US20070280823A1 - Seal device for a fluid machine - Google Patents

Seal device for a fluid machine Download PDF

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Publication number
US20070280823A1
US20070280823A1 US11/812,023 US81202307A US2007280823A1 US 20070280823 A1 US20070280823 A1 US 20070280823A1 US 81202307 A US81202307 A US 81202307A US 2007280823 A1 US2007280823 A1 US 2007280823A1
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Prior art keywords
ring
pressure area
gap
bore
main
Prior art date
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Abandoned
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US11/812,023
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English (en)
Inventor
Yuji Kanemori
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.)
Torishima Pump Manufacturing Co Ltd
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Torishima Pump Manufacturing Co Ltd
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Assigned to TORISHIMA PUMP MFG. CO., LTD. reassignment TORISHIMA PUMP MFG. CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KANEMORI, YUJI
Publication of US20070280823A1 publication Critical patent/US20070280823A1/en
Abandoned legal-status Critical Current

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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
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • 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
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel

Definitions

  • the present invention relates to a seal device for a fluid machine (turbo machine) such as a pump, turbine, compressor, and gas turbine.
  • a fluid machine such as a pump, turbine, compressor, and gas turbine.
  • the present invention relates to a seal device for preventing leakage of a fluid from a high pressure area to a low pressure area in a casing of the fluid machine through a gap between the casing and a rotor disposed in the casing.
  • seal device installed between a casing and a rotor such as a main shaft or an impeller of a fluid machine is disclosed in Japanese Utility Model Application Laid-open Publication No. 6-018694.
  • the seal device uses a wear-ring. Specifically, a gap is formed between an inner peripheral surface of the wear-ring fixed to the casing and an outer peripheral surface of the rotor, and a size of the gap is set to as small as possible, thereby preventing the fluid leakage from a high pressure side to a low pressure side via the gap.
  • the gap size needs to be set to a certain level with consideration for assembling, thereby placing limitation on possible leak reduction.
  • the seal device disclosed in the above-mentioned Japanese Utility Model Application Laid-open Publication No. 6-018694 has a lining made from an organic material and attached to the wear-ring for preventing seizure.
  • the lining wears off due to contact of the rotor and wear-ring, long term operation of the fluid machine can cause exposure of the metal material covered by the lining which results in seizure.
  • a fluid flow from the high pressure side to the low pressure side through the gap between the wear-ring and rotor has a high flow rate corresponding to the difference in pressure between the high pressure side and low pressure side.
  • the fluid flowing with the high flow rate passing through the gap causes wear of the wear-ring
  • rapid pressure drop due to remarkably increased flow rate can cause cavitation by which vibrations and wearing are occurred.
  • the present invention provides a seal device for a fluid machine for preventing leakage of a fluid from a high pressure to a low pressure area in a casing of the fluid machine through a gap between the casing and a rotor disposed in the casing, comprising, a main ring having a single-piece structure, fixed to a portion of the casing corresponding to a boundary between the high pressure area and the low pressure area, being formed therein with a main through bore which extends between the high pressure area and the low pressure area and into which the rotor is inserted so as to define a first gap between an inner peripheral wall of the main through bore and an outer peripheral surface of the rotor, and a thin auxiliary ring having an outer circumferential portion accommodated in an annular accommodation groove formed at a portion of the inner peripheral wall of the main through bore at a high pressure area side, being formed therein with an auxiliary through bore of a smaller outer diameter than that of the main through bore which extends between the high pressure area and the low pressure area and into which the
  • the diameter of the auxiliary through bore formed in the thin auxiliary ring can be set much less than the diameter of the main through bore formed in the main ring so as to set the second gap much narrower than the first gap.
  • the amount of fluid leaking from the high pressure area to the low pressure area through the first and second gaps can be minimized.
  • Such reduction in the amount of fluid leakage can decrease leakage losses, thereby increasing an efficiency of the fluid machine.
