WO2016030952A1 - シール機構、回転機械 - Google Patents
シール機構、回転機械 Download PDFInfo
- Publication number
- WO2016030952A1 WO2016030952A1 PCT/JP2014/072203 JP2014072203W WO2016030952A1 WO 2016030952 A1 WO2016030952 A1 WO 2016030952A1 JP 2014072203 W JP2014072203 W JP 2014072203W WO 2016030952 A1 WO2016030952 A1 WO 2016030952A1
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- WIPO (PCT)
- Prior art keywords
- hole
- rotor
- seal
- row
- peripheral surface
- 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
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/083—Sealings especially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
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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
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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
- F04D29/10—Shaft sealings
- F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
-
- 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
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/44—Free-space packings
- F16J15/444—Free-space packings with facing materials having honeycomb-like structure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/44—Free-space packings
- F16J15/447—Labyrinth packings
- F16J15/4472—Labyrinth packings with axial path
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/10—Two-dimensional
- F05D2250/19—Two-dimensional machined; miscellaneous
- F05D2250/191—Two-dimensional machined; miscellaneous perforated
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/20—Three-dimensional
- F05D2250/28—Three-dimensional patterned
- F05D2250/283—Three-dimensional patterned honeycomb
Definitions
- the present invention relates to a seal mechanism and a rotary machine provided in a rotary machine such as a turbine.
- a centrifugal compressor that compresses gas is widely known as one of rotating machines.
- an impeller is provided inside the casing, and the gas sucked from the suction port by the rotation of the impeller is compressed and discharged from the discharge port.
- a cap seal is provided at the impeller base, an intermediate seal is provided between the impeller stages, and a balance piston part seal is provided at the final stage to reduce the amount of leaked gas compressed by the impeller.
- a damper seal or a labyrinth seal may be used for such various seals.
- the labyrinth seal includes, for example, an annular projecting portion provided on a rotating rotating shaft and a projecting portion projecting annularly from the stationary member facing the rotating shaft with a gap toward the rotating shaft. In many cases, it is constituted by providing a plurality of stages alternately. In this labyrinth seal, fluid leakage can be reduced by causing pressure loss in the fluid flowing near the tip of the protrusion.
- Known damper seals include honeycomb seals and hole pattern seals. For example, in a hole pattern seal, a plurality of hole portions are formed in an opposing surface facing the rotation shaft in an annular stationary side member arranged with a gap from the rotation shaft. Leakage can be reduced (see, for example, Patent Document 1).
- the hole pattern seal has a greater damping effect than the labyrinth seal and is advantageous in terms of stabilizing the vibration of the rotating shaft, whereas the labyrinth seal can further reduce the amount of fluid leakage compared to the damper seal.
- the seal structure may vibrate due to a swirling flow (hereinafter simply referred to as swirl) of the flowing fluid.
- swirl a swirling flow
- the clearance must be set so that the stationary side and the rotating side do not come into contact with each other due to this self-excited vibration. Therefore, in the non-contact type seal mechanism, the clearance cannot be reduced, and it is difficult to further reduce the amount of fluid leakage.
- the swirl can be suppressed by causing the vortex generated in the hole to interfere with the swirl.
- swirl can be reduced by the vortex generated by the hole pattern seal. However, since swirl is not completely canceled, further swirl reduction is desired.
- the present invention can further reduce the swirl generated between the rotating side and the stationary side, and reduce the amount of leakage of the process gas G from the high pressure side to the low pressure side while preventing self-excited vibration due to the swirl.
- An object of the present invention is to provide a sealing mechanism and a rotating machine that can be used.
- the sealing mechanism is a sealing mechanism that is disposed on the outer peripheral side of the rotor extending along the axis and seals with the outer peripheral surface of the rotor.
- the sealing mechanism has a cylindrical shape, and a main body portion into which the rotor is inserted, and a plurality of holes formed on the inner peripheral surface of the main body portion so as to face the outer peripheral surface of the rotor.
- the hole has a hole depth h in a range of a hole diameter d or less.
- the sealing mechanism is configured such that the hole portion has a hole depth h with respect to the hole diameter d. 0.5d ⁇ h ⁇ d You may make it be.
- the hole may have a circular cross section or a hexagonal cross section.
- the sealing mechanism is the sealing mechanism according to any one of the first to third aspects, wherein the plurality of hole portions have the same hole diameter d and hole depth h. It may be unified.
- the bottom surface of the hole portion may have a conical shape or a flat bottom shape.
- the seal mechanism protrudes toward the rotor side on the inner peripheral surface of the main body and extends in the circumferential direction. You may make it have a fin part.
- the rotating machine includes a rotor extending along the axis, and a stator that is disposed on the outer peripheral side of the rotor and relatively rotates around the axis with respect to the rotor.
- the rotating machine is fixed to the stator and divides a space between the rotor and the stator into a high pressure side and a low pressure side, and a plurality of holes facing the outer peripheral surface of the rotor are spaced in the circumferential direction.
- a hole pattern seal having a row of holes formed by opening a hole.
- the hole portion of the rotating machine has a hole depth in a range equal to or smaller than the hole diameter.
- the rotary machine may include a fin portion that is formed on the inner peripheral surface of the hole pattern seal, protrudes toward the rotor side, and extends in the circumferential direction.
