EP3140550B1 - Dichtungsanordnung für eine hochdruckpumpe sowie hochdruckpumpe mit einer solchen - Google Patents

Dichtungsanordnung für eine hochdruckpumpe sowie hochdruckpumpe mit einer solchen Download PDF

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Publication number
EP3140550B1
EP3140550B1 EP15718826.9A EP15718826A EP3140550B1 EP 3140550 B1 EP3140550 B1 EP 3140550B1 EP 15718826 A EP15718826 A EP 15718826A EP 3140550 B1 EP3140550 B1 EP 3140550B1
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EP
European Patent Office
Prior art keywords
sealing
pressure
pump
accordance
arrangement
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
EP15718826.9A
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German (de)
English (en)
French (fr)
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EP3140550A1 (de
Inventor
Thomas Welschinger
Marco Carvalho
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.)
Sulzer Management AG
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Sulzer Management AG
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Publication date
Application filed by Sulzer Management AG filed Critical Sulzer Management AG
Publication of EP3140550A1 publication Critical patent/EP3140550A1/de
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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
    • 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
    • F04D29/086—Sealings especially adapted for liquid pumps

Definitions

  • the invention relates to a sealing arrangement for sealing a pressure chamber in a high-pressure pump and a high-pressure pump with such a sealing arrangement.
  • the pressure chamber in a pump in which the pressurized fluid to be pumped by the pump is located, must be sealed from its environment.
  • the environment of the pressure chamber may be the usually under atmospheric pressure environment of the pump or-for example in the case of a multi-stage pump - another pressure chamber of the pump, in which the fluid to be delivered is at a higher or lower pressure.
  • the pressurization of the groove cause elastic or plastic deformation of its wall, so as to avoid or reduce the pressure-induced opening of gaps between the components.
  • an existing of an elastomer O-ring is provided, which is arranged in a groove provided in this sealing surface. This O-ring is a reliable seal between the two contacting sealing surfaces.
  • a generic seal arrangement for sealing a pressure chamber in a turbomachine is also in the US Pat. No. 4,239,124 and the DE 696 21 545 T2 shown.
  • a sealing arrangement for sealing a pressure chamber in a high-pressure pump, which is delimited by a first and a second limiting element, with a separate sealing element having a first sealing surface for cooperation with the first limiting element and a second sealing surface for cooperation with the second limiting element wherein the two sealing surfaces are inclined relative to each other and each having a groove for receiving a sealing ring, and wherein the sealing element is arranged and configured so that it is displaceable in total along one of the limiting elements when pressure is applied.
  • the entire sealing element can move when pressurized along one of the limiting elements.
  • This causes a pressure-opening gap between the two limiting elements to be reliably covered by the displacement of the sealing element by the sealing element, so that extrusion of a sealing ring into the opening gap is avoided.
  • This ensures an efficient sealing effect even at very high pressures of, for example, up to 1000 bar.
  • a separate sealing element with the grooves for receiving sealing rings also has the advantage that for this Sealing element, a different material can be selected as, for example, the material from which the boundary elements are made. Therefore, a material can be selected for the sealing element whose mechanical properties, such. B. the elastic properties are as optimal as possible under the pressure load.
  • the two sealing surfaces of the sealing element enclose an angle of substantially 90 °. This measure is particularly advantageous for the displaceability of the sealing element under pressure load.
  • An advantageous measure is when a support ring is provided for positioning the sealing element, in particular in the unpressurized state. This makes it possible to realize that the sealing element has a defined initial position or starting position, so that it reacts in the desired manner under pressure load.
  • the support ring is in the non-pressurized state on a support surface of the sealing element, wherein the support surface is different from the two sealing surfaces of the sealing element. In this way it is ensured that the sealing element can move when pressurized by the support ring without obstruction.
  • the sealing element has a substantially L-shaped cross section with a long leg, which forms the first sealing surface, and with a short leg, which forms the second sealing surface.
  • the sealing element is arranged displaceably along the second limiting element.
  • This is particularly preferred in the embodiment with the substantially L-shaped cross section.
