US20150337851A1 - Sealing device and rotating machine - Google Patents

Sealing device and rotating machine Download PDF

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Publication number
US20150337851A1
US20150337851A1 US14/647,711 US201214647711A US2015337851A1 US 20150337851 A1 US20150337851 A1 US 20150337851A1 US 201214647711 A US201214647711 A US 201214647711A US 2015337851 A1 US2015337851 A1 US 2015337851A1
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United States
Prior art keywords
seal
sealing device
rotary body
swirl
fluid
Prior art date
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Abandoned
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US14/647,711
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English (en)
Inventor
Kei HASHIZUME
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Compressor Corp
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Mitsubishi Heavy Industries Compressor Corp
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Assigned to MITSUBISHI HEAVY INDUSTRIES COMPRESSOR CORPORATION reassignment MITSUBISHI HEAVY INDUSTRIES COMPRESSOR CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HASHIZUME, KEI
Publication of US20150337851A1 publication Critical patent/US20150337851A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • 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
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • 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
    • 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
    • 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

Definitions

  • the present invention relates to a sealing device and a rotating machine.
  • a sealing device which reduces an amount of leakage of a fluid from a clearance between a stationary side and a rotating side between which a differential pressure is present, is typically provided.
  • non-contact type seal As the sealing device, one that is a non-contact type and has high reliability is frequently used.
  • non-contact type seal As a representative non-contact type sealing device (hereinafter referred to simply as “non-contact type seal”), a labyrinth-shaped sealing device has been known.
  • pressure distribution circumferential asymmetrical pressure distribution
  • swirl flow hereinafter referred to simply as “swirl”
  • annular clearance a technique of providing an annular chamber in an outer circumference of a seal ring in order to relieve circumferential pressure distribution in a seal and providing a cavity part causing the annular chamber and a clearance between a stationary body and a rotary body (hereinafter referred to as “seal clearance”) to communicate with each other at an interval in a circumferential direction is proposed (e.g., see Patent Literature 2).
  • a damper type sealing device As a non-contact type seal other than the labyrinth-shaped sealing device, a damper type sealing device (hereinafter referred to simply as “damper seal”) is sometimes used from the viewpoint of giving a damping force exceeding a destabilizing force occurring in the rotating machine.
  • the damper seal includes a packet-shaped sealing device, a honeycomb-shaped sealing device, a hole-pattern-shaped sealing device, and so on. These damper seals can reduce a swirl in the sealing device and obtain a high damping force by partitioning a seal clearance between a seal rotary body and a seal stationary body in a circumferential direction and in an axis direction.
  • the present invention has been made in consideration of the above circumstances and an object of the present invention is to provide a sealing device capable of reducing an amount of leakage, reducing a force from a fluid flowing through a seal clearance responsible for shaft vibration, and increasing damping that suppresses the shaft vibration, and a rotating machine equipped with the sealing device.
  • the seal stationary body is formed with a plurality of holes in an inner surface facing the outer circumferential surface of the seal rotary body, and grooves in a circumferential direction of the inner surface.
  • the seal rotary body has first protrusions that protrude toward the grooves.
  • the grooves in the sealing device of the first aspect may each have an uneven portion configured to disturb the flow of the fluid on at least one of both wall surfaces in a direction of an axis.
  • the uneven portion in the sealing device of the first or second aspect may be formed by a part of each of the holes which each of the grooves crosses.
  • the grooves are formed to cross the holes, and thereby the uneven portions can be formed.
  • the uneven portions can be easily formed.
  • the sealing device of any one of the first to third aspects may include a swirl flow prevention mechanism configured to blow the fluid that flows into the clearance between the outer circumferential surface of the seal rotary body and the seal stationary body in a direction against a swirl included in the fluid.
  • the fluid flowing into the clearance between the outer circumferential surface of the seal rotary body and the seal stationary body is blown in the direction against the swirl included in the fluid, and thereby the swirl of the fluid flowing into the clearance between the seal stationary body and the seal rotary body can be counteracted.
