WO2020220693A1 - 气体脉冲器 - Google Patents

气体脉冲器 Download PDF

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Publication number
WO2020220693A1
WO2020220693A1 PCT/CN2019/125042 CN2019125042W WO2020220693A1 WO 2020220693 A1 WO2020220693 A1 WO 2020220693A1 CN 2019125042 W CN2019125042 W CN 2019125042W WO 2020220693 A1 WO2020220693 A1 WO 2020220693A1
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WIPO (PCT)
Prior art keywords
rotor
gas
sleeve
solid lubrication
pulser
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Ceased
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PCT/CN2019/125042
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English (en)
French (fr)
Inventor
裘钧
魏加华
王光谦
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Tsinghua University
Qinghai University
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Tsinghua University
Qinghai University
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Application filed by Tsinghua University, Qinghai University filed Critical Tsinghua University
Publication of WO2020220693A1 publication Critical patent/WO2020220693A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01G—HORTICULTURE; CULTIVATION OF VEGETABLES, FLOWERS, RICE, FRUIT, VINES, HOPS OR SEAWEED; FORESTRY; WATERING
    • A01G15/00—Devices or methods for influencing weather conditions
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01H—STREET CLEANING; CLEANING OF PERMANENT WAYS; CLEANING BEACHES; DISPERSING OR PREVENTING FOG IN GENERAL CLEANING STREET OR RAILWAY FURNITURE OR TUNNEL WALLS
    • E01H13/00—Dispersing or preventing fog in general, e.g. on roads, on airfields
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/12—Fluid oscillators or pulse generators

Definitions

  • the present application relates to a gas pulser, in particular to a gas pulser applied to the field of strong acoustic waves.
  • gas pulsers gas pulse generators
  • a method for obtaining gas pulses by high-speed control of the high-pressure gas source switch by a solenoid valve is proposed, and a mechanical rotary pulse gas generator is also proposed.
  • the pulse generator rotor When the gas pulse generator emits high-pressure pulse airflow, the pulse generator rotor is in asymmetrical force state.
  • the high-pressure gas dozens of times the standard atmospheric pressure makes the bearing bear a great radial force, which will also cause excessive wear of the sliding bearing.
  • the bearing sliding speed level is high and the radial load is also large, the PV value that controls the heat generation of the bearing is also at a high level, and the bearing is very prone to overheating and bonding problems. That is, the application of bimetallic solid lubrication bearings in gas pulsers faces the problems of wear failure and bonding failure at the same time.
  • This application is proposed in view of the above problems, and its purpose is to provide a gas pulser, which can successfully avoid the gluing failure problem of high-speed large-diameter bimetal solid lubricating bearings through clever design, and effectively reduce the wear failure problem.
  • Another object of the present application is to provide a gas pulser, which can effectively reduce the calorific value of the bimetal oil-free bearing.
  • the purpose of the present application is also to provide a gas pulser, which can provide strong gas pulse intensity and strong intermittent pulse strong sound waves.
  • a gas pulser includes a motor and a control system, a support frame, a housing, an air inlet end cover, an air inlet, an air outlet end cover and an air outlet, and is characterized in that it further includes: An elastic connection system; and a rotor pair, which includes a rotor with a vent hole and a solid lubrication rotor sleeve with the same vent hole, which has a gas stop switch function, and the solid lubrication rotor sleeve is fixed and statically installed in the In the housing, the rotor is driven to rotate in the solid lubrication rotor sleeve by the motor through the elastic connection system, and the high-pressure gas pulse frequency is controlled by controlling the rotation speed of the rotor. Pressure and flow to control the intensity of gas pulse.
  • the rotor adopts a multi-action working mode, that is, a plurality of exhaust holes are opened on the rotor one circle, so that a plurality of gas pulses are generated during the rotation of the rotor one circle.
  • the solid lubrication rotor sleeve adopts a multi-channel parallel operation mode, that is, the solid lubrication rotor sleeve is provided with a plurality of exhaust holes, and one of the exhaust holes faces the outlet
  • the air port is installed, the distribution phase of the multiple exhaust holes on the solid lubrication rotor sleeve in the circumferential direction is the same as the distribution phase of the multiple exhaust holes on the rotor, so that when the rotor is rotating, the multiple pairs
  • the exhaust holes on the rotor and the solid lubrication rotor sleeve are opened at the same time or closed at the same time to realize multi-channel parallel operation and increase the intensity of gas pulse.
  • a one-way thrust ball bearing is installed between the shaft end of the rotor and the housing, so that the rotor can bear the action of high-pressure gas internally, and externally interact with the solid body.
  • the lubricated rotor sleeves only leave a very small gap to produce low resistance torque.
  • the shaft ring of the one-way thrust ball bearing and the shaft end of the rotor adopt an interference fit
  • the seat ring of the one-way thrust ball bearing and the housing Use clearance fit
  • connection form of the one-way thrust ball bearing with the housing and the rotor shaft enables the shaft ring and the seat ring of the one-way thrust ball bearing to be automatically aligned through balls. To ensure that the bearing is free from radial forces.
