EP1672221B1 - Seitenkanalverdichter - Google Patents

Seitenkanalverdichter Download PDF

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Publication number
EP1672221B1
EP1672221B1 EP05026935A EP05026935A EP1672221B1 EP 1672221 B1 EP1672221 B1 EP 1672221B1 EP 05026935 A EP05026935 A EP 05026935A EP 05026935 A EP05026935 A EP 05026935A EP 1672221 B1 EP1672221 B1 EP 1672221B1
Authority
EP
European Patent Office
Prior art keywords
sealing
ring
spring
sealing ring
spring element
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.)
Active
Application number
EP05026935A
Other languages
English (en)
French (fr)
Other versions
EP1672221A3 (de
EP1672221A2 (de
Inventor
Jürgen KRINES
Evgenij Rjabchenko
Robert Seufert
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.)
Gardner Denver Deutschland GmbH
Original Assignee
Gardner Denver Deutschland GmbH
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 Gardner Denver Deutschland GmbH filed Critical Gardner Denver Deutschland GmbH
Publication of EP1672221A2 publication Critical patent/EP1672221A2/de
Publication of EP1672221A3 publication Critical patent/EP1672221A3/de
Application granted granted Critical
Publication of EP1672221B1 publication Critical patent/EP1672221B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative 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
    • F04D29/08—Sealings
    • F04D29/083—Sealings especially adapted for elastic fluid pumps

