WO2016038661A1 - 回転機械 - Google Patents
回転機械 Download PDFInfo
- Publication number
- WO2016038661A1 WO2016038661A1 PCT/JP2014/073685 JP2014073685W WO2016038661A1 WO 2016038661 A1 WO2016038661 A1 WO 2016038661A1 JP 2014073685 W JP2014073685 W JP 2014073685W WO 2016038661 A1 WO2016038661 A1 WO 2016038661A1
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- WIPO (PCT)
- Prior art keywords
- casing
- impeller
- axis
- axial direction
- rotating shaft
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D1/06—Multi-stage pumps
- F04D1/08—Multi-stage pumps the stages being situated concentrically
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
- F04D17/12—Multi-stage pumps
- F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/051—Axial thrust balancing
- F04D29/0516—Axial thrust balancing balancing pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/16—Sealings between pressure and suction sides
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/52—Casings; Connections of working fluid for axial pumps
Definitions
- the present invention relates to a rotating machine.
- Rotating machines such as a centrifugal compressor compress a working fluid using centrifugal force generated when the impeller rotates by circulating the working fluid inside the rotating impeller.
- a centrifugal compressor a multistage centrifugal compressor that compresses a working fluid in stages by providing a plurality of impellers is known.
- the centrifugal compressor described in Patent Document 1 is a single-shaft multistage centrifugal compressor in which a large number of impellers are attached to the same rotating shaft.
- a plurality of impellers are attached to the rotating shaft side by side in the axial direction within the casing.
- the impeller rotates and compresses the working fluid, so that a thrust force is generated so as to press against the rotating shaft toward one side in the axial direction in which the working fluid flows. .
- this thrust force is increased. Therefore, in such a centrifugal compressor, in order to weaken the thrust force in one axial direction generated by the impeller, a balance piston that generates a thrust force in the opposite direction and balances the thrust force acting on the rotating shaft is provided. , Arranged adjacent to the last stage of the impeller.
- the present invention provides a rotating machine capable of preventing the formation of a gap and balancing the thrust force acting on the rotating shaft.
- a rotating machine includes a rotating shaft that rotates about an axis, and a disk that rotates together with the rotating shaft, and the working fluid that flows in from one side in the axial direction in which the axis extends extends in diameter.
- An internal flow path is formed to discharge outward in the direction of the direction, and a plurality of the impellers arranged side by side in the axial direction and the impeller adjacent to the other side from the impeller disposed on one side in the axial direction
- a plurality of impellers arranged at least on the othermost side in the axial direction are in a space communicating with the upstream side of the casing flow path.
- a convex portion that is formed integrally with the disc so as to protrude from a back surface facing the other side of the axial direction of the disc, and the convex portion is formed on the rotating shaft. Is formed parallel to the outer surface, wherein has a sealing surface for sealing the radial gap between the casing, and said extending from said outer surface of the rotary shaft to said seal surface pressure-receiving surface.
- the thrust force generated by the other plurality of impellers by the last stage impeller can be reduced. Can generate a thrust force in the opposite direction on the rotating shaft. Thereby, the thrust force which acts on a rotating shaft can be adjusted.
- the balance piston and the disk can be substantially integrally formed. It is possible to prevent the formation of a gap.
- the casing may be formed with a suction port through which the working fluid flows from the outside into the casing flow path, and the suction port and the space may be in communication.
- the space communicates with the suction port, it is possible to maximize the force that acts to pull the pressure receiving surface from one side in the axial direction toward the other side. For this reason, it is possible to increase the thrust force from the impeller toward the other side in the axial direction acting on the rotation shaft through the disk provided with the convex portion. Thereby, even when a large thrust force is generated on the rotating shaft, the thrust force generated on the rotating shaft can be balanced stably.
- the convex portion may have a concave portion that is radially inward of the seal surface and is recessed from the pressure receiving surface toward one side in the axial direction.
- An impeller according to a second aspect of the present invention includes a rotating shaft that rotates about an axis, and a disk that rotates together with the rotating shaft, and the working fluid that flows in from one side in the axial direction in which the axis extends extends in the radial direction.
- the working fluid is formed into a plurality of impellers arranged in a line in the axial direction, and a plurality of impellers arranged side by side in the axial direction, and an impeller adjacent to the other side from the impeller arranged on one side in the axial direction.