- the rotating machine may further include a convex portion that protrudes from the outer peripheral surface of the rotor toward the hole portion and extends in the circumferential direction and faces the hole portion on the low-pressure side of the fin portion.
- the swirl generated between the rotating side and the stationary side is further reduced, and the self-excited vibration caused by the swirl is prevented, and the process gas G from the high pressure side to the low pressure side is reduced. It becomes possible to reduce the amount of leakage.
- FIG. 1 is a cross-sectional view showing a schematic configuration of a centrifugal compressor 1 according to the first embodiment of the present invention.
- the centrifugal compressor 1 in this embodiment is a multistage centrifugal compressor.
- the centrifugal compressor 1 includes, for example, two sets of three-stage impeller groups.
- the centrifugal compressor 1 includes a rotating shaft (rotor) 2, an impeller 3, a casing (stator) 5, and a seal mechanism 20A.
- the rotating shaft 2 rotates around the axis O.
- the impeller 3 is attached to the rotating shaft 2 and compresses the process gas (fluid) G using centrifugal force.
- the casing 5 supports the rotating shaft 2 in a rotatable manner.
- the casing 5 is formed with a return flow path 4 for flowing the process gas G from the high pressure side to the low pressure side.
- the seal mechanism 20 ⁇ / b> A is provided along the outer peripheral surface of the rotating shaft 2.
- the casing 5 is formed in a circular column shape in cross section.
- the rotating shaft 2 is arranged so as to penetrate the center of the casing 5.
- a journal bearing 5a and a thrust bearing 5b are provided at both ends of the casing 5, respectively. Both ends of the rotary shaft 2 are rotatably supported by the journal bearing 5a and the thrust bearing 5b. That is, the rotating shaft 2 is supported by the casing 5 via the journal bearing 5a and the thrust bearing 5b.
- Suction ports 5c and 5e for sucking the process gas G from the radially outer side are provided on the side surfaces near both ends of the casing 5.
- Discharge ports 5d and 5f are provided in the central portion of the casing 5 in the direction of the axis O in order to discharge the process gas G radially outward.
- the casing 5 is formed with an internal space 6a (6) for communicating the suction port 5c and the discharge port 5d, and an internal space 6b (6) for communicating the suction port 5e and the discharge port 5f.
- the plurality of impellers 3 housed in the casing 5 include two sets of three-stage impeller groups 3A and three-stage impeller groups 3B in which the directions of the blades 3b are opposite to each other in the direction of the axis O of the rotary shaft 2. Is configured.
- the three-stage impeller group 3A and the three-stage impeller group 3B are attached to the rotary shaft 2 with their back surfaces directed toward the center in the axis O direction.
- the impeller 3 includes a disk 3a, a blade 3b, and a cover portion 3c.
- the disk 3a is formed in a substantially disk shape having a diameter gradually increased toward the discharge ports 5d and 5f in the direction of the axis O.
- the blades 3b are formed radially on the disk 3a. That is, a plurality of blades 3b are arranged in the circumferential direction.
- the cover portion 3c is formed in a disc shape so as to cover the tip side of the plurality of blades 3b.
- the impeller 3 constituting the three-stage impeller group 3A and the impeller 3 constituting the three-stage impeller group 3B are directed in opposite directions in the axis O direction.
- the three-stage impeller group 3A distributes and compresses the process gas G from the suction port 5c toward the discharge port 5d.
- the three-stage impeller group 3B distributes and compresses the process gas G from the suction port 5e toward the discharge port 5f.
- the internal space 6 includes a return flow path 4.
- the return flow path 4 allows the process gas G to flow from the flow path outlet of the impeller 3 toward the flow path inlet.
- the return flow path 4 has a diffuser part 12, a bend part 13, and a return part 14.
- the diffuser portion 12 guides the process gas G compressed by the impeller 3 and discharged radially outward from the flow path outlet of the impeller 3 to the radially outer side.
- the radially outer portion of the diffuser portion 12 communicates with the return portion 14 via the bend portion 13. However, in the radially outer portion of the diffuser portion 12 connected to the third-stage impeller 3 of each of the three-stage impeller group 3A and the three-stage impeller group 3B, a discharge port 5d, 5f is formed.
- the bend portion 13 forms a curved flow path.
- the first end on the upstream side of the bend portion 13 is connected to the diffuser portion 12.
- a second end on the downstream side of the bend portion 13 is connected to the return portion 14.
- the bend unit 13 reverses the direction of the process gas G flowing radially outward through the diffuser unit 12 so as to be directed radially inward, and sends the gas to the return unit 14.
- the return portion 14 is connected to the second end of the bend portion 13 on the radially outer side.
- the return portion 14 is connected to the flow path inlet of the impeller 3 on the radially inner side.
- the centrifugal compressor 1 of this embodiment has the above configuration. Next, the operation of the centrifugal compressor 1 will be described. First, in the three-stage impeller group 3A, the process gas G sucked from the suction port 5c is caused to flow into the return flow path 4, and the impeller 3, the diffuser part 12, the bend part 13, and the return part 14 are in this order. Compress while flowing from stage 3 to stage 3. Thereafter, the compressed process gas G that has flowed up to the third-stage diffuser section 12 is discharged from the discharge port 5d. The process gas G discharged from the discharge port 5d is sent to the suction port 5e through a pipe line (not shown) connected from the discharge port 5d to the suction port 5e.