  • the thin auxiliary ring is provided as the separate element from the main ring, and the gap (second gap) between the inner peripheral wall of the auxiliary through bore formed in the thin auxiliary ring and the outer peripheral surface of the rotor is set less than the gap (first gap) between the inner peripheral wall of the main through bore formed in the main ring and the outer peripheral surface of the rotor.
  • the first gap at the main ring side is located on the low pressure area side with respect to the second gap at the thin auxiliary ring side, and the first gap is wider than the second gap. Therefore, the flow rate of fluid flowing through the first gap from the high pressure area side to the low pressure area side can be reduced and, thereby preventing wear of the main ring (wear of the inner peripheral wall of the main through bore). Further, because the flow rate of the fluid flowing in the vicinity of the exit of the first gap on the side of the low pressure area is reduced, the rapid pressure drop in this portion does not occur, thereby preventing the cavitation.
  • Both the main ring and the thin auxiliary ring have single-piece structures constituted by a single component rather than structures obtained by assembling a plurality of components, and the thin auxiliary ring can be easily assembled to the main ring by merely bending the thin auxiliary ring to be fitted in the annular accommodation groove of the main ring. Therefore, the seal device according to the present invention can be easily manufactured. Further, if necessary, the thin auxiliary ring can be removed from the main ring by bending the thin auxiliary ring and to be pulled out from the annular accommodation groove of the main ring, and then a new thin auxiliary ring for replacement can be assembled to the main ring by bending the new thin auxiliary ring to be fitted into the annular accommodation groove of the main ring. Accordingly, the seal device according to the present invention can be easily maintained.
  • FIG. 1 is a cross sectional illustrating a centrifugal pump comprising a seal device of an embodiment of the present invention
  • FIG. 2 is a partially enlarged view of a portion II in FIG. 1 ;
  • FIG. 3 is an exploded perspective view illustrating a wear-ring and a floating ring
  • FIG. 4A is a partially enlarged view illustrating an example of roulette processing of the wear-ring
  • FIG. 4B is a partially enlarged view illustrating another example of roulette processing of the wear-ring
  • FIG. 5 is a partially enlarged view of the wear-ring viewed from an arrow V in FIG. 3 ;
  • FIG. 6 is a partially enlarged view of a seal device at a mouth ring portion (in a state where the floating ring is pressed against the wear-ring);
  • FIG. 7 is a partially enlarged view of the seal device at the mouth ring portion (in a state where the outer circumference of floating ring abuts against the wear-ring);
  • FIG. 8 is a partially enlarged cross sectional view illustrating an alternative of the a seal device at the mouth ring portion
  • FIG. 10 is an enlarged view of a portion X in FIG. 9 .
  • FIG. 1 shows a two-stage centrifugal pump 1 comprising seal devices according to embodiments of the present invention.
  • First stage and second stage volute sections 4 A, 4 B are formed inside a casing 2 of the centrifugal pump 1 .
  • a partition portion 2 a of the casing 2 Positioned between the first stage volute section 4 A and the second stage volute section 4 B is a partition portion 2 a of the casing 2 , to which an inter bush 3 is fixed as described later in detail.
  • a first stage impeller 5 A and a second stage impeller 5 B are respectively disposed, with a left-right symmetry, in the volute sections 4 A, 4 B.
  • These impellers 5 A, 5 B are fixed to a main shaft (rotary shaft) 6 extending in the horizontal direction.
  • the main shaft 6 extends through the casing 2 .
  • a pair of bearing brackets 7 A, 7 B are fixed to the casing 2 , and both ends of the main shaft 6 are rotatably supported by bearings 8 A, 8 B accommodated in these bearing brackets 7 A, 7 B. Further, a pair of gland packing 9 A, 9 B for sealing is respectively installed in portions where the main shaft 6 passes through the casing 2 . The right end of the main shaft 6 in this figure is connected to a motor (not shown).
  • the impellers 5 A, 5 B rotate inside the volute sections 4 A, 4 B.