  • the swirl flow prevention mechanism of the fourth aspect may include fins that extend toward an outer circumference side of the seal rotary body and passages that lead from outer circumferential portions of the fins to the clearance.
  • the swirl adjacent to the seal rotary body can be guided to and decelerated at the outer circumference side by the fins, and the fluid can be guided to the clearance between the seal rotary body and the seal stationary body via the passages and disturb the flow. An amount of the swirl included in the fluid flowing into the clearance can be reduced.
  • the fins of the swirl flow prevention mechanism of the fourth or fifth aspect may be configured to be inclined in a direction in which a swirl flow is scooped up with respect to the radial direction of the seal rotary body.
  • a greater swirl can be guided to and decelerated at the outer circumference side by the fins, and the fluid can be guided to the clearance between the seal rotary body and the seal stationary body via the passages and disturb the flow.
  • the amount of the swirl included in the fluid flowing to the clearance can be reduced.
  • the swirl flow prevention mechanism of the fifth or sixth aspect may include a cover portion covering the outer circumferential portions of the fins.
  • a pressure of the fluid guided by the fins is recovered by the cover portion, and thereby an amount of the fluid flowing into the passages can be increased.
  • the swirl flow prevention mechanism of any one of the fifth to seventh aspects may include a non-contact seal between Openings of the passages at a side of the clearance and the fins in the direction of the axis.
  • the fluid with the swirl is prevented from flowing into the sealing device in a large quantity, and the fluid flowing in the direction against the swirl can be configured to mainly flow downstream from the non-contact seal.
  • the non-contact seal is provided, and thereby when the fluid having a higher pressure than the fluid upstream from the seal is used for the fluid flowing against the swirl, the fluid flowing against the swirl can be prevented from flowing upstream.
  • the non-contact seal of the eighth aspect may have damping holes in the inner surface facing the outer circumferential surface of the seal rotary body.
  • the swirl included in the fluid flowing into the clearance from the high pressure side can be reduced between the fins and the openings of the passages at the side of the clearance by the damping holes.
  • the sealing device of any one of the first to ninth aspects may include a second protrusion, which disturbs the flow of the fluid before the fluid flows into the clearance, at a higher pressure side than the seal stationary body on the outer circumferential surface of the seal rotary body.
  • the swirl flow prevention mechanism is provided at the high pressure side of the seal stationary body, the fluid disturbing the flow at the second protrusion is supplied to the swirl flow prevention mechanism, and can be effectively used as the fluid blown by the swirl flow prevention mechanism.
  • the seal stationary body in the sealing device of any one of the first to tenth aspects may include narrow passages that communicate with the holes and has a narrower flow passage area than the holes, and annular passages with which some of the narrow passages communicate and which are disposed on an outer circumference side of the holes.
  • a rotating machine according to the present invention includes the sealing device of any one of the first to eleventh aspects.
  • the sealing device and the rotating machine relating to the above aspects of the present invention, the flow of the fluid flowing through the seal clearance is greatly disturbed, and the amount of the swirl is reduced. Thereby, it is possible to reduce the amount of leakage, to reduce the force from the fluid flowing through the seal clearance responsible for the shaft vibration, and to increase the damping that suppresses the shaft vibration.
  • FIG. 1 is a front view illustrating a centrifugal compressor that is a rotating machine in an embodiment of the present invention.
  • FIG. 2 is a perspective view illustrating a partial cross section of a seal stationary body in the same embodiment.
  • FIG. 3 is a sectional view of a sealing device in the same embodiment.
  • FIG. 4 is a development view illustrating arrangement of holes in the same embodiment.
  • FIG. 5 is an enlarged sectional view of the vicinity of a groove in the same embodiment.
  • FIG. 6 is a sectional view taken along line A-A of FIG. 5 in the same embodiment.
  • FIG. 7 is a view of a swirl flow prevention mechanism viewed from a high pressure side in a direction of an axis in the same embodiment.
  • FIG. 8 is a view corresponding to FIG. 7 in a first modification of the same embodiment.
  • FIG. 9 is a view corresponding to FIG. 6 in a second modification of the same embodiment.
  • FIG. 10 is an enlarged view of the swirl flow prevention mechanism in a third modification of the same embodiment.
  • FIG. 1 illustrates a centrifugal compressor 1 that is the rotating machine of the present embodiment.