- the process gas G sucked from the suction port 5e is caused to flow into the return flow path 4, and the impeller 3, the diffuser part 12, the bend part 13, and the return part 14 are arranged in this order. And further compress while flowing to the third stage. Thereafter, the compressed process gas G reaching the third-stage diffuser section 12 is discharged from the discharge port 5f.
- the process gas G in the vicinity of the outlet 5f of the three-stage impeller group 3B is compressed by the three-stage impeller group 3B in comparison with the process gas G in the vicinity of the outlet 5d of the three-stage impeller group 3A.
- the pressure is high enough. That is, a pressure difference is generated between the process gas G around the rotation axis 2 near the discharge port 5d in the axis O direction and around the rotation axis 2 near the discharge port 5f in the axis O direction. Therefore, between the third stage impellers 3, while allowing the rotation shaft 2 to rotate, the high pressure side and the low pressure side in the direction of the axis O of the rotation shaft 2 are partitioned to prevent leakage of the process gas G.
- a seal mechanism 20A is provided.
- the seal mechanism 20 ⁇ / b> A is disposed on the outer peripheral side of the rotary shaft 2 and is rotatable relative to the rotary shaft 2 around the axis O.
- a hole pattern seal (main body part) 21A constituting a seal mechanism 20A is arranged on the inner periphery of the annular casing 5 arranged with a gap from the rotary shaft 2.
- the hole pattern seal 21A has a cylindrical shape, and the rotating shaft 2 is inserted through the hole pattern seal 21A.
- FIG. 2 is a perspective view showing a hole pattern seal of the sealing mechanism of the centrifugal compressor.
- FIG. 3 is a partial cross-sectional view of the sealing mechanism of the centrifugal compressor.
- FIG. 4 is a development view of the inner peripheral surface of the hole pattern seal.
- a plurality of hole portions 22 opening toward the inner peripheral side are formed on the inner peripheral surface 21a of the hole pattern seal 21A.
- the plurality of hole portions 22 are formed in a circular cross section having the same hole diameter.
- These hole portions 22 are arranged such that their axis lines (not shown) all extend in the radial direction of the rotary shaft 2.
- the bottom surface 22a of each hole 22 has a conical shape (see FIG. 3). In other words, the bottom surface 22a is formed so as to decrease in diameter toward the radially outer side.
- the openings 22b of the holes 22 are arranged in a staggered pattern on the inner peripheral surface 21a.
- the hole pattern seal 21 ⁇ / b> A is equidistant from the first side (left side in FIG. 4), which is the high pressure side in the axis O direction, toward the circumferential direction (up and down direction in FIG. 4).
- a first row L1 in which the openings 22b of the plurality of hole portions 22 are arranged is formed.
- a third row L3 is formed on the second side (the right side in FIG. 4) which is the low pressure side in the direction of the axis O of the first row L1.
- the openings 22b of the plurality of hole portions 22 are arranged at equal intervals in the circumferential direction as in the first row L1.
- a second row L2 in which the openings 22b of the plurality of hole portions 22 are arranged at equal intervals in the circumferential direction is formed.
- the opening 22b constituting the second row L2 is the center of the openings 22b adjacent to each other in the first row L1 (and the third row L3) in the circumferential direction, and the first row L1 and the third in the axis O direction. It arrange
- the symbols of the first row L1 to the third row L3 are drawn from a straight line (a chain line in FIG. 4) passing through the center of each opening 22b.
- a plurality of sets of row groups R are formed side by side in the direction of the axis O, with the first row L1 and the second row L2 described above as a set of row groups R.
- the process gas G including the swirl is contracted by the gap g between the end portion on the highest pressure side of the hole pattern seal 21A and the outer peripheral surface 2a of the rotating shaft 2.
- the process gas G that has entered the gap g advances in the direction of the axis O toward the low pressure side. Then, a part of this process gas G goes to the hole 22 side of the first row L1 of the hole pattern seal 21A.
- a part of the process gas G coming out of the hole 22 interferes with the main flow F0 of the process gas G flowing in the direction of the axis O toward the low pressure side.
- the direction of flow differs between the vortex flow F1 caused by part of the process gas G generated in the hole 22 and the main flow F0 of the process gas G flowing to the low pressure side along the axis O direction. Thereby, the energy of the main flow F0 of the process gas G flowing to the low pressure side along the axis O direction is attenuated.
- the process gas G flows to the low pressure side along the direction of the axis O, and a part of the process gas G enters the holes 22 in the third row L3 and thereafter. Thereby, the process gas G meanders in the radial direction while proceeding in the direction of the axis O of the rotating shaft 2. Thereafter, the above-described operation is repeated by the number of row groups R of the hole pattern seal 21A.
- the hole portion 22 in each row has a hole depth h that is equal to or less than the hole diameter d (h ⁇ d).
- the hole depth h increases with respect to the hole diameter d, the flow velocity of the process gas G that has entered the hole portion 22 decreases, and the energy attenuation effect of the process gas G on the main flow F0 decreases. Further, if the hole depth h of the hole 22 is increased, the processing cost increases. On the other hand, when the hole depth h is too small with respect to the hole diameter d, the hole portion 22 becomes shallow, so that the process gas G is difficult to enter the hole portion 22 and the energy attenuation effect is difficult to obtain.
