor is poor.
Disclosure of Invention
In view of the above, the embodiments of the present application provide a centrifugal air compressor and a pressurization system, which aim to improve the high-pressure air conversion efficiency of the air compressor by adjusting the output air pressure ratio.
In a first aspect, embodiments of the present application provide a centrifugal air compressor comprising a rotor dynamic balance assembly, a bearing housing assembly, an intake cap, an intake air brake assembly, a diffuser brake assembly, and an exhaust volute; the bearing seat assembly and the air inlet cap cover are respectively positioned at two ends of the rotor dynamic balance assembly, and the air inlet machine brake assembly, the diffuser machine brake assembly and the exhaust volute are respectively connected to the outside of the rotor dynamic balance assembly;
the rotor dynamic balance assembly is used for enabling the air inlet machine brake assembly to suck air and apply work to the air flow through rotary motion, and enabling the air flow to enter the diffuser machine brake assembly;
the diffuser gate assembly is used for carrying out speed reduction and diffusion on the airflow to obtain pressurized gas;
and the exhaust volute is used for collecting the pressurized gas.
Optionally, the rotor dynamic balance assembly comprises a central pull rod, a centrifugal impeller, an unloading disc and a transmission shaft;
The central pull rod is connected with the centrifugal impeller, the first end of the unloading disc is connected with the second end of the central pull rod, and the second end of the unloading disc is connected with the transmission shaft;
the first end of the central pull rod is connected with the front bearing assembly, and the unloading disc is connected with the transmission shaft through the rear bearing assembly.
Optionally, the front bearing assembly and the rear bearing assembly comprise bearings, bearing adjustment pads and bearing positioning rings.
Optionally, the bearing seat assembly comprises a bearing seat, a spring support, a nozzle oil seal ring assembly, a seal ring, a ventilation joint, an oil supply pipe joint and an oil return pipe joint;
The nozzle oil seal ring assembly is arranged at the first end of the bearing seat through the elastic support, the sealing ring is arranged at the second end of the bearing seat, and the bearing seat comprises the ventilation joint, the oil supply pipe joint and the oil return pipe joint.
Optionally, the nozzle oil seal assembly comprises a nozzle oil seal, an oil supply pipe and a pressing plate, wherein the oil supply pipe and the pressing plate are respectively connected to the nozzle oil seal.
Optionally, the air compressor further comprises an outer machine brake and a centrifugal brake which are positioned outside the rotor dynamic balance assembly, and the air inlet machine brake assembly, the outer machine brake, the centrifugal brake, the diffuser machine brake assembly and the exhaust volute are sequentially connected.
Optionally, the air compressor further comprises a guide basin and an air inlet filter screen assembly, wherein the guide basin is positioned on the outer wall of the rotor dynamic balance assembly;
The air guide basin is used for forming an air inlet channel with the air inlet machine gate assembly, and the air inlet filter screen assembly is located at an air inlet of the air inlet channel.
In a second aspect, an embodiment of the present application provides a supercharging system, where the supercharging system includes a centrifugal air compressor according to the first aspect, a power mechanism and a transmission mechanism, the power mechanism is connected to the transmission mechanism through a low-speed coupling, and the transmission mechanism is connected to a transmission shaft of the air compressor through a high-speed coupling.
Optionally, the power mechanism includes a driver and a controller; the controller is used for controlling the rotating speed of the driving piece so as to adjust the rotating speed of the air compressor;
The transmission mechanism comprises a speed increasing box and a coupler, the coupler comprises a high-speed coupler and a low-speed coupler, an input shaft of the speed increasing box is connected with the low-speed coupler, and an output shaft of the speed increasing box is connected with a transmission shaft of the air compressor through the high-speed coupler.
In a third aspect, embodiments of the present application provide an acoustic wave device comprising a centrifugal air compressor, a resonant horn, a whistle sound generator, and a generator as described in the first aspect.