  • the pressurized surface of the sealing element formed by the long leg is larger than the pressure-applied area formed by the short leg. This results from the pressure of a greater force on the first leg formed by the long leg, so that the sealing element is reliably displaced by this larger force along the second limiting element, which cooperates with the sealing surface formed by the shorter leg.
  • the sealing element is displaceably arranged along the first and the second limiting element, because this allows the sealing element to follow pressure-induced displacements or bulges of both the first and the second limiting element.
  • a reliable seal can be realized both in the radial direction and in the axial direction.
  • a further advantageous measure consists in that the first sealing surface between the groove provided in it and its end facing the second sealing surface is conical.
  • the first sealing surface is designed bevelled starting from the groove provided in it starting in the direction of the contact line between the two sealing surfaces.
  • the first sealing surface moves away from the groove in the direction of the contact line farther and farther from the first limiting element.
  • This measure ensures that the edge which delimits the groove in the first sealing surface and is closer to the contact line first comes into contact with the first limiting element when pressure is applied, and that at this edge or in the region of this edge the highest Surface pressure occurs.
  • This measure provides additional security that an inserted in the groove sealing ring, z. As an O-ring, undergoes an extrusion when pressurized.
  • the second sealing surface between the groove provided in it and its end facing the first sealing surface is conical.
  • the angle of the cone is at most 2 °, preferably at most 1 °.
  • the seal assembly is configured as a radial seal arrangement.
  • the invention further proposes a high-pressure pump with a sealing arrangement according to the invention.
  • the high-pressure pump can be operated safely and reliably even at very high pressures of, for example, up to 1000 bar.
  • the high-pressure pump is provided with a pump cover and a pump housing, wherein the seal assembly is provided for sealing between the pump cover and the pump housing.
  • the high pressure pump is designed as a multi-stage pump.
  • the sealing arrangement is provided for sealing between a pressure chamber and an intermediate pressure chamber.
  • Another preferred embodiment of the high pressure pump is when the seal assembly is provided for sealing between a separator and the pump housing or between the pump cover and the pump housing.
  • Fig. 1 shows a schematic sectional view of an embodiment of an inventive seal assembly, which is generally designated by the reference numeral 1 and for sealing a pressure chamber 2 in a high-pressure pump 100 (see Fig. 6 ) serves.
  • the pressure chamber 2 is bounded by a first limiting element 3 and a second limiting element 4.
  • the sealing arrangement 1 further comprises a separate sealing element 5, which has a first sealing surface 51 for co-operation with the first limiting element 3 and a second sealing surface 52 for co-operation with the second limiting element 4.
  • a separate sealing element is meant that the sealing element 5 is not an integral part of, for example, one of the limiting elements 3, 4, but is designed as a separate component.
  • the illustration in Fig. 1 only a part of the seal assembly 1, namely, for example, the upper half.
  • the sealing element 5 is generally designed rotationally symmetrical with respect to the pump shaft, which in Fig. 1 is indicated by a rotation axis A, around which rotate the rotating parts of the pump in the operating state. That is, the sealing element 5 is usually designed annular.
  • the pressure chamber 2 is usually designed as an annular space surrounding the pump shaft.
  • each of the two sealing surfaces 51, 52 of the sealing element 5 is provided in each case a groove, namely a first groove 53 and a second groove 54, each of which serves to receive a sealing ring 55, which is configured for example as an O-ring.
  • the sealing rings 55 are used in a manner known per se for sealing between the respective sealing surface 51 or 52 and the limiting element 3 or 4 cooperating therewith and are e.g. made of an elastomeric material.
  • sealing rings can be other known sealing means, for example metallic rings or washers or sealants made of a plastic such as PTFE or PEEK.
  • the two sealing surfaces 51, 52 of the sealing member 5 are inclined towards each other and adjoin one another along a contact line 56.
  • the two sealing surfaces 51, 52 an angle of substantially 90 °.
  • the sealing element 5 according Fig. 1 has a substantially L-shaped cross section with a long leg 57, which forms the first sealing surface 51 and cooperates with the first limiting element 3, and with a short leg 58, which forms the second sealing surface 52 and cooperates with the second limiting element 4.
  • the sealing element 5 is arranged and designed so that it is displaceable overall at least along one of the limiting elements 3, 4 when pressure is applied. This will be explained below with reference to Fig. 1 explained.
  • the first limiting element 3 rests on the boundary surface 43 of the second limiting element 4.
