• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A multi-flow gas-dynamic pressure-wave machine, the rotor of which comprises at least one intermediate tube which subdivides the cell zone into at least two flow channels. The cell walls of adjacent flow channels are circumferentially staggered by essentially one-half the circumferential interface between such cells to produce a reduction in noise due to the beat interference produced by the sound pressures occurring in the cells adjacent to one another in the radial direction. The rotor may be provided with a concertina-shaped or undulation-shaped intermediate tube whereby there occurs a more balanced distribution of stresses, requiring less accelerating power.
    公开号:SU867325A3
    申请号:SU792820448
    申请日:1979-09-28
    公开日:1981-09-23
    发明作者:Фрид Райнхард；Кудернач Гюнтер
    申请人:Ббц Аг Браун,Бовери Унд Ко. (Фирма)；
    IPC主号:
    专利说明:

    The invention relates to a machine structure, namely, machines using shock waves to compress one gaseous operating current to another. Known multi-threaded wave pressure exchangers containing a rotor with a peripheral bandage, a Central sleeve and at least one intermediate pipe that separates in the rotor covering and covered concentric flows, divided into cells using side walls that are offset in each flow relative to the side walls of the adjacent a half-step flow, a housing covering a 15 bandage, and air and gas casings with channels for supplying and discharging air and gas to the mouth cells located at the ends of the rotor, equipped with pockets ora through windows with control side edges [1].
    The displacement of the side walls of the cells in each flow makes it possible to reduce the level of aerodynamic noise, however, the noise of such pressure exchangers remains quite high. In addition, the annular cross-sectional shape of the intermediate pipes does not contribute to the compensation of thermal stresses,.
    and the mass of pipes causes an additional 30 centrifugal loads. The present invention eliminates these disadvantages.
    The purpose of the invention is to reduce noise.
    To achieve this goal, the cells of the enveloping flow in a section perpendicular to the axis of the rotor are made with a displacement of the Pere -– points. the middle lines of the side walls with the middle line of the intermediate pipe toward the bandage compared with the intersection points with the same line of the side walls of the cells of the male stream.
    The intermediate pipe in a section perpendicular to the axis · can be made zigzag or 'Wavy.
    The channels of the gas casing can be divided by means of partitions into flows in accordance with the flows of the rotor.
    The flows in the rotor can be equal either in area or in height.
    (Pockets in the gas and air jacket can be separated by partitions in the radial direction.
    Windows in the air and / or gas casing may be arranged with at least one of the control edges disposed tangent to an imaginary auxiliary circle concentric with the rotor.
    The control side edges of the windows within each stream can be made S-shaped.
    The side walls of the cells can be made expanding towards their intersection with the bandage, sleeve and intermediate pipe.
    In FIG. 1 shows a two-line pressure exchanger, a longitudinal section; in FIG. 2 is a view of the windows for gas and air in the casings; in FIG. 3 is a section along the rotor shown in FIG. 1; in FIG. 4 - implementation of the control edges of the windows according to the preferred embodiment; in FIG. 5 is a preferred embodiment of windows; in FIG. 6 is a preferred embodiment of the walls and their interface with the bandage, sleeve and intermediate pipe .; in FIG. 7 is one embodiment of an intermediate pipe; FIG. 8 is an embodiment of a rotor with unequal cells; in FIG. 9 - three-flow rotor.
    The housing 1 covers the rotor 2, which is rigidly connected with the shaft 3, mounted in bearings with the possibility of rotation in two bearings 4 and 5, connected to the drive by means of a pulley 6 and V-belt drive.