  • the centrifugal compressor 1 is equipped with a rotating shaft 2 rotating about an axis O. Multiple impellers 3 compressing a process gas (fluid) G using a centrifugal force are mounted on the rotating shaft 2 . Also, the centrifugal compressor 1 is equipped with a casing 5 having a flow passage 4 causing the process gas G to flow from a low pressure side to a high pressure side.
  • Each end of the casing 5 in a direction of the axis O is provided with a shaft sealing device 5 a, a journal bearing 5 b, and a thrust bearing 5 c. Both ends of the rotating shaft 2 are rotatably supported on the casing 5 by the journal bearings 5 b.
  • Impellers 3 of the centrifugal compressor 1 in the present embodiment constitute two impeller groups 3 A and 3 B whose blades turn to sides opposite to each other in the direction of the axis O of the rotating shaft 2 .
  • the impeller group 3 A and the impeller group 3 B compress the process gas G from suction ports 5 d and 5 f toward discharge ports 5 e and 5 g, respectively, while causing the process gas G to flow.
  • the centrifugal compressor 1 causes the process gas G suctioned from the suction port 5 d to flow into the flow passage 4 in the impeller group 3 A, and compresses the process gas G while causing the process gas G to flow from a first stage of the impeller group 3 A to a third stage.
  • the process gas G compressed by flowing to the third stage of the impeller group 3 A is discharged from the discharge port 5 e.
  • the process gas G discharged from the discharge port 5 e is sent to the suction port 5 f through a pipeline (not shown) connected from the discharge ports 5 e to the suction port 5 f.
  • the centrifugal compressor 1 causes the process gas G suctioned from the suction port 5 f to flow into the flow passage 4 in the impeller group 3 B, and further compresses the process gas G while causing the process gas G to flow from a first stage of the impeller group 3 B to a final stage.
  • the process gas G compressed by flowing to the final stage of the impeller group 3 B is discharged from the discharge port 5 g.
  • the process gas G adjacent to the discharge port 5 g of the aforementioned impeller group 3 B has a high pressure in proportion to the extent to which it is compressed by the impeller group 3 B. That is, a pressure difference occurs between the process gas G present in the around of the rotating shaft 2 at the side of the discharge port 5 e in the direction of the axis O and the process gas G present in the around of the rotating shaft 2 at the side of the discharge port 5 g in the direction of the axis O.
  • the sealing device 20 by which the high pressure side and the low pressure side are sectioned off in the direction of the axis O of the rotating shaft 2 and which reduces an amount of leakage of the process gas G while allowing of the rotation of the rotating shaft 2 , is provided between the final stages of the impellers 3 of the impeller groups 3 A and 3 B.
  • FIG. 2 is a perspective view illustrating a partial cross section of a seal stationary body 30 constituting the sealing device 20 .
  • FIG. 3 is a meridian sectional view of an upper portion of the sealing device 20 .
  • a seal rotary body 40 that is an approximately annular sleeve is fixed to the rotating shaft 2 so as to cover an outer circumferential surface of the rotating shaft 2 .
  • the seal stationary body 30 having an approximately annular shape is mounted on an inner circumferential surface 5 h of the casing 5 which faces the outer circumferential surface 2 a of the rotating shaft 2 with a clearance from an outer circumferential surface 40 a of the seal rotary body 40 in a radial direction.
  • the seal stationary body 30 is fixed, for instance, in such a manner that an engagement protrusion 30 c thereof is engaged with an engagement recess 5 i formed in an inner circumferential surface of, for instance, the casing 5 or a partition plate (not shown).
  • the seal stationary body 30 is a so-called damping seal ring having a hole pattern, and an inner circumferential surface 30 a thereof is formed with a plurality of holes 31 that are open toward a radial inner side in a circular shape. Openings 31 a of these holes 31 are disposed at predetermined intervals from each other in a zigzag pattern.
  • FIG. 4 the basic arrangement of the holes 31 in the inner circumferential surface 30 a of the seal stationary body 30 is shown in FIG. 4 .
  • a leftward/rightward direction is equivalent to the direction of the axis O of the seal stationary body 30
  • an upward/downward direction is equivalent to the circumferential direction of the seal stationary body 30 .
  • positions at which grooves 32 to be described below are formed are shown by a line composed of alternating long and short dashes.
  • the inner circumferential surface 30 a of the seal stationary body 30 is formed with annular grooves 32 having a predetermined width in the direction of the axis O.
  • These grooves 32 are recessed from the inner circumferential surface 30 a toward a radial outer side, and are each formed to cross the holes 31 formed in the seal stationary body 30 in the circumferential direction.
