High-load three-dimensional centrifugal compressor

Abstract

This invention discloses a high-load three-dimensional centrifugal compressor. The centrifugal unit includes a primary compression unit A, a primary compression unit B, a secondary compression unit, and a tertiary compression unit. Primary compression units A and B are connected in parallel and then lead to the secondary compression unit, which in turn connects in series to the tertiary compression unit. Each compression unit's impeller includes a corresponding disk with blades. Each blade has a working section and a wake section; the working section is a circular arc segment, and the wake section is an elliptical arc segment. Each compression unit's volute has a corresponding expansion channel and a resonant cavity. The expansion channel leads to the resonant cavity through several resonant channels. A sound-absorbing material layer is fixedly installed at the outer end of the resonant cavity through a perforated plate, and elastic sound-absorbing spheres are embedded within the sound-absorbing material layer. This centrifugal compressor not only suppresses the generation of eddies in the blade wake region and improves compressor operating efficiency but also effectively reduces compressor noise, achieving broadband noise reduction.

Description

Technical Field

[0001] This invention relates to a centrifugal compressor, and more particularly to a three-dimensional centrifugal compressor for conveying and compressing low molecular weight mixed gases, which can achieve high compression ratio and large flow rate gas compression. Background Technology

[0002] With the development of the chemical industry, centrifugal compressors have become key machines for compressing and transporting various gases in chemical production, occupying an extremely important position. The impeller is the heart of the centrifugal compressor, and the three-dimensional impeller is an advanced type of impeller with high efficiency, a wide operating range, and the ability to meet the requirements of high flow rate and high pressure ratio operation.

[0003] When centrifugal compressors compress and transport mixed gases with a high proportion of hydrogen, methane, and carbon monoxide and a low overall density, the centrifugal compressor impeller needs to operate at a high speed to achieve a high compression ratio and high energy head. The impeller speed reaches 20,000 RPM, which places higher technical requirements on the design and manufacturing of centrifugal compressors and impeller casings. First, the impeller flow channel formed by two adjacent blades of the compressor impeller is not only rotating at high speed, but the flow velocity and pressure are constantly changing along the streamline. Moreover, the cross-sectional area of ​​the inlet side channel of two adjacent blades is always smaller than that of the outlet side channel. The channel formed by adjacent blades is in an expanding state, and the inlet flow velocity and outlet flow velocity are extremely uneven, forming flow separation points and low-energy flow regions, i.e., wake regions. Gas vortices are generated in the wake region, which not only reduce the actual flow cross-sectional area of ​​the impeller outlet side and reduce the gas flow of the impeller, but also lead to the loss of gas kinetic energy, forming cavitation, shortening the impeller's service life, and even causing impeller damage. Secondly, the high-speed rotation of the impeller and the intensification of impeller cavitation generate sharp whistling sounds from bubble bursting and gas flow. These whistling sounds become increasingly harsh as the compressor's flow rate and impeller speed increase, causing severe pollution to the working environment and significantly impacting the compressor's lifespan. The sharp whistling noise generated by the high-speed rotating impeller mainly consists of rotational noise and eddy current noise. Rotational airflow noise is predominantly low-to-mid-frequency, while eddy current noise has a continuous noise spectrum with prominent mid-to-high-frequency components. Therefore, existing high-speed centrifugal compressors exhibit a wide noise spectrum and high intensity. Summary of the Invention

[0004] In view of the above-mentioned technical problems existing in the prior art, the technical problem to be solved by the present invention is to provide a high-load three-dimensional flow centrifugal compressor that can not only suppress the generation of eddies in the blade wake region and improve the compressor operating efficiency, but also effectively reduce compressor noise and achieve wideband noise reduction.

[0005] To solve the above-mentioned technical problems, the present invention provides a high-load three-dimensional flow centrifugal compressor, comprising a centrifugal unit, wherein the centrifugal unit includes a primary compression unit A, a primary compression unit B, a secondary compression unit, and a tertiary compression unit. The primary compression units A and B are connected in parallel and then connected to the secondary compression unit, which is in series with the tertiary compression unit. The primary compression unit A includes a primary volute A and a primary impeller A; the primary compression unit B includes a primary volute B and a primary impeller B; the secondary compression unit includes a secondary volute and a secondary impeller; and the tertiary compression unit includes a tertiary volute and a tertiary impeller. The first-stage impeller A, first-stage impeller B, second-stage impeller, and third-stage impeller are rotatably supported on the centrifuge gearbox housing. Each of the first-stage impeller A, first-stage impeller B, second-stage impeller, and third-stage impeller includes a corresponding disk, on which blades are arranged. Each blade includes a working section and a wake section. The working section is a circular arc section, and the wake section is an elliptical arc section. Each of the first-stage volute A, first-stage volute B, second-stage volute, and third-stage volute is provided with a corresponding expansion channel and a resonant cavity. The expansion channel leads to the resonant cavity through several resonant channels. At the outer end of the resonant cavity, a sound-absorbing material layer is fixedly arranged through a partition plate. Elastic sound-absorbing spheres are embedded in this sound-absorbing material layer.