- the hole 22 has a hole depth h with respect to the hole diameter d. h ⁇ d It is preferable that More preferred is d / 2 ⁇ h ⁇ d It is.
- all the hole portions 22 constituting the hole pattern seal 21A have the same hole diameter d and hole depth h.
- the vortex F1 formed in the hole 22 by the part of the process gas G that has entered the hole 22 of the hole pattern seal 21A is transferred to the hole 22. It is possible to make the axis O direction interfere with the main flow F0 flowing to the low pressure side without entering. Therefore, the swirl contained in the process gas G can be removed by attenuating the energy of the main flow F0 of the process gas G. Furthermore, by setting the hole depth h of the hole 22 to be equal to or smaller than the hole diameter d, the vortex F1 can be easily generated, and the above-described swirl reduction effect and energy attenuation effect can be effectively exhibited. As a result, the amount of leakage of the process gas G from the high pressure side to the low pressure side can be reduced while preventing self-excited vibration due to swirl.
- all the hole portions 22 of the hole pattern seal 21A can be easily and reliably processed without mistakes by unifying the hole diameter d and the hole depth h to the same size. it can. Furthermore, since the attenuation effect by the hole 22 is the same in the circumferential direction and the axial direction, anisotropy is hardly generated in the attenuation effect.
- the bottom surface 22a of the hole 22 has a conical shape. As a result, part of the process gas G that has entered the hole 22 hits the bottom surface 22a to easily change the flow direction, and the vortex F1 is likely to be generated in the hole 22.
- FIG. 5 is a diagram showing an analysis result regarding the relationship between the hole depth h and the equivalent attenuation.
- the equivalent attenuation of Example 2 when the equivalent attenuation of Example 2 is 1.0, the equivalent attenuation of Example 1 is 0.98, and the equivalent attenuation of the comparative example is 0.6. That is, Examples 1 and 2 in which the hole depth h is equal to or smaller than the hole diameter d of the hole 22 are equivalent to the comparative example in which the hole depth h is larger than the hole diameter d of the hole 22.
- the attenuation was 1.5 times or more. Thereby, it was confirmed that a high attenuation was obtained by making the hole depth h equal to or less than the hole diameter d of the hole portion 22.
- centrifugal compressor shown in the second embodiment is different from the centrifugal compressor of the first embodiment only in the configuration in which the hole pattern seal is provided with the fin portion. Therefore, in the description of the second embodiment, the same portions as those in the first embodiment are denoted by the same reference numerals and redundant description is omitted. That is, the description of the overall configuration of the centrifugal compressor common to the configuration described in the first embodiment is omitted.
- FIG. 6 is a perspective view showing a hole pattern seal in the sealing mechanism of the centrifugal compressor according to the second embodiment of the present invention.
- FIG. 7 is a development view of the inner peripheral surface of the hole pattern seal.
- FIG. 8 is a partial cross-sectional view of a sealing mechanism in the centrifugal compressor.
- the hole pattern seal (main body portion) 21B of the seal mechanism 20B of the centrifugal compressor 1 in this embodiment has a hole portion 22 and a fin portion 24 on its inner peripheral surface 21a. I have.
- the hole pattern seal 21B has a plurality of first spaces at the same interval S1 in the circumferential direction (up and down direction in FIG. 7) on the first side (left side in FIG.
- a first row L1 in which the opening portions 22b of the hole portions 22A are arranged is formed. Further, a third row L3 is formed on the second side (the right side in FIG. 7) of the first row L1 which is the low pressure side in the direction of the axis O with an interval S2 sufficiently smaller than the interval S1. Yes.
- the openings 22b of the plurality of third hole portions 22C are arranged at intervals S1 in the circumferential direction in the same manner as the first row L1.
- a second row L2 is formed in which the openings 22b of the plurality of second hole portions 22B are arranged at intervals S1 in the circumferential direction.
- the opening 22b constituting the second row L2 is the center of the interval S1 between the adjacent openings 22b of the first row L1 (and the third row L3) in the circumferential direction and the first row L1 in the axis O direction.
- the third row L3 are arranged at positions that are the center of the interval S2 between the openings 22b adjacent in the axis O direction.
- the symbols of the first row L ⁇ b> 1 to the third row L ⁇ b> 3 are drawn from a straight line (a chain line in FIG. 7) passing through the center of each opening 22 b.
- a plurality of sets of row groups R are formed side by side in the direction of the axis O, with the first row L1 to the third row L3 described above as a set of row groups R.
- the opening 22b in the first row L1 and the opening 22b in the third row L3 of each adjacent row group R are arranged with an interval S2.
- a fin portion 24 is formed that protrudes radially toward the inner peripheral side, that is, the rotating shaft 2 side. Yes.
- the fin portion 24 is continuously formed on the entire circumference in the circumferential direction of the hole pattern seal 21B.
- the fin portion 24 is formed in an annular plate shape having a uniform thickness. In other words, the fin portion 24 extends toward the rotating shaft 2 from the high-pressure side partition K1 (see FIG. 8) surrounding the first hole portion 22A of the first row L1.