  • This can be realized in a pump, for example, in that the component which forms the first limiting element 3, with the component which forms the second limiting element 4, is firmly screwed. If now in the pressure chamber 2, an ever higher pressure is generated, it can by Pressure-induced deformations, for example bulges, of the first or the second limiting element 3 or 4 happen that a gap 6 opens between the limiting elements 3, 4. This condition is in Fig. 1 shown.
  • the entire sealing element 5 moves upward as shown and thereby closes the gap 6 with respect to the pressure chamber 2, so that no fluid from the pressure chamber 2 through can escape the gap 6, but the sealing effect is maintained even at very high pressures.
  • the sealing element 5 can also follow this movement, namely, by the sealing element 5 shifting in its entirety along the first limiting element 3. During this displacement, the substantially annular sealing element 5 expands.
  • the sealing element 5 can thus be positioned both in the radial direction and in the illustration in FIG Fig. 1 to the top (or bottom) - as well as in the axial direction - so in accordance with illustration in Fig. 1 move to the right (or to the left).
  • the displacement in the axial direction is of course accompanied by a widening of the substantially annular sealing element 5.
  • the radial displaceability of the sealing element 5 ensures that the pressure-opening gap 6 between the two limiting elements 3 and 4 is reliably closed by the sealing element 5.
  • the sealing element 5 When the sealing element 5 is pressurized, its displaceability is usually combined with a deformation of the sealing element 5, i. In addition to or during the displacement of the sealing element 5, this can also deform.
  • This deformation is preferably an elastic deformation, i. a deformation that is completely reversible when depressurized.
  • the sealing element 5 Since the sealing element 5 is configured as a separate component, that is, for example, is not an integral part of one of the limiting elements 3, 4, one has the greatest possible freedom with regard to the choice of material for the sealing element 5.
  • a material can be selected for the sealing element 5, which is optimal in terms of its elastic properties for the particular application.
  • titanium As a particularly preferred material for the sealing element 5, titanium has been found.
  • the first sealing surface 51 is configured conically between the first groove 53 and the contact line 56, at which the two sealing surfaces 51, 52 abut one another such that in the pressureless state, the distance between the first sealing surface 51 and the first limiting element 3 at that Boundary edge of the first groove 53 closer to the contact line 56 (in FIG Fig. 1 the illustration according to the left Begrenzungshunt), is minimal and then enlarged in the direction of the contact line 56.
  • This bevel of the first sealing surface 51 is in Fig. 1 shown and the associated angle of the cone is denoted by ⁇ .
  • the second sealing surface 52 between the second groove 54 and the contact line 56, at which the two sealing surfaces 51, 52 abut each other conical in such a way that in the pressureless state, the distance between the second sealing surface 52 and the second limiting element. 4 at the boundary edge of the second groove 54, which is closer to the contact line 56 (in Fig. 1 the upper bounded edge according to the illustration), is minimal and then increases in the direction of the contact line 56.
  • This bevel of the second sealing surface 52 is in Fig. 1 shown and the associated angle of the cone is denoted by ⁇ .
  • FIG. 1 Another optional advantageous measure is when the long leg 57 or the short leg 58 or preferably both legs 57, 58 in the area between the first and second groove 53, 54 and the end facing away from the contact line 56 each cylindrical (that is not conical or not inclined) are designed and cut back.
  • Fig. 1 This is evident from the fact that these regions each extend parallel to the first or second limiting element 3, 4 and have a larger distance from the first or second limiting element 3, 4 than the respective boundary edge of the first and second groove 53, 54, the closer to the contact line 56 is located.
  • This measure also supports the effect that the respectively greatest surface pressure of the first or second sealing surface 51, 52 occurs in the region of the boundary edge of the first and second groove 53, 54 which is closer to the contact line 56.
  • the two angles ⁇ and ⁇ of the respective cone of the first and the second sealing surface 51, 52 may be the same or different. In practice, it has proven useful if ⁇ and ⁇ are in each case at most 2 ° and preferably at most 1 °. In particular, values between 0.1 ° and 0.2 ° have also proven suitable for ⁇ and ⁇ .
  • thermally induced gaps such as may be caused by different thermal expansion coefficients of adjacent components, can be closed by the displacement of the sealing element 5.
  • the two legs 57 and 58 may also have the same length, so that the cross-sectional area is an isosceles angle profile, or it may be rounded be.
  • a first variant for the arrangement of the sealing element 5 is shown.
  • this is an arrangement for the radial seal that can be used in a multi-stage pump.