Definitions

  • the invention relates to a compressor, in particular a lateral channel compressor, comprising a casing member and an impeller which is disposed therein rotatably about an axial axis of rotation and which is spaced from the casing member by a sealing gap, the sealing gap being sealed by a sealing arrangement which comprises a sealing ring.
  • a lateral channel compressor of the species is described for example in DE 100 41 332 C1 or EP 0 708 248 B1 .
  • the efficiency is substantially determined by a leakage flow which, owing to pressure conditions, originates across the sealing gap between a lateral channel and a hub of fihe impeller. For optimal efficiency, such a leakage flow must be avoided.
  • a sealing arrangement is customarily provided, closing the sealing gap between the impeller and the casing.
  • DE 100 41 332 C1 or EP 0 708 248 B1 provision is made for a plastics or metal sealing ring in the form of sealing tape which is clamped by fastening screws, bearing against the casing by the aid of a retaining ring.
  • the sealing ring is a slit ring which can be expanded upon installation for minimization, as far as possible, of the gap towards the impeller.
  • sealing the gap as accurately as possible requires highly precise installation of the sealing ring, the retaining ring and the fastening screws, which is complicated and costly.
  • compressors are described in GB 1 448 578 A , which is considered to represent the closest prior art, and in DE 44 15 566 A1 , DE 103 17 010 A1 , FR 2 185 155 A and DE 42 44 45 8 A1 .
  • the object is attained in a compressor, in particular a lateral channel compressor, which comprises a casing and an impeller wheel which is disposed therein rotatably about an axial axis of rotation and which is sealed by means of a sealing arrangement which comprises an encircling sealing ring.
  • the sealing arrangement comprises a spring element which forces the sealing ring against a contact surface in particular on the casing.
  • the spring element helps subject the sealing ring to permanent, flexible spring load.
  • This is accompanied with the special advantage that, upon changes in volume during operation, for instance due to temperature fluctuations, these volumetric changes are dynamically compensated by the spring load applied.
  • This means automatically tracking compensation of any changes in volume by the sealing ring, which ensures that the remaining gap between the two rotating parts, namely the casing on the one hand and the impeller on the other, is kept constant and as small as possible for any operating status so that constantly good efficiency is obtained.
  • the flexible spring load applied by the spring element reduces the risk of the sealing ring being abraded, which is the case with a conventional prior art sealing ring that is tightly clamped, resulting in damages or at least in deterioration of characteristic curves. Installation is not at all susceptible to tolerances and thus simple. With pre-load no longer being set by a fastening screw that is adjusted upon installation, but rather automatically by reason of the springiness of the spring element, the risk of faulty installation is clearly reduced.
  • the contact surface is a wall area of a groove worked into the casing and that the wall area is oriented and configured in such a way that the sealing ring, when in a position of contact, has the tolerance clearance towards the impeller during standard operation.
  • a sectional surface of the sealing ring is pressed against a side wall of the groove, while another sectional surface laps over the sealing gap which is to be sealed, and over a sectional surface, adjoining the sealing gap, of the impeller.
  • a clamping ring which bears against, and acts on, the sealing ring and on which acts the spring element.
  • the clamping ring transmits the spring load that is exerted by the spring element on to the sealing ring.
  • the pre-load of the spring element is adjustable be a setting element. This is a simple way of compensating, without any problems, fluctuations of tolerance and dimensional accuracy of the sealing and clamping ring during assembly.
  • the spring load of the spring element works in the radial direction so that the sealing ring is radially expanded towards the contact surface or compressed in the radial direction.
  • the spring element is in particular configured as a compression or extension spring.
  • the spring element is a spring washer, bearing by its circumference against the sealing ring.
  • spring washer is to be understood as a ring exhibiting spring load in its radial direction.
  • the clamping ring or the sealing ring prefferably have a point of separation with two opposed ring ends which the spring element acts on.
  • the two ring ends are either spread apart or contracted for the clamping or sealing ring to the expanded or compressed radially.
  • the spring element comprises two spring legs, the spring load of which acting on one of the two ring ends.
  • the two spring legs are in particular the free ends of a spring wire that is bent approximately in the shape of a U or a leaf spring that is bent approximately in the shape of a U. In the vicinity of the bight of the U, the spring element is held up in a fixed point.
  • the free ends act flexibly on the ring ends.
  • the adjusting element is suitably disposed between the two spring legs.
  • the spring pre-load is set simultaneously for both spring legs so that symmetric overall springiness is exercised
  • the spring element rests by both spring legs on an intermediate element which is disposed between the spring element and a lateral wall, extending in the radial direction, of the casing.
  • This intermediate element comprises groove-type guides for the ends of the sealing ring and/or clamping ring.
  • the groove-type guides ensure controlled transfer of the spring load in the vicinity of the spring element in particular for the clamping ring.
  • the intermediate elements are simple stampings.
  • the spring element is safeguarded by a fastener against axial migration or displacement.
  • the principle of sealing by the separate spring element that acts on the sealing ring is suitable for radial as well as axial sealing.
  • the sealing ring is pressed in a direction towards an encircling inside periphery and outside periphery of the impeller, the perpendicular of which periphery extends in the radial direction.
  • the sealing ring is pressed in a direction towards a ring-type front face of the impeller, the perpendicular of which extends in the axial direction.
  • the lateral channel compressor comprises a two-piece casing, namely a casing member 2 and a cover 4.
  • An impeller 6 is disposed in the casing; it is rotatable about an axial axis of rotation.
  • the axial direction 8 is roughly outlihed by a doubleheaded arrow.
  • the impeller 6 is driven by a driving motor (not shown) and a drive shaft.
  • the impeller 6 has a hub 10 which extends in the radial direction and, on the side of its end, terminates in a supporting ring 14 on which are mounted a plurality of individual blades 16 which are distributed along the circumference.