  • portions recessed toward both outer sides in the direction of the axis O in a circular arc shape in a cross section are intermittently formed in two sidewalls 32 a of each groove 32 which face each other in the direction of the axis O, and thereby uneven portions 32 b are formed on the sidewalls 32 a.
  • a leftward/rightward direction is equivalent to the direction of the axis O of the seal stationary body 30
  • an upward/downward direction is equivalent to the circumferential direction of the seal stationary body 30 .
  • the width of each groove 32 is a width greater than an allowable movement amount of the rotating shaft 2 in the direction of the axis O such that each of first protrusions 34 of the seal rotary body to be described below and the sidewalls 32 a of each groove 32 do not come into contact with each other, and may be a width dimension that the uneven portions 32 b are formed on the sidewalls 32 a. Also, the uneven portions 32 b have been described as being formed on the sidewalls 32 a. However, when the holes 31 are disposed within the width of each groove 32 , the openings 31 a of the holes 31 are also formed in the bottom of each groove 32 .
  • Each of the first protrusions 34 is formed on the outer circumferential surface 40 a of the seal rotary body 40 which faces the inner circumferential surface 30 a of the seal stationary body 30 throughout the circumference of the radial outer side so as to protrude toward each groove 32 of the seal stationary body 30 .
  • a width dimension of the first protrusion 34 need only be necessary and sufficient in view of strength, and a height of the first protrusion 34 may also be a height (e.g., similar to or somewhat higher than the seal clearance S) required to disturb the flow of the fluid leaking from the seal clearance.
  • narrow passages 35 are connected to each predetermined number of holes 31 in the seal stationary body 30 among the holes 31 arranged in the direction of the axis O.
  • the narrow passages 35 extend from the bottoms 31 b of the holes 31 to the radial outer side, and are formed to have circumferential cross sections (in other words, flow passage areas) smaller than those of the holes 31 .
  • the circumferential cross sections of the narrow passages 35 have an adequate size in consideration of the conditions of use.
  • annular passages 36 are formed at the radial outer side (outer circumference side) of the narrow passages 35 throughout the circumference of the seal stationary body 30 .
  • the plurality of narrow passages 35 aligned in the circumferential direction are connected to the annular passages 36 from the radial inner side. In this way, the narrow passages 35 and the annular passages 36 are connected, and thereby internal flow passages of the holes 31 and the annular passages 36 communicate with each other via the narrow passages 35 .
  • the narrow passages 35 and the annular passages 36 may, for instance, be formed by forming the annular passages 36 , the narrow passages 35 , and the holes 31 with separate parts and coupling the parts to each other.
  • the seal stationary body 30 is provided with a swirl flow prevention mechanism 37 at the high pressure side thereof.
  • the swirl flow prevention mechanism 37 blows the process gas G in a direction against a swirl (swirl flow).
  • the direction against the swirl is any direction between the radial direction and the circumferential direction that becomes a direction opposite to the direction of rotation.
  • the swirl flow prevention mechanism 37 is equipped with a plurality of fins 38 in approximately rectangular plate shapes. These fins 38 are obliquely provided such that short sides 38 a thereof are directed in the direction of the axis O and long sides 38 b scoop up the swirl in a swirling direction of the process gas G rather than the radial direction. Further, the swirl flow prevention mechanism 37 is equipped with openings 39 a at a radial outer portion (outer circumferential portion) of the low pressure side relative to the fins 38 . Radial outer ends of blowoff passages 39 b that extend toward the radial inner side after being directed in the direction of the axis O are connected to these openings 39 a.
  • blowoff passages 39 b face the seal clearance S between the inner circumferential surface 30 a of the seal stationary body 30 and the outer circumferential surface 40 a of the seal rotary body 40 and are connected to openings 39 c directed in the direction against the swirl.
  • a second protrusion 42 is formed on the outer circumferential surface 40 a of the seal rotary body 40 mounted on the rotating shaft 2 at a position that becomes a higher pressure side than the seal stationary body 30 in the direction of the axis O in order to disturb the flow of the process gas G.
  • the second protrusion 42 is disposed adjacent to the fins 38 .
  • the second protrusion 42 is continuously formed in the circumferential direction, and has a height that is at least equal to a distance between the short side 38 a of the inner circumferential side of each fin 38 and the outer circumferential surface 40 a of the seal rotary body 40 .
  • a portion of the process gas G that disturbs the flow by providing the second protrusion 42 can be caused to flow along the aforementioned fins 38 toward the radial outer side.