    The gas casing 7 is made with channels 8 and partitions 9, separating the flows in each channel in accordance with the rotor flows. Between the sleeve 10 and the bandage 11, an intermediate pipe 12 is placed in the rotor, separating the covered 13 and covering 14 flows in the rotor. From the section shown in FIG. 3, it can be seen that the sleeve 10 and the bandage 11 are cylindrical, and the intermediate pipe 12 in a section perpendicular to the axis is zigzag. Both streams 13 and 14 are divided into cells by the side walls 15 and 16 into inner and outer cells 17 and 18, which in each stream are offset relative to the side walls of the adjacent stream, mainly by a half step. Moreover, the areas occupied by all cells, including walls, in each flow, can be equal. Streams can be made equal in height. The intersection points of the middle lines of the side walls 16 of the cells 18 of the female stream 14 with the middle line of the intermediate pipe 12 are shifted to the side of the band 11 in comparison with the points of intersection with the same line of the side walls 15 of the male stream 13, and are adjacent to the vertices of the zigzag intermediate pipe 12.
    In FIG. 2 shows a view of the flange of the gas casing 8 along section 11-11 of FIG. 1. Position 19 marks two inlet streams of inlet channels for pressure gas, position 20 indicates pockets that expand the area of operation of the pressure exchanger, and position 21 indicates windows for exhaust gas discharge.
    The flange of the air casing 22 has a similar appearance.
    The control edge 23 of the exhaust gas exhaust window is straightforward. It intersects with the radial line 24 passing through the axis of the rotor, forms an angle 25 with it and is located on a tangent to the imaginary auxiliary circle 26, concentric to the rotor. The second, in the direction of rotation, rear control edge 27 is also located at an angle to the corresponding radial line.
    Another embodiment of the control edges is shown in FIG. 5 for compressed air exhaust windows. The control edges 28 and 29 are made S-shaped. While the opening control edge 28 provides a large increase in cross-section in the first phase of opening. The intermediate pipe is shown annular and has no advantages compared to a zigzag or wavy, partially shown in FIG. 7.
    The zigzag design of the intermediate pipe 12 (Fig. 3) has advantages in terms of strength compared to a conventional annular pipe. In the latter, significant bending stresses arise during operation, in which the maximum tensile stress reaches the tensile yield strength for the rotor material, which has a relatively low value due to the high operating temperature. The zigzag-shaped intermediate pipe 30 (Fig. 6) and corrugated (Fig. 7) work with lower stresses due to the absence of bending moments at the transition to the walls and 33. The offset of the intersection point 34 provides less expansion of the band, but the sleeve is loaded. This results in a more uniform stress distribution and thus better use of the material, which allows to reduce the wall thickness in the middle compared to the thickness at the intersection with the bandage, sleeve and intermediate pipe. The result is an additional advantage - a decrease in the moment of inertia of the rotor masses and less acceleration power.
    Partitions 35 divide the pockets in the radial direction in accordance with the flow of the rotor.
    Since the implementation of a multi-threaded pressure exchanger reduces the rotor length, alternating loads acting on the walls due to the pressure difference also decrease, which helps to reduce the wall thickness. A local increase in this thickness helps to reduce stresses at the embedment sites.
    In the rotor (Fig. 8) the intermediate pipe is made wavy, and the cells of each of the flows are made different wide width to obtain a more varied and physiologically better tolerated noise spectrum. Moreover, according to a certain calculated scheme, a certain number of narrow cells alternate with a certain number of wide cells. The walls in the flows are also shifted by about a half step.
    The rotor of FIG. 9 is made three-threaded with zigzag intermediate pipes and the side walls in each stream are shifted by about half a step compared to the walls of the adjacent stream so that the walls of the surrounding external stream and the covered internal stream lie on the same radial line.
    During operation, pressure is exchanged between the gas and air in the cells as a result of the propagation of direct and reflected pressure waves.
    Moreover, by dividing the cells into two streams, the number of pressure pulses generating noise doubles. The shift of the cells by half a step provides a shift of the pressure pulses exactly half the period. Due to the interference thus generated, the amplitude of the fundamental frequency decreases. The effectiveness of this event is largely dependent on the spectrum of noise generated by the rotor. The proportion of higher harmonics in noise generation is relatively small; the second harmonic component is 20 decibels quieter than the noise created by the fundamental frequency. But in fact, it is not possible to achieve complete damping of the fundamental frequency. Theoretically, this would be possible with an infinitely small cell height, since pressure fluctuations * can mutually influence each other only in the immediate vicinity of the intermediate pipe.