  • Water that flows into the volute section 4 A from an intake port 11 is pressurized by the first stage impeller 5 A, and then flows into the volute section 4 B via a flow channel 12 shown schematically in the figure.
  • the water that has flown into the volute section 4 B is further pressurized by the second stage impeller 5 B, and then discharged from a discharge port 13 .
  • the impellers 5 A, 5 B is provided with a boss portion 15 fixed to the main shaft 6 , and a main plate 16 of a circular disc configuration extending from the boss portion 15 in a radial direction of the main shaft 6 .
  • Proximal end sides of a plurality of vanes 17 are fixed to the main plate 16 .
  • the distal end sides of the vanes 17 are joined by a side plate 18 having a round outer circumference.
  • the side plate 18 has, a the center thereof, a mouth ring portion 19 of a cylindrical shape open at both ends and protrudes in a direction away from the main plate 16 .
  • the opening surrounded by the mouth ring portion 19 constitutes an impeller entrance 21 .
  • an impeller exit 22 a portion defined between the outer circumference of the main plate 16 and side plate 18 constitutes an impeller exit 22 .
  • the main plate 16 and side plate 18 are disposed coaxially with the main shaft 6 . Therefore, an axial line “L” of the main shaft 6 is also a rotation center of the main plate 16 and side plate 18 .
  • the water in the volute sections 4 A, 4 B is sucked in from the impeller entrance 21 to the rotating impellers 5 A, 5 B to be pressurized by the vanes 17 , and then discharged from the impeller exit 22 . Therefore, with respect to each of the volute sections 4 A, 4 B, an area including the impeller entrance 21 is a low pressure area 4 a , and an area including the impeller exit 22 is a high-pressure area 4 b.
  • the seal devices 25 A, 25 B prevent water in the volute sections 4 A, 4 B from leaking from the high pressure area 4 b to the low pressure area 4 a . Specifically, the seal devices 25 A, 25 B prevent water in the high pressure areas 4 b in the volute sections 4 A, 4 B form leaking into the low pressure areas 4 a by passing through a gap between the casing 2 and the outer peripheral surface of the mouth ring portion 19 of the impeller 5
  • the seal device 25 A installed in the first stage volute section 4 A and the seal device 25 B installed in the second-stage volute section 4 B have the same structure and the same functions, and differ only in attachment postures in the left-right direction in the figure. Thus, the seal device 25 B installed in the second stage volute section 4 B will be described below in detail.
  • the seal device 25 B has a wear-ring (main ring) 31 fixed to the outer circumference to the casing by means of screws, and a floating ring (thin auxiliary ring) 32 attached to the wear-ring so that it can move to a certain extent with respect to the wear-ring 31 both in directions perpendicular to the axial line L of the main shaft 6 and along the axial line L.
  • the wear-ring 31 is composed of a material having rigidity, i.e. rigid material, such as stainless steel, cast iron, or bronze casting, and has an integrated or a single-piece structure composed of a single component, rather than a structure obtained by assembling a plurality of parts.
  • the floating ring 32 is composed of a material that excels in sliding performance and resistance to wear, and also has a certain elastic deformation ability (deformable material).
  • synthetic resins e.g., a fluorine resin such as polytetrafluoroethylene (PTFE), a polyamide resin such as polyether ether ketone (PEEK), hard rubbers, soft metals, and leather can be used as the material for the floating ring 32 .
  • PTFE polytetrafluoroethylene
  • PEEK polyether ether ketone
  • the floating ring 32 has an integrated structure composed of a single component, rather than a structure obtained by assembling a plurality of parts.
  • the wear-ring 31 generally has a thin annular shape and is formed therein with a through bore 31 a (main through bore) of a round cross section.
  • the through bore 31 a passes from one end surface on the side of the low-pressure area 4 a (end surface on the left side in the figure) to the other end surface on the side of the high-pressure area 4 b (end surface on the right side in the figure).
  • the mouth ring portion 19 of the impeller 5 B is inserted into the through bore 31 a from the side of the high-pressure area 4 b .