  • multi-stage pumps especially those with a so-called back-to-back arrangement (see also Fig. 6 ) exists between the pressure at the inlet of the pump, for example atmospheric pressure, and the highest pressure in the pressure chamber 2, which is usually connected to the outlet of the pump, at least one intermediate pressure, which in a back-to-back arrangement typically in the middle between the Pressure at the entrance and the highest pressure in the pressure chamber 2 is, so for example, the pressure at the entrance to be atmospheric pressure, the pressure in the pressure chamber 2 is about 1000 bar and the intermediate pressure is 500 bar.
  • Fig. 6 the pressure at the inlet of the pump, for example atmospheric pressure
  • the highest pressure in the pressure chamber 2 which is usually connected to the outlet of the pump
  • at least one intermediate pressure which in a back-to-back arrangement typically in the middle between the Pressure at the entrance and the highest pressure in the pressure chamber 2 is, so
  • the first limiting element 3 is designed as a pump housing 3 and the second limiting element 4 serves the separation between the two intermediate pressure chambers 7, 8 and the respective separation of each of the intermediate pressure chambers 7, 8 from the pressure chamber 2.
  • a support ring 9 is provided in these seal assemblies, whose function is the positioning of the respective Dichtungselemnts 5 is in the depressurized state.
  • the Sauerring 9 may for example be designed as a split ring, that is, consist of two or more segments, for example, placed in the pressure chamber 2 and bolted to its wall.
  • the support ring 9 is screwed or fastened with respect to the sealing element 5 with play, because the support ring 9 is the sealing element 5 only position, but not jamming or prevent the displaceability of the sealing member 5 in an undesirable manner or affect.
  • the support ring 9 does not have a sealing function, it should only ensure that the sealing element 5 is in the pressureless state in a defined position.
  • the support ring 9 each has a substantially L-shaped cross section. With one of the legs of the L, the support ring is supported on the inner wall of the pressure chamber 2, the other leg forms the surface which supports the sealing element 5 in the unpressurized state.
  • the support surface of the sealing element 5, which rests against the support ring in the pressureless state, is in each case the end face of the long leg 57 of the sealing element 5.
  • the pressure chamber 2 can lead to a buckling or other expansion of the pump housing 3, which can open a gap between the pump housing 3 and the second limiting element 4. This will be - as related to Fig. 1 explained by the displacement of the sealing elements 5 effectively closed.
  • a second variant of the arrangement of the sealing element 5 is shown.
  • the sealing element 5 serves for sealing between the pump housing, which here represents the first limiting element 3, and a pump cover, which here represents the second limiting element 4.
  • the pump cover 4 is with a plurality of screws 41 screwed to the pump housing 3, of which in Fig. 3 only one is shown there is typically outside of the pump housing 3 atmospheric pressure, while in the pressure chamber 2, an elevated pressure prevails. At very high pressures in the pressure chamber 2, the pump cover 4 bulges, whereby a gap between the pump housing 3 and the pump cover 4 opens.
  • the sealing element 5 in the axial direction - ie in the direction of the axis of rotation A - can move, the sealing element shifts under pressure as shown to the right and thus reliably closes the gap between the pump cover 4 and the pump housing 3.
  • the pump housing 3 also stretch, so to speak expand. This movement can also follow the sealing element 5, because it is also displaceable with respect to the radial direction. This displacement with respect to the radial direction is generally accompanied by a widening of the sealing element 5, since the inner diameter also increases when the pump housing 3 expands in the radial direction.
  • sealing element is "displaceably arranged" is therefore to be understood in the context of this application as meaning also an expansion or expansion of an annular sealing element.
  • the sealing element 5 is used to seal the pressure chamber 2 of a pump against an intermediate pressure chamber 7.
  • the maximum pressure prevails, for example 1000 bar
  • the intermediate pressure chamber 7 there is any intermediate pressure which is between the atmospheric pressure or the ambient pressure and the pressure in the pressure chamber 2, for example, the intermediate pressure is half the pressure in the pressure chamber second
  • the pump housing forms the first limiting element 3.
  • the second limiting element 4 is a component, for example a separating element 4, which delimits the intermediate pressure chamber 7 from the pressure chamber 2.
  • Fig. 5 illustrated fourth variant for the arrangement of sealing elements 5 is similar to the in Fig. 2 shown.
  • This arrangement is especially suitable for multi-stage pumps in back-to-back arrangements.
  • These pumps have two substantially identical blocks, each of which can contain multiple stages of pumps. These two blocks are mirror images - ie back to back - arranged to each other, so that the pressure chamber 2, in which the highest pressure prevails and which is connected to the outlet of the pump, is usually arranged as an annular space in the middle of the pump.