    The radially inward displacement of the cells of the end walls 16 of the cells of the female stream 14 and the corresponding displacement of the walls of the male stream extends the range of action of the wall displacement by half a step.
    Since along with the fundamental frequency there are other harmonic frequencies, and due to the displacement of the walls, only the amplitude of the fundamental frequency and the odd harmonics decrease, only the even harmonics of the fundamental frequency dominate in the remaining noise spectrum. The division of flows with equal heights is more favorable from the point of view of thermodynamics, while the division with equal areas provides a more effective noise reduction. That is, if noise reduction is a priority, then · division into equal areas is carried out.
    The inclined position of the control edges 23 and 27 with respect to the cell walls provides an unstressed entry of the air or gas flow and a gradual increase in cross section, which reduces the noise associated with this.
    The S-shape of the control edge provides a similar acoustic effect. In this case, each cell communicates with two half-spaced edges with corresponding interference of sound waves and noise reduction.
    Thus, the noise generated by the proposed pressure exchanger is significantly reduced.
    权利要求:
    Claims (8)
    [1]
    The invention relates to mechanical engineering, in particular, to machines using shock waves to compress one gaseous operating current. Others are known multithreaded wave pressure exchangers containing a rotor with a peripheral band, a central bushing and at least one projectile tube separating the rotor from covered concentric streams divided by nets by side walls that are displaced in each flow with respect to the side walls of an adjacent stream by half a step; Already located and along the rotor ends, air pockets and gas jackets with pockets for supplying and discharging air and gas to the rotor cells through the windows with control side edges 1. Offsetting the side walls of the cells in each flow reduces the level of aerodynamic noise, however such pressure exchangers remain fairly high. In addition, the annular cross-sectional shape of the intermediate pipes does not contribute to the compensation of thermal stresses,. and the mass of pipes causes additional centrifugal loads. The present invention eliminates these disadvantages. The purpose of the invention is to reduce noise. To achieve the goal, the cells of the surrounding flow in the section perpendicular to the rotor axis are made with the displacement of the intersection points of the middle lines of the side walls with the middle line of the intermediate pipe in the direction of the bandage compared to the intersection points with the same line of the side walls of the cells of the circumscribed flow. The intermediate pipe in cross section, perpendicular to the axis, can be made of zigzag sludge and; wavy. The channels of the gas casing can be divided with the help of baffles into flows in accordance with the flows of the rotor. The flows in the rotor can be equal either in area or in height. | Pockets in the gas and air casing can be separated by partitions in the radial direction. The windows in the air and / or gas casing can be made with at least one of the control edges on a tangent to an imaginary auxiliary circle concentric to the rotor. The control side edges of the windows within each flow can be made S-shaped. The side walls of the cells can be made expanding in the direction of their intersection with the bandage, sleeve and intermediate pipe. Fig. 1 shows a double-flow pressure exchanger, longitudinal section; in fig. 2 is a view of the windows for gas and air in the enclosures; in fig. 3 is a section along the rotor shown in FIG. 1 in FIG. 4 illustrates the implementation of the control edges of the windows in a preferred embodiment; in fig. 5 shows a preferred embodiment of the windows in FIG. b - the preferred embodiment of the walls and their interface with the bandage, sleeve and intermediate pipe .; in fig. 7 shows one embodiment of an intermediate pipe; FIG. 8 is an embodiment of a rotor with unequal cells; in fig. 9 - three-flow rotor. The housing 1 encloses the rotor 2, which is rigidly connected to the shaft 3, which is mounted in bearings for rotation in two bearings 4 and 5, is connected to the drive by means of a pulley b and V-belt transmission. The gas jacket 7 is made with channels 8 and partitions 9, which separate the flows in each channel in accordance with the flows of the rotor. An intermediate pipe 12 is placed between the sleeve Yu and the bandage 11 in the