- An impeller disposed on the othermost side in the axial direction of a rotary machine, and protruding from a back surface facing the other side in the axial direction of the disk.
- a convex portion formed integrally with the disk and disposed in a space communicating with the upstream side of the casing flow path, the convex portion being parallel to the outer surface of the rotating shaft; Made that has a sealing surface for sealing the radial gap between the casing and a pressure receiving surface extending from said outer surface of said rotary shaft to said seal surface.
- the thrust force acting on the rotating shaft can be balanced by the convex portion formed integrally with the disk. Further, it is possible to prevent the gap on the back surface of the disk from being formed.
- the rotary machine of this embodiment is a centrifugal compressor 1, and is a single-shaft multistage centrifugal compressor in this embodiment.
- the centrifugal compressor 1 of the present embodiment is used, for example, in a nitric acid plant or the like, and compresses nitric acid as a working fluid F by circulating it.
- the centrifugal compressor 1 of the present embodiment includes a rotating shaft 2 that rotates about an axis O, a plurality of impellers 3 that are integrally fixed to the rotating shaft 2, and a rotating shaft 2. And a casing 4 that houses the impeller 3 therein.
- the rotary shaft 2 has a cylindrical shape extending along the axis O, and rotates around the axis O by a power source such as an electric motor (not shown).
- the impeller 3 accommodated in the casing 4 is fitted on the rotary shaft 2 and rotates around the axis O together with these.
- the rotary shaft 2 is rotatably supported with respect to the casing 4 by a journal bearing 41 and a thrust bearing 42, and is rotated by an electric motor (not shown).
- the plurality of impellers 3 are arranged side by side at intervals in the direction of the axis O, which is the direction in which the axis O of the rotating shaft 2 extends, and are housed inside the casing 4.
- the first stage disposed at the foremost stage on the most one side in the axis O direction (left side in FIG. 1) so as to correspond to each impeller 3 disposed in the axis O direction.
- the compressor stages 11, 12, 13, 14, 15 are provided.
- the casing 4 is formed to have a substantially cylindrical outer shape, and the rotary shaft 2 is disposed so as to penetrate the center.
- journal bearings 41 are provided on both sides in the direction of the axis O, and thrust bearings 42 are provided on one side in the direction of the axis O. That is, the casing 4 supports the rotating shaft 2 via the journal bearing 41 and the thrust bearing 42.
- the casing 4 is provided with an internal space in which the diameter reduction and the diameter expansion are repeated, and the plurality of impellers 3 are accommodated in the internal space.
- a casing flow path 43 is formed to flow the working fluid F from the impeller 3 disposed on the upstream side that is one side in the axis O direction to the impeller 3 that is adjacent to the downstream side that is the other side in the axis O direction.
- the casing 4 is formed with a low-pressure space 44 that is a space communicating with the upstream side of the casing channel 43.
- the casing channel 43 is connected to the one side and the axis O direction from the suction port 431 through which the working fluid F provided at the end of the casing 4 on one side, which is the first side in the axis O direction of the rotating shaft 2, flows.
- the inside of the casing 4 is communicated through the impeller 3 to the discharge port 434 that discharges the working fluid F provided at the other end that is the second side facing the opposite side.
- the casing flow path 43 of the present embodiment includes a suction port 431 through which the working fluid F flows from the outside, and a diffuser flow path 432 into which the working fluid F is introduced from an internal flow path 34 of the impeller 3 described later.
- the return passage 433 introduces the working fluid F from the diffuser passage 432 and introduces the working fluid F into the internal passage 34 of the impeller 3, and the discharge port 434 discharges the working fluid F to the outside. .
- the suction port 431 is in communication with the outside of the casing 4 at one end of the casing 4 in the direction of the axis O.
- the suction port 431 is connected to the inlet of the internal flow path 34 of the frontmost impeller 3 provided at one end portion in the axis O direction.
- the radially inner side of the casing 4 centering on the rotating shaft 2 communicates with the outlet of the internal flow path 34 of the impeller 3, and the working fluid F pressurized by the impeller 3 is radially outward. Circulate towards
- the return flow path 433 has one end communicating with the diffuser flow path 432 and the other end communicating with the inlet of the internal flow path 34 of the impeller 3.
- the return flow path 433 is reversed so that the direction of the working fluid F that has flowed radially outward through the diffuser flow path 432 is directed radially inward.
