EP0484582B1 - Pompe centrifuge pour pomper des fluides chauds - Google Patents

Pompe centrifuge pour pomper des fluides chauds Download PDF

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Publication number
EP0484582B1
EP0484582B1 EP90121433A EP90121433A EP0484582B1 EP 0484582 B1 EP0484582 B1 EP 0484582B1 EP 90121433 A EP90121433 A EP 90121433A EP 90121433 A EP90121433 A EP 90121433A EP 0484582 B1 EP0484582 B1 EP 0484582B1
Authority
EP
European Patent Office
Prior art keywords
chamber
sealing
housing
gap
annular clearance
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP90121433A
Other languages
German (de)
English (en)
Other versions
EP0484582A1 (fr
Inventor
Ralph Dipl.-Ing. Mann
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.)
Sihi GmbH and Co KG
Original Assignee
Sihi GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sihi GmbH and Co KG filed Critical Sihi GmbH and Co KG
Publication of EP0484582A1 publication Critical patent/EP0484582A1/fr
Application granted granted Critical
Publication of EP0484582B1 publication Critical patent/EP0484582B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/126—Shaft sealings using sealing-rings especially adapted for liquid pumps
    • F04D29/128—Shaft sealings using sealing-rings especially adapted for liquid pumps with special means for adducting cooling or sealing fluid

Definitions

  • the invention relates to a centrifugal pump for conveying especially hot liquids with at least one shaft passage through the pump housing to the outside and seals the shaft passage by means of a mechanical seal and a flushing and cooling flow branched off from the pumped medium for the mechanical seal, which from a room higher pressure, preferably the Pressure, spiral or spiral side space of the pump is removed and through at least one channel formed in the housing cover, an annular gap formed between the housing cover and an intermediate housing inserted into the housing cover from the impeller side and from this near the sealing surface of the mechanical seal into the ones containing the mechanical seal Seal space is guided and after flowing through the seal space through a throttle gap is supplied to a room of low pressure of the pump.
  • the flushing and cooling flow is taken from the spiral side space, via a setting throttle, the channel in the housing cover and then fed to an annular gap that is narrow and is axially elongated to serve in the heat exchange with the surface of the housing cover of the cooling.
  • the current emerges from the annular gap axially parallel in the seal chamber. Before it is deflected to the sealing gap area at the end of the sealing space, it runs through a distance which lies in the area of the liquid which is caused to rotate by the mechanical seal. This will distract him and therefore affect the intensity of his cooling effect in the sealing gap area.
  • Throttling still occurs when the flushing and cooling flow leaves the sealing chamber through the throttling gap and the shaft bearing; however, the throttling effect provided in the flow path upstream of the sealing space leads to a comparatively low pressure in the sealing space, which favors the formation of gas bubbles.
  • a pump (DE-U-86 01 166) in which the flushing and cooling flow is supplied to the sealing space through a radial bore in the intermediate housing, an annular space being provided between the intermediate housing and the housing cover, which receives the current from the channel in the cover of the hole of the intermediate housing.
  • Such an arrangement has the disadvantage that the flushing and cooling occur unevenly due to one-sided impingement of the flushing and cooling flow on the sealing arrangement, which on the one hand leads to thermal distortion and erosion of the mechanical seal and on the other hand can lead to the accumulation of gas bubbles in the seal space.
  • the invention has for its object to improve the heat dissipation from the mechanical seal.
  • the solution according to the invention consists in that a distribution annular space is arranged between the channel and the annular gap, the width of which is a multiple of the annular gap directed with the radial directional component on the sealing surface area of the mechanical seal, and that the pressure drop in the throttle gap is several times greater than the pressure drop from the higher pressure space to the seal space.
  • the annular gap should be directed as steeply as possible towards the sealing surface area, namely at an angle of less than 60 ° to the axis.
  • the annular gap should be directed at the sealing gap itself or at the area immediately adjacent to it on the side facing away from the throttle gap, since the increased heat transfer coefficient in the region of the deflection of the current results in better cooling of the sealing gap area. It can also be achieved by this feature that the free path of the current in the seal chamber briefly and thus the risk of its impairment by the liquid rotating in the seal chamber is low.
  • the throttle gap which is arranged between a fixed housing part and a part rotating with the shaft, is arranged according to the invention with the smallest possible diameter, because in this way the greatest possible pressure drop can be set.
  • the shaft sleeve can also be understood to mean a hub part of the impeller or the like.
  • the throttle gap is expediently designed to be bearing-free so as not to be determined by the bearing dimensions.
  • a housing insert for accommodating the counter ring of the mechanical seal is expediently arranged in the housing cover and, together with the intermediate housing, forms the annular gap.
  • an impeller 4 rotates on the shaft 5.
  • a spiral side space 7 is arranged, of which a bore 8 in the housing cover 10 has liquid as a flushing and cooling flow for the mechanical seal 14, 15 transported into the distribution annulus 9, which is limited by the housing cover 10, the intermediate housing 11 and Housing insert 12.
  • the channel 8 and the distribution annulus 9 are designed with a large flow cross-section in order to supply the liquid with little pressure loss and evenly distributed over the circumference to the annular gap 13 which is formed between conical surfaces of the intermediate housing 11 and the housing insert 12 which are located opposite one another.
  • the cooling and rinsing liquid is supplied to the mechanical seal evenly distributed over the circumference via this annular gap.
  • the flushing and cooling flow is either directed directly at the sealing gap, which lies radially between the sliding ring 14 and the counter ring 15 of the mechanical seal, or at the area immediately adjacent to the sealing gap, and preferably on the side facing away from the throttle gap.
  • the current should reach the sealing gap as long as it is still being deflected and thereby ensures a high heat transfer coefficient. It is also achieved by the invention that the current reaches the area of the sealing gap before it can be weakened, loosened or rotated by rotating parts of the seal or by the rotating area of the liquid. As a result, the area in which the gas bubbles are preferably located near the mechanical seal is pushed away from the sealing gap area.
  • the flushing and cooling flow flowing out of the sealing gap area transports the gas and air bubbles present in this area.
  • the flushing and cooling flow then sweeps in the axial direction across the mechanical seal through the sealing space 16 and, possibly loaded with gas or air bubbles, is fed back to the pump space through the throttle gap 17.
  • the throttle gap is formed between the wall 18 projecting radially inward from the intermediate housing 11 and the hub of the impeller 4.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (6)