Compared with the prior art, the embodiment of the application has the following beneficial effects:
The embodiment of the application provides a centrifugal air compressor and a supercharging system, wherein the air compressor comprises a rotor dynamic balance assembly, a bearing seat assembly, an air inlet cap cover, an air inlet machine brake assembly, a diffuser machine brake assembly and an exhaust volute; the bearing seat assembly and the air inlet cap cover are respectively positioned at two ends of the rotor dynamic balance assembly, and the air inlet machine brake assembly, the diffuser machine brake assembly and the exhaust volute are respectively connected to the outside of the rotor dynamic balance assembly. The rotor dynamic balance assembly is used for enabling the air inlet machine brake assembly to suck air and apply work to the air flow through rotary motion, and enabling the air flow to enter the diffuser machine brake assembly; the diffuser gate assembly is used for carrying out speed reduction and diffusion on the air flow to obtain pressurized air; and the exhaust volute is used for collecting the pressurized gas.
Therefore, the air inlet machine brake assembly can be driven by the rotary motion of the rotor dynamic balance assembly to suck air from the air and apply work to the air flow, so that the speed and the pressure of the air flow are improved. And then the air flow enters a diffuser gate assembly to be subjected to speed reduction and diffusion, the speed of the air flow is converted into static pressure rise, the pressure of the air is further improved, and finally the pressurized air can be collected through an exhaust volute. Through the rotational speed adjustment of rotor dynamic balance subassembly, can adjust gas flow in real time to can adjust the atmospheric pressure ratio of output in real time, and then promote air compressor's high-pressure air conversion efficiency.
Drawings
In order to more clearly illustrate this embodiment or the technical solutions of the prior art, the drawings that are required for the description of the embodiment or the prior art will be briefly described, it being obvious that the drawings in the following description are only some embodiments of the present application, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
Fig. 1 is a schematic structural view of a centrifugal air compressor according to an embodiment of the present application;
FIG. 2 is a schematic diagram of an air intake filter assembly according to an embodiment of the present application;
Fig. 3 is a schematic structural diagram of a rotor dynamic balance assembly according to an embodiment of the present application;
Fig. 4 is a schematic structural view of a bearing seat assembly according to an embodiment of the present application;
fig. 5 is a schematic structural diagram of each joint on a bearing seat according to an embodiment of the present application;
Fig. 6 is a schematic structural view of a nozzle oil seal ring assembly according to an embodiment of the present application;
Fig. 7 is a schematic structural diagram of a supercharging system according to an embodiment of the present application.
Detailed Description
In order to make the present application better understood by those skilled in the art, the following description will clearly and completely describe the technical solutions in the embodiments of the present application with reference to the accompanying drawings, and it is apparent that the described embodiments are only some embodiments of the present application, not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the application without making any inventive effort, are intended to be within the scope of the application.
At present, the performance of low-frequency strong sound wave equipment mainly depends on the high-pressure air conversion efficiency of an air compressor, when the air pressure of the existing air compressor is improved, due to the fact that an assembly for adjusting the air flow is lacking, the air pressure is limited by a structure and a working principle, the output air pressure is low, the high-pressure air conversion efficiency of the existing air compressor is poor, the applicability of the air compressor in the application of some high-pressure air pressurization requirements is limited, and the requirement on high-pressure air in certain specific scenes cannot be met.
Based on the above, in order to solve the above problems, the embodiments of the present application provide a centrifugal air compressor, in which the air intake valve assembly is driven by the rotational movement of the rotor dynamic balance assembly, and the air is sucked from the air and acts on the air flow, so as to increase the speed and pressure of the air flow. And then the air flow enters a diffuser gate assembly to be subjected to speed reduction and diffusion, the speed of the air flow is converted into static pressure rise, the pressure of the air is further improved, and finally the pressurized air can be collected through an exhaust volute. Through the rotational speed adjustment of rotor dynamic balance subassembly, can adjust gas flow in real time to can adjust the atmospheric pressure ratio of output in real time, can adjust the ratio of gas flow and the gas pressure of output in real time, and then promote air compressor's high-pressure air conversion efficiency.