  • the supporting ring 14 projects on both sides over the hub 10 in the axial direction 8.
  • the supporting ring 14 forms a cylindrical inside periphery which extends in the axial direction 8 towards the two casing members 2, 4.
  • a gap which is termed sealing gap 18 and which must be sealed for leakage flows to be avoided.
  • the casing members 2, 4 are substantially adapted to the contour of the impeller 6, in particular in the vicinity of the hub 10 and the supporting ring 1,4.
  • a sealing arrangement is provided for closing the sealing gap. It comprises a sealing ring 20 which consists for example of plastics, in particular Teflon, or of metal, and which is forced by spring load against a contact surface 22 on the casing member 2, 4.
  • the spring load is transferred to the sealing ring by means of a clamping ring 24 that is embodied in particular as metal strip.
  • the sealing ring 20 as well as the clamping ring 24 jointly rest in a sealing groove 26. It is worked into the respective casing member 2, 4, extending in the axial direction so that the bottom of the groove extends in the radial direction 12 and the two side walls 28 run in the axial direction 8.
  • a sealing ring 20 which consists for example of plastics, in particular Teflon, or of metal, and which is forced by spring load against a contact surface 22 on the casing member 2, 4.
  • the spring load is transferred to the sealing ring by means of a clamping ring 24 that is embodied in particular as metal strip.
  • the contact surface 22 is formed by the top side wall 28 that is oriented towards the blades 16.
  • the sealing ring 20 is pressed against this side wall 28.
  • the sealing ring 20 projects in the axial direction 8 over the sealing gap 18, standing out in the axial direction 8 from a sectional area of the inside periphery of the supporting ring 14.
  • the inside periphery of the supporting ring 14 has a radius or diameter that slightly exceeds the side wall 28 which constitutes the contact surface 22 so that, with the sealing ring 20 resting on the contact surface 22, there is still some minor tolerance clearance between the sealing ring 20 and the inside periphery of the supporting ring 14, This helps prevent the impeller 6 from rubbing on the sealing ring 20.
  • FIG. 2 A first embodiment of the sealing arrangement is illustrated in Figs. 2 to 4 , According to Fig. 2 , the sealing ring 20 rests outwards and the clamping ring 24 inwards in the sealing groove 26. Both rings 20, 24 are slit, having a gap and opposed ring ends 30.
  • a spring-element-34 incorporation chamber 32 which extends in the radial direction 12.
  • the spring element 34 of the embodiment is designed in the way of a spring wire bent in the shape of a U and having two spring legs 34A, B.
  • the spring element 34 In the front area of the spring legs 34A, B, the spring element 34 has a crimp; it is entirely inserted in the incorporation chamber 32 where it is fixed by a fastening screw 35 and safeguarded in particular against displacement in the axial direction 8.
  • the spring legs 34A, B rest on an intermediate element 36 which is clamped between the spring legs 34A, B and a side wall of radial extension of the casing member 2, 4.
  • the intermediate element 36 In its radially outward marginal area, the intermediate element 36 has two opposed guiding grooves 38, with the ring ends 30 of the clamping ring 24 resting therein.
  • the spring load of the spring legs 34A, B acts in the circumferential direction on the ring ends 30, thus expanding the clamping ring 24 so that overall spring load of the clamping ring 24 acts throughout the periphery in the radial direction 12 on the sealing ring 20.
  • a setscrew 42 In the vicinity of the crimp of the two spring legs 34A, B, provision is made for another screw in the form of a setscrew 42.
  • This adjusting or regulating element helps set the pre-load of the spring element 34 during assembly.
  • the shank of the setscrew 42 is for example eccentric so that the spring legs 34A, B are forced outwards by rotation of the setscrew 42.
  • the sealing ring 20 is compressed in the radial direction by way of the clamping ring 24.
  • the two ring ends 30 of the clamping ring 24 are connected to each other by way of an extension spring 44 in the form of a helical spring.
  • a compression spring 46 of the type of a helical spring acts directly on the sealing ring 20. In doing so, the compression spring 46 supports itself by its rear end on the casing member 2, 4.
  • FIG. 7 corresponds to the embodiment according to Fig. 1 , in which the sealing arrangement of Figs. 2 to 4 is used i.e., in which the sealing ring 20 is expanded radially outwards.
  • the sealing ring 20 is compressed radially - as shown by way of example in the embodiment according to Fig. 5 .
  • the sealing ring 20 seals the sealing gap 18 towards an external periphery of the supporting ring 14.
  • this external periphery has a radius smaller than the contact surface 22.
  • a axial seal which is strongly simplified by way of example in Fig. 6 .
  • the sealing ring 20 is pressed against the contact surface 22 which extends in the radial direction 12, and the sealing ring 20 projects over the sealing gap 18 as well as a sectional surface of the supporting ring 14 in the radial direction 12.
  • a spring element of the type of a spring assembly 48 for exertion of the spring load that acts in the axial direction 8, with several compression springs 46, in this spring assembly 48, being distributed along the circumference between two retaining rings and combined to constitute a pre-fabricated constructional unit.
  • the sealing ring 20 being automatically and dynamically entrained by the spring element, varying thermally conditioned deformations of the sealing ring 20, the clamping ring 24 and the casing member 2, 4 are not critical. Moreover, any uncontrolled expansion or displacement of the sealing ring 20 is avoided, which ensures that the impeller 6 does not rub on the sealing ring 20.
  • Another advantage consists in the improved emergency running properties. If, for example, the supporting ring 14 hits on the sealing ring 20 in the case of bearing damages, the sealing ring 20 is able to yield, owing to the flexible accommodation, which will keep the friction between the sealing ring 20 and supporting ring 14 low.
  • a lateral channel compressor With the sealing, ring 20 adjusting dynamically to respective current spatial geometries, such a lateral channel compressor is less susceptible with a view to tolerances in shape and dimension during the manufacture of the individual parts of the lateral channel compressor, such as sealing ring 20, groove 26, diameter of the supporting ring 14 and contact surface 22, width of the sealing gap 18 etc.
  • the spring-element arrangement enables the sealing ring 20 to rest uniformly on the sealing groove 26 even in the case of fluctuations in load and temperature. Necessary tolerance clearances do not affect the sealing effect.