  • two sealing elements 5 are provided.
  • the first limiting element 3 is formed by the pump housing 3, while the second limiting element 4 as a separating element is the dividing wall between the two blocks arranged back to back. Outside the pump housing 3, the atmospheric or ambient pressure prevails and in the two intermediate pressure chambers 7 and 8 there is substantially the same pressure, which is typically half as large is like the pressure in the pressure chamber 2.
  • Fig. 6 is schematically and in section an embodiment of an inventive high-pressure pump shown, which is generally designated by the reference numeral 100.
  • the high-pressure pump 100 is a multi-stage - here four-stage - high-pressure pump with back-to-back arrangement, which is designed as a radial centrifugal pump.
  • the high-pressure pump 100 has a pump housing 103, a pump cover 112 for closing the pump housing 103, an inlet 110 through which the fluid to be delivered, for example, a liquid such as water or petroleum, enters the high-pressure pump 100 and an outlet 111 through which then pressurized fluid leaves the high pressure pump 100.
  • a pump shaft 113 is provided, which rotates in the operating state about the axis of rotation A and is driven by a drive unit, not shown.
  • the high-pressure pump 100 has four essentially identically designed stages, namely a first stage 114, a second stage 115, a third stage 116 and a fourth stage 117. Each of these stages 114-117 has an impeller 120, respectively. Each impeller 120 is non-rotatable with the pump shaft 113 connected.
  • the first and second stages 114, 115 belong to a first one Block 130.
  • the third and fourth stages 116, 117 belong to a second block 140.
  • the two blocks 130, 140 are separated from each other by a partition 104 which is fixed with respect to the pump housing 103.
  • the two essentially identically configured blocks 130, 140 are arranged in mirror image with respect to the separating element 104, ie, back to back, which is why this structure is also referred to as a back-to-back arrangement.
  • the flow path of the fluid through the high-pressure pump 100 is in Fig. 6 represented by arrows, of which only the first at the inlet 110 is designated by the reference numeral 150.
  • the fluid flows from the input 110 in the axial direction to the impeller 120 of the first stage 114 and is guided from the outlet in the axial direction to the impeller of the second stage 115.
  • the fluid is passed through a flow connection 160, which is provided in the separating element 104, into an intermediate pressure chamber 108 of the second block 140, through which the fluid flows to the inlet of the second block 140 third stage 116 passes.
  • the fluid is conducted in the axial direction to the input of the fourth stage 117, which finally promotes the fluid to the high pressure with which it is available at the outlet 111 of the high-pressure pump 100.
  • a high pressure flow connection 170 leads to the pressure chamber 102, which is connected to the outlet 111 of the high pressure pump 100.
  • the pressure chamber 102 is configured essentially as an annular space, which leads around the separating element 104 radially outward.
  • an intermediate pressure chamber 107 is provided, which is designed substantially as an annular space and arranged on the inside of the pump housing 103.
  • This intermediate pressure space 107 is connected via an in Fig. 6 Flow connection, not shown, connected to the output of the second stage 115, so that in the two intermediate pressure chambers 107 and 108, the same pressure prevails, which corresponds due to the substantially same configuration of the four stages 114-117, about half the pressure of the pressure in the pressure chamber 2.
  • the separating element 104 adjoins, on the one hand, the pressure chamber 102, in which the highest pressure acts, and, on the other hand, the two intermediate pressure chambers 107 and 108, in which an approximately half the pressure acts as in the pressure chamber 2 Fig. 2 illustrated configuration.
  • a sealing element 5 is provided in each case, which forms an embodiment of the inventive sealing arrangement 1 with the adjacent boundary elements.
  • the pump housing 103 forms the first limiting element 3 and the separating element forms the second limiting element 4.
  • This sealing arrangement 1 is suitable for very high pressures.
  • the pressure in the pressure chamber 102 may be 1000 bar.
  • the pressure in the intermediate pressure spaces 107 and 108 is about 500 bar each.
  • seal assembly 1 can also be used in other places a high-pressure pump.
  • a sealing element 5 may be provided at the in Fig. 6 illustrated embodiment, for example, at the boundary between the pump cover 112 and the pump housing 103.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Sealing Devices (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
EP15718826.9A 2014-05-05 2015-04-14 Dichtungsanordnung für eine hochdruckpumpe sowie hochdruckpumpe mit einer solchen Active EP3140550B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14167034 2014-05-05
PCT/EP2015/058067 WO2015169548A1 (de) 2014-05-05 2015-04-14 Dichtungsanordnung für eine hochdruckpumpe sowie hochdruckpumpe mit einer solchen