Referring to fig. 1, the schematic structural diagram of a centrifugal air compressor according to an embodiment of the present application is shown in fig. 1, and may specifically include:
The air compressor comprises a rotor dynamic balance assembly 1, a bearing seat assembly 2, an air inlet cap 13, an air inlet machine brake assembly 3, a diffuser machine brake assembly 4 and an exhaust volute 5.
The bearing seat assembly 2 and the air inlet cap 13 are respectively positioned at two ends of the rotor dynamic balance assembly 1, and the air inlet machine brake assembly 3, the diffuser machine brake assembly 4 and the exhaust volute 5 are respectively connected to the outside of the rotor dynamic balance assembly 1 in a matched mode.
The intake damper assembly 3 is caused to suck air from the atmosphere by the rotational movement of the rotor dynamic balance assembly 1, and the rotor dynamic balance assembly 1 can apply work to the air flow by means of the blades and then cause the air flow to enter the diffuser damper assembly 4. The speed of the air flow is reduced and diffused in the diffuser gate assembly 4, so that the speed of the air flow can be converted into static pressure rise, the pressure of the air is further increased, and the pressurized air can be obtained. Finally, the pressurized gas can be collected through the exhaust volute 5, and the air compressor is supported through the exhaust volute and the volute base and is mounted on the test platform.
In one possible embodiment, the centrifugal air compressor further comprises a guide basin 8 and an air inlet filter screen assembly 9, wherein the guide basin 8 is arranged on the outer wall of the end part of the rotor dynamic balance assembly 1, which is close to the air inlet cap 13, so that an air inlet channel is formed between the guide basin 8 and the air inlet casing assembly 3, and the air inlet filter screen assembly 9 is positioned at the air inlet of the air inlet channel. Wherein, water conservancy diversion basin 8 is used for the water conservancy diversion to promote the effect of admitting air. The air inlet filter screen assembly 9 is used for filtering impurities in the air, so that the following gas is prevented from entering the air compressor, and other influencing factors are reduced.
Specifically, referring to fig. 2, fig. 2 is a schematic structural diagram of an air intake filter assembly according to an embodiment of the present application, where the air intake filter assembly 9 includes a filter outer ring 90, a filter inner ring 91, and a filter 92 disposed between the filter outer ring 90 and the filter inner ring 91, and the filter 92 is detachable, so that the filter 92 is easy to be replaced or cleaned.
In addition, during the operation of the air compressor, the air compressor bearings require lubricating oil for lubrication and cooling, and therefore, in the embodiment of the application, an oil station is provided for the air compressor for lubricating and cooling the air compressor bearings. The lubricating oil station of the air compressor can be connected to the test platform through a support.
Referring to fig. 3, fig. 3 is a schematic structural diagram of a dynamic balance assembly of a rotor according to an embodiment of the present application, a central pull rod 10, a centrifugal impeller 11, an unloading disc 12 and a transmission shaft 18.
The centrifugal impeller 11 is connected to the central pull rod 10, a first end of the unloading disc 12 is connected to a second end of the central pull rod 10, a second end of the unloading disc 12 is connected to the transmission shaft 18, i.e. an end of the unloading disc 12 remote from the central pull rod 10 is connected to the transmission shaft 18.
The first end of the central pull rod 10 is connected with a front bearing assembly 15, i.e. the end of the central pull rod 10 remote from the unloading disc 12 is provided with the front bearing assembly 15, and the unloading disc 12 is connected with a transmission shaft 18 through a rear bearing assembly 16. The front bearing assembly 15 and the rear bearing assembly 16 each include a bearing 150, a bearing adjustment pad 151, and a bearing retainer ring 152.