  • annular accommodation groove 31 b is formed at a portion of the inner peripheral wall of the through bore 31 on a side of the high pressure area 4 b , more specifically, in the portion of the inner peripheral wall of the through bore 31 a close to the end surface of the wear-ring 31 on the side of the high-pressure area 4 b , and the floating ring 32 is accommodated in the annular accommodation groove 31 b .
  • a chamfer portion (enlarged portion) 31 c in which a diameter of the through bore 31 a increases gradually from the side of the low pressure area 4 a to the side of the high pressure area 4 b is formed in a portion facing the end surface of the floating ring 32 of the through bore 31 a on the side of the low pressure area 47 a , that is, in the connection portion of the hole circumferential wall of the through bore 31 a and one side wall of a pair of side walls of the annular accommodation groove 31 b that is located on the side of the low-pressure area 4 b .
  • the amount of protrusion of the side wall on the side of the high-pressure area 4 a of the annular accommodation groove 31 b from the bottom wall of the annular accommodation groove 31 b is set to a minimum limit amount necessary to prevent the floating ring 32 from falling out from the annular accommodation groove 31 b.
  • the floating ring 32 has an annular shape and is much thinner than the wear-ring 31 .
  • the thickness of floating ring 32 is 1/32 to 1 ⁇ 4 of the thickness of wear-ring 31 .
  • the thickness of the floating ring 32 is set such that a force where the mouth ring portion 19 rotates the wear-ring 31 together is smaller than a pushing force F a described bellow.
  • Formed in the floating ring 32 is a through bore (auxiliary through bore) 32 a of a round cross section that passes from one end surface on the side of the low pressure area 4 a (end surface on the left side in the figure) to the other end surface on the side of the high pressure area 4 b (end surface on the right side in the figure) is formed in the floating ring 32 .
  • the mouth ring portion 19 of the impeller 5 B passes into the through bore 32 a from the side of the high pressure area 4 b .
  • the floating ring 32 is engaged into the annular accommodation groove 31 b from the end surface of the wear-ring 31 on the side of the high pressure area 4 b by bending the floating ring.
  • a diameter D m1 of the through bore 31 a of the wear-ring 31 is set larger than a diameter (outer diameter) D r of the mouth ring portion 19 of the impeller 5 B. Therefore, an annular gap (first gap) 35 having a width C 2 corresponding to the difference between the diameter D m1 and diameter D r is formed between the inner peripheral wall of the through bore 31 a and the outer peripheral surface of the mouth ring portion 19 . Further, an end portion of the chamfer portion 31 c on the side of the high pressure area 4 b has a diameter D c larger than the diameter D m1 of the through bore 31 a .
  • the opening of the through bore 31 a in the end surface of the wear-ring 31 on the side of the high pressure area 4 b has a diameter D m3 much larger than the diameters D m1 , D c of other portions (including the chamfer portion 31 c ) of the through bore 31 a.
  • a diameter D a1 of the through bore 32 a of the floating ring 32 is set larger than the diameter D r of the mouth ring portion 19 of the impeller 5 B. Therefore, an annular gap (second gap) 36 having a width C 1 corresponding to the difference between the diameter D a1 and the diameter D r is formed between the inner peripheral wall of the through bore 32 a and the outer peripheral surface of the mouth ring portion 19 .
  • the diameter D a1 of the through bore 32 a is set smaller than the diameter D m1 of the through bore 31 a . Therefore, the width C 1 of the gap 36 is less than the width C 2 of the gap 35 .
  • An outer diameter (diameter) D a2 of the floating ring 32 is set smaller than a diameter D m2 of the bottom wall of the annular accommodation groove 31 b formed in the wear-ring 31 . Therefore, an annular gap (third gap) 37 having a width C s (sufficiently larger than the width C 1 of the gap 36 ) is formed between the bottom wall of the annular accommodation groove 31 b and the outer periphery of the floating ring 32 . Therefore, the floating ring 32 can move in the direction perpendicular to the axial line L (radial direction of the floating ring 32 itself) through the distance corresponding to the width C s of the gap 37 at maximum.