  1. Pompe centrifuge pour refouler en particulier un liquide chaud, avec au moins un passage d'arbre à travers le carter de pompe vers l'extérieur et une étanchéification du passage d'arbre au moyen d'une garniture étanche à anneau glissant (14, 15), ainsi qu'un courant de rinçage et de refroidissement, dérivé du liquide refoulé, de la garniture étanche à anneau glissant, courant qui est extrait d'un compartiment à haute pression, de préférence de la chambre de pression (3), de la chambre en spirale (6) ou de la chambre latérale en spirale (7) de la pompe et qui est amené par au moins un canal (8) formé dans un couvercle de carter (10) à un interstice annulaire (13) formé entre le couvercle de carter (10) et un carter intermédiaire (11) placé du côté rotor dans le couvercle de carter (10), et qui est amené depuis l'interstice à proximité de la surface d'étanchéité de la garniture étanche à anneau glissant (14, 15) dans la chambre d'étanchéité (16) contenant la garniture étanche à anneau glissant et qui est amené par l'intermédiaire d'un interstice d'étranglement (17), après avoir traversé la chambre d'étanchéité (16), à une chambre à basse pression de la pompe, caractérisée en ce qu'une chambre annulaire de distribution (9) est disposée entre le canal (8) et l'interstice annulaire (13), sa largeur étant un multiple de l'interstice annulaire (13) selon une composante directionnelle radiale sur la zone de la surface d'étanchéité de la garniture étanche à anneau glissant (14, 15), et en ce que la chute de pression dans l'interstice d'étranglement (17) est de plusieurs fois supérieure à la chute de pression depuis la chambre à haute pression (3, 6, 7) à la chambre d'étanchéité (16).
  2. Pompe centrifuge selon la revendication 1, caractérisée en ce que l'interstice annulaire (13) est incliné avec un angle inférieur à 60° par rapport à l'axe.
  3. Pompe centrifuge selon la revendication 1 ou 2, caractérisée en ce que l'interstice annulaire (13) est dirigé vers l'interstice d'étanchéité ou vers la zone immédiatement voisine de celui-ci du côté opposé à l'interstice d'étranglement.
  4. Pompe centrifuge selon l'une quelconque des revendications 1 à 3, caractérisée en ce que l'interstice d'étranglement (17) est formé sans appui entre l'arbre ou un manchon d'arbre d'une part et une paroi (18) étirée radialement vers l'intérieur du carter intermédiaire (11).
  5. Pompe centrifuge selon l'une quelconque des revendications 1 à 4, caractérisée en ce qu'un élément rapporté de carter (12) est contenu dans le couvercle de carter (10) pour recevoir le contre-anneau (15) de la garniture étanche à anneau glissant (14, 15) et cet élément rapporté constitue avec le carter intermédiaire (11) l'interstice annulaire.
  6. Pompe centrifuge selon l'une quelconque des revendications 1 à 5, caractérisée en ce que la plus grande partie de la chute de pression entre la chambre à haute pression (3, 6, 7) et la chambre d'étanchéité (16) se produit dans l'interstice annulaire (13).
EP90121433A 1989-05-03 1990-11-08 Pompe centrifuge pour pomper des fluides chauds Expired - Lifetime EP0484582B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE3914652A DE3914652A1 (de) 1989-05-03 1989-05-03 Kreiselpumpe