- the discharge port 434 communicates with the outside of the casing 4 at the other end of the casing 4 in the direction of the axis O.
- the discharge port 434 is connected to the outlet of the internal flow path 34 of the last stage impeller 3 provided at the other end portion in the axis O direction.
- the low pressure space 44 is formed on the other side in the direction of the axis O of the impeller 3 at the last stage of the casing 4.
- the low pressure space 44 communicates with the casing flow path 43 on the upstream side of the last stage impeller 3. That is, the low pressure space 44 communicates with a portion of the casing flow path 43 that has a lower pressure than the working fluid F compressed by the last stage impeller 3.
- the low pressure space 44 communicates with the suction port 431 having the lowest pressure in the casing flow path 43, and has the same pressure as the suction port 431.
- each impeller 3 rises from the surface of the disk 31 toward the one side in the direction of the axis O of the rotary shaft 2.
- a plurality of blades 32 that are radially attached to the disk 31 and arranged in the circumferential direction.
- the impeller 3 includes a cover 33 attached so as to cover the plurality of blades 32 in the circumferential direction from one side in the axis O direction.
- Each impeller 3 may be an open impeller that does not have the cover 33.
- the impeller 3 has an internal flow path 34 that is a space through which the working fluid F flowing from one side in the direction of the axis O is circulated so as to be discharged radially outward.
- the internal flow path 34 is defined by the surfaces of the disk 31 and the cover 33 provided on both sides of the blade 32 in the axis O direction, along with the two surfaces of the pair of blades 32 adjacent to each other in the circumferential direction.
- the internal flow path 34 takes in and discharges the working fluid F as the blade 32 rotates integrally with the disk 31. Specifically, the internal flow path 34 takes in the working fluid F flowing through the inside as an inlet into which the working fluid F flows in one side of the blade 32 in the direction of the axis O, that is, the inside in the radial direction.
- the internal flow path 34 discharges the working fluid F guided as an outlet from which the working fluid F flows out on the radially outer side.
- the front surface of the disk 31 facing one side in the axis O direction has a small diameter
- the back surface 311 facing the other side in the axis O direction has a large diameter.
- the diameter of the disk 31 gradually increases from the front surface on one side in the direction of the axis O toward the back surface 311 on the other side. That is, the disk 31 has a substantially disk shape when viewed in the direction of the axis O, and has a generally umbrella shape as a whole.
- the disk 31 is formed with a through hole penetrating the disk 31 in the direction of the axis O on the radially inner side.
- the impeller 3 is fixed to the rotating shaft 2 and can be rotated together with the rotating shaft 2 by inserting the rotating shaft 2 into the through-hole and fitting with a shrink fit (not shown) or via a key. It has become.
- the impeller 3 arranged at least on the other side in the direction of the axis O has a convex portion 5 formed integrally with the disk 31.
- the impeller 3 arranged in the last fifth-stage compressor stage 15 which is the other side in the direction of the axis O has the convex part 5.
- the convex portion 5 protrudes rearward in the axis O direction from the back surface 311 of the disk 31 which is a surface intersecting the outer surface 21 of the rotating shaft 2.
- the convex portion 5 is disposed in the low pressure space 44.
- the convex portion 5 of the present embodiment protrudes in an annular shape from the back surface 311 of the disk 31 so as to surround the through hole of the disk 31.
- the convex portion 5 of the present embodiment includes a seal surface 51 formed in parallel with the outer surface 21 of the rotating shaft 2, and a pressure receiving surface 52 extending from the outer surface 21 of the rotating shaft 2 to the seal surface 51. And a recess 53 that is recessed from the pressure receiving surface 52.
- the sealing surface 51 seals the radial gap between the casing 4 and the disk 31.
- the seal surface 51 is a horizontal surface facing the radially outer side of the convex portion 5 and extends parallel to the axis O.
- the seal surface 51 of the present embodiment has a labyrinth seal 51a and extends from the back surface 311 of the disk 31 by a width necessary for sealing the working fluid F from one side in the direction of the axis O toward the other side. ing. That is, the sealing surface 51 of the present embodiment seals the space between the casing 4 and the horizontal plane facing inward in the radial direction. Therefore, the seal surface 51 prevents the high-pressure working fluid F discharged from the internal flow path 34 of the impeller 3 from leaking toward the low-pressure space 44.