[0006] In the above structure, the centrifugal compressor unit adopts a three-stage, four-unit compression path. The first-stage compression unit A and the first-stage compression unit B, which are connected in parallel, perform primary compression on the incoming gas with a low input pressure. Through the two compression units, the compressed gas achieves a larger input gas volume and a higher compression ratio. Then, it passes through the second-stage compression unit and the third-stage compression unit in sequence, continuously compressing and increasing the pressure of the gas medium entering the compressor unit. The compressed gas medium per unit mass can obtain higher energy and a higher energy head after passing through the compressor unit. This three-stage unit compression path design can greatly reduce the load and space size of a single first-stage compression unit, which is conducive to the integrated arrangement of the unit's drive, compacting the overall structure of the compressor unit. It also helps to reduce the size of the impeller and volute of the first-stage compression unit, avoid the vibration and noise caused by large-sized impellers, and facilitate the design and manufacture of impellers.

[0007] Furthermore, since the blade cross-section includes a working section and a wake section, the working section adopts a circular arc segment, while the wake section located near the blade exit edge adopts an elliptical arc segment. This is actually achieved by changing the radius of curvature of different sections of the blade, reducing the rate of change of the cross-sectional area of ​​the flow channel formed by two adjacent blades, reducing the unevenness of the flow velocity at the blade inlet edge and the blade outlet edge, and making the low-energy flow zone near the blade outlet edge smaller, so as to avoid the generation of eddies. This not only effectively reduces the occurrence of blade cavitation and extends the service life of the impeller, but also greatly reduces gas energy and flow loss, which is conducive to improving the working efficiency of the compressor.

[0008] Furthermore, the compressor unit's volute is equipped with expansion channels and resonant cavities, which are connected by resonant channels. A layer of sound-absorbing material is fixedly separated at the outer end of the resonant cavity by a perforated plate, and elastic sound-absorbing spheres are embedded within this layer. The resonant channels and cavities constitute a Helmholtz-type side-branch resonant silencing structure. When noise propagates to the intersection of the expansion channel and the resonant channel, the sudden change in acoustic impedance causes some sound energy to be reflected back, while some is transmitted into the resonant channels and cavities, consuming energy. This is especially true when the sound wave frequency is similar to the resonant frequency. When the natural frequencies of the resonant cavity are close to or equal, resonance will be excited, absorbing and consuming a large amount of sound energy, and providing good attenuation of high-frequency noise from the impeller blades. The partition plate and sound-absorbing material layer on the outside of the resonant cavity constitute a resistive silencer, which uses friction, viscosity and damping to convert sound energy into heat energy for dissipation. In particular, the sound-absorbing material layer is filled with elastic sound-absorbing spheres, thereby enhancing the dissipation effect of noise energy. This silencer structure achieves broadband noise silencing through a composite silencer structure of resistive and resistive silencers, effectively reducing the operating noise of the centrifugal compressor and the environmental noise.

[0009] In a preferred embodiment of the present invention, the radius of the circle containing the working section is R, the major semi-axis a = R of the ellipse containing the wake section, and the minor semi-axis b = (0.50-0.75)R; the ratio of the wake section length S1 to the working section length S is 1:(5-6); the center point of the ellipse containing the wake section is located at the center of the circle containing the working section. This structure effectively reduces the wake region of low-energy flow at the blade exit edge and reduces the generation of gas vortices.

[0010] In a further embodiment of the present invention, each of the first-stage impeller A, first-stage impeller B, second-stage impeller, and third-stage impeller includes a disk and blades, wherein the disk and blades are an integral structure. The centrifuge main shaft is rotatably supported on the centrifuge gearbox housing. The first-stage impeller gear shaft and the second and third-stage impeller gear shafts are rotatably supported on the centrifuge gearbox housing via tilting pad bearings. The driving gear on the centrifuge main shaft meshes with the driven gears on the first-stage and second / third-stage impeller gear shafts for transmission. A sealing assembly is installed on the outer side of the tilting pad bearings. The first-stage impeller A and first-stage impeller B are respectively fixedly installed at both ends of the first-stage impeller gear shaft, and the second-stage and third-stage impellers are respectively fixedly installed at both ends of the second and third-stage impeller gear shafts. This design features a compact structure and reasonable transmission.

[0011] In a further embodiment of the present invention, the primary volute A, primary volute B, secondary volute, and tertiary volute are fixedly installed on the centrifuge gearbox body, forming corresponding flow channels between the primary volute A, primary volute B, secondary volute, and tertiary volute and the centrifuge gearbox body, which lead to corresponding expansion channels. Each of the primary volute A, primary volute B, secondary volute, and tertiary volute is fixedly fitted with a corresponding sound-absorbing cavity cover plate, which is fitted onto the outer wall of the air inlet. The sound-absorbing material layer is located between the partition plate and the sound-absorbing cavity cover plate; the partition plate is an annular disc-shaped perforated plate with several through holes; the resonant cavity is an annular groove cavity, and the sound-absorbing material layer is filled with rock wool or glass fiber. The gas flow layout is reasonable and conducive to noise reduction.