Claims (9)

  1. Seitenkanalverdichter mit
    a. einem Gehäuseteil (2, 4) und
    b. einem Laufrad (6),
    i. welches im Gehäuseteil (2, 4) um eine axiale Drehachse drehbar angeordnet ist und
    ii. welches vom Gehäuseteil (2, 4) um einen Dichtspalt (18) beabstandet ist,
    c. der mittels einer einen Dichtring (20) aufweisenden Dichtungseinrichtung abgedichtet ist,
    d. wobei die Dichtungseinrichtung ein Federelement (34, 34A, 34B, 44) aufweist, das den Dichtring (20) gegen eine Anlagefläche (22) drückt,
    e. dadurch gekennzeichnet, dass der Dichtring (20) eine Trennstelle mit zwei gegenüberliegenden Ringenden (30) aufweist, auf die das Federelement (34, 34A, 34B, 44) in Umfangsrichtung wirkt.
  2. Verdichter nach Anspruch 1, dadurch gekennzeichnet, dass die Anlagefläche (22) ein Wandungsbereich (28) einer in das Gehäuseteil (2, 4) eingearbeiteten Dichtnut (26) ist, und dass der Wandungsbereich (28) derart ausgebildet ist, dass bei anliegendem Dichtring (20) dieser im Normalbetrieb einen Toleranzspielraum zum Laufrad (6) aufweist.
  3. Verdichter nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass ein am Dichtring (20) anliegender Spannring (24) vorgesehen ist, auf den das Federelement (34, 34A, 34B, 44) einwirkt und der die Federspannung auf den Dichtring (20) überträgt.
  4. Verdichter nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Federvorspannung über ein Stellelement (42) einstellbar ist.
  5. Verdichter nach Anspruch 1, dadurch gekennzeichnet, dass der Spannring (24) eine Trennstelle mit zwei gegenüberliegenden Ringenden (30) aufweist, auf die das Federelement (34, 34A, 34B, 44) wirkt.
  6. Verdichter nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Federelement (34) zwei Federschenkel (34A, 34B) aufweist, deren Federspannung auf ein entsprechendes Ringende (30) wirkt.
  7. Verdichter nach Anspruch 6, dadurch gekennzeichnet, dass das Stellelement (42) zum Einstellen der Federvorspannung zwischen den Federschenkeln (34A, 34B) angeordnet ist.
  8. Verdichter nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, dass zwischen dem Federelement (34, 34A, 34B, 44) und einer sich in radialer Richtung erstreckenden Seitenwand des Gehäuseteils (2, 4) ein Zwischenelement (36) angeordnet ist, welches Führungsnuten (38) für die Ringenden (30) des Dichtrings (20) und/oder des Spannrings (24) aufweist.
  9. Verdichter nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Federelement (34, 34A, 34B, 44) gegen ein Verschieben in axialer Richtung durch ein Fixierelement (35) gesichert ist.
EP05026935A 2004-12-15 2005-12-09 Seitenkanalverdichter Active EP1672221B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE202004019366U DE202004019366U1 (de) 2004-12-15 2004-12-15 Verdichter, insbesondere Seitenkanalverdichter