- the protrusion amount of the convex portion 5 from the back surface 311 of the disk 31 is determined by the width of the seal surface 51 in the axis O direction.
- the seal surface 51 is formed at a position away from the outer surface 21 of the rotating shaft 2 by a predetermined distance.
- the predetermined distance from the outer surface 21 of the rotating shaft 2 on which the seal surface 51 is formed in the present embodiment is the outside of the rotating shaft 2 when the pressure receiving surface 52 is viewed from the other side in the axis O direction. This is the radial length of the pressure receiving surface 52 from the surface 21.
- the predetermined distance is a value set in advance for each centrifugal compressor 1.
- the predetermined distance is determined according to the magnitude of the force received by the pressure receiving surface 52 in order to balance the thrust force acting on the rotating shaft 2.
- the predetermined distance in the present embodiment is determined by a ratio between the magnitude of the pressure in the low pressure space 44 and the magnitude of the pressure of the working fluid F compressed by the last stage impeller 3.
- the seal surface 51 of the present embodiment is, for example, only the last stage impeller 3 provided with the convex portion 5, and the axis O generated on the rotating shaft 2 by the other four impellers 3 other than the last stage impeller 3.
- the pressure receiving surface 52 is a surface which is formed facing the low pressure space 44 and faces the other side of the convex portion 5 in the axis O direction.
- the pressure receiving surface 52 receives a force so as to be drawn toward the other side in the direction of the axis O toward the low pressure space 44.
- the pressure receiving surface 52 of the present embodiment includes a main pressure receiving surface 521 formed by being connected to the other end of the seal surface 51 in the direction of the axis O, and a first pressure receiving surface 522 and a second pressure formed by a recess 53 described later. And a pressure receiving surface 523.
- the main pressure receiving surface 521 is a surface extending vertically from the other end of the seal surface 51 in the direction of the axis O toward the radially inner side. That is, the main pressure receiving surface 521 is a surface orthogonal to the outer surface 21 of the rotating shaft 2 and faces the other side in the direction of the axis O.
- the recess 53 is recessed radially inward of the seal surface 51 from the pressure receiving surface 52 to one side in the axis O direction.
- the concave portion 53 of the present embodiment is recessed from the main pressure receiving surface 521, and is a part of the pressure receiving surface 52, and includes a first pressure receiving surface 522 orthogonal to the outer surface 21 of the rotating shaft 2, and the first pressure receiving surface 522. And a second pressure receiving surface 523 formed to be inclined so as to face the outer surface 21 of the rotary shaft 2 on the radially outer side.
- the first pressure receiving surface 522 is a surface extending vertically from the other end of the through hole of the disk 31 in the direction of the axis O toward the radially outer side. That is, the first pressure receiving surface 522 is formed in parallel with the main pressure receiving surface 521 and the back surface 311 of the disk 31 and faces the other side in the axis O direction.
- the first pressure receiving surface 522 of the present embodiment is formed so that the position in the axis O direction is the same position as the back surface 311 of the disk 31.
- the second pressure receiving surface 523 is a surface connecting the first pressure receiving surface 522 and the main pressure receiving surface 521. Specifically, the second pressure receiving surface 523 is located on the other side in the direction of the axis O and radially inward of the main pressure receiving surface 521 from the radially outer end of the first pressure receiving surface 522 toward the radially outer side. It is formed so as to be connected to the end. That is, the second pressure receiving surface 523 is formed to be inclined so as to face the other side in the axis O direction and the radially inner side.
- the centrifugal compressor 1 which is the rotating machine having the above configuration will be described.
- the working fluid F flowing in from the suction port 431 flows into the internal flow path 34, the diffuser flow path 432, the return flow of the first stage impeller 3 arranged in the first stage compressor stage 11.
- the working fluid F that has flowed from the last stage impeller 3 arranged in the fifth stage compressor stage 15 to the diffuser flow path 432 is discharged to the outside through the discharge port 434.
- the working fluid F is compressed by flowing through the internal flow path 34 of each impeller 3 while flowing in the order described above. That is, in the centrifugal compressor 1 of the present embodiment, the working fluid F is compressed stepwise by the plurality of impellers 3, thereby obtaining a large compression ratio.
- the working fluid F is compressed stepwise by the plurality of impellers 3 so that the rotary shaft 2 fixed to the impeller 3 via the disk 31 has an axis line.
- a thrust force is generated toward one side in the O direction.