[0012] In a further embodiment of the present invention, the sealing assembly includes a sealing housing, a rotating ring support disk is movably disposed within the housing cavity, and rotating ring support disks are fixedly installed on the journals of the first-stage impeller gear shaft and the second and third-stage impeller gear shafts; rotating ring seats are symmetrically disposed on both sides of the rotating ring support disk, and a rotating ring is fixedly embedded in each rotating ring seat; a stop pin is installed on the rotating ring support disk, and the two ends of the stop pin are respectively inserted into the rotating ring seats on the corresponding sides; a plurality of rotating ring springs are also disposed between the two rotating ring seats; a stationary ring connected to the end face of the rotating ring is embedded in the stationary ring seat, and the stationary ring seat is fixedly installed within the housing cavity of the sealing housing. The stop pin is installed with a gap in the stop pin hole of the moving ring support plate, and the moving ring spring is sleeved on the stop pin; a labyrinth toothed ring is fixedly installed at the inner end of the sealing housing cavity, and labyrinth grooved rings are fixedly installed on the journals of the first-stage impeller gear shaft and the second and third-stage impeller gear shafts, with corresponding labyrinth grooved rings movably inserted into the labyrinth toothed rings; a component cover is fixedly installed at the outer end of the sealing housing cavity, and a lip seal ring is installed in the center hole of the component cover. It has a tight sealing effect, and the mechanical seal can form a stable hydrodynamic pressure effect, which is beneficial for separating the sealing end faces to achieve non-contact sealing. Attached Figure Description

[0013] The high-load three-dimensional flow centrifugal compressor of the present invention will be further described below with reference to the accompanying drawings and specific embodiments.

[0014] Figure 1 This is an overall structural diagram of a specific embodiment of the present invention;

[0015] Figure 2 yes Figure 1 A schematic diagram of the gas compression path in the embodiment shown;

[0016] Figure 3 yes Figure 1 Cross-sectional view of the centrifuge unit in the embodiment shown;

[0017] Figure 4 yes Figure 3Installation structure diagram of the impeller and volute;

[0018] Figure 5 yes Figure 4 Cross-sectional view of the intermediate impeller;

[0019] Figure 6 This is a schematic diagram of the end face structure of the impeller and blades;

[0020] Figure 7 This is a schematic diagram of the blade structure shape;

[0021] Figure 8 This is a cross-sectional view of the volute.

[0022] Figure 9 yes Figure 8 Sectional view A-A;

[0023] Figure 10 yes Figure 8 Structural diagram of the orifice plate;

[0024] Figure 11 yes Figure 3 Cross-sectional view of the sealing assembly;

[0025] Figure 12 yes Figure 11 End face structure diagram of the moving ring;

[0026] Figure 13 yes Figure 12 Structural diagram of section B-B;

[0027] Figure 14 yes Figure 11 End face structure diagram of the central stationary ring;

[0028] Figure 15 yes Figure 14 Structural diagram of the C-C section;

[0029] Figure 16 yes Figure 3 End face structure diagram of a tilting pad bearing;

[0030] Figure 17 yes Figure 16 D-D cross-sectional structural diagram;

[0031] Figure 18 yes Figure 16 Structural diagram of the end face of the central bearing;

[0032] Figure 19 yes Figure 18 Cross-sectional view;

[0033] Figure 20 yes Figure 1 External structural diagram of the central air intake duct;

[0034] Figure 21 yes Figure 20 Top view;

[0035] Figure 22 yes Figure 20 Cross-sectional view of the valve assembly;

[0036] Figure 23 yes Figure 22 End view of the middle valve seat;

[0037] Figure 24 yes Figure 23 Cross-sectional structural diagram of the middle E-E section;

[0038] Figure 25 yes Figure 22 End view of the middle valve cover;

[0039] Figure 26 yes Figure 25 Cross-sectional structural diagram of the middle F-F section;

[0040] Figure 27 yes Figure 25 Cross-sectional structural diagram of G-G section;

[0041] Figure 28 yes Figure 22 End view of the center pressure fork plate;

[0042] Figure 29 yes Figure 28 Middle H-H cross-sectional structural diagram;

[0043] Figure 30 yes Figure 22 End view of the tie rod;

[0044] Figure 31 yes Figure 30 Sectional structure diagram of section I-I.