- the fin portion 24 is provided on the high-pressure side of each first row L1.
- a second row L2 and a third row L3 are arranged on the low pressure side of the first row L1.
- the front end portion 24a of the fin portion 24 is disposed with an outer peripheral surface 2a of the rotating shaft 2 and a predetermined clearance c.
- the rotating shaft 2 has a convex portion 25 on the outer peripheral surface 2a facing the hole pattern seal 21B described above.
- the convex part 25 protrudes toward the hole pattern seal 21B and is formed continuously on the entire circumference in the circumferential direction.
- the convex portion 25 faces the opening 22b of the first hole portion 22A in the first row L1 on the lower pressure side than the fin portions 24.
- the convex portion 25 has a high-pressure-side vertical wall 25b arranged in the axis O direction on the high-pressure side of the partition K3 on the high-pressure side.
- the outer peripheral surface 25a of the convex portion 25 is disposed between the fin portions 24 adjacent to each other.
- the outer peripheral surface 25a is formed on the partition wall K3 between the first hole portion 22 in the first row L1 and the third hole portion 22C in the third row L3 so as to overlap the fin portion 24 when viewed from the direction of the axis O.
- the fin part 24 is arrange
- the hole portions 22 of each row constituting the hole pattern seal 21B have a hole depth h with respect to the hole diameter d.
- h ⁇ d Is preferable. More preferred is d / 2 ⁇ h ⁇ d It is.
- FIG. 9 is an explanatory view of the action of the sealing mechanism.
- sticker 21B mentioned above is demonstrated, referring FIG.
- FIG. 9 when the rotating shaft 2 described above rotates, a shearing force acts on the process gas G around the rotating shaft 2 from the rotating body including the impeller 3 in the rotational tangential direction.
- a swirl having a velocity component in the circumferential direction is generated by the action of the shearing force.
- the process gas G including the swirl tends to flow from the high pressure side toward the low pressure side due to a pressure difference between both sides in the axis O direction.
- the process gas G including the swirl is contracted by the gap g1 between the tip 24a of the fin portion 24 on the highest pressure side of the hole pattern seal 21B and the outer peripheral surface 2a of the rotating shaft 2.
- the process gas G that has entered the gap g1 advances in the direction of the axis O toward the low pressure side.
- the process gas G collides with the vertical wall 25b on the high pressure side of the convex portion 25, and flows toward the radially outer side of the convex portion 25, that is, the first hole portion 22A side of the first row L1 of the hole pattern seal 21B. It becomes.
- the process gas G proceeds toward the gap g3 disposed on the lower pressure side and radially inward than the outer peripheral surface 25a of the convex portion 25, and meanders in the radial direction.
- the flow is disturbed by this meandering so that a sealing effect similar to that of a general labyrinth seal can be obtained.
- the above-described operation is repeated by the number of the row groups R of the hole pattern seal 21B.
- a vortex F1 of the same level as that of the general hole pattern seal 21B is generated, which contributes to the reduction of swirl.
- the process gas G that has entered from the gap g1 between the fin portion 24 of the hole pattern seal 21B and the rotating shaft 2 is moved vertically to the convex portion 25 of the rotating shaft 2. It can be made to flow toward the hole 22 side of the hole pattern seal 21B in contact with the wall 25b. Therefore, the flow of the process gas G in the swirl direction can be inhibited by the partition walls K2 arranged in the circumferential direction of the rotating shaft 2 among the partition walls of the hole 22, and swirl can be reduced.
- the gaps g1 and g3 formed by the fin portion 24 and the gap g2 formed by the convex portion 25 are arranged at positions shifted in the radial direction, whereby the process gas G meanders in the radial direction. Therefore, the leakage amount of the process gas G can be reduced by a sealing effect by a so-called labyrinth structure. As a result, the amount of leakage of the process gas G from the high pressure side to the low pressure side can be reduced while preventing self-excited vibration due to swirl.
- the hole depth h of the hole 22 is set to be equal to or smaller than the hole diameter d.
- the above-described swirl reduction effect and energy attenuation effect can be effectively exhibited.
- the amount of leakage of the process gas G from the high pressure side to the low pressure side can be reduced while preventing self-excited vibration due to swirl.
- the row group R The swirl and leakage amount of the process gas G can be reduced as the number of.
- the present invention is not limited to the above-described embodiments, and design changes can be made without departing from the spirit of the present invention.
- the fin portions 24 are provided.
- the interval at which the fin portions 24 are provided that is, the number of rows of the hole portions 22 constituting each row group R can be appropriately changed.
- the hole portions 22 are arranged in a staggered pattern in the hole pattern seals 21A and 21B, but the circumferential and axial intervals can be set as appropriate.
- the hole portions 22 constituting the hole pattern seals 21A and 21B are not limited to a staggered shape in which the rows of the hole portions 22 adjacent to each other in the axial direction are phased in the circumferential direction, and the interval and the phase of the adjacent hole portions 22 are arranged. May be arranged in the same square arrangement.
- the fin portion 24 has the tip portion 24a extending in the radial direction, whereas the fin portion 24 is arranged such that the tip portion 24a is arranged on the high pressure side with respect to the base portion 24b. It may be formed in an inclined state. Furthermore, in each of the embodiments described above, the fin portion 24 is formed with a constant thickness, whereas the fin portion 24 is formed in a tapered shape with a width dimension that decreases toward the distal end portion 24a. May be.