  • the plurality of exhaust holes on the rotor and the solid lubrication rotor sleeve are all square holes, and the square holes are evenly distributed in the circumferential direction, and the long sides of the square holes are
  • the axial direction of the rotor and the solid-lubricated rotor sleeve, the length of the square holes on the rotor and the solid-lubricated rotor sleeve are equal, or may not be equal, the short sides of the square holes are along the length of the rotor and the solid-lubricated rotor sleeve
  • the length of the short side of the rotor is smaller than the length of the short side of the solid lubrication rotor sleeve, and the reasonable selection of the length of the short side determines the time ratio between the opening process and the closing process of the high-pressure gas exhaust.
  • the time ratio between the opening process and the closing process of the high-pressure gas exhaust is greater than or equal to 1.
  • a lubricating oil channel is provided on the housing, and the opening of the lubricating oil channel is located directly above the gas pulser housing, so that the rotor shaft end and the housing are installed between The one-way thrust ball bearing can run smoothly for a long time.
  • the elastic connection system includes:
  • Torque is transmitted between the motor shaft and the rotor through the motor shaft connecting sleeve and the rotor connecting plate, using a cross elastic connection form,
  • the connecting plate is integrally embedded in the recess of the connecting end of the rotor, and the end of the motor shaft and sleeve is embedded in the inner hole of the connecting plate.
  • a large clearance fit is adopted in a pair of vertical directions, and a large clearance fit is adopted in the other pair of vertical directions. Use small clearance fit to realize cross elastic connection,
  • the four inner corners of the connecting plate are rounded to relieve stress and increase the fatigue life of the connecting plate.
  • the connecting plate material is 65Mn spring steel, and the thickness of the connecting plate ranges from 6 to 8 mm.
  • the motor shaft and the shaft sleeve adopt an integral molding design
  • the coupling sleeve and the flat key adopt an interference fit
  • the flat key and the motor shaft adopt a clearance fit
  • the motor shaft connects
  • the shaft sleeve is machined and formed, first use a milling cutter to mill out the U-shaped groove, and then use a broach to pull out the keyway.
  • the motor shaft and sleeve are not designed as blind holes. If you have to design as blind holes, you can cut off the sleeve. , It is designed as two parts, and the two parts are fitted together by interference pressure.
  • the structure of the present application has both the bearing function with excellent sealing performance and the high-pressure gas pulse switch function, which can successfully avoid the gluing failure problem of the high-speed large-diameter bimetal solid lubricating bearing and effectively reduce the wear failure problem.
  • Fig. 1 is a schematic structural diagram of a gas pulser according to the present application.
  • Fig. 2 is a schematic diagram for explaining the concept of multi-action design according to the present application.
  • Fig. 3 is a schematic diagram for explaining the concept of multi-channel parallel design according to the present application.
  • Fig. 4 shows a schematic cross-sectional view of a four-acting, four-channel parallel structure of an embodiment of a gas pulser according to the present application.
  • Fig. 5 shows a schematic diagram of the realization of the cross elastic connection structure according to the present application.
  • Fig. 6 shows a schematic diagram of the structure of the motor shaft connecting sleeve according to the present application.
  • Fig. 7 shows a design example diagram of the gas pulser according to the present application.
  • Fig. 1 is a schematic structural diagram of a gas pulser according to the present application.
  • the structure of the gas pulser of the present application includes: motor assembly 1; fastening bolts 2; housing fastening bolts 3; bracket 4; rotor connecting plate 5; rotor assembly 6; Paper pad 7; inlet end cover 8; housing assembly 9; outlet end cover grease-resistant paper pad 10; outlet end cover 11, etc.
  • the motor assembly 1 may include a DC servo motor for driving the rotor in the housing of the gas pulse generator of the gas pulser to rotate.
  • the housing fastening bolt 3 is used to fasten the housing of the gas pulse generator of the gas pulser to the bracket (or support frame) 4.
  • the bracket (or support frame) 4 is used to firmly support the motor assembly 1 and the gas pulse generator of the gas pulser.
  • the rotor connecting plate 5 is used to transmit torque between the motor shaft of the motor assembly 1 and the rotor in the gas pulse generator housing of the gas pulse generator through the motor shaft coupling sleeve.
  • the rotor assembly 6 includes a rotor pair, which is composed of a rotor with vent holes and a solid lubrication rotor sleeve also with vent holes, which is located inside the housing of the gas pulse generator of the gas pulser.
  • Fig. 7 shows a design example diagram of the gas pulser according to the present application.
  • the gas pulser includes an air inlet end cover, an air inlet, an air outlet end cover, an air outlet, a shell, a support frame, and a DC servo motor.
  • the inlet end cover, the inlet port, the outlet end cover, the gas outlet, the casing and the components inside the casing are assumed to be the gas pulse generator of the gas pulse generator.
  • the working principle of the gas pulser of the present application is: continuous high-pressure gas is blown in from the air inlet of the gas pulser, the constant pressure is continuously compressed air, and the motor is driven by a motor to turn on and off.
  • the vented rotor and the vented rotor that are in a static state open and close regularly to form a pulse jet.
  • high-pressure gas forms a pulse jet from the gas pulser through the rotor pair; when the gas pulser rotor opening and the rotor sleeve opening are misaligned, the high-pressure gas is sealed in Inside the gas pulser, jet discontinuities are formed; jets and discontinuities appear repeatedly to form gas pulse jets.
  • the gas pulse is emitted from the gas outlet of the gas pulser.
  • the gas pulser includes a pulser rotor pair, an elastic connection system, a motor, and a control system (not shown).
  • the pulse generation principle is based on a pair of pulser rotor pairs with gas stop switches.