[0045] In the diagram, 1—Main air inlet pipe, 101—Pull plate, 102—Pull rod, 103—Valve seat, 104—Valve cover, 105—Valve plate, 106—Valve plate compression spring, 107—Pressure fork plate, 108—Mandrel, 109—Sliding sleeve, 110—Buffer spring, 111—Spring sleeve, 112—Spring washer, 113—Valve motor, 114—Valve rocker arm, 115—Valve connecting rod, 116—Pull plate screw, 117—Valve air supply pipe, 118—Compressor air inlet pipe, 119—Air inlet, 120—Valve seat through groove, 121—Valve seat transverse rib, 122—Valve cover through groove, 123—Fork head hole, 124—Pull rod hole, 125— Control fork head; 126—Pull rod hole; 2—First-stage centrifuge A outlet duct; 3—First-stage centrifuge A inlet duct; 4—Third-stage centrifuge inlet duct; 5—Third-stage centrifuge outlet duct; 6—Centrifuge unit; 601—Main shaft gear; 602—Centrifuge main shaft; 603—Third-stage impeller; 604—Third-stage volute; 605—Second and third-stage impeller gear shafts; 606—Tilting pad bearing; 607—Sealing assembly; 608—Second-stage volute; 609—Second-stage impeller; 610—First-stage volute B; 611—First-stage impeller B; 612—First-stage impeller gear shaft; 613—First-stage impeller A; 614—First-stage volute A; 615—Centrifuge gearbox body; 61 6—Impeller connecting screw, 617—Locking nut, 618—Resonance channel, 619—Resonance cavity, 620—Separating plate, 621—Baffle snap ring, 622—Sound-absorbing material layer, 623—Elastic sound-absorbing ball, 624—Air inlet, 625—Inlet flange, 626—Sound-absorbing cavity cover, 627—Expansion channel, 628—Flow guide channel, 629—Impeller shaft hole, 630—Disc, 631—Blade, 632—Sealing snap ring, 633—Spacer ring, 634—O-ring seal, 635—Sealing housing, 636—Oil collection groove, 637—Oil collection ring, 638—Oil collection channel, 639—Oil drain hole, 640—Component cover 641—Sealing ring baffle; 642—Lip seal; 643—Stop pin; 644—Dynamic ring spring; 645—Dynamic ring support plate; 646—Labyrinth toothed ring; 647—Labyrinth grooved ring; 648—Static ring seat; 649—Static ring; 650—Dynamic ring; 651—Dynamic ring seat; 652—Dynamic ring groove; 653—Static ring groove; 654—Bearing outer ring; 655—Bearing support screw; 656—Oil injection bolt; 657—Bearing shell; 658—Temperature sensor; 659—Bearing shell wear layer; 7—Secondary centrifuge outlet duct; 8—Secondary centrifuge inlet duct; 9—First-stage centrifuge B inlet duct; 10—First-stage centrifuge B outlet duct. Detailed Implementation

[0046] like Figure 1The high-load three-dimensional centrifugal compressor shown includes a centrifuge unit 6 and a main air inlet duct 1. The centrifuge unit 6 is fixedly equipped with a primary centrifuge A outlet duct 2, a primary centrifuge A inlet duct 3, a tertiary centrifuge inlet duct 4, a tertiary centrifuge outlet duct 5, a secondary centrifuge outlet duct 7, a secondary centrifuge inlet duct 8, a primary centrifuge B inlet duct 9, and a primary centrifuge B outlet duct 10. The two ports of the main air inlet duct 1 are respectively connected to the primary centrifuge A inlet duct 3 and the primary centrifuge B inlet duct 9.

[0047] Figure 2 It shows Figure 1 The gas compression path of the centrifugal compressor is as follows: the first-stage compression unit A and the first-stage compression unit B are connected in parallel and then lead to the second-stage compression unit. The second-stage compression unit is then connected in series with the third-stage compression unit. The first-stage compression unit A, the first-stage compression unit B, the second-stage compression unit, and the third-stage compression unit are all centrifugal compressors including impellers and volutes. The air inlets of the first-stage centrifugal compressor A inlet pipe 3 and the first-stage centrifugal compressor B inlet pipe 9 of the first-stage compression unit A and B are respectively connected to the two ports of the main air inlet pipe 1. The air outlet pipes of the first-stage centrifugal compressor A and the first-stage centrifugal compressor B inlet pipe 10 of the first-stage compression unit A and B are both connected to the second-stage centrifugal compressor inlet pipe 8 of the second-stage compression unit. The second-stage centrifugal compressor outlet pipe 7 of the second-stage compression unit is connected to the third-stage centrifugal compressor outlet pipe 5 of the second-stage compression unit.

[0048] like Figure 3 As shown, the centrifuge unit 6 includes a centrifuge gearbox housing 615, on which a centrifuge main shaft 602 is rotatably supported. The centrifuge gearbox housing 615 also rotatably supports a high-speed rotating first-stage impeller gear shaft 612 and a second- and third-stage impeller gear shaft 605 via tilting pad bearings 606. Sealing components 607 are installed on the outer sides of the two tilting pad bearings 606 supporting the first-stage impeller gear shaft 612 and the second- and third-stage impeller gear shafts 605. The centrifuge main shaft 602, the first-stage impeller gear shaft 612, and the second- and third-stage impeller gear shafts 605 all employ a gear shaft structure, and the number of teeth on the gear on the centrifuge main shaft 602 is much greater than the number of teeth on the first-stage impeller gear 612 and the second- and third-stage impeller gear shafts 605, thus forming a speed-increasing gear transmission. The centrifuge gearbox 615 contains lubricating oil, which lubricates the four tilting bearings 606 and regulates and controls the oil temperature of the gears and bearings through the side circulation of the lubricating oil.

[0049] The first-stage impeller gear shaft 612 extends out of the centrifuge gearbox housing 615, and first-stage impellers B611 and A613 are fixedly mounted at both ends. Correspondingly, first-stage volutes B610 and A614 are also mounted on the housing wall of the centrifuge gearbox housing 615. First-stage impellers A613 and first-stage volutes A constitute the first-stage compression unit A, and first-stage impellers B611 and first-stage volutes B610 constitute the first-stage compression unit B.