- the convex portion 5 is provided on the disk 31 of the last stage impeller 3 on the othermost side in the axis O direction, the last stage impeller 3 causes the first stage to the fourth stage impeller 3.
- a thrust force directed to the other side in the direction of the axis O which is the direction opposite to the thrust force, can be generated on the rotary shaft 2.
- the convex portion 5 is provided in the low pressure space 44, and the high pressure working fluid F discharged from the internal flow path 34 of the last stage impeller 3 by the seal surface 51 does not leak toward the low pressure space 44. It is sealed as follows. Therefore, the pressure in the low pressure space 44 on the other side in the axis O direction is lower than that in the space around the impeller 3 on the one side in the axis O direction with the seal surface 51 as a boundary. Therefore, a lower pressure than the cover 33 and the back surface 311 acts on the pressure receiving surface 52 constituted by the first pressure receiving surface 522, the second pressure receiving surface 523, and the main pressure receiving surface 521. Thereby, it is possible to generate a thrust force toward the other side in the direction of the axis O from the last stage impeller 3 via the disk 31 provided with the convex portion 5 with respect to the rotating shaft 2.
- the thrust force received by the rotating shaft 2 by the impellers 3 from the first stage to the fourth stage can be weakened by the impeller 3 at the last stage.
- the thrust force which acts on the rotating shaft 2 can be adjusted. Therefore, it can suppress that the rotating shaft 2 shifts
- the centrifugal compressor 1 when used in a nitric acid plant and nitric acid is used as the working fluid F, a part of ammonia used in the previous step is erroneously casing.
- nitric acid and ammonia react to produce ammonium nitrate as a solid product. Therefore, when an annular separate member is arranged as a balance piston on the back surface 311 of the disk 31 of the impeller 3 at the last stage to adjust the thrust force generated in the rotating shaft 2, when the high-pressure working fluid F flows, In the gap formed between the rear surface 311 of 31 and another member, the solid product is accumulated in the gap.
- the working fluid F that flows in is at a high pressure. It is difficult to prevent the working fluid F from flowing in.
- the balance piston and the disk 31 can be substantially integrally formed by adjusting the thrust force generated in the rotating shaft 2 by the convex portion 5 formed integrally with the disk 31, so that it is necessary to use a separate member. And unnecessary gaps can be prevented from being formed.
- the low pressure space 44 since the low pressure space 44 communicates with the suction port 431 having the lowest pressure in the casing flow path 43, the low pressure space 44 functions to pull from the one side in the axis O direction toward the other side with respect to the pressure receiving surface 52.
- the power can be maximized. Therefore, it is possible to increase the thrust force directed from the last stage impeller 3 to the other side in the direction of the axis O acting on the rotary shaft 2 through the disk 31 provided with the convex portions 5.
- the convex portion 5 is simply provided. Is formed, the convex portion 5 is greatly formed in the radial direction. However, since the concave portion 53 that is recessed from the pressure receiving surface 52 is formed, the convex portion 5 can be formed small by shaving the flesh of the convex portion 5 while forming the pressure receiving surface 52. Therefore, an increase in the weight of the impeller 3 having the convex portion 5 can be suppressed by forming the concave portion 53.
- the convex portion 5 is formed integrally with the disk 31, it is not necessary to fix another member such as a balance piston with the back surface 311 of the disk 31. Therefore, it is not necessary to secure a space on the outer surface 21 of the rotating shaft 2 in order to shrink-fit another member to the rotating shaft 2 and fix it. As a result, the length of the rotating shaft 2 in the axis O direction can be shortened, and vibration of the rotating shaft 2 can be suppressed.
- the seal surface 51 is formed in parallel with the outer surface 21 of the rotary shaft 2, in the rotary machine such as the centrifugal compressor 1 having the plurality of impellers 3, the extension in the direction of the axis O is applied to the rotary shaft 2. Even if it occurs, it is possible to suppress the influence. For example, when the seal surface 51 is formed to be inclined or formed in a step shape, the seal surface 51 comes into contact with the casing 4 by causing the rotation shaft 2 to extend in the axis O direction. There is a risk that. As a result, not only the sealing performance is impaired, but also the rotating shaft 2 may be damaged. However, since the seal surface 51 is formed in parallel with the outer surface 21 of the rotating shaft 2, even when the position of the seal surface 51 moves in the direction of the axis O, the sealing performance without contacting the casing 4. Can be secured.