  • the pair is composed of a rotor with a vent hole and a solid lubrication rotor sleeve with the same vent hole.
  • the high-pressure gas pulse frequency can be controlled by controlling the rotating speed of the gas pulser rotor; the intensity of the gas pulse can be controlled by setting the pressure and flow rate of the gas flowing through the pulser.
  • the gas pulser can generate strong intermittent pulses from the high-pressure gas jet, causing strong oscillations in the air near the exit of the pulser, thereby causing strong sound waves.
  • the pulser rotor adopts a multi-action working mode.
  • Fig. 2 shows a schematic diagram for explaining the concept of multi-action design according to the present application.
  • the rotor is provided with 3 vents on a circle, so that when the rotor rotates one circle in the direction of the rotation arrow in the housing, 3 gas pulses are generated in the direction of the air flow in the figure.
  • the technical effect of this multi-acting design is that the linear velocity of the large-diameter rotor is reduced under a certain pulse frequency, that is, when a certain pulse frequency is obtained
  • the rotor only needs to work at a lower speed level, thereby effectively reducing the heat generation of the bimetal oil-free bearing.
  • the gas pulse frequency is mHz
  • the rotor working speed is m/n*60rpm
  • n can be designed to be 2, 3, 4, etc.
  • n is designed to be 3.
  • the solid-lubricated rotor sleeve of the pulser adopts a multi-channel parallel working mode.
  • Fig. 3 shows a schematic diagram for explaining the concept of multi-channel parallel design according to the present application.
  • the solid lubrication rotor sleeve is fixedly installed in the housing.
  • the rotor rotates in the rotor sleeve according to the rotor rotation direction shown in the figure.
  • the rotor sleeve and the housing There are airways between the bodies.
  • FIG. 3 there are 3 exhaust ports on the rotor sleeve, and 3 exhaust ports on the rotor.
  • the distribution phase of the three exhaust ports on the rotor sleeve in the circumferential direction is the same as that of the rotor.
  • the three exhaust ports on the upper side have the same distribution phase.
  • the rotor sleeve is fixed and statically installed in the housing, and one of the upper exhaust ports must be installed directly opposite to the gas pulser.
  • the three pairs of rotors and the exhaust ports on the rotor sleeve will be opened or closed at the same time.
  • the gas After the gas is discharged from the three exhaust ports of the rotor sleeve, it will pass between the rotor sleeve and the shell.
  • the air passages are connected in parallel to the outlet of the pulser, and are ejected from the outlet along the direction of the airflow to form a pulse jet.
  • the technical effect of this multi-channel parallel structure design is: under the same pulsed air flow intensity, the diameter of the rotor can be reduced, that is, when the rotor is rotating, the n pairs of the exhaust ports on the rotor and the rotor sleeve are opened or simultaneously Closed to realize multi-channel parallel operation, thereby increasing the gas pulse intensity.
  • n can be designed as 2, 3, 4, etc.
  • n is designed to be 3.
  • FIG. 4 shows a specific embodiment of the gas pulser according to the present application, which is a schematic cross-sectional view of the gas pulse generating part of the gas pulser along the radial direction, and adopts a four-function, four-channel parallel structure.
  • the distribution phase of the 4 exhaust holes on the rotor sleeve in the circumferential direction is the same as that of the 4 exhaust holes on the rotor.
  • the rotor is driven by the motor to rotate around the center of rotation in the solid-lubricated rotor sleeve in the direction of the rotation arrow.
  • the rotor sleeve is statically fixed in the housing of the gas pulser.
  • An exhaust hole of the sleeve is installed facing the gas outlet of the gas pulser, and an air passage is provided between the rotor sleeve and the casing.
  • both the rotor of the gas pulser and the solid lubrication rotor sleeve are provided with n exhaust holes (ports), n being 2, 3, 4, etc.
  • n exhaust holes ports
  • all the n exhaust holes (ports) should be designed as square holes, and the square holes are evenly distributed along the circumferential direction. This is because the applicant found that the square hole is the opening method with the highest opening efficiency of the exhaust valve.
  • the long sides of the square holes are along the axial direction of the rotor and the rotor sleeve.
  • the lengths of the square holes on the rotor and the rotor sleeve are equal or unequal (if unequal will reduce the exhaust efficiency), the longer the better .
  • the longer the length, the greater the opening and closing speed of the exhaust valve, the stronger the discontinuity of the airflow, and the extreme length is limited by the strength and rigidity of the rotor and rotor sleeve.
  • the short side of the square hole is along the circumference of the rotor and the rotor sleeve.
  • the length of the short side on the rotor is smaller than the length of the short side on the rotor sleeve.
  • the reasonable choice of the short side length determines the time ratio between the opening process and the closing process of the high-pressure gas exhaust.
  • Reasonable selection of the length ratio of the short side that is, the length ratio of the short side of the rotor opening to the short side of the rotor sleeve opening, can achieve a good balance between the high-pressure air displacement and the gas pulse intermittent strength.
  • the time ratio between the opening process and the closing process of the high-pressure gas exhaust is greater than or equal to 1.
  • the exhaust valve opening process is defined as the process from the exhaust valve begins to open, to fully open, to begin to close, and finally to fully close.
  • the exhaust valve closing process is defined as the exhaust valve fully closed state.