  • the width C 2 of the gap 35 is set larger than the sum of the width C 1 of the gap 36 and the width C s of the gap 37 .
  • the widths C 1 , C 2 , C s satisfy the relationship represented by a formula (1) below.
  • a distance t 1 between the pair of opposing side walls of the annular accommodation groove 31 b is set larger than a thickness t 2 of the floating ring 32 . Therefore, the floating ring 32 can move in the direction of axial line L (thickness direction of the floating ring 32 itself) through a distance corresponding to the difference between the distance t 1 and the thickness t 2 .
  • a portion of the inner peripheral wall of the through bore 31 a is subjected to roulette processing 38 to increase surface roughness so as to increase fluid friction resistance acting upon water that passes through the gap 35 .
  • the roulette processing 38 is shown to be performed only on part of the circumference of the inner peripheral wall of the through bore 31 a , but actually the roulette processing 38 is performed on the entire circumference of the inner peripheral wall of the through bore 31 a .
  • the roulette processing 38 may be performed so that linear protrusions 38 b surround tetragonal concave portions 38 a as shown in FIG. 4A , or so that linear convex portions surround triangular concave portions 38 a as shown in FIG. 4B . Further, surface roughness of the hole circumferential wall of the through bore 31 a may be increased by performing processing other than the roulette processing 38 , provided that fluid friction resistance acting upon water that passes through the gap 35 can be sufficiently increased.
  • the floating ring 32 can move to a certain extent in the radial direction as described above, the floating ring moves autonomously to a position determined by hydrostatic balance with respect the rotating mouth ring portion 19 and retains this position.
  • the gap 36 of almost uniform width C 1 over the entire circumference is formed between the inner peripheral wall of through bore 32 a of floating ring 32 and the outer peripheral surface of the mouth ring portion 19 .
  • the floating ring 32 can move also in the thickness direction and is pushed from the high pressure area 4 b to the low pressure area 4 a by a pushing force F a generated by the difference between the pressures acing on the end surfaces of the floating ring on the sides of high pressure area 4 b and low-pressure area 4 a .
  • a pushing force F a generated by the difference between the pressures acing on the end surfaces of the floating ring on the sides of high pressure area 4 b and low-pressure area 4 a .
  • the pushing force F a is represented by a formula (2) below.
  • P H represents a pressure of the high pressure area 4 b and P C represents a pressure at the chamfer portion 31 c.
  • the pushing force F a can be adjusted by changing the pressure P c at the chamfer portion 31 c . Further, the pressure at the chamfer portion 31 c can be adjusted by changing the diameter D c of the right end portion of the chamfer portion 31 c in this figure (ratio of diameter increase from the side of low pressure area 4 a to the side of high pressure area 4 b ). Therefore, the pushing force F a can be easily adjusted by changing the dimensions and shape of the chamfer portion 31 c.
  • Water leakage from the high pressure area 4 b to the low pressure area 4 a is caused due to a difference between the pressure P H of high pressure area 4 b and the pressure P L of low pressure area 4 a .
  • the leaking water first flows from the high pressure area 4 b into the gap 36 between the through bore 32 a of the floating ring 32 and the mouth ring portion 19 , and then flows from the chamfer portion 31 c into the low pressure area 4 a via the gap 35 between the through bore 31 a of the wear-ring 31 and the mouth ring portion 19 .
  • the seal device 25 B is provided with the floating ring 32 as a separate element from the wear-ring 31 , the diameter D a1 of the through bore formed in the floating ring 32 is set smaller than the diameter D m1 of the through bore 31 a formed in the wear-ring 31 , and the gap 36 is set narrower than the gap 35 (widths C 1 , C 2 ).
  • the amount of fluid leaking from the high pressure area 4 b to the low pressure area 4 a via the gap 36 and gap 35 can be remarkably reduced.