Publications (2)

Publication Number Publication Date
EP0484582A1 EP0484582A1 (fr) 1992-05-13
EP0484582B1 true EP0484582B1 (fr) 1993-01-27

Family

ID=6380039

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90121433A Expired - Lifetime EP0484582B1 (fr) 1989-05-03 1990-11-08 Pompe centrifuge pour pomper des fluides chauds

Country Status (4)

Country Link
EP (1) EP0484582B1 (fr)
AT (1) ATE85106T1 (fr)
DE (2) DE3914652A1 (fr)
ES (1) ES2038030T3 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3914652A1 (de) * 1989-05-03 1990-11-08 Sihi Gmbh & Co Kg Kreiselpumpe
GB2290113B (en) * 1994-05-31 1998-07-15 Ingersoll Dresser Pump Co Centrifugal pump
GB2390398B (en) * 1999-03-30 2004-02-25 Concentric Pumps Ltd Improvements in pumps
GB9907372D0 (en) * 1999-03-30 1999-05-26 Concentric Pumps Ltd Improvements in pumps
DE102006004266A1 (de) * 2006-01-31 2007-08-02 Wilo Ag Kreiselpumpe
KR101430686B1 (ko) * 2007-04-05 2014-08-14 위어 미네랄즈 오스트레일리아 리미티드 산업용 펌프의 공기 확산 시스템

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1400545A1 (de) * 1961-12-22 1969-11-13 Wernert Geb Schaafhausen Gleitringdichtung fuer umlaufende Wellen bei Kreiselpumpen
GB1120231A (en) * 1964-07-08 1968-07-17 Worthington Simpson Rotary pumps
DE1528677A1 (de) * 1965-06-11 1969-10-16 Itt Ind Gmbh Deutsche Kreiselpumpe
DE3438662C2 (de) * 1984-10-22 1997-01-30 Sihi Gmbh & Co Kg Kreiselpumpe für heiße Medien
US4621975A (en) * 1984-10-25 1986-11-11 Graco Inc. Centrifugal pump seal
DE8601166U1 (de) * 1986-01-18 1986-02-27 Sihi Gmbh & Co Kg, 2210 Itzehoe Pumpe zur Förderung von Heißwasser
DE3843429A1 (de) * 1988-12-23 1990-06-28 Klein Schanzlin & Becker Ag Wellenabdichtung an stroemungsmaschinen
DE3914652A1 (de) * 1989-05-03 1990-11-08 Sihi Gmbh & Co Kg Kreiselpumpe

Also Published As

Publication number Publication date
ATE85106T1 (de) 1993-02-15
DE3914652A1 (de) 1990-11-08
DE59000825D1 (de) 1993-03-11
EP0484582A1 (fr) 1992-05-13
ES2038030T3 (es) 1993-07-01

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