  • the setting range of the exhaust valve opening process angle is 60° ⁇ 80°
  • the setting range of the exhaust valve closing process angle is 60° ⁇ 40°
  • the setting range of the exhaust valve opening process angle is 45° ⁇ 55°
  • the setting range of the exhaust valve closing process angle is 45° ⁇ 35°.
  • the rotor shaft end and the housing Install one-way thrust ball bearings.
  • the shaft ring of the one-way thrust ball bearing adopts an interference fit with the rotor shaft end, and the seat ring of the one-way thrust ball bearing adopts a clearance fit between the housing and the housing.
  • the connection form of the one-way thrust ball bearing with the housing and the rotor shaft enables the shaft and seat ring of the one-way thrust ball bearing to realize automatic centering through the balls, ensuring that the bearing is not subjected to radial forces.
  • the driving torque of the one-way thrust ball bearing is calculated.
  • the calculation method is
  • D is the diameter of the bearing
  • P is the axial pressure of the bearing
  • ⁇ is the friction coefficient of the ball bearing.
  • the calculated driving torque is about 1N ⁇ m. This will provide a reference for the selection of the drive motor.
  • a lubricating oil channel is provided on the pulse transmitter housing, and the lubricating oil channel opening is located in the housing of the pulse generating part of the gas pulser Right above (not shown).
  • Fig. 5 shows a schematic diagram of the realization of the cross elastic connection structure according to the present application. As shown in Figure 5, it shows the connection relationship between the motor shaft, the motor shaft sleeve, the flat key, the rotor and the cross elastic plate. For the understanding of the following description, it also shows a large clearance fit in the horizontal direction and a large vertical direction. The meaning of clearance fit.
  • the connecting plate is embedded in the recess of the connecting end of the rotor, and the end of the motor shaft and sleeve is embedded in the inner hole of the connecting plate.
  • Large clearance fit is adopted in a pair of vertical directions.
  • a pair of vertical direction adopts small clearance fit to realize cross elastic connection.
  • the four inner corners of the connecting plate are rounded to relieve stress.
  • the connecting plate material needs to have good elasticity, 65Mn spring steel is selected, and the connecting plate needs to have sufficient strength, so the thickness needs to be greater than 5mm.