- the hole portions 22 constituting the hole pattern seals 21A and 21B of the seal mechanisms 20A and 20B are formed in a circular cross section having substantially the same hole diameter d.
- the hole diameter d may be varied according to the axial position, the circumferential position, and the like of the hole 22.
- the hole portion 22 is not limited to a circular cross section, and may have a hexagonal cross section to form a so-called honeycomb seal.
- the bottom surface 22a of the hole 22 is not limited to a conical shape, and may be a flat bottom shape. In these cases as well, similar effects can be achieved by setting the relationship between the hole diameter d of the hole 22 and the hole depth h in the same manner as in the above embodiment.
- the hole depth of the hole part constituting the seal mechanism equal to or less than the hole diameter, it is possible to reduce the leakage of the process gas G from the high pressure side to the low pressure side while preventing self-excited vibration due to swirl.
Abstract
Description
ダンパーシールは、ハニカムシール、ホールパターンシール等が知られている。例えばホールパターンシールでは、回転軸と間隙を有して配される環状の静止側部材において、回転軸に対向する対向面に複数の穴部が形成され、この穴部で生じる圧力損失により流体の漏れを低減可能である(例えば特許文献1参照)。
ホールパターンシールはラビリンスシールと比較して減衰効果が大きく、回転軸の振動の安定化の点で優位である一方、ラビリンスシールはダンパーシールと比較して流体の漏れ量をより低減できる。
0.5d≦h≦d
であるようにしてもよい。
以下、この発明の第1実施形態における回転機械である遠心圧縮機について図面に基づき説明する。
図1は、この発明の第1実施形態に係る遠心圧縮機1を示す概略構成を示す断面図である。
図1に示すように、この実施形態における遠心圧縮機1は、多段式遠心圧縮機である。この遠心圧縮機1は、例えば2組の3段式インペラ群を備えている。
回転軸2は、軸線O回りに回転する。
インペラ3は、回転軸2に取り付けられ遠心力を利用してプロセスガス(流体)Gを圧縮する。
ケーシング5は、回転軸2を回転可能に支持する。このケーシング5には、プロセスガスGを高圧側から低圧側に流すリターン流路4が形成されている。
シール機構20Aは、回転軸2の外周面に沿って設けられている。
ディスク3aは、軸線O方向で排出口5d,5f側に向かって漸次拡径された略円盤状に形成されている。
ブレード3bは、ディスク3aに放射状に形成されている。つまり、ブレード3bは、周方向に複数並んでいる。
カバー部3cは、複数のブレード3bの先端側を覆うように円盤状に形成されている。
まず、3段式インペラ群3Aにおいて、吸込口5cから吸込まれたプロセスガスGを、リターン流路4に流入させて、インペラ3、ディフューザ部12、ベンド部13、および、リターン部14の順に1段目から3段目まで流しながら圧縮する。その後、3段目のディフューザ部12まで流過した圧縮されたプロセスガスGを排出口5dから排出する。排出口5dから排出されたプロセスガスGは、排出口5dから吸込口5eへとつながる図示しない管路を通って吸込口5eへと送られる。
図2に示すように、ホールパターンシール21Aの内周面21aには、内周側に向かって開口する複数の穴部22が形成されている。これら複数の穴部22は、穴径が等しい断面円形に形成されている。これら穴部22は、その軸線(図示せず)が全て回転軸2の径方向に延びるように配置されている。図3に示すように、各穴部22は、その底面22aが円錐状(図3参照)とされている。言い換えれば、底面22aは、径方向外側に向かって縮径するように形成されている。このホールパターンシール21Aは、その内周面21aに、穴部22の開口部22bが千鳥状に配置されている。
ここで、上述した回転軸2が回転すると、回転軸2の周囲のプロセスガスGには、インペラ3を含む回転体から回転接線方向にせん断力が作用する。このせん断力の作用によって周方向の速度成分を有するスワールが発生する。このスワールを含むプロセスガスGが、軸線O方向両側の圧力差によって高圧側から低圧側に向かって流れようとする。
穴深さhが穴径dに対して大きくなればなるほど、穴部22に入り込んだプロセスガスGの流速が遅くなり、プロセスガスGの主流F0に対するエネルギー減衰効果が小さくなる。また、穴部22の穴深さhを大きくすると、加工コストが増大する。
また、穴深さhが穴径dに対して小さすぎると、穴部22が浅くなるので穴部22にプロセスガスGが入り込みにくく、エネルギー減衰効果が得にくい。また、穴部22にスケールが溜まって穴部22が浅くなりやすく、この点においてもエネルギー減衰効果が減少してしまう。
したがって、穴部22は、穴深さhが、穴径dに対し、
h≦d
とすることが好ましい。さらに好ましいのは、
d/2≦h≦d
である。
さらに、穴部22の穴深さhを穴径d以下とすることで、渦流F1を生じやすくし、上記したスワール低減効果、エネルギー減衰効果を有効に発揮することができる。
その結果、スワールによる自励振動を防止しつつ、高圧側から低圧側へのプロセスガスGの漏れ量を低減することができる。
比較のため、以下の3条件で、穴深さhと等価減衰との関係について解析した。