Publications (3)

Publication Number Publication Date
EP1672221A2 EP1672221A2 (de) 2006-06-21
EP1672221A3 EP1672221A3 (de) 2007-03-28
EP1672221B1 true EP1672221B1 (de) 2009-08-19

Family

ID=35840375

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05026935A Active EP1672221B1 (de) 2004-12-15 2005-12-09 Seitenkanalverdichter

Country Status (5)

Country Link
US (1) US20070020084A1 (de)
EP (1) EP1672221B1 (de)
AT (1) ATE440219T1 (de)
DE (2) DE202004019366U1 (de)
ES (1) ES2330016T3 (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006009054B4 (de) 2006-02-27 2007-11-22 Woco Industrietechnik Gmbh Gehäuse für Radialverdichter
DE102007009781B4 (de) 2007-02-27 2009-09-17 Woco Industrietechnik Gmbh Kunststoffverdichtergehäuse sowie Verfahren zu dessen Herstellung
DE102007027282B3 (de) 2007-06-11 2008-11-13 Woco Industrietechnik Gmbh Kunststoffverdichtergehäuse und Verfahren zur Herstellung eines Kunststoffverdichtergehäuses
DE102009009389B4 (de) * 2009-02-18 2011-03-24 Woco Industrietechnik Gmbh Verdichtergehäuse, Verdichter umfassend ein solches Verdichtergehäuse und Verfahren zur Herstellung eines Verdichtergehäuses
DE102016222430A1 (de) * 2016-11-15 2018-05-17 Gardner Denver Deutschland Gmbh Seitenkanalverdichter
CN112761743B (zh) * 2020-12-29 2022-08-16 杭州汽轮动力集团有限公司 一种燃气轮机排气扩散器密封结构

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US1773250A (en) * 1929-02-04 1930-08-19 Smalley Accessories Corp Piston ring
US2117986A (en) * 1935-03-11 1938-05-17 Wilkening Mfg Co Piston ring construction
US2604050A (en) * 1948-04-27 1952-07-22 Standard Oil Dev Co Centrifugal pump impeller seal ring
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US3512788A (en) * 1967-11-01 1970-05-19 Allis Chalmers Mfg Co Self-adjusting wearing rings
FR2185155A5 (de) * 1972-05-18 1973-12-28 Diosgyoeri Gepgyar
CH560326A5 (de) * 1972-09-13 1975-03-27 Siemens Ag
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US4576548A (en) * 1984-01-17 1986-03-18 Westinghouse Electric Corp. Self-aligning static seal for gas turbine stator vanes
DE8704066U1 (de) * 1987-03-18 1988-07-14 Siemens Ag, 1000 Berlin Und 8000 Muenchen, De
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DE4415566C2 (de) * 1994-05-03 1999-02-18 Sero Pumpenfabrik Gmbh Seitenkanalpumpe
US5658126A (en) * 1994-10-20 1997-08-19 Siemens Aktiengesellschaft Side channel compressor
DE10041332C1 (de) 2000-08-23 2001-08-30 Siemens Ag Seitenkanalverdichter
CA2432250C (en) * 2002-06-12 2009-10-06 Poly-Tec Products, Inc. Novel packaging design incorporating gasket clamping assemblies and installation instructions
DE10317010A1 (de) * 2003-04-11 2004-11-04 Schmitt-Kreiselpumpen Gmbh & Co. Kg Wirbelpumpe
US7540501B2 (en) * 2004-11-05 2009-06-02 Flowserve Management Company Segmented shaft seal

Also Published As

Publication number Publication date
US20070020084A1 (en) 2007-01-25
ATE440219T1 (de) 2009-09-15
EP1672221A3 (de) 2007-03-28
ES2330016T3 (es) 2009-12-03
DE602005016062D1 (de) 2009-10-01
EP1672221A2 (de) 2006-06-21
DE202004019366U1 (de) 2006-04-20

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