  • the thickness of the connecting plate ranges from 6 to 8mm .
  • the motor shaft and shaft sleeve adopts a one-piece design, and an interference fit is adopted between the shaft sleeve and the flat key.
  • the design effect is that the flat key will not move along the motor shaft. If it moves, it will be affected both front and rear. Restriction: Clearance fit is adopted between the flat key and the motor shaft.
  • the design effect is that the motor shaft is not subject to other forces in a stationary state, which is convenient for replacing the motor.
  • Fig. 6 shows a schematic diagram of the structure of the motor shaft connecting sleeve according to the present application.
  • the U-shaped groove can be milled out with a milling cutter first, and then the key groove can be pulled out with a broach during machining and forming of the motor shaft and sleeve.
  • the coupling sleeve cannot be designed as a blind hole. If you have to design a blind hole, you can also cut off the sleeve and design it into two parts, which are fitted together by interference pressure.

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Abstract

公开了一种气体脉冲器，包括电机及控制系统、支撑架(4)、壳体、进气端盖(8)、进气口、出气端盖(11)和出气口，弹性连接系统；以及转子副，其包括开有排气孔的转子与同样开有排气孔的固体润滑转子套，具有气体止开开关作用，固体润滑转子套被固定静止地安装在壳体内，转子在固体润滑转子套内由电机通过弹性连接系统连接被驱动旋转，通过控制转子的转速来控制高压气体脉冲频率，通过设定流入气体的压强和流量，来控制气体脉冲的强度。该气体脉冲器能够成功规避高速大口径双金属固体润滑轴承的胶合失效问题和有效减轻磨损失效问题，能够使高压气体射流产生强间断脉冲，从而获得频率可调的强声波。

Description

气体脉冲器
交叉引用
本申请要求于2019年04月28日递交的中国申请的优先权，申请号为201910350944.4，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及一种气体脉冲器，尤其涉及应用于强声波领域的气体脉冲器。
背景技术
现有技术中，气体脉冲器(气体脉冲发生器)具有广泛的应用，人们也进行了很多研究。例如，提出了通过电磁阀高速控制高压气源开关来获得气体脉冲的方法，也提出了机械旋转式脉冲气发生器的方案等。
对于通过电磁阀获得气体脉冲的方法，一般认为其存在密封不可靠有泄露现象、电磁阀高频切换的频率有限适用范围窄以及寿命短、工作可靠性差等缺点。
对于机械旋转式脉冲气发生器，一般来说，现有技术的结构比较复杂等。
参考文献：专利文献CN107402194A，CN102966643A
在现有技术中，本发明人注意到，存在固体镶嵌润滑轴承，但是所有固体镶嵌润滑轴承都没有高压气体脉冲开关功能；存在气体脉冲开关器，但是脉冲开关器都不能同时具有封严性能优异的轴承功能。本申请人研究了双金属固体润滑轴承在气体脉冲器中的应用。
气体脉冲发生器在发射高压脉冲气流时，脉冲发生器转子处于非对称受力状态，几十倍标准大气压的高压气体使轴承承受很大的径向作用力，也会导致滑动轴承过度磨损。当轴承滑动速度水平较高，径向载荷也较大时，控制轴承发热量的PV值也处于较高水平，轴承非 常容易产生过热胶合问题。即双金属固体润滑轴承在气体脉冲器中的应用同时面临磨损失效和胶合失效问题。
而且，在强声波应用技术领域，特别是强声增雨技术，需要一种结构简单、性能可靠安全、能够迅速产生强大的连续气体脉冲的气体脉冲发生器。
发明内容
本申请是鉴于上述问题提出的，其目的在于提供一种气体脉冲器，通过巧妙设计，其能够成功规避高速大口径双金属固体润滑轴承的胶合失效问题，并有效减轻磨损失效问题。
本申请的又一目的在于提供一种气体脉冲器，其能够有效减小双金属无油轴承的发热量。
本申请的目的还在于提供一种气体脉冲器，其能够提供强大气体脉冲强度和强间断脉冲的强声波。