[0050] The two ends of the second and third stage impeller gear shafts 605 extending out of the centrifuge gearbox housing 615 are respectively fixedly mounted with a second-stage impeller 609 and a third-stage impeller 603. A second-stage volute 608 and a third-stage volute 604 are also installed on the housing wall of the centrifuge gearbox housing 615. The second-stage impeller 609 and the second-stage volute 608 constitute a second-stage compression unit, and the third-stage impeller 603 and the third-stage volute 604 constitute a third-stage compression unit.

[0051] Depending on the different operating states and compression ratios of each compression unit, the impellers and volutes of each compression unit have different dimensional parameters, but their structural forms are consistent. Therefore, their volutes and impellers have a consistent structural form.

[0052] Figure 4 Taking the first-stage compression unit B as an example, the structure of each compression unit is explained. The first-stage volute B610 is fixedly mounted on the centrifuge gearbox housing 615. A circular guide channel 628 is formed between the first-stage volute B610 and the centrifuge gearbox housing 615, which surrounds the outer periphery of the first-stage impeller B611. An expansion channel 627 and an air inlet 624 are also provided on the first-stage volute B610. The gas entering through the air inlet 624, under the work of the first-stage impeller B611, enters the air outlet along the guide channel 628 and the expansion channel 627, and then enters the second-stage compression unit.

[0053] like Figure 5 , Figure 6 As shown, the impeller includes blades 631 of a disc 630. An impeller shaft hole 629 is provided at the center of the disc 630 to securely mount the impeller shaft hole 629 to the corresponding impeller tooth journal position. The disc 630 has a diameter of 360 mm. The disc 630 and blades 631 are an integral structure, formed by molding.

[0054] like Figure 6 and Figure 7As shown, the blade 631 on the wheel 630 includes a working section and a wake section. The working section is a circular arc segment, while the wake section is an elliptical arc segment. In this embodiment, the radius of the circle containing the outer surface of the circular arc blade in the working section is R1 = 352 mm, and the radius of the circle containing the inner surface of the circular arc blade in the working section is R2 = 248 mm. Therefore, the radius of the circle containing the circular arc blade in the working section is R = (R1 + R2) / 2 = 350 mm, and the blade thickness is 4 mm. The major semi-axis of the ellipse containing the wake section is a = R = 350 mm, and the minor semi-axis is b = 226 mm. Similarly, a = (a1 + a2) / 2, b = (b1 + b2) / 2, where a1 and a2 are the major semi-axis of the inner and outer surfaces of the ellipse containing the wake section, respectively, and b1 and b2 are the minor semi-axis of the inner and outer surfaces of the ellipse containing the wake section, respectively. The center point of the ellipse containing the wake section is located at the center of the circle containing the working section. The length of the wake segment S1 = 13.80 mm, and the length of the working segment S = 78 mm. After repeated data analysis and a large number of experiments by the applicant, it is preferred that the major radius a = R of the ellipse containing the wake segment, the minor semi-axis b = (0.50-0.75)R of the ellipse, and the ratio of the length of the wake segment S1 to the length of the working segment S is 1:(5-6).

[0055] like Figure 8 As shown, a resonant cavity 619 is provided on the first-stage volute B610. The resonant cavity 619 is an annular groove arranged circumferentially along the axis of the volute and opening upwards. Figure 9 As shown, several resonance channels 618 are evenly distributed circumferentially on the bottom surface of the annular groove of the resonance cavity 619. These resonance channels 618 are axially arranged through holes, allowing the expansion channel 627 to communicate with the resonance cavity 619. A partition plate 620 is fixedly installed on the upper wall of the annular groove via a partition spring 621. The annular groove above the partition plate 620 is filled with a sound-absorbing material layer 622, in which elastic sound-absorbing balls 623 are embedded. The sound-absorbing material layer 622 is made of rock wool or glass fiber, and the elastic sound-absorbing balls 623 are small silicone elastic balls. A sound-absorbing cavity cover plate 626 is fixedly installed at the opening of the annular groove. The sound-absorbing cavity cover plate 626 is an annular pressure plate fitted onto the volute casing. An inlet flange 625 is also welded to the outer wall of the air inlet 624. Figure 10 As shown, the partition plate 620 is a disc-shaped circular plate with a central hole, and several through holes are distributed on the disc surface of the partition plate 620.

[0056] like Figure 11 The sealing assembly shown includes a sealing housing 635, on the outer shell of which three sealing grooves and O-rings embedded in the grooves are provided. An oil collection groove 636 is also provided on the outer shell of the sealing housing 635. The sealing housing 635 is fixedly mounted in the shaft hole of the centrifuge gearbox body 615 via sealing elements.