  • the swirl included in the process gas G generated by the rotary body such as the rotating shaft 2 or the impeller 3 is enlarged in the vicinity of the rotary body.
  • the swirl is reduced in the vicinity of the stationary body due to a frictional loss of a wall surface of the stationary body. That is, it is possible to guide most of the swirl adjacent to the rotating shaft 2 to the vicinity of the stationary body disposed at the radial outer side of the rotating shaft 2 by the fins 38 , and the swirl can be decelerated. Thereby, an amount of the swirl of the process gas G flowing into the seal clearance S can also be reduced.
  • Labyrinth fins 39 d protrude from the inner circumferential surface 30 a of the seal stationary body 30 toward the radial inner side between the fins 38 and the openings 390 in the direction of the axis O.
  • the labyrinth fins 39 d are continuously formed in the circumferential direction of the inner circumferential surface 30 a of the seal stationary body 30 . Due to the labyrinth fins 39 d, the seal clearance S between the inner circumferential surface 30 a of the seal stationary body 30 and the outer circumferential surface 40 a of the seal rotary body 40 is partly narrowed.
  • a pressure of the low pressure side becomes a pressure at which an amount of leakage of the damping seal (the seal stationary body 30 and the seal rotary body 40 ) downstream from the blowoff passages 39 b and the labyrinth fins 39 d balances an amount of leakage of the labyrinth fins 39 d and an amount of blowoff from the blowoff passages 39 b.
  • the process gas G is set to be blown off from the blowoff passages 39 b to the low pressure side of the labyrinth fins 39 d using a pressure difference between a static pressure of the process gas G of an outer diameter portion of the aforementioned fins 38 and a pressure of the low pressure side of the aforementioned fins 38 .
  • an annular cover part 50 may be mounted to cover the radial outer portion of the fins 38 from the high pressure side.
  • the sealing device 20 of the aforementioned embodiment when the process gas G flows along the seal clearance S between the seal stationary body 30 and the seal rotary body 40 from the high pressure side toward the low pressure side, the flow in the direction of the axis O and the circumferential direction is greatly disturbed together by the first protrusions 34 , the grooves 32 , and the holes 31 . For this reason, the flow causes great resistance to the flow of the process gas G, and suppresses the swirl of the process gas G flowing along the seal clearance S, and it is possible to reduce the amount of leakage and increase the damping.
  • the grooves 32 are formed to cross the holes 31 , and thereby the uneven portions 32 b can be formed on the sidewalls 32 a of each groove 32 .
  • the uneven portions 32 b can be easily formed.
  • the process gas G is blown against the process gas G flowing into the seal clearance S in the direction against the swirl by the swirl flow prevention mechanism 37 , and thereby the amount of the swirl can be reduced.
  • flowing of the swirl of the process gas G flowing into the seal clearance S between the seal stationary body 30 and the seal rotary body 40 can be counteracted.
  • the swirl of the vicinity of the seal rotary body 40 can be guided to the outer circumference side and decelerated by the fins 38 of the swirl flow prevention mechanism 37 , the process gas G is guided to the seal clearance S via the blowoff passages 39 b and disturbs the flow, and the amount of the swirl included in the process gas G flowing to the seal clearance S can be reduced.
  • the fins 38 are inclined in the direction in which they scoop up the swirl with respect to the radial direction. Thereby, a greater swirl can be guided to the outer circumference side and decelerated by the fins 38 .
  • the labyrinth fins 39 d are provided in the direction of the axis O between the openings 39 c of the blowoff passages 39 b which are at the side of the seal clearance S and the fins 38 . Thereby, the process gas G with the swirl can be prevented from flowing into the seal clearance S in a large quantity, and the process gas G flowing in the direction against the swirl can be made to mainly flow downstream from the labyrinth fins 39 d.
  • the labyrinth fins 39 d are provided. Thereby, when a process gas G having a higher pressure than a fluid pressure upstream from the seal is used for the process gas G flowing against the swirl, the process gas G flowing against the swirl can be prevented from flowing upstream.
  • the swirl flow prevention mechanism 37 is provided at the high pressure side of the seal stationary body 30 , the process gas G whose flow is disturbed by the second protrusion 42 is supplied to the swirl flow prevention mechanism 37 , and can be effectively used as the process gas G blown by the swirl flow prevention mechanism 37 .
  • centrifugal compressor 1 of this embodiment it is possible to suppress the swirl of the process gas G, reduce the amount of leakage, and increase the damping, and thus it is possible to improve running performance.