  • Such reduction in the amount of leakage makes can decrease the leakage loss, thereby increasing the efficiency of centrifugal pump 1 .
  • the fluid friction resistance acting upon water flowing through the gap 35 is increased by performing roulette processing 38 on the inner peripheral wall of the through bore 31 a , the amount of water leaking from the high pressure area 4 b into the low pressure area 4 a can be further decreased. As a result, the leakage loss is further reduced and the efficiency is further increased.
  • V 2 V 1 ⁇ A 1 /A 2 (3)
  • a 1 represents a cross section area of the gap 36
  • a 2 represents a cross section area of the gap 35 . Because the width C 1 of the gap 36 is less than the width C 2 of the gap 35 as described above and the cross section area A 1 is less than the cross section area A 2 , the flow rate V 2 in the gap 35 is smaller than the flow rate V 1 in the gap 36 .
  • the reduced flow rate V 1 in the gap 35 can prevent the inner peripheral wall of the through bore 31 a of mouth ring 31 from wear.
  • the amount of wear is generally proportional to the fifth power of flow velocity. Therefore, the wear of the wear-ring 31 can be effectively prevented by reducing the flow rate V 1 . Further, because the flow rate of water in the vicinity of outlet of the port 35 on the side of low pressure area is reduced, no rapid drop in pressure occurs in this portion, resulting in that the occurrence of cavitation can be prevented.
  • the width C 1 of the gap 36 of floating ring 32 is set narrower than the width C 2 of the gap 35 of wear-ring 31 , the mouth ring portion 19 comes into contact with the floating ring 32 before coming into contact with the wear-ring 31 .
  • the floating ring 32 can move in the radial direction through the distance corresponding to the width C s of the gap 37 at maximum, the damage or wear of the floating ring 32 caused by this radial direction movement can be reduced.
  • the width C 2 of the gap 35 is set larger than the sum of the width C 1 of the gap 36 and the width C s of the gap 37 , even if the floating ring 32 pushed by the mouth ring portion 19 moves in the radial direction, the outer circumference of the floating ring 32 comes into contact with the bottom wall of the annular accommodation groove 31 b before the mouth ring portion 19 hits the inner peripheral wall of the through bore 31 a of wear-ring 31 as shown in FIG. 7 . Therefore, the occurrence of vibrations caused by impacts of the mouth ring portion 19 and wear-ring 31 and seizure of the mouth ring portion 19 and wear-ring 31 can be reliably prevented.
  • This friction force F v can prevent a phenomenon where mouth ring portion rotates together the floating ring 32 . Because the pushing force F a can be adjusted by changing the dimensions and shape of the chamfer portion 31 c , as described above, the friction force F v also can be easily adjusted by the dimensions and shape of the chamfer portion 31 c .
  • the friction force F v is set so as to be larger than the force where the mouth ring portion 19 rotates the wear-ring 31 together.
  • Both the wear-ring 31 and the floating ring 32 have single-piece structures constituted by a single component, rather than structures obtained by assembling a plurality of components, and the floating ring 32 can be incorporated in the wear-ring 31 by bending the floating ring 32 and fitting in the annular accommodation groove 31 b of the wear-ring 31 . Therefore, the seal device 25 B can be easily manufactured. Furthermore, if necessary, the floating ring 32 can be removed from the wear-ring 31 by merely bending the floating ring and pulling it out from the annular accommodation groove 31 b of the wear-ring 31 , and a new floating ring 32 for replacement can be mounted on the wear-ring 31 by bending the floating ring and fitting into the annular accommodation groove 31 b of the wear-ring 31 . Accordingly, the seal device 25 B can be easily maintained.
  • a seal device 125 similar to the seal devices 25 A, 25 B is provided in a portion where the boss portions 15 of the impellers 5 A, 5 B pass through the partition portion 2 a of the casing 2 .
  • An outer circumference of the inter bush 3 is fixed to the partition portion 2 a as described above.