[0057] A rotating ring support disk 645 is rotatably disposed within the cavity of the sealing housing 635. The rotating ring support disk 645 is fixedly mounted to the corresponding impeller gear shaft via a connecting key. A gap is left between the rotating ring support disk 645 and the cavity wall of the sealing housing 635. A rotating ring seat 651 is provided on each side of the rotating ring support disk 645. An O-ring seal 634 is installed between the rotating ring seat 651 and the corresponding impeller gear shaft. A corresponding rotating ring 650, which has a disc-shaped structure, is embedded in each rotating ring seat 651. A stop pin 643 is provided on the rotating ring support plate 645. Both ends of the stop pin 643 are inserted into the pin holes of the corresponding rotating ring seats 651. When the impeller gear shaft rotates, the rotating ring support plate 645 drives the rotating ring seats 651 on both sides to rotate together with the gear shaft via the stop pin 643. An axial spring through hole is provided on the rotating ring support plate 645, and a rotating ring spring 644 is installed in the spring through hole. Both ends of the rotating ring spring 644 abut against the corresponding rotating ring seats 651 to apply a sealing pressure to the rotating ring. In this embodiment, the rotating ring spring 644 is fitted onto the stop pin 643, making the rotating ring spring 644 and the stop pin 643 an integral unit. Obviously, it is also possible to provide the rotating ring spring 644 and the stop pin 643 separately, with the stop pin 643 fixedly mounted on the rotating ring support plate 645, and the rotating ring spring 644 located in the corresponding spring hole of the rotating ring support plate 645.

[0058] A stationary ring 649 is also connected to the end face of the rotating ring 650. The rotating ring 650 and the stationary ring 649 constitute a mechanical seal. The stationary ring 649 is fixedly embedded in the stationary ring seat 648, which is then fixedly installed in the cavity of the sealing shell 635 by the O-ring 634 at the top. This structure of the present invention constitutes a symmetrically arranged double mechanical seal structure.

[0059] Inside the cavity of the sealing housing 635, a labyrinth toothed ring 646 is fixedly installed on the side by a corresponding O-ring. Spacers 633 are provided on both ends of the labyrinth toothed ring 646. Corresponding to the labyrinth toothed ring 646, a labyrinth grooved ring 647 is fixedly installed on the impeller gear shaft by an O-ring. A sealing retainer 632 is provided on one side of the labyrinth grooved ring 647, which is snapped onto the impeller gear shaft. The labyrinth toothed ring 646 and the labyrinth grooved ring 647, which are inserted into each other, constitute a labyrinth sealing structure.

[0060] A component cover 640 is fixedly installed on the outer side of the sealing housing 635 cavity by connecting bolts. Three lip seals 642 are installed in the center hole of the component cover 640, and the lip seals 642 are press-fitted onto the component cover 640 by sealing ring baffles 641. An oil collecting ring 637 is fixedly installed between the component cover 640 and the corresponding stationary ring seat 648. The annular oil collecting ring 637 is provided with an oil drain hole 639. The oil collecting ring 637 forms an oil collecting ring cavity between the component cover 640 and the stationary ring seat 648. The oil collecting ring cavity leads to the oil collecting groove 636 through the oil drain hole 639 and the oil collecting channel 638, which is provided on the sealing housing 635.

[0061] like Figure 12 , Figure 13 As shown, the rotating ring 650 has a disc-shaped structure. A central hole is located at the center of the rotating ring 650. Twelve rotating ring grooves 652 are evenly distributed circumferentially on the rotating ring sealing surface of the rotating ring 650. The cross-section of each rotating ring groove 652 is a rectangular groove, and the opening of the groove 652 faces the outer side of the rotating ring. Figure 14 , Figure 15 As shown, the stationary ring 649 also has a disc-shaped structure. A stationary ring center hole is provided at the center of the stationary ring 649. Twelve stationary ring grooves 653 are evenly distributed around the circumference of the stationary ring sealing surface. The cross-section of the stationary ring groove 653 is a triangular groove with an inclined slope. The groove opening of the stationary ring groove 653 faces the outside of the stationary ring.

[0062] like Figure 16 , Figure 17 The tilting pad bearing 606 shown includes an outer ring 654. Five bearing shells 657 are mounted on the inner wall of the outer ring 654. The bearing shells 657 are supported on the inner wall of the outer ring 654 by bearing shell support screws 655. The bearing shell support screws 655 can adjust the position of the bearing shells 657 and also allow the bearing shells 657 to tilt slightly during operation to form an oil wedge. Oil injection bolts 656 are provided between the lower bearing shells 657. These oil injection bolts 656 are fixedly installed on the outer ring 654. The oil injection bolts 656 can inject lubricating oil into the bearing shell support surface to determine the lubrication effect between the journal and the bearing shell, and can also regulate the bearing operating temperature by changing the amount of oil injected. Temperature sensors 658 are also embedded in the lower bearing shells 657. These temperature sensors 658 are platinum resistance thermometers, but fiber optic or other suitable temperature sensors can also be used.

[0063] like Figure 18 , Figure 19 As shown, a bearing wear-resistant layer 659 is provided on the bearing bearing surface 657 to enhance the bearing bearing's wear resistance and corrosion resistance. The bearing wear-resistant layer 659 is made of polyamide coating, or it can be made of materials such as tetrafluoroethylene coating.