  • the present invention is not limited to the aforementioned embodiment, and includes various ways of modifying the aforementioned embodiment without departing from the spirit and scope of the present invention. That is, the specific shape and constitution represented in the embodiment are merely examples and can be appropriately modified.
  • sealing device 20 may be divided and installed in the direction of the axis O.
  • the sealing device 20 may be installed at multiple places in the centrifugal compressor 1 that is the rotating machine.
  • the seal rotary body 40 on which the first protrusions 34 are formed and which has a circular pipe is mounted on the rotating shaft 2 has been described.
  • the first protrusions 34 may be formed on the outer circumferential surface 2 a of the rotating shaft 2 , and the rotating shaft 2 may be used as the seal rotary body.
  • the arrangement of the holes 31 is not limited to the zigzag shape, and may be, for instance, a square arrangement.
  • the seal stationary body 30 having the hole pattern shape has been described by way of example.
  • the seal stationary body 30 may be a seal stationary body that has holes demarcated in the circumferential direction and in the direction of the axis O and can apply a damping force, and may be a seal stationary body having a pocket shape or a honeycomb shape. Even when the seal stationary body having the pocket shape or the honeycomb shape is used, similar to the seal stationary body 30 having the hole pattern shape, the grooves 32 are formed in the circumferential direction of the seal stationary body and are formed to cross the holes 31 . Thereby, the uneven portions 32 b can be formed on the sidewalls 32 a.
  • the uneven portions 32 b are formed on both of the sidewalls 32 a in the direction of the axis O of each groove 32 has been described.
  • the uneven portions 32 b may be formed on any one of the sidewalls 32 a.
  • the uneven portions 32 b formed on the sidewalls 32 a of each groove 32 may be omitted. Even in this case, the flow of the process gas G is disturbed by the grooves 32 , the first protrusions 34 , and the holes 31 , and the swirl included in the process gas G can be reduced.
  • the swirl flow prevention mechanism 37 is provided at the high pressure side relative to the seal stationary body 30 .
  • the swirl flow prevention mechanism 37 may be provided at an intermediate portion of the seal stationary body 30 .
  • the swirl flow prevention mechanism 37 may be provided or omitted according to necessity.
  • the narrow passages 35 and the annular passages 36 are formed has been described.
  • the narrow passages 35 and the annular passages 36 may be omitted when the swirl caused by the rotation of, for instance, the rotating shaft 2 is reduced.
  • the uneven portions 32 b may be adapted to be formed on the sidewalls 32 a of each groove 32 by methods other than cutting. For example, a process of recessing the sidewalls 32 a of each groove 32 in the direction of the axis O may be performed, or a process of protruding inward from the sidewalls 32 a of each groove 32 in the direction of the axis O may be performed.
  • the holes 31 are also formed in the bottoms of the grooves 32 facing the first protrusions 34 , but the holes 31 are not necessarily provided.
  • the number of holes 31 formed in the bottoms of the grooves 32 need only be set to a proper number corresponding to desired seal performance, and may, for example, be smaller than the number of holes 31 of the seal stationary body 30 other than the grooves 32 in the circumferential direction.
  • the second protrusion 42 may be omitted according to a state of the swirl at the high pressure side of the sealing device 20 .
  • the swirl flow prevention mechanism 37 may have a plurality of damping holes 45 formed in an inner surface facing the outer circumferential surface of the seal rotary body between the openings 39 c of the blowoff passages (paths) 39 b which are at the side of the seal clearance S and the fins 38 in the direction of the axis O.
  • the damping holes 45 have the same constitution as the aforementioned holes 31 .
  • the swirl included in the process gas G flowing from the high pressure side into the seal clearance S between the fins 38 and the openings 39 c of the blowoff passages 39 b which are at the side of the seal clearance S can be reduced by the damping holes 45 .
  • the number of rows of the damping holes 45 in the direction of the axis O is not limited to that of FIG. 10 , and the damping holes 45 may be formed in at least one row.
  • another non-contact seal for instance, a pocket-shaped or honeycomb-shaped non-contact seal
  • the present invention may be applied as a sealing device that reduces a flow of a fluid on an outer circumferential surface of a rotary body in a direction of an axis or a sealing device that adds damping in order to improve a vibration-resistant force of a rotor.
  • the present invention may be applied to a rotating machine equipped with the sealing device.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressor (AREA)
US14/647,711 2012-12-06 2012-12-06 Sealing device and rotating machine Abandoned US20150337851A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/081618 WO2014087512A1 (ja) 2012-12-06 2012-12-06 シール装置、および、回転機械