Publications (2)

Publication Number Publication Date
EP3140550A1 EP3140550A1 (de) 2017-03-15
EP3140550B1 true EP3140550B1 (de) 2018-06-06

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EP15718826.9A Active EP3140550B1 (de) 2014-05-05 2015-04-14 Dichtungsanordnung für eine hochdruckpumpe sowie hochdruckpumpe mit einer solchen

Country Status (12)

Country Link
US (1) US10584710B2 (es)
EP (1) EP3140550B1 (es)
KR (1) KR20160148522A (es)
CN (1) CN106232995B (es)
AU (1) AU2015258040B2 (es)
BR (1) BR112016023078B1 (es)
CA (1) CA2941677A1 (es)
ES (1) ES2674258T3 (es)
MX (1) MX2016013774A (es)
RU (1) RU2668052C2 (es)
SG (1) SG11201607376VA (es)
WO (1) WO2015169548A1 (es)

Families Citing this family (1)

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Publication number Priority date Publication date Assignee Title
US11118594B2 (en) * 2017-05-16 2021-09-14 Dresser-Rand Company Seal apparatus for a turbomachine casing

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JPS57173595A (en) * 1981-04-20 1982-10-25 Hitachi Ltd Internal seal construction of boiler feed-water pump, etc.
US5236202A (en) * 1991-09-23 1993-08-17 Rosemount Inc. Spring loaded resin seal
JPH0988864A (ja) * 1995-09-26 1997-03-31 Ebara Corp 二重胴型高圧多段ポンプの構造
EP0916850A1 (de) * 1997-11-13 1999-05-19 Sulzer Pumpen AG Gehäuse für Aggregate mit einem Fluid von hohem Druck
RU2232921C2 (ru) 2001-05-21 2004-07-20 Открытое Акционерное Общество "Сумское Машиностроительное Научно-Производственное Объединение Им. М.В. Фрунзе" Система уплотнений турбокомпрессора
DE50301139D1 (de) * 2002-11-12 2005-10-13 Sulzer Pumpen Ag Winterthur Hochdruck-Kreiselpumpe in einem Topfgehäuse mit einem Druckdeckel
JP4601942B2 (ja) * 2003-11-20 2010-12-22 イーグル工業株式会社 シール装置
DE102004044775A1 (de) * 2004-09-16 2006-04-06 Leybold Vacuum Gmbh Vakuumpumpen-Schwingungsdämpfer
DE102008030077A1 (de) * 2008-06-25 2009-12-31 Fissler Gmbh Druckbehälter
DE102009028131A1 (de) * 2009-07-30 2011-02-03 Trelleborg Sealing Solutions Germany Gmbh Dichtung und Dichtungsanordnung
DE102010046929A1 (de) * 2010-09-29 2012-03-29 Robert Bosch Gmbh Dichtbuchsenanordnung und hydraulisches Gerät
DE102011084831B4 (de) * 2011-10-19 2021-01-28 Robert Bosch Gmbh Förderaggregat zum Fördern von Kraftstoff
JP5717662B2 (ja) * 2012-01-27 2015-05-13 三菱電線工業株式会社 金属シール
US9702371B2 (en) * 2012-02-14 2017-07-11 Sulzer Management Ag Sealing arrangement and pump having a sealing arrangement
JP7093658B2 (ja) 2018-03-27 2022-06-30 三菱重工業株式会社 タービン動翼及びガスタービン

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Also Published As

Publication number Publication date
US10584710B2 (en) 2020-03-10
RU2016145419A (ru) 2018-06-05
KR20160148522A (ko) 2016-12-26
RU2668052C2 (ru) 2018-09-25
EP3140550A1 (de) 2017-03-15
BR112016023078B1 (pt) 2022-08-02
CN106232995A (zh) 2016-12-14
BR112016023078A2 (es) 2017-08-15
CN106232995B (zh) 2019-09-03
ES2674258T3 (es) 2018-06-28
AU2015258040A1 (en) 2016-11-10
MX2016013774A (es) 2017-01-20
US20170122331A1 (en) 2017-05-04
AU2015258040B2 (en) 2018-11-01
RU2016145419A3 (es) 2018-08-14
CA2941677A1 (en) 2015-11-12
WO2015169548A1 (de) 2015-11-12
SG11201607376VA (en) 2016-12-29

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