In one possible embodiment, the centrifugal air compressor further comprises an outer machine brake 6 and a centrifugal brake 7 which are arranged outside the rotor dynamic balance assembly, and the air inlet machine brake assembly 3, the outer machine brake 6, the centrifugal brake 7, the diffuser machine brake assembly 4 and the exhaust volute 5 are sequentially connected. Since the power mechanism in the supercharging system is connected with the transmission mechanism through the low-speed coupling, the transmission mechanism is connected with the transmission shaft 18 of the air compressor through the high-speed coupling. The drive shaft 18 is driven by the power mechanism, so that the drive shaft 18 drives the centrifugal impeller 11 to rotate under the drive of the power mechanism, thereby sucking air from the atmosphere through the air inlet valve assembly 3, and acting on the air flow by virtue of the blades, so as to improve the speed and pressure of the air flow. The airflow is then caused to enter the diffuser damper assembly 4. The speed of the air flow is reduced and diffused in the diffuser gate assembly 4, so that the speed of the air flow can be converted into static pressure rise, and the air pressure is further improved.
Referring to fig. 4, fig. 4 is a schematic structural diagram of a bearing seat assembly according to an embodiment of the present application, where the bearing seat assembly 2 includes a bearing seat 20, a spring support 22, a nozzle oil seal ring assembly 21, and a seal ring 23, and fig. 5 is a schematic structural diagram of each joint on the bearing seat, a ventilation joint 25, an oil supply pipe joint 26, and an oil return pipe joint 27 according to an embodiment of the present application.
The nozzle oil seal ring assembly 21 is arranged at a first end of the bearing seat 20 through the spring support 22, the seal ring 23 is arranged at a second end of the bearing seat 20, namely, the seal ring 23 is arranged at one end of the bearing seat 20 far away from the nozzle oil seal ring assembly 21, and the bearing seat 20 further comprises a ventilation joint 25, an oil supply pipe joint 26 and an oil return pipe joint 27.
Referring to fig. 6, fig. 6 is a schematic structural diagram of a nozzle oil seal assembly according to an embodiment of the present application, and the nozzle oil seal assembly 21 includes a nozzle oil seal 210, an oil supply pipe 211 and a pressure plate 212, where the oil supply pipe 211 and the pressure plate 212 are respectively connected to the nozzle oil seal 210.
The centrifugal air compressor provided by the embodiment of the application comprises a rotor dynamic balance assembly, a bearing seat assembly, an air inlet cap cover, an air inlet machine brake assembly, a diffuser machine brake assembly and an exhaust volute; the bearing seat assembly and the air inlet cap cover are respectively positioned at two ends of the rotor dynamic balance assembly, and the air inlet machine brake assembly, the diffuser machine brake assembly and the exhaust volute are respectively connected to the outside of the rotor dynamic balance assembly. The rotor dynamic balance assembly is used for enabling the air inlet machine brake assembly to suck air and apply work to the air flow through rotary motion, and enabling the air flow to enter the diffuser machine brake assembly; the diffuser gate assembly is used for carrying out speed reduction and diffusion on the air flow to obtain pressurized air; and the exhaust volute is used for collecting the pressurized gas.
Therefore, the air inlet machine brake assembly can be driven by the rotary motion of the rotor dynamic balance assembly to suck air from the air and apply work to the air flow, so that the speed and the pressure of the air flow are improved. Then the air flow enters the diffuser gate assembly to be subjected to speed reduction and diffusion, the speed of the air flow is converted into static pressure rise, the pressure of the air is further improved, the supercharging effect is good, and finally the supercharged air can be collected through the exhaust volute. Through the rotational speed adjustment of rotor dynamic balance subassembly, can adjust gas flow in real time to can adjust the atmospheric pressure ratio of output in real time, and then promote air compressor's high-pressure air conversion efficiency.
The supercharging system in the prior art has a remarkable problem that the flow rate of the supercharging system in the prior art is limited, and the requirement of some industrial requirements on high flow rate cannot be met. The high-pressure air conversion efficiency of the traditional supercharging system is poor because the power mechanism and the transmission mechanism in the traditional supercharging system are relatively rigid in design, flow output is difficult to flexibly adjust, the adjusting capacity is limited, requirements of different working conditions cannot be precisely matched, the supercharging system is limited in performance under the high-flow requirements, and the high-pressure air conversion efficiency of the traditional supercharging system is poor.