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US20150337851A1 true US20150337851A1 (en) 2015-11-26

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US14/647,711 Abandoned US20150337851A1 (en) 2012-12-06 2012-12-06 Sealing device and rotating machine

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US (1) US20150337851A1 (ja)
EP (1) EP2913567B1 (ja)
JP (1) JP5922796B2 (ja)
CN (1) CN104813082B (ja)
WO (1) WO2014087512A1 (ja)

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US20170175754A1 (en) * 2015-12-21 2017-06-22 General Electric Company Apparatus for pressurizing a fluid within a turbomachine and method of operating the same
US20170260991A1 (en) * 2016-03-10 2017-09-14 Hitachi, Ltd. Turbomachine
US10066750B2 (en) * 2012-11-13 2018-09-04 Mitsubishi Heavy Industries Compressor Corporation Rotary machine
CN113775763A (zh) * 2021-08-25 2021-12-10 浙江工业大学 一种孔深可变分瓣式气囊支承孔型阻尼密封
CN113775762A (zh) * 2021-08-25 2021-12-10 浙江工业大学 一种带燕尾导流槽的孔型阻尼密封结构

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JP2016089856A (ja) * 2014-10-29 2016-05-23 三菱重工業株式会社 シール装置及び回転機械
EP3034784A1 (de) * 2014-12-19 2016-06-22 Siemens Aktiengesellschaft Kühlmöglichkeit für strömungsmaschinen
DE102015104994A1 (de) * 2015-03-31 2016-10-06 Areva Gmbh Dichtungsanordnung für eine drehbeweglich gelagerte Komponente einer Rotationsmaschine
JP2018053952A (ja) * 2016-09-27 2018-04-05 三菱重工コンプレッサ株式会社 シール機構、回転機械
JP2019161798A (ja) * 2018-03-09 2019-09-19 本田技研工業株式会社 回転電機の冷却構造体
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

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US10066750B2 (en) * 2012-11-13 2018-09-04 Mitsubishi Heavy Industries Compressor Corporation Rotary machine
US20170175754A1 (en) * 2015-12-21 2017-06-22 General Electric Company Apparatus for pressurizing a fluid within a turbomachine and method of operating the same
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CN113775763A (zh) * 2021-08-25 2021-12-10 浙江工业大学 一种孔深可变分瓣式气囊支承孔型阻尼密封
CN113775762A (zh) * 2021-08-25 2021-12-10 浙江工业大学 一种带燕尾导流槽的孔型阻尼密封结构

Also Published As

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EP2913567A4 (en) 2015-10-21
WO2014087512A1 (ja) 2014-06-12
JPWO2014087512A1 (ja) 2017-01-05
EP2913567B1 (en) 2016-10-19
CN104813082A (zh) 2015-07-29
JP5922796B2 (ja) 2016-05-24
EP2913567A1 (en) 2015-09-02
CN104813082B (zh) 2016-12-07

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