rotor, separating the covered 13 and covering 14 streams in the rotor. From the section shown in Fig. 3 it can be seen that the sleeve 10 and the band 11 are cylindrical, and the intermediate pipe 12, in a section perpendicular to the axis, is zigzag. Both streams 13 and 14 are divided into cells with the help of side walls 15 and 16 into internal and external cells 17 and 18, which are displaced in each stream with respect to the side walls of the adjacent stream, mainly half a step. In this case, the areas occupied by all the cells, including the walls, in each flow can be equal. Flows can be made equal in height. The intersection points of the midline of the side walls 16 of the cells 18 of the surrounding flow 14 with the middle line of the intermediate pipe 12 are shifted towards the bandage 11 compared to the intersection points with the same line of the side walls 15 of the male flow 13, and are adjacent to the tops of the zigzag intermediate pipe 12. In FIG. . 2 shows a view of the flange of the gas housing 8 in cross section 11-11 shown in FIG. 1. Position 19 denotes two inlet streams of inlet channels for pressurized gas, position 20 denotes pockets expanding the operating area of the pressure exchanger, and oz 21 indicates windows for tapping off the exhausted gas. The air casing flange 22 has a tax appearance. The control edge 23 of the exhaust gas outlet is made straight. It intersects with a radial straight 24 passing through the axis of the rotor, forms an angle of 25 with it, and is located on a tangent to an imaginary auxiliary circle 26 concentric with the rotor. Secondly, in the direction of rotation of the rear, the control edge 27 is also at an angle to the corresponding radial straight line. Another embodiment of the control edges is shown in FIG. 5 for compressed air exhaust windows. Control edges 28 and 29 are S-shaped. At the same time, the opening control edge 28 provides a large increase in the cross section in the ne: open phase. The intermediate pipe is shown annular and has no advantages over a zigzag or undulating one, partially shown in FIG. 7. The zigzag structure of the intermediate tube 12 (FIG. 3) has advantages in terms of strength compared to a conventional ring tube. In the latter, significant bending stresses occur during operation, in which the maximum tensile stress reaches the tensile yield strength for a rotor material having a relatively low value due to the high operating temperature. The zigzag intermediate tube 30 (Fig. 6) and the wavy 31 (Fig. 7) operate with lower stresses due to the absence of bending moments at the transition to the walls 32 and 33. The displacement of the intersection point 34 provides for a smaller expansion of the band, but the sleeve is loaded. . This results in a more even distribution of stresses and thus a better utilization of the material, which makes it possible to reduce the wall thickness in the middle compared to the thickness at the intersection with the bandage, sleeve and intermediate pipe. The result is an additional advantage — lower rotor mass inertia and lower acceleration power. The baffles 35 divide the pockets in the radial direction in accordance with the rotor flows. Since the implementation of a multi-stream pressure exchanger reduces the length of the rotor, alternating loads. acting on the walls due to pressure differences are also reduced, which contributes to reducing the thickness of the walls. A local increase in this thickness contributes to a decrease in stresses at the termination points. In the rotor (Fig. 8), the intermediate tube is made wavy, and the cells of each of the flows are made with different widths to obtain a more varied and physiologically better tolerated noise spectrum. In this case, according to a certain calculated scheme, a number of narrow cells alternate with a number of wide cells. The walls in the streams are also shifted by about half a step. The rotor of FIG. 9 is made three-flow with zigzag intermediate pipes and offset side walls in each flow approximately by half a step compared with the walls of the adjacent flow so that the walls of the surrounding external flow and the covered internal flow lie on one radial line. During operation, the cells exchange pressure between the gas and the air as a result of the propagation of direct and reflected pressure waves. In this case, by dividing the cells into two streams, the number of pressure pulses that generate noise is doubled. Shifting the cells by half a step ensures that the pressure pulses shift by exactly half the period. Due to the interference thus generated, the amplitude of the fundamental frequency is reduced. The effectiveness of