実施例1)穴部22の穴径dに対し、穴深さhを同一とした(h=d)。
実施例2)穴部22の穴径dに対し、穴深さhを1/2とした(h=0.5d)。
比較例)穴部22の穴径dに対し、穴深さhを2倍とした(h=2d)。
この図5に示すように、実施例2の等価減衰を1.0とした場合、実施例1の等価減衰は0.98、比較例の等価減衰は0.6であった。つまり、穴部22の穴径dに対し、穴深さhが同一以下である実施例1,2は、穴部22の穴径dに対し、穴深さhが大きい比較例に対し、等価減衰が1.5倍以上であった。これにより、穴部22の穴径dに対して穴深さhを同一以下とすることで、高い減衰が得られることが確認できた。
次に、この発明にかかる回転機械である遠心圧縮機の第2実施形態について説明する。この第2実施形態で示す遠心圧縮機は、第1実施形態の遠心圧縮機に対して、ホールパターンシールにフィン部を備える構成が異なるのみである。したがって、第2実施形態の説明においては、第1実施形態と同一部分に同一符号を付して説明するとともに重複説明を省略する。つまり、第1実施形態で説明した構成と共通する遠心圧縮機の全体構成については、その説明を省略する。
図6~図8に示すように、この実施形態における遠心圧縮機1のシール機構20Bのホールパターンシール(本体部)21Bは、その内周面21aに、穴部22とフィン部24と、を備えている。
ホールパターンシール21Bは、軸線O方向において高圧側となる第一の側(図7の紙面左側)に、周方向(図7の紙面上下方向)に向かって同じ間隔S1をあけて複数の第一穴部22Aの開口部22bが並んだ第1列L1が形成されている。また、この第1列L1の軸線O方向の低圧側となる第二の側(図7の紙面右側)には、間隔S1よりも十分に小さい間隔S2をあけて第3列L3が形成されている。第3列L3は、複数の第三穴部22Cの開口部22bが、上記第1列L1と同様に周方向に向かって間隔S1をあけて並んでいる。
h≦d
とするのが好ましい。さらに好ましいのは、
d/2≦h≦d
である。
次に、上述したホールパターンシール21Bによる、作用について図9を参照しながら説明する。
図9に示すように、ここで、上述した回転軸2が回転すると、回転軸2の周囲のプロセスガスGには、インペラ3を含む回転体から回転接線方向にせん断力が作用する。このせん断力の作用によって周方向の速度成分を有するスワールが発生する。このスワールを含むプロセスガスGが、軸線O方向両側の圧力差によって高圧側から低圧側に向かって流れようとする。
その結果、スワールによる自励振動を防止しつつ、高圧側から低圧側へのプロセスガスGの漏れ量を低減することができる。
この発明は、上述した各実施形態に限定されるものではなく、この発明の趣旨を逸脱しない範囲において、設計変更可能である。
例えば、上記第2実施形態では、フィン部24を設けるようにしたが、フィン部24を設ける間隔、つまり各列群Rを構成する穴部22の列の数は、適宜変更することができる。
また、ホールパターンシール21A,21Bを構成する穴部22は、軸方向において互いに隣接する穴部22の列どうしを周方向に位相させる千鳥状に限らず、互いに隣接する穴部22の間隔及び位相を同一とした正方配列として配置しても良い。
さらに、上記各実施形態では、フィン部24は、一定の厚さで形成されていたのに対して、フィン部24を、先端部24aに向かうほど幅寸法が薄く形成された先細り状に形成してもよい。
加えて、穴部22は、断面円形に限らず、断面六角形状として、いわゆるハニカムシールを構成しても良い。
また、穴部22の底面22aは、円錐状に限らず、平底状としてもよい。
これらの場合も、穴部22の穴径dと穴深さhとの関係を上記実施形態と同様に設定することで、同様の作用効果を奏することができる。
2 回転軸(ロータ)
2a 外周面
3 インペラ
3A 3段式インペラ群
3B 3段式インペラ群
3a ディスク
3b ブレード
3c カバー部
4 リターン流路
5 ケーシング(ステータ)
5a ジャーナル軸受
5b スラスト軸受
5c 吸込口
5d 排出口
5e 吸込口
5f 排出口
6 内部空間
6a 内部空間
6b 内部空間
12 ディフューザ部
13 ベンド部
14 リターン部
20A,20B シール機構
21A,21B ホールパターンシール(本体部)
21a 内周面
22 穴部
22A 第一穴部
22B 第二穴部
22C 第三穴部
22a 底面
22b 開口部
24 フィン部
24a 先端部
24b 基部
25 凸部
25a 外周面
25b 縦壁
c クリアランス
d 穴径
F0 主流
F1 渦流
h 穴深さ
G プロセスガス
g1,g2,g3 隙間
K1,K2,K3 隔壁
L1 第1列
L2 第2列
L3 第3列
O 軸線
R 列群
S1,S2 間隔
Claims (8)
- 軸線に沿って延びるロータの外周側に配置され、前記ロータの外周面との間のシールを行うシール機構であって、
筒状をなし、内部に前記ロータが挿通される本体部と、
前記本体部の内周面に、前記ロータの外周面に対向するよう形成された複数の穴部と、を備え、
前記穴部は、穴深さhが穴径d以下の範囲であるシール機構。 - 前記穴部は、前記穴深さhが前記穴径dに対し、
0.5d≦h≦d
である請求項1に記載のシール機構。 - 前記穴部は、断面円形または断面六角形状である請求項1または2に記載のシール機構。
- 複数の前記穴部は、穴径dおよび穴深さhがそれぞれ同一寸法に統一されている請求項1から3の何れか一項に記載のシール機構。
- 前記穴部は、その底面が円錐状または平底状である請求項1から4の何れか一項に記載のシール機構。
- 前記本体部の内周面に、前記ロータ側に向かって突出し、周方向に延びるフィン部を有する請求項1から5の何れか一項に記載のシール機構。
- 軸線に沿って延びるロータと、
前記ロータの外周側に配置され、前記ロータに対して前記軸線回りに相対回転するステータと、
前記ステータに固定されて前記ロータと前記ステータとの間の空間を高圧側と低圧側とに区画するとともに、前記ロータの外周面に対向する複数の穴部が周方向に間隔をあけて形成された穴列を有するホールパターンシールと、を備え、
前記穴部は、穴深さhが穴径d以下の範囲である回転機械。 - 前記ホールパターンシールの内周面に形成され、前記ロータ側に向かって突出し、周方向に延びるフィン部と、
前記ロータの外周面から前記穴部に向かって突出して周方向に延びて、前記フィン部の低圧側で前記穴部に対向する凸部と、