[0064] like Figure 20 , Figure 21 The main air inlet duct shown is symmetrically designed and includes two opposing valve assemblies. The air inlet sides of both valve assemblies face the air inlet duct port 119. A valve-driven motor 113 is fixedly mounted on the casing between the two valve assemblies. A valve-driven rocker arm 114 with two outwardly extending ends is fixedly mounted on the output shaft of the valve-driven motor 113. The two outwardly extending ends of the valve-driven rocker arm 114 are respectively hinged to corresponding valve-driven connecting rods 115. The other end of the valve-driven connecting rod 115 is connected to the corresponding valve assembly. The valve-driven motor 113 is a servo motor. When the valve-driven motor 113 rotates clockwise, the valve-driven rocker arm 114 at its shaft end also swings clockwise. The clockwise swinging valve-driven rocker arm 114 drags the valve-driven connecting rods 115 on both sides closer to the center, thus driving the valve assembly to move. Conversely, the counterclockwise swinging valve-driven rocker arm 114 pushes the valve-driven connecting rod 115 to move outward from the centerline.

[0065] A valve air supply pipe 117 is fixedly installed at the air outlet of the valve assembly. The valve air supply pipe 117, which is bent at a right angle, is fixed and connected to the compressor air inlet pipe 118. The compressor air inlet pipe 118 is also a right-angle bent pipe. The compressor air inlet pipe 118 is connected to the air inlet pipe 3 of the first-stage centrifuge A and the air inlet pipe 9 of the first-stage centrifuge B on the corresponding side.

[0066] like Figure 22 As shown, the valve assembly includes a valve seat 103 and a valve cover 104. The valve seat 103 is sealed to the port end of the valve air supply pipe 117 via a sealing gasket. The valve cover 104 is fixedly mounted on the valve seat 103, and a sealing gasket or sealing ring is provided on the contact surface between the valve seat 103 and the valve cover 104. A valve plate 105 is movably disposed in the cavity between the valve seat 103 and the valve cover 104, and a plurality of valve plate compression springs 106 are supported between the valve plate 105 and the valve cover 104. The valve plate compression springs 106 are helical compression springs. A pressure fork plate 107 is provided on the outside of the valve cover 104. The control fork 125 on the pressure fork plate 107 extends through the valve cover 104 toward the valve plate 105. When the pressure fork plate 107 moves axially, the control fork 125 on it presses against the valve plate 105, and the valve plate 105 presses against the valve seat 103 to close the valve. When the control fork 125 leaves the valve plate 105, the valve plate 105 leaves the valve seat 103 under the action of the flowing gas, and the valve opens.

[0067] A spring sleeve 111 is also fixedly installed on the back side of the pressure fork plate 107. The spring sleeve 111 is located at the axial position of the pressure fork plate 107. A spindle 108 is fixedly installed at the center position of the valve seat 103 and the valve cover 104. The spindle 108 is slidably fitted onto the spring sleeve 111 through the sliding sleeve 109. A spring washer 112 is installed on the shoulder of the spindle 108. A buffer spring 110 is provided between the spring washer 112 and the spring sleeve 111. The buffer spring 110 is a cylindrical helical compression spring.

[0068] like Figure 23 , Figure 24 As shown, the valve seat 103 has a disc-plate structure. On the nine concentric circles of the valve seat 103 disc surface, valve seat grooves 120 and valve seat transverse ribs 121 are provided alternately along the circumference of each concentric circle. For example... Figure 25 , Figure 26 and Figure 27 As shown, the valve cover 104 also has a disc-plate structure, with valve cover through slots 122 spaced apart along the circumference of each of the nine concentric circles on the disc surface of the valve cover 104. A fork hole 123 for the control fork 125 to pass through is provided on the disc surface of the valve cover 104; a rod hole 124 for sliding through the rod 102 is also provided on the disc surface of the valve cover 104.

[0069] like Figure 28 , Figure 29 As shown, the pressure fork plate 107 includes a central body and a fork arm extending radially outward. The central body is provided with a spindle hole for fixing and installing the spindle 108, and a control fork 125 is vertically arranged on the extended fork arm.

[0070] like Figure 30 , Figure 31 As shown, the pull plate 101 includes a central main body and a pull plate arm extending radially outward. The central main body is fixedly provided with a pull plate screw 116. The pull plate screw 116 is hinged to the valve moving connecting rod 115 through a corresponding hinge support. A pull rod hole 126 for sliding through the pull rod 102 is provided on the outwardly extending pull plate arm.