- the recessed part 53 was formed so that the 1st pressure receiving surface 522 and the 2nd pressure receiving surface 523 may be formed in the convex part 5, it is not limited to such a structure.
- the recess 53 may have any shape such that the recess 53 is formed so as to be recessed from the main pressure receiving surface 521 in a semicircular cross section.
- the concave portion 53 itself may not be formed in the convex portion 5.
- the impeller 3 is not limited to the structure arrange
- the structure may be at least six stages or more than six stages.
- the convex portion 5 formed integrally with the disk 31 can prevent a gap from being generated, and can balance the thrust force acting on the rotary shaft 2.
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Abstract
Description
本実施形態の回転機械は、遠心圧縮機1であり、本実施形態では一軸多段式遠心圧縮機となっている。本実施形態の遠心圧縮機1は、例えば、硝酸プラント等に用いられ、作動流体Fとして硝酸を流通させて圧縮している。本実施形態の遠心圧縮機1は、図1に示すように、軸線Oを中心として回転する回転軸2と、回転軸2に一体に回転可能に固定された複数のインペラ3と、回転軸2及びインペラ3を内部に収容するケーシング4とを備える。
なお、各々のインペラ3はカバー33を有していないオープンインペラであってもよい。
また、本実施形態では、ディスク31の背面311からの凸部5の突出量は、シール面51の軸線O方向の幅によって定められている。
上記のような遠心圧縮機1では、吸込口431から流入した作動流体Fは、第一段圧縮機段11に配置された一段目のインペラ3の内部流路34、ディフューザ流路432、リターン流路433の順に流れた後、第二圧縮機段12に配置された二段目のインペラ3の内部流路34、ディフューザ流路432、リターン流路433という順に圧縮されながら流れていく。そして、第五段圧縮機段15に配置された最後段のインペラ3からディフューザ流路432まで流れた作動流体Fは、吐出口434を介して外部に排出される。作動流体Fは、前述した順で流れる途中、各インペラ3の内部流路34を流通することによって圧縮される。つまり、本実施形態の遠心圧縮機1では、作動流体Fを複数のインペラ3によって段階的に圧縮し、これによって大きな圧縮比を得るようになっている。
F 作動流体
1 遠心圧縮機
2 回転軸
21 外表面
3 インペラ
31 ディスク
311 背面
32 ブレード
33 カバー
34 内部流路
5 凸部
51 シール面
51a ラビリンスシール
52 受圧面
521 主受圧面
522 第一受圧面
523 第二受圧面
53 凹部
4 ケーシング
41 ジャーナル軸受
42 スラスト軸受
43 ケーシング流路
431 吸込口
432 ディフューザ流路
433 リターン流路
434 吐出口
44 低圧空間
Claims (4)
- 軸線を中心として回転する回転軸と、
前記回転軸とともに回転するディスクを有し、前記軸線の延びる軸線方向の一方側から流入する作動流体を径方向外側に向かって排出する内部流路が形成され、前記軸線方向に複数並んで配置されるインペラと、
前記軸線方向の一方側に配置されたインペラから他方側に隣接するインペラに、前記作動流体を流通させるケーシング流路が形成されているケーシングとを備え、
複数の前記インペラのうち、少なくとも前記軸線方向の最も他方側に配置されるインペラは、
前記ケーシング流路の上流側と連通する空間に配置され、前記ディスクの前記軸線方向の他方側を向く背面から突出して前記ディスクと一体的に形成される凸部を有し、
前記凸部は、
前記回転軸の外表面と平行に形成され、前記ケーシングとの間の径方向の隙間を封止するシール面と、
前記回転軸の前記外表面から前記シール面まで延びる受圧面とを有する回転機械。 - 前記ケーシングは、前記作動流体を外部から前記ケーシング流路に流入させる吸込口が形成され、前記吸込口と前記空間とが連通している請求項1に記載の回転機械。
- 前記凸部は、
前記シール面よりも径方向内側で、前記受圧面から前記軸線方向の一方側に向かって凹む凹部を有する請求項1または請求項2に記載の回転機械。 - 軸線を中心として回転する回転軸と、
前記回転軸とともに回転するディスクを有し、前記軸線の延びる軸線方向の一方側から流入する作動流体を径方向外側に向かって排出する内部流路が形成され、軸線方向に複数並んで配置される複数のインペラと、
前記軸線方向の一方側に配置されたインペラから他方側に隣接するインペラに、前記作動流体を流通させるケーシング流路が形成されているケーシングと、を備える回転機械の前記軸線方向の最も他方側に配置されるインペラであって、
前記ディスクの前記軸線方向の他方側を向く背面から突出して前記ディスクと一体的に形成され、前記ケーシング流路の上流側と連通する空間に配置される凸部を有し、
前記凸部は、
前記回転軸の外表面と平行に形成され、前記ケーシングとの間の径方向の隙間を封止するシール面と、
前記回転軸の前記外表面から前記シール面まで延びる受圧面とを有するインペラ。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2016547270A JPWO2016038661A1 (ja) | 2014-09-08 | 2014-09-08 | 回転機械 |
US15/503,237 US20170227012A1 (en) | 2014-09-08 | 2014-09-08 | Rotary machine |