  • the boss portions 15 of the impellers 5 A, 5 B fixed to the main shaft 6 pass through the inter bush 3 and the partition portion 2 a and extend into the first-stage and second-stage volute sections 4 A, 4 B.
  • the seal device 125 prevents the fluid leakage from an area in the second stage volute section 4 B occupying the impeller exit 22 side of the second stage impeller 5 B and a rear surface side of the main plate 16 of the impeller 5 B to an area in the first stage volute section 4 A occupying the impeller exit side of the first stage impeller 5 A and a rear surface side of the main plate 16 of the impeller 5 A (an arrow “FL” in FIG. 9 ).
  • the former area is a high pressure area 126 a
  • the latter area is a low pressure area 126 b .
  • the high pressure area 126 a and low-pressure area 126 b are partitioned by the boss portion 15 and partition wall portion 2 a .
  • the seal device 125 is provided with an inter bush 3 as an element equivalent to the wear-ring 31 in the seal devices 25 A, 25 B and a floating ring 127 that is attached to the inter bush 3 .
  • the inter bush 3 has generally round annular shape and is formed a through bore (main through bore) 3 a of a round cross section therein.
  • This through bore 3 a extends from one end surface of the inter bush 3 on the side of the low pressure area 126 b (end surface on the right side in FIG. 9 ) to the other end surface of the inter bush 3 on the side of the high pressure area 126 b (end surface on the left side in the figure).
  • the boss portions 15 of the impellers 5 A, 5 B are inserted into the through bore 3 a .
  • An annular gap 134 is formed between the inner peripheral wall of the through bore 3 a and the outer peripheral surface of the boss portion 15 .
  • annular accommodation groove 129 is formed in a portion on the side of the high pressure area 126 a of the inner peripheral wall of the through bore 3 a .
  • the floating ring 127 is accommodated in the annular accommodation groove 129 .
  • a chamfer portion 3 b is formed in a portion of the through bore 129 that faces an end surface of the floating ring 127 on the side of the low pressure area 126 b.
  • a through bore (auxiliary through bore) 127 a having a round cross section is formed in the floating ring 127 .
  • the through bore 127 a passes from the end surface of the floating ring on the side of the low pressure area 126 b to the end surface on the side of the high pressure area 126 a .
  • the boss portion 15 passes through the through bore 127 a .
  • An annular gap 135 is formed between the inner peripheral wall of the through bore 131 and the outer peripheral surface of the boss portion 15 .
  • An annular groove 133 is formed between a bottom wall of the annular accommodation groove 129 and the outer circumference of the floating ring 127 .
  • seal device 125 The structure and functions of the seal device 125 are identical to those of the seal devices 25 A, 25 B. Elements and dimensions in FIG. 9 identical to those in FIG. 2 are assigned with identical reference symbols.
  • the seal device of a fluid mechanism in accordance with the present invention has a relatively simple structure can minimize the amount of leakage, reduce vibrations, prevent seizure, and inhabit wear and cavitation with achieving relatively simple structure and easy manufacturing and maintenance.
  • the present invention is not limited to the embodiments, and various modifications thereof are possible.
  • the present invention can be applied to pumps other than centrifugal pumps, as well as fluid machines other than pumps such as compressors and gas turbines.
  • a plurality of floating rings may be provided.