[0071] Finally, it should be noted that the above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments or make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A high-load three-dimensional flow centrifugal compressor, comprising a centrifugal unit (6), wherein the centrifugal unit (6) comprises a primary compression unit A, a primary compression unit B, a secondary compression unit and a tertiary compression unit, wherein the primary compression unit A and the primary compression unit B are connected in parallel to the secondary compression unit, and the secondary compression unit is connected in series to the tertiary compression unit; The first-stage compression unit A includes a first-stage volute A (614) and a first-stage impeller A (613); the first-stage compression unit B includes a first-stage volute B (610) and a first-stage impeller B (611); the second-stage compression unit includes a second-stage volute (608) and a second-stage impeller (609); and the third-stage compression unit includes a third-stage volute (604) and a third-stage impeller (603). The first-stage impeller A (613), first-stage impeller B (611), second-stage impeller (609), and third-stage impeller (603) are rotatably supported on the centrifuge gearbox housing (615). Each of the first-stage impeller A (613), first-stage impeller B (611), second-stage impeller (609), and third-stage impeller (603) includes a corresponding impeller disc (630), on which blades (631) are provided; characterized in that: The blade (631) includes a working section and a wake section. The working section is a circular arc segment, and the wake section is an elliptical arc segment. The radius of the circle containing the working section is R. The major semi-axis of the ellipse containing the wake section is a = R, and the minor semi-axis of the ellipse is b = (0.50-0.75)R. The ratio of the wake section length S1 to the working section length S is 1:(5-6). The center point of the ellipse containing the wake section is located at the center of the circle containing the working section. The first-stage impeller A (613) and the first-stage impeller B (611) are respectively fixedly installed at both ends of the first-stage impeller gear shaft (612), and the second-stage impeller (609) and the third-stage impeller (603) are respectively fixedly installed at both ends of the second- and third-stage impeller gear shafts (605); the first-stage impeller gear shaft (612) and the second- and third-stage impeller gear shafts (605) are rotatably supported on the centrifuge gearbox housing (615) by tilting pad bearings (606), and a sealing assembly (607) is installed on the outside of the tilting pad bearings (606). The sealing assembly (607) includes a sealing housing (635), and a moving ring support disk (645) is movably arranged in the cavity of the sealing housing (635). A rotating ring support plate (645) is fixedly installed on the journal of the shaft (612) and the second and third stage impeller gear shaft (605); a rotating ring seat (651) is symmetrically arranged on both sides of the rotating ring support plate (645), and a rotating ring (650) is fixedly embedded in each rotating ring seat (651). A stop pin (643) is installed on the rotating ring support plate (645), and the two ends of the stop pin (643) are respectively inserted into the rotating ring seat (651) on the corresponding side; a number of rotating ring springs (644) are also arranged between the two rotating ring seats (651); a stationary ring (649) connected to the end face of the rotating ring (650) is embedded in the stationary ring seat (648), and the stationary ring seat (648) is fixedly installed in the cavity of the sealing housing (635); Each of the first-stage volute A (614), first-stage volute B (610), second-stage volute (608), and third-stage volute (604) is provided with a corresponding expansion channel (627) and a resonant cavity (619). The expansion channel (627) leads to the resonant cavity (619) through several resonant channels (618). At the outer end of the resonant cavity (619), a sound-absorbing material layer (622) is fixedly provided through a partition plate (620). Elastic sound-absorbing balls (623) are embedded in the sound-absorbing material layer (622).

2. The high-load three-dimensional centrifugal compressor according to claim 1, characterized in that: The first-stage impeller A (613), the first-stage impeller B (611), the second-stage impeller (609), and the third-stage impeller (603) all include a disc (630) and blades (631), and the disc (630) and blades (631) are integral structures.

3. The high-load three-dimensional flow centrifugal compressor according to claim 1 or 2, characterized in that: The centrifuge gearbox housing (615) is rotatably supported by a centrifuge main shaft (602), and the driving gear on the centrifuge main shaft (602) meshes with the driven gears on the first-stage impeller gear shaft (612) and the second and third-stage impeller gear shafts (605) for transmission.

4. The high-load three-dimensional flow centrifugal compressor according to claim 1, characterized in that: The primary volute A (614), primary volute B (610), secondary volute (608), and tertiary volute (604) are fixedly installed on the centrifuge gearbox body (615). The primary volute A (614), primary volute B (610), secondary volute (608), and tertiary volute (604) form corresponding flow channels (628) with the centrifuge gearbox body (615), and the flow channels (628) lead to the corresponding expansion channels (627).

5. The high-load three-dimensional flow centrifugal compressor according to claim 4, characterized in that: Each of the first-stage volute A (614), first-stage volute B (610), second-stage volute (608), and third-stage volute (604) is fixedly equipped with a corresponding sound-absorbing cavity cover plate (626), which is fitted onto the outer wall of the air inlet (624).

6. The high-load three-dimensional flow centrifugal compressor according to claim 5, characterized in that: The sound-absorbing material layer (622) is located between the partition perforated plate (620) and the sound-absorbing cavity cover plate (626); the partition perforated plate (620) is an annular disc-shaped perforated plate with several through holes; the resonant cavity (619) is an annular groove cavity, and the sound-absorbing material layer (622) is filled with rock wool or glass fiber.

7. The high-load three-dimensional centrifugal compressor according to claim 1, characterized in that: The stop pin (643) is installed with a gap in the stop pin hole of the moving ring support plate (645), and the moving ring spring (644) is fitted on the stop pin (643); a labyrinth toothed ring (646) is fixedly installed at the inner end of the cavity of the sealing housing (635), and labyrinth grooved rings (647) are fixedly installed on the journals of the first-stage impeller toothed shaft (612) and the second and third-stage impeller toothed shafts (605), and the corresponding labyrinth grooved rings (647) are movably inserted into the labyrinth toothed rings (646); a component cover (640) is fixedly installed at the outer end of the cavity of the sealing housing (635), and a lip seal ring (642) is installed in the center hole of the component cover (640).

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