PCT/JP2014/073685 WO2016038661A1 (ja) | 2014-09-08 | 2014-09-08 | 回転機械 |
EP14901462.3A EP3168479A4 (en) | 2014-09-08 | 2014-09-08 | Rotary machine |
CN201480081005.XA CN106574622A (zh) | 2014-09-08 | 2014-09-08 | 旋转机械 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2014/073685 WO2016038661A1 (ja) | 2014-09-08 | 2014-09-08 | 回転機械 |
Publications (1)
Publication Number | Publication Date |
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WO2016038661A1 true WO2016038661A1 (ja) | 2016-03-17 |
Family
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Family Applications (1)
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PCT/JP2014/073685 WO2016038661A1 (ja) | 2014-09-08 | 2014-09-08 | 回転機械 |
Country Status (5)
Country | Link |
---|---|
US (1) | US20170227012A1 (ja) |
EP (1) | EP3168479A4 (ja) |
JP (1) | JPWO2016038661A1 (ja) |
CN (1) | CN106574622A (ja) |
WO (1) | WO2016038661A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
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US11608833B2 (en) | 2018-12-25 | 2023-03-21 | Gree Electric Appliances, Inc. Of Zhuhai | Centrifugal compressor and air conditioning equipment |
WO2023189043A1 (ja) * | 2022-03-30 | 2023-10-05 | ダイキン工業株式会社 | ターボ機械 |
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EP3140504A4 (en) * | 2014-07-24 | 2018-01-10 | Halliburton Energy Services, Inc. | Downhole electrical submersible pump with upthrust balance |
US10539147B2 (en) * | 2016-01-13 | 2020-01-21 | Wisconsin Alumni Research Foundation | Integrated rotor for an electrical machine and compressor |
JP2022011812A (ja) * | 2020-06-30 | 2022-01-17 | 三菱重工コンプレッサ株式会社 | 回転機械のインペラ及び回転機械 |
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2014
- 2014-09-08 WO PCT/JP2014/073685 patent/WO2016038661A1/ja active Application Filing
- 2014-09-08 US US15/503,237 patent/US20170227012A1/en not_active Abandoned
- 2014-09-08 JP JP2016547270A patent/JPWO2016038661A1/ja active Pending
- 2014-09-08 CN CN201480081005.XA patent/CN106574622A/zh active Pending
- 2014-09-08 EP EP14901462.3A patent/EP3168479A4/en not_active Withdrawn
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JP2002257080A (ja) * | 2001-03-02 | 2002-09-11 | Mitsubishi Heavy Ind Ltd | 遠心圧縮機の軸位置自動調整装置 |
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11608833B2 (en) | 2018-12-25 | 2023-03-21 | Gree Electric Appliances, Inc. Of Zhuhai | Centrifugal compressor and air conditioning equipment |
WO2023189043A1 (ja) * | 2022-03-30 | 2023-10-05 | ダイキン工業株式会社 | ターボ機械 |
JP2023148588A (ja) * | 2022-03-30 | 2023-10-13 | ダイキン工業株式会社 | ターボ機械 |
Also Published As
Publication number | Publication date |
---|---|
US20170227012A1 (en) | 2017-08-10 |
JPWO2016038661A1 (ja) | 2017-04-27 |
EP3168479A4 (en) | 2017-08-23 |
EP3168479A1 (en) | 2017-05-17 |
CN106574622A (zh) | 2017-04-19 |
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