In addition, the pressure and the flow output by the traditional pressurizing system are in direct proportion to the size, the flow of the small pressurizing system is limited, and the requirement of the sound wave equipment on high flow cannot be met. The power mechanism and the transmission mechanism adopted by the large-scale pressurizing system are relatively heavy in structure, occupy a large space, limit the flexibility of the sound wave equipment and the selection of the installation site, and cannot be suitable for scenes with strict requirements on the volume of the sound wave equipment.
Referring to fig. 7, fig. 7 is a schematic structural diagram of a supercharging system according to an embodiment of the present application, where the supercharging system includes a centrifugal air compressor, a power mechanism and a transmission mechanism, the power mechanism is connected to the transmission mechanism through a low-speed coupling 103, and the transmission mechanism is connected to a transmission shaft 18 of the air compressor through a high-speed coupling 104.
The power mechanism includes a driving member 100 and a controller 101, and the controller 101 is used to control the driving state of the driving member 100, so that the rotational speed of the driving member 100 can be controlled by the controller 101, thereby adjusting the rotational speed of the air compressor. As one example, the drive 100 may be an electric motor, an internal combustion engine, a ground gas turbine, an aviation scroll, or a turbine blade engine. The controller 101 can adopt a frequency converter, and adjusts the rotating speed of the variable frequency motor by adjusting the frequency of the frequency converter, so that the purpose of adjusting the rotating speed of the air compressor is achieved, and the air pressure ratio and the air flow of the air compressor are further adjusted. The driving member 100 may be fixed to a motor support by bolts, and the motor support may be fixed to the test platform by anchor bolts.
The transmission mechanism comprises a speed increasing box 102 and a coupler, the coupler comprises a high-speed coupler 104 and a low-speed coupler 103, an input shaft of the speed increasing box 102 is connected with the low-speed coupler 103, and an output shaft of the speed increasing box 102 is connected with a transmission shaft 18 of the air compressor through the high-speed coupler 104.
The power mechanism is connected with an input shaft of a speed increasing box 102 of the transmission mechanism through a low-speed coupler 103, so that the speed increasing box 102 is driven to rotate, the speed increasing box 102 increases the rotation speed of the input shaft according to a certain transmission ratio through a plurality of gear transmissions in the speed increasing box 102, and the increased rotation speed is output by an output shaft. The output shaft of the speed increasing box 102 is connected with the transmission shaft 18 of the air compressor through the high-speed coupling 104, so that the air compressor can be driven to rotate. The power mechanism drives the transmission mechanism to increase the rotating speed, so that the air compressor can be driven to rotate at a high speed, and the effect of increasing the air flow pressure is achieved.
In addition, during operation of the transmission mechanism, gears in the speed increasing box 102 mesh and bearings require lubricating oil for lubrication and cooling, so in the embodiment of the present application, a lubricating oil station is provided for the speed increasing box 102, for providing lubricating oil for lubrication and cooling of the speed increasing box 102. The speed increasing box 102 and the lubricating oil station of the speed increasing box 102 are connected to the test platform through a support and bolts. If the lubricating oil marks and the lubricating parameters adopted by the lubricating oil stations of the air compressor and the lubricating oil stations of the speed increasing box are the same or similar, the air compressor and the speed increasing box can adopt the same lubricating oil station.
The supercharging system provided by the embodiment of the application comprises an air compressor, a power mechanism and a transmission mechanism, wherein the power mechanism is connected with the transmission mechanism through a low-speed coupler 103, and the transmission mechanism is connected with a transmission shaft 18 of the air compressor through a high-speed coupler 104. The power mechanism drives the transmission mechanism to increase the rotating speed, so that the air compressor can be driven to rotate at a high speed, and the effect of increasing the air flow pressure is achieved. Therefore, the flow and the air pressure ratio can be adjusted by adjusting the rotation speed, the higher the rotation speed is, the larger the air flow is, the higher the air pressure ratio is, the real-time adjustment of the air pressure intensity, the air flow and the air pressure ratio can be realized, the high-pressure air conversion efficiency of the supercharging system is improved, and the requirements of different specific scenes on high-pressure air can be met. And the supercharging system has reliable structure and high stability, and can be suitable for scenes with strict requirements on the volume of sound wave equipment, and has wide application range and strong maneuverability.