を備える請求項7に記載の回転機械。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP14900847.6A EP3168510A4 (en) | 2014-08-25 | 2014-08-25 | Seal mechanism and rotating machine |
CN201480080754.0A CN106537007A (zh) | 2014-08-25 | 2014-08-25 | 密封机构及旋转机械 |
PCT/JP2014/072203 WO2016030952A1 (ja) | 2014-08-25 | 2014-08-25 | シール機構、回転機械 |
US15/503,536 US20170241427A1 (en) | 2014-08-25 | 2014-08-25 | Seal mechanism and rotating machine |
JP2016545110A JPWO2016030952A1 (ja) | 2014-08-25 | 2014-08-25 | シール機構、回転機械 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2014/072203 WO2016030952A1 (ja) | 2014-08-25 | 2014-08-25 | シール機構、回転機械 |
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WO2016030952A1 true WO2016030952A1 (ja) | 2016-03-03 |
Family
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US (1) | US20170241427A1 (ja) |
EP (1) | EP3168510A4 (ja) |
JP (1) | JPWO2016030952A1 (ja) |
CN (1) | CN106537007A (ja) |
WO (1) | WO2016030952A1 (ja) |
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JP2016180349A (ja) * | 2015-03-24 | 2016-10-13 | 三菱重工業株式会社 | 回転機械 |
CN108397416B (zh) * | 2018-02-24 | 2020-04-28 | 西安交通大学 | 一种非均匀可控腔旋转密封结构 |
CN110332016B (zh) * | 2019-06-24 | 2021-05-28 | 西安交通大学 | 一种能够增强密封性能的孔型密封结构 |
US11492910B2 (en) * | 2019-11-27 | 2022-11-08 | General Electric Company | Damper seals for rotating drums in turbomachines |
US11692557B2 (en) * | 2021-01-04 | 2023-07-04 | Danfoss A/S | Step seal for refrigerant compressors |
CN114033753A (zh) * | 2021-11-11 | 2022-02-11 | 顺达空调设备集团有限公司 | 一种便于拆装固定的地铁风机安装结构 |
JP2023084574A (ja) * | 2021-12-07 | 2023-06-19 | 三菱重工業株式会社 | 回転機械 |
JP2023134235A (ja) * | 2022-03-14 | 2023-09-27 | 三菱重工業株式会社 | シール装置、回転機械、及びシール装置の設計方法 |
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WO2004113769A2 (en) * | 2003-06-20 | 2004-12-29 | Elliott Company | Stepped labyrinth damper seal |
JP4655123B2 (ja) * | 2008-08-07 | 2011-03-23 | 株式会社日立プラントテクノロジー | 遠心圧縮機 |
JP5484990B2 (ja) * | 2010-03-30 | 2014-05-07 | 三菱重工業株式会社 | タービン |
US20120129475A1 (en) * | 2010-11-24 | 2012-05-24 | Visteon Global Technologies, Inc. | Radio system including terrestrial and internet radio |
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- 2014-08-25 EP EP14900847.6A patent/EP3168510A4/en not_active Withdrawn
- 2014-08-25 US US15/503,536 patent/US20170241427A1/en not_active Abandoned
- 2014-08-25 JP JP2016545110A patent/JPWO2016030952A1/ja active Pending
- 2014-08-25 CN CN201480080754.0A patent/CN106537007A/zh active Pending
- 2014-08-25 WO PCT/JP2014/072203 patent/WO2016030952A1/ja active Application Filing
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Publication number | Publication date |
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EP3168510A1 (en) | 2017-05-17 |
JPWO2016030952A1 (ja) | 2017-04-27 |
US20170241427A1 (en) | 2017-08-24 |
CN106537007A (zh) | 2017-03-22 |
EP3168510A4 (en) | 2017-08-09 |
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