  • a step 31 d may be provided in the portion where the through bore 31 a is connected to the annular accommodation groove 31 b instead of the chamfer portion 31 c.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Sealing Of Bearings (AREA)
US11/812,023 2005-12-16 2007-06-14 Seal device for a fluid machine Abandoned US20070280823A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005363622A JP4456062B2 (ja) 2005-12-16 2005-12-16 流体機械のシール装置
JP2005-363622 2005-12-16

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Cited By (10)

* Cited by examiner, † Cited by third party
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CN103321950A (zh) * 2013-07-02 2013-09-25 台州豪贝泵业有限公司 一种泵用自适应性调节口环装置
WO2015038616A1 (en) * 2013-09-10 2015-03-19 Schlumberger Canada Limited Wear rings for electric submersible pump stages
DE102014224285A1 (de) * 2014-11-27 2016-06-02 Robert Bosch Gmbh Verdichter mit einem Dichtkanal
DE102014224757A1 (de) * 2014-12-03 2016-06-09 Robert Bosch Gmbh Verdichter mit einem Dichtkanal
US9803650B2 (en) 2014-11-04 2017-10-31 Hanwha Techwin Co., Ltd. Sealing device
US20170321713A1 (en) * 2014-11-27 2017-11-09 Robert Bosch Gmbh Compressor having a sealing channel
US20180087512A1 (en) * 2016-09-27 2018-03-29 W.S. Darley & Co. Double volute end suction pump
US10533570B2 (en) 2015-12-07 2020-01-14 Fluid Handling Llc Opposed impeller wear ring undercut to offset generated axial thrust in multi-stage pump
CN111033054A (zh) * 2017-09-26 2020-04-17 赛莱默欧洲有限公司 具有耐磨环的泵
KR20200123163A (ko) * 2018-02-21 2020-10-28 캔두 에너지 인코포레이티드 원자력 냉각재 펌프 시일 및 밀봉 방법

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KR100895346B1 (ko) 2007-01-10 2009-04-29 다이헤이요 기코 가부시키가이샤 하나의 축에 대칭으로 장착한 임펠러를 내장한 원심 슬러지펌프의 케이싱
JP4685903B2 (ja) * 2008-06-11 2011-05-18 株式会社酉島製作所 流体機械のシール装置
JP2013160297A (ja) * 2012-02-03 2013-08-19 Mitsubishi Heavy Ind Ltd シール構造及びこれを備えた回転機械

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CN103321950A (zh) * 2013-07-02 2013-09-25 台州豪贝泵业有限公司 一种泵用自适应性调节口环装置
WO2015038616A1 (en) * 2013-09-10 2015-03-19 Schlumberger Canada Limited Wear rings for electric submersible pump stages
GB2532169A (en) * 2013-09-10 2016-05-11 Schlumberger Holdings Wear rings for electric submersible pump stages
US10968918B2 (en) 2013-09-10 2021-04-06 Schlumberger Technology Corporation Wear rings for electric submersible pump stages
US9803650B2 (en) 2014-11-04 2017-10-31 Hanwha Techwin Co., Ltd. Sealing device
US10801513B2 (en) 2014-11-27 2020-10-13 Robert Bosch Gmbh Compressor having a sealing channel
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US20170321713A1 (en) * 2014-11-27 2017-11-09 Robert Bosch Gmbh Compressor having a sealing channel
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US10851790B2 (en) * 2016-09-27 2020-12-01 W.S. Darley & Co. Double volute end suction pump
US20180087512A1 (en) * 2016-09-27 2018-03-29 W.S. Darley & Co. Double volute end suction pump
CN111033054A (zh) * 2017-09-26 2020-04-17 赛莱默欧洲有限公司 具有耐磨环的泵
US11236750B2 (en) 2017-09-26 2022-02-01 Xylem Europe Gmbh Pump with a wear ring
CN111033054B (zh) * 2017-09-26 2022-07-26 赛莱默欧洲有限公司 具有耐磨环的泵
KR20200123163A (ko) * 2018-02-21 2020-10-28 캔두 에너지 인코포레이티드 원자력 냉각재 펌프 시일 및 밀봉 방법
US20200392965A1 (en) * 2018-02-21 2020-12-17 Candu Energy Inc. Nuclear coolant pump seal and methods of sealing
US11913465B2 (en) * 2018-02-21 2024-02-27 Candu Energy Inc. Nuclear coolant pump seal and methods of sealing
KR102659848B1 (ko) * 2018-02-21 2024-04-22 캔두 에너지 인코포레이티드 원자력 냉각재 펌프 시일 및 밀봉 방법

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