为了实现上述目的，根据本申请的一种气体脉冲器，包括电机及控制系统、支撑架、壳体、进气端盖、进气口、出气端盖和出气口，其特征在于，还包括：弹性连接系统；以及转子副，其包括开有排气孔的转子与同样开有排气孔的固体润滑转子套，具有气体止开开关作用，所述固体润滑转子套被固定静止地安装在所述壳体内，所述转子在所述固体润滑转子套内由所述电机通过所述弹性连接系统连接被驱动旋转，通过控制所述转子的转速来控制高压气体脉冲频率，通过设定流入气体的压强和流量，来控制气体脉冲的强度。
根据本申请的气体脉冲器，优选地，所述转子采用多作用工作模式，即所述转子一周开有多个排气孔，使得所述转子旋转一周的过程中，产生多个气体脉冲。
根据本申请的气体脉冲器，优选地，所述固体润滑转子套采用多通道并联工作模式，即所述固体润滑转子套上开有多个排气孔，其中一个排气孔正对所述出气口安装，所述固体润滑转子套上的多个排气孔沿周向的分布相位与所述转子上的多个排气孔的分布相位相同，使 得当所述转子在转动过程中，多对所述转子和所述固体润滑转子套上的排气孔同时开启，或同时关闭，实现多通道并联工作，增大气体脉冲强度，气体从所述固体润滑转子套的多个排气孔排出后，经过所述固体润滑转子套和所述壳体之间的气道，以并联形式汇集到所述出气口，从所述出气口喷出，形成脉冲射流。
根据本申请的气体脉冲器，优选地，在所述转子的轴端与所述壳体之间安装单向推力球轴承，用于使所述转子在内部承受高压气体作用、外部与所述固体润滑转子套之间仅保留极小间隙的情况下产生较低阻力扭矩。
根据本申请的气体脉冲器，优选地，所述单向推力球轴承的轴圈与所述转子的轴端采用过盈配合，所述单向推力球轴承的座圈和所述壳体之间采用间隙配合。
根据本申请的气体脉冲器，优选地，所述单向推力球轴承与所述壳体及转子轴的连接形式，使得所述单向推力球轴承的轴圈和座圈能够通过滚珠实现自动对心，确保轴承不受径向作用力。
根据本申请的气体脉冲器，优选地，所述转子和所述固体润滑转子套上开有的多个排气孔都为方形孔，方形孔沿周向均匀分布，方形孔的长边沿所述转子及所述固体润滑转子套的轴向，所述转子及所述固体润滑转子套上方形孔的长度相等，也可以不等，方形孔的短边沿所述转子及所述固体润滑转子套的周向，所述转子上的短边长度小于所述固体润滑转子套上的短边长度，短边长度的合理选择决定高压气体排气开启过程和关闭过程的时间比。
根据本申请的气体脉冲器，优选地，所述高压气体排气开启过程和关闭过程的时间比大于等于1。
根据本申请的气体脉冲器，优选地，在所述壳体上设置润滑油道，润滑油道开口位于气体脉冲器壳体正上方，以使所述转子轴端与所述壳体之间安装的所述单向推力球轴承能够长久平稳运行。
根据本申请的气体脉冲器，优选地，所述弹性连接系统包括:
电机轴与所述转子之间通过电机轴连轴套和转子连接板传递扭 矩，采用十字弹性连接形式,
连接板整体嵌于所述转子的连接端凹窝内，电机轴连轴套端部嵌于连接板内孔，在一对垂直的方向上分别采用大间隙配合，在另一对垂直的方向上采用小间隙配合，实现十字弹性连接，
连接板四个内角进行倒内圆角处理，释放应力，以增加连接板疲劳寿命，
连接板材料选择65Mn弹簧钢，连接板的厚度范围为6～8mm。
根据本申请所述的气体脉冲器，优选地，电机轴连轴套采用一体成型设计，连轴套与平键之间采用过盈配合，平键与电机轴之间采用间隙配合，电机轴连轴套在机加工成型时先用铣刀铣出U形槽，再用拉刀拉出键槽，电机轴连轴套不设计成盲孔，如果非要设计成盲孔，可以把轴套从中截断，设计成两个零件，两个零件之间通过过盈压配到一起。
技术效果：
根据本申请的气体脉冲器，由于采用由开有排气孔的转子与同样开有排气孔的固体润滑转子套构成的转子副，转子采用多作用工作模式，固体润滑转子套采用多通道并联工作模式，因此本申请的结构既具有封严性能优异的轴承功能，又具有高压气体脉冲开关功能，能够成功规避高速大口径双金属固体润滑轴承的胶合失效问题和有效减轻磨损失效问题，能够获得可以有效减小双金属无油轴承的发热量、能够使高压气体射流产生强间断脉冲、引起脉冲器出气口附近空气发生强振荡、从而引起频率可调的强声波的技术效果，可用于但不限于强声波增雨、消雾、除尘等领域。
从以下结合附图对实施例的描述中，本申请的上述和/或其它方面将变得清楚和更容易理解。
附图说明
图1是根据本申请的气体脉冲器的结构示意图。
图2是用于说明根据本申请的多作用设计概念示意图。
图3是用于说明根据本申请的多通道并联设计概念示意图。
图4示出根据本申请的气体脉冲器一个实施例的四作用、四通道并联结构的剖面示意图。
图5示出根据本申请的十字弹性连接方式结构实现示意图。
图6示出根据本申请的电机轴连轴套结构示意图。
图7示出根据本申请的气体脉冲器的一个设计实例图。
具体实施方式
下面结合附图说明本申请的具体实施例，但是本申请的范围不局限于说明的具体实施例。
图1是根据本申请的气体脉冲器的结构示意图。如图1所示，本申请的气体脉冲器的结构包括：电机组件1；紧固螺栓2；壳体紧固螺栓3；托架4；转子连接板5；转子组件6；进气端盖耐油纸垫7；进气端盖8；壳体组件9；出气端盖耐油纸垫10；出气端盖11等。
电机组件1可以包括直流伺服电机，用于驱动气体脉冲器的气体脉冲发生部壳体内的转子旋转。壳体紧固螺栓3用于将气体脉冲器的气体脉冲发生部的壳体紧固在托架(或者支撑架)4上。托架(或者支撑架)4用于牢固支撑电机组件1和气体脉冲器的气体脉冲发生部。转子连接板5用于通过与电机轴连轴套配合在电机组件1的电机轴与气体脉冲器的气体脉冲发生部壳体内的转子之间传递扭矩。转子组件6包括转子副，转子副由开有通气孔的转子与同样开有通气孔的固体润滑转子套构成，其位于气体脉冲器的气体脉冲发生部的壳体的内部。
图7示出根据本申请的气体脉冲器的一个设计实例图。气体脉冲器包括进气端盖、进气口、出气端盖、出气口、壳体、支撑架和直流伺服电机等部分。在本说明书中，将进气端盖、进气口、出气端盖、出气口、壳体以及壳体内部的各组件部分假设为气体脉冲器的气体脉冲产生部。