In addition, the embodiment of the application also provides an acoustic wave device, which comprises a centrifugal air compressor, a generator, a siren sounder and a resonance loudspeaker, wherein the sound production efficiency of the acoustic wave device mainly depends on the power of the air compressor, and the working principle of the acoustic wave device is as follows: the air compressor outputs high-pressure air flow, and the air is conveyed into the cavity of the siren sounder through the diversion channel. The rotary flute comprises a stator and a rotor, the stator and the rotor comprise a plurality of gas nozzles, the rotor can be driven by the generator to periodically rotate, and when the vent holes on the rotor are partially or completely overlapped with the vent holes of the stator cavity, high-pressure air in the cavity of the rotary flute sounder can be released to form pulse jet flow, so that a basic sound source with fixed frequency is generated. Then the basic sound source is transmitted into the resonant horn, and when the local oscillation frequency of the resonant horn is consistent with the basic sound source, the sound wave energy of the sound wave device can be concentrated on the new target frequency, so that the high-sound-intensity simple harmonic sound wave can be generated. It follows that the higher the compression efficiency of the air compressor, the higher the sound emission efficiency of the acoustic wave device.
The generator can be a diesel generator, and the resonance loudspeaker can be a Bessel resonance loudspeaker. Therefore, the local oscillation frequency corresponding to the resonant horn can be calculated through the acoustic principle, and the calculation formula for calculating the local oscillation frequency of the resonant horn can be formula 1 according to the basic property that the radial energy of the sound wave in the acoustic horn is 0.
Y (k) =sin kl J 0(kl)+ cos kl*J1 (kl) (formula 1)
When Y (k) =0, the frequency f corresponding to the calculated wave number k value is the resonant frequency of the resonant horn, l is the main body height of the resonant horn, J 0 represents the 0-order bessel function, and J 1 represents the 1-order bessel function.
The above is an embodiment of the present application, and because the air displacement of the acoustic wave device is constant when the acoustic wave device works at a fixed frequency, the centrifugal air compressor provided by the embodiment of the present application can adjust the air flow and the air pressure ratio in real time, so that the high-pressure air conversion efficiency can be improved, and the sound production efficiency of the acoustic wave device is further improved.
The "first" and "second" in the names of "first", "second" (where present) and the like in the embodiments of the present application are used for name identification only, and do not represent the first and second in sequence.
It should be noted that, in the present specification, each embodiment is described in a progressive manner, and identical and similar parts of each embodiment are all referred to each other, and each embodiment is mainly described in a different point from other embodiments. In particular, for the device embodiments, since they are substantially similar to the method embodiments, the description is relatively simple, and reference is made to the description of the method embodiments for relevant points. The apparatus embodiments described above are merely illustrative, wherein elements illustrated as separate elements may or may not be physically separate, and elements illustrated as elements may or may not be physical elements, may be located in one place, or may be distributed over a plurality of network elements. Some or all of the modules may be selected according to actual needs to achieve the purpose of the solution of this embodiment. Those of ordinary skill in the art will understand and implement the present invention without undue burden.
The foregoing is only one specific embodiment of the present application, but the scope of the present application is not limited thereto, and any changes or substitutions easily contemplated by those skilled in the art within the technical scope of the present application should be included in the scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.