this measure largely depends on the spectrum of noise generated by the rotor. The proportion of higher harmonics in the generation of noise is relatively small; already the second harmonic component is 20 decibels quieter than the noise generated by the fundamental frequency. But in fact, it is not possible to achieve complete quenching of the main part of the time. Theoretically, this would be possible at an infinitely small height of others, since pressure fluctuations can mutually influence each other only in the immediate vicinity of the intermediate pipe. The displacement radially inward of the cells of the end walls 16 of the cells of the enclosing Flow 14 and the corresponding displacement of the walls of the enclosed flow expands the range of action of the displacement of the walls by half a step. Since there are other harmonic frequencies along with the fundamental frequency, and due to the wall displacement only the fundamental frequency amplitude and odd harmonics are reduced, only the even harmonics of the fundamental frequency dominate in the remaining noise spectrum. The division of flows with equal heights is more favorable from the point of view of thermodynamics, while the division with equal areas provides a more effective noise reduction. That is, if noise reduction is the first priority, then division into equal areas is performed. The oblique position of the control edges 23 and 27 with respect to the cell walls provides an unaccented entry of air or gas flow and a gradual increase in the cross section, which reduces the associated noise. The S-shaped control edge provides a similar acoustic effect. In this case, each cell communicates with two edges shifted by half a step with a corresponding interference of sound waves and a reduction in noise. Thus, the noise created by the proposed exchanger. pressure decreases significantly. Claim 1. Multi-threaded wave pressure exchanger comprising a rotor with a peripheral band, a central bushing and at least one intermediate tube separating the enclosing and enclosed concentric flows in the rotor, divided into cells using side walls that are offset in each flow with respect to to the side walls of the adjacent stream by half a step, a housing covering the bandage and located along the ends of the rotor, equipped with pockets air and gas shrouds with channels for supplying and discharging air and gas rotor cells through windows with control side edges, so that, in order to reduce the noise, the cell of the surrounding flow in a section perpendicular to the axis of the rotor, are shifted from the point of intersection of the lateral center lines the walls with the middle line of the intermediate pipe in the direction of the band as compared with the points of intersection with the same line of the side walls of the cells of the male flow.
    [2]
    2. The pressure exchanger according to claim 1, commencing with the fact that the transit pipe, in a section, with a perpendicular axis, is zigzagged.
    [3]
    3. The pressure exchanger according to claim 1, which is indicated by the fact that the intermediate pipe in the cross section, perpendicular to the axis, is made wavy.
    [4]
    4. The pressure exchanger according to claim 1, commensurate with the fact that the channels of the Azov casing are separated. Three relief partitions into threads, in accordance with the rotor flows.
    [5]
    5. Pressure exchanger according to claim 1, characterized in that the flows in the rotor are equal in area.
    [6]
    6. A pressure exchanger according to claim 1, characterized in that the flows in the rotor are equal in height.
    [7]
    7.-Pressure exchanger according to claim 1, 5, 6, characterized in that the pockets in the gas and air casing are divided by partitions in the radial direction.
    [8]
    8. The pressure exchanger according to claim 1, differing in that the windows in the air and / or gas casing are arranged with at least 3 13 1 0 2 86732 5 to 15 8 at least one of the control edges on the tangent to the imaginary auxiliary circle, concentric rotor. 9, a pressure exchanger according to claim 1, characterized in that the control side edges of the windows within each flow are S-shaped. 10. The pressure exchanger according to claim 1, characterized in that the side walls of the cells are widening. naprar - an echiyu to their intersection with a bandage, the plug and an intermediate pipe. Sources of information taken into account in the examination 1. US patent number 3109580, cl.417-64, published. 1963. J2 11
    867325
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    法律状态:
    优先权:
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