参考图1和图7，本申请气体脉冲器的工作原理是：连续高压气 体从气体脉冲器的进气口中吹入，将该恒压连续压缩空气，通过由电机驱动处于旋转状态的开有通气孔的转子和处于静止状态的同样开有通气孔的转子套上出气孔的规律开闭，形成脉冲射流。当气体脉冲器转子开孔与转子套开孔存在重叠时，高压气体从气体脉冲器内部通过转子副形成脉冲射流；当气体脉冲器转子开孔与转子套开孔错位时，高压气体被密闭在气体脉冲器内部，形成射流间断；射流和间断重复出现形成气体脉冲射流。气体脉冲从气体脉冲器的出气口射出。
根据本申请的气体脉冲器，其包括脉冲器转子副、弹性连接系统、电机及控制系统(未图示)，其脉冲发生原理是基于一对具有气体止开开关作用的脉冲器转子副，转子副由开有通气孔的转子与同样开有通气孔的固体润滑转子套构成。根据本申请，可以通过控制气体脉冲器转子的转速，来控制高压气体脉冲频率；可以通过设定流经脉冲器气体的压强和流量，来控制气体脉冲的强度。气体脉冲器能够使高压气体射流产生强间断脉冲，引起脉冲器出口附近空气发生强振荡，从而引起强声波。
根据本申请的气体脉冲器，脉冲器转子采用多作用工作模式。图2示出用于说明根据本申请的多作用设计概念示意图。作为一个优选实施例，在图2中，转子一周开有3个通气孔，使得转子在壳体内沿旋转箭头方向旋转一周的过程中，在图中的气流方向上，产生3个气体脉冲射出。与转子一周只开有1个通气孔的单作用设计相比，这种多作用设计的技术效果是：在一定脉冲频率下降低了大直径转子线速度，也就是说，在获得一定脉冲频率的气体脉冲时只需转子工作在较底转速水平，从而有效减小双金属无油轴承的发热量。通常，在气体脉冲频率为mHz时，转子工作转速为m/n*60rpm，n可设计为2、3、4等。本例图2中，n设计为3。
根据本申请的气体脉冲器，脉冲器固体润滑转子套采用多通道并联工作模式。图3示出用于说明根据本申请的多通道并联设计概念示意图。如图3所示，固体润滑转子套固定静止地安装在壳体内，转子在转子套内按图示的转子旋转方向旋转，转子与固体润滑转子套之间 仅保留极小间隙，转子套与壳体之间有气道。作为一个优选实施例，在图3中，转子套上开有3个排气口，转子上也开有3个排气口，转子套上的3个排气口沿周向的分布相位与转子上的3个排气口的分布相位相同，其中，转子套固定静止地安装在壳体内，其上的一个排气口必须正对气体脉冲器出气口安装。当转子在转子套内转动过程中，这3对转子和转子套上的排气口会同时开启或者同时关闭，气体从转子套的3个排气口排出后，经过转子套和壳体之间的气道，以并联形式汇集到脉冲器出口，沿气流方向从出口喷出，形成脉冲射流。这种多通道并联结构设计的技术效果是：在相同脉冲气流强度下，可以降低转子直径，也就是说，当转子在转动过程中，n对转子和转子套上的排气口同时开启或者同时关闭，实现多通道并联工作，由此增大气体脉冲强度。气体从转子套的n个排气口排出后，经过转子套和壳体之间的气道，以并联形式汇集到脉冲器出口，从出口喷出，形成脉冲射流。根据本申请，n可设计为2，3，4等。本例图3中，n设计为3。
图4示出根据本申请的气体脉冲器的一个具体实施例，其是气体脉冲器的气体脉冲产生部沿径向的剖面示意图，采用了四作用、四通道并联结构。如图4所示，转子套排气孔为4个，转子排气孔为4个，转子套上的4个排气孔沿周向的分布相位与转子上的4个排气孔的分布相位相同，转子在电机驱动下在固体润滑转子套内沿旋转箭头方向围绕转子转动中心旋转，转子与固体润滑转子套之间仅保留极小间隙，转子套静止固定在气体脉冲器的壳体内，转子套的一个排气孔正对气体脉冲器的出气口安装，在转子套和壳体之间具有气道。当转子在转子套内转动过程中，这4对转子和转子套上的排气孔会同时开启或者同时关闭，气体从转子套的4个排气孔排出后，经过转子套和壳体之间的气道，以并联形式汇集到气体脉冲器出气口，从出气口喷出，形成脉冲射流。
根据本申请，气体脉冲器的转子和固体润滑转子套上都开有n个排气孔(口)，n为2，3，4等。根据本申请，优选地，n个排气孔(口) 都应设计为方形孔，方形孔沿周向均匀分布。这是因为，本申请人发现方形孔是排气气门开启效率最大的开孔方式。
根据本申请，方形孔的长边沿转子及转子套的轴向，转子及转子套上方形孔的长度相等，也可以不等(如不等则会降低排气效率)，其长度越长越好，长度越长，排气门开启和关闭的速度越大，气流的间断性越强，长度极值受限于转子及转子套的强度及刚度。方形孔的短边沿转子及转子套的周向，优选地，转子上的短边长度小于转子套上的短边长度。短边长度的合理选择决定了高压气体排气开启过程和关闭过程的时间比。合理选择短边的长度比，即转子开孔的短边与转子套开孔的短边的长度比，能够使得高压空气排气量和气体脉冲间断强度之间取得很好的平衡。
根据本申请的气体脉冲器，优选地，高压气体排气开启过程和关闭过程的时间比大于等于1。排气气门开启过程定义为从排气门开始开启、到完全开启、到开始关闭、最后到完全关闭的过程。排气门关闭过程定义为排气门完全关闭状态。在本发明人的设计实例中，当周向开孔数n＝3时，排气气门开启过程角设置范围为60°～80°，排气气门关闭过程角设置范围为60°～40°；当周向开孔数n＝4时，排气气门开启过程角设置范围为45°～55°，排气气门关闭过程角设置范围为45°～35°。
在本申请的气体脉冲器中，为了使转子在内部承受高压气体作用、外部与固体润滑转子套之间仅保留极小间隙的情况下产生较低阻力扭矩，在转子轴端与壳体之间安装单向推力球轴承。单向推力球轴承的轴圈与转子轴端采用过盈配合，单向推力球轴承的座圈和壳体之间采用间隙配合。单向推力球轴承与壳体及转子轴的连接形式，使得单向推力球轴承的轴圈和座圈能够通过滚珠实现自动对心，确保轴承不受径向作用力。
单向推力球轴承的驱动扭矩进行核算，核算方法为
Figure PCTCN2019125042-appb-000001
其中，D为轴承直径，P为轴承所受轴向压力，μ为球轴承摩擦系数。在本申请的设计实例中，带入具体数值，计算得到驱动力矩约为1N·m。这将为驱动电机选型提供参考。