Claims (10)
1. A centrifugal air compressor, characterized in that the air compressor comprises a rotor dynamic balance assembly, a bearing seat assembly, an air inlet cap, an air inlet machine brake assembly, a diffuser machine brake assembly and an exhaust volute; the bearing seat assembly and the air inlet cap cover are respectively positioned at two ends of the rotor dynamic balance assembly, and the air inlet machine brake assembly, the diffuser machine brake assembly and the exhaust volute are respectively connected to the outside of the rotor dynamic balance assembly;
the rotor dynamic balance assembly is used for enabling the air inlet machine brake assembly to suck air and apply work to the air flow through rotary motion, and enabling the air flow to enter the diffuser machine brake assembly;
the diffuser gate assembly is used for carrying out speed reduction and diffusion on the airflow to obtain pressurized gas;
and the exhaust volute is used for collecting the pressurized gas.
2. The centrifugal air compressor of claim 1, wherein the rotor dynamic balance assembly comprises a center pull rod, a centrifugal impeller, an unloading disc, and a transmission shaft;
The central pull rod is connected with the centrifugal impeller, the first end of the unloading disc is connected with the second end of the central pull rod, and the second end of the unloading disc is connected with the transmission shaft;
the first end of the central pull rod is connected with the front bearing assembly, and the unloading disc is connected with the transmission shaft through the rear bearing assembly.
3. The centrifugal air compressor of claim 2, wherein the front bearing assembly and the rear bearing assembly include bearings, bearing adjustment pads, and bearing retainer rings.
4. The centrifugal air compressor of claim 1, wherein the bearing housing assembly comprises a bearing housing, a spring support, a nozzle oil seal ring assembly, a seal ring, a breather fitting, an oil supply pipe fitting, and an oil return pipe fitting;
The nozzle oil seal ring assembly is arranged at the first end of the bearing seat through the elastic support, the sealing ring is arranged at the second end of the bearing seat, and the bearing seat comprises the ventilation joint, the oil supply pipe joint and the oil return pipe joint.
5. The centrifugal air compressor of claim 4, wherein the nozzle oil seal assembly includes a nozzle oil seal, an oil supply tube, and a pressure plate, the oil supply tube and the pressure plate being respectively connected to the nozzle oil seal.
6. The centrifugal air compressor of claim 1, further comprising an outer sluice and a centrifuge sluice external to the rotor dynamic balancing assembly, the inlet sluice assembly, the outer sluice, the centrifuge sluice, the diffuser sluice assembly, and the exhaust volute being sequentially connected.
7. The centrifugal air compressor of claim 1, further comprising a baffle basin and an intake screen assembly, the baffle basin being located on an outer wall of the rotor dynamic balancing assembly;
The air guide basin is used for forming an air inlet channel with the air inlet machine gate assembly, and the air inlet filter screen assembly is located at an air inlet of the air inlet channel.
8. A supercharging system comprising a centrifugal air compressor as claimed in any one of claims 1 to 7, a power mechanism and a transmission mechanism, the power mechanism being connected to the transmission mechanism by a low speed coupling, the transmission mechanism being connected to a drive shaft of the air compressor by a high speed coupling.
9. The supercharging system of claim 8, wherein the power mechanism comprises a drive and a controller; the controller is used for controlling the rotating speed of the driving piece so as to adjust the rotating speed of the air compressor;
The transmission mechanism comprises a speed increasing box and a coupler, the coupler comprises a high-speed coupler and a low-speed coupler, an input shaft of the speed increasing box is connected with the low-speed coupler, and an output shaft of the speed increasing box is connected with a transmission shaft of the air compressor through the high-speed coupler.
10. An acoustic wave device comprising a centrifugal air compressor, a resonant horn, a siren sounder, and a generator as claimed in any one of claims 1 to 7.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410216871.0A CN118008841A (en) | 2024-02-27 | 2024-02-27 | Centrifugal air compressor and supercharging system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410216871.0A CN118008841A (en) | 2024-02-27 | 2024-02-27 | Centrifugal air compressor and supercharging system |
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| Publication Number | Publication Date |
|---|---|
| CN118008841A true CN118008841A (en) | 2024-05-10 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202410216871.0A Pending CN118008841A (en) | 2024-02-27 | 2024-02-27 | Centrifugal air compressor and supercharging system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN118008841A (en) |
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- 2024-02-27 CN CN202410216871.0A patent/CN118008841A/en active Pending
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