为了使转子轴端与壳体之间安装的单向推力球轴承能够长久平稳运行，在脉冲发射器壳体上设置了润滑油道，润滑油道开口位于气体脉冲器的脉冲产生部的壳体正上方(未图示)。
由于单向推力球轴承本身对本领域技术人员来说是已知结构，这里不予以赘述。
根据本申请的气体脉冲器，电机轴与转子之间通过电机轴连轴套和转子连接板传递扭矩，采用十字弹性连接形式。图5示出根据本申请的十字弹性连接方式结构实现示意图。如图5，其示出了电机轴、电机轴连轴套、平键、转子和十字弹性板之间的连接关系，为了下面说明的理解，还示出了水平方向大间隙配合、垂直方向大间隙配合的含义。
如图5所示，连接板整体匹配地嵌于转子的连接端凹窝内，电机轴连轴套端部嵌于连接板内孔，在一对垂直的方向上分别采用大间隙配合，在另一对垂直的方向上采用小间隙配合，实现十字弹性连接。
为增加连接板疲劳寿命，根据本申请，连接板四个内角进行倒内圆角处理，释放应力。
根据本申请，连接板材料需要具有较好的弹性，选择65Mn弹簧钢，连接板需要有足够的强度，因此需要厚度大于5mm，在本申请的设计实例中，连接板的厚度范围为6～8mm。
如图5所示，电机轴连轴套采用一体成型设计，连轴套与平键之间采用过盈配合，设计效果是平键不会沿电机轴方向移动，若发生移动，前后也均受约束；平键与电机轴之间采用间隙配合，设计效果是电机轴在静止状态不受其他作用力，方便更换电机。
图6示出根据本申请的电机轴连轴套结构示意图。参见图6，电机轴连轴套在机加工成型时可先用铣刀铣出U形槽，再用拉刀拉出键槽。从加工工艺上考虑，连轴套不能设计成盲孔。如果非要设计成盲孔，那也可以把轴套从中截断，设计成两个零件，两个零件之间通过过盈压配到一起。
上面结合具体实施例说明了本申请，应当理解，本申请不限于公开的具体实施例。能够改进本申请以进行改变、替换或者等同配置，但是其是与本申请的精神和范围相当。因此，本申请范围不应被看着由前述说明书限制。

Claims (11)

  1. 一种气体脉冲器，包括电机及控制系统、支撑架、壳体、进气端盖、进气口、出气端盖和出气口，其特征在于，还包括：
    弹性连接系统；以及
    转子副，其包括开有排气孔的转子与同样开有排气孔的固体润滑转子套，具有气体止开开关作用，
    所述固体润滑转子套被固定静止地安装在所述壳体内，所述转子在所述固体润滑转子套内由所述电机通过所述弹性连接系统连接被驱动旋转，
    通过控制所述转子的转速来控制高压气体脉冲频率，通过设定流入气体的压强和流量，来控制气体脉冲的强度。
  2. 根据权利要求1所述的气体脉冲器，其特征在于，所述转子采用多作用工作模式，即所述转子一周开有多个排气孔，使得所述转子旋转一周的过程中，产生多个气体脉冲。
  3. 根据权利要求2所述的气体脉冲器，其特征在于，所述固体润滑转子套采用多通道并联工作模式，即所述固体润滑转子套上开有多个排气孔，其中一个排气孔正对所述出气口安装，所述固体润滑转子套上的多个排气孔沿周向的分布相位与所述转子上的多个排气孔的分布相位相同，使得当所述转子在转动过程中，多对所述转子和所述固体润滑转子套上的排气孔同时开启，或同时关闭，实现多通道并联工作，增大气体脉冲强度，气体从所述固体润滑转子套的多个排气孔排出后，经过所述固体润滑转子套和所述壳体之间的气道，以并联形式汇集到所述出气口，从所述出气口喷出，形成脉冲射流。
  4. 根据权利要求1所述的气体脉冲器，其特征在于，在所述转子的轴端与所述壳体之间安装单向推力球轴承，用于使所述转子在内部承受高压气体作用、外部与所述固体润滑转子套之间仅保留极小间隙的情况下产生较低阻力扭矩。
  5. 根据权利要求4所述的气体脉冲器，其特征在于，所述单向推力球轴承的轴圈与所述转子的轴端采用过盈配合，所述单向推力球轴承的座圈和所述壳体之间采用间隙配合。
  6. 根据权利要求5所述的气体脉冲器，其特征在于，所述单向推力球轴承与所述壳体及转子轴的连接形式，使得所述单向推力球轴承的轴圈和座圈能够通过滚珠实现自动对心，确保轴承不受径向作用力。
  7. 根据权利要求3所述的气体脉冲器，其特征在于，所述转子和所述固体润滑转子套上开有的多个排气孔都为方形孔，方形孔沿周向均匀分布，
    方形孔的长边沿所述转子及所述固体润滑转子套的轴向，所述转子及所述固体润滑转子套上方形孔的长度相等，也可以不等，
    方形孔的短边沿所述转子及所述固体润滑转子套的周向，所述转子上的短边长度小于所述固体润滑转子套上的短边长度，短边长度的合理选择决定高压气体排气开启过程和关闭过程的时间比。
  8. 根据权利要求7所述的气体脉冲器，其特征在于，所述高压气体排气开启过程和关闭过程的时间比大于等于1。
  9. 根据权利要求4所述的气体脉冲器，其特征在于，在所述壳 体上设置润滑油道，润滑油道开口位于气体脉冲器壳体正上方，以使所述转子轴端与所述壳体之间安装的所述单向推力球轴承能够长久平稳运行。
  10. 根据权利要求1所述的气体脉冲器，其特征在于，所述弹性连接系统包括:
    电机轴与所述转子之间通过电机轴连轴套和转子连接板传递扭矩，采用十字弹性连接形式,
    连接板整体嵌于所述转子的连接端凹窝内，电机轴连轴套端部嵌于连接板内孔，在一对垂直的方向上分别采用大间隙配合，在另一对垂直的方向上采用小间隙配合，实现十字弹性连接，
    连接板四个内角进行倒内圆角处理，释放应力，以增加连接板疲劳寿命，
    连接板材料选择65Mn弹簧钢，连接板的厚度范围为6～8mm。
  11. 根据权利要求10所述的气体脉冲器，其特征在于，电机轴连轴套采用一体成型设计，连轴套与平键之间采用过盈配合，平键与电机轴之间采用间隙配合，
    电机轴连轴套在机加工成型时先用铣刀铣出U形槽，再用拉刀拉出键槽，电机轴连轴套不设计成盲孔，如果非要设计成盲孔，可以把轴套从中截断，设计成两个零件，两个零件之间通过过盈压配到一起。
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