WO2015090881A1 - Compresseur pour machine de cogénération - Google Patents

Compresseur pour machine de cogénération Download PDF

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Publication number
WO2015090881A1
WO2015090881A1 PCT/EP2014/075716 EP2014075716W WO2015090881A1 WO 2015090881 A1 WO2015090881 A1 WO 2015090881A1 EP 2014075716 W EP2014075716 W EP 2014075716W WO 2015090881 A1 WO2015090881 A1 WO 2015090881A1
Authority
WO
WIPO (PCT)
Prior art keywords
sealing
compressor
ring
radial
radial groove
Prior art date
Application number
PCT/EP2014/075716
Other languages
German (de)
English (en)
Inventor
Jan Hinrichs
Said Jennaoui
Original Assignee
Magna Powertrain Bad Homburg 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 Magna Powertrain Bad Homburg GmbH filed Critical Magna Powertrain Bad Homburg GmbH
Priority to DE112014005773.8T priority Critical patent/DE112014005773A5/de
Publication of WO2015090881A1 publication Critical patent/WO2015090881A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
    • F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
    • F16J15/3412—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities

Definitions

  • the invention relates to a compressor for a power-heat engine according to the preamble of claim 1.
  • Compressors of the type discussed here are known.
  • International Patent Application Publication No. WO 01/1276 A1 discloses a compressor which is adapted to compress a gaseous refrigerant under normal conditions, namely carbon dioxide.
  • the compressor has a drive shaft and a sealing device encompassing the drive shaft, which has two sealing elements, namely a sliding ring and a counter ring.
  • the two sealing elements lie sealingly against each other, each with a sealing surface, so that a sealing gap is formed between the sealing surfaces.
  • a centrifugal lubricating device which is adapted to lubricate the sealing device.
  • the sliding ring and the mating ring have an identical diameter in the region of the sealing surfaces, wherein none of the sealing surfaces projects radially beyond the other sealing surface. In order not to let the friction in the region of the sealing gap become too great, the diameter of the sealing elements in the region of the sealing gap is comparatively small. Therefore, the sealing surfaces have a comparatively small extent. However, such small areas are difficult to machine, especially with very great effort or not to läppen with the actual desired precision plan.
  • the invention is therefore an object of the invention to provide a compressor in which the disadvantages mentioned do not occur.
  • the object is achieved by providing a compressor with the features of claim 1. This is characterized by the fact that one of the sealing elements in the region of the sealing surfaces has a larger diameter than the other
  • the sealing element with the larger diameter has in its sealing surface at least one radial groove which extends in the direction of the sealing gap. That sealing element which has the larger diameter can be plangeläppt with comparatively little effort and high quality, so that there is an improved sealing effect. The fact that only one of the sealing elements has a larger diameter, an increased friction in the region of the sealing gap is avoided.
  • the problem of a larger centrifugal effect for the lubricant is countered by the fact that the sealing element with the larger diameter in its sealing surface has at least one radial groove extending in the direction of the sealing gap, so that lubricant can get into the radial groove, where its spin-related Tan - Gentialiolo is deflected in a radially inward movement, so that it is promoted efficiently to the sealing gap. Efficient cooling and lubrication is guaranteed.
  • the sliding ring and / or the counter ring preferably have a ceramic material, more preferably at least one of the sealing elements consists of a ceramic material. Particularly preferably, both the sliding ring and the counter ring on a ceramic material or consist of such.
  • a ceramic material is particularly suitable for, on the one hand, an effective seal also with respect to a gas under normal conditions. to provide migen refrigerant, and on the other hand to withstand the occurring in the region of the sealing gap thermal stress undamaged due to a relative movement between the seal ring and the mating ring.
  • An axial direction here and in the following refers to a direction along which the drive shaft extends or which runs parallel to a rotational axis of the drive shaft.
  • a radial direction refers to a direction that is perpendicular to the axial direction.
  • a circumferential direction responds to a direction which concentrically surrounds the axial direction.
  • the compressor is preferably adapted for use in a power-heat engine configured as an air conditioner or a heat pump. Particularly preferably, the compressor is set up for use in one
  • the compressor is preferably designed for the compression of carbon dioxide as a refrigerant, in particular as a refrigerant of an air conditioning system of a motor vehicle.
  • the compressor is designed as an axial piston pump.
  • the radial groove preferably has - measured in the axial direction - a depth which is at least 5% to at most 20%, preferably at least 10% to at most 15%, particularly preferably 13% of a - also measured in the axial direction - thickness of the sealing element which having the radial groove. In this way, the sealing element is weakened by the radial groove at most to a negligible extent, at the same time ensuring efficient supply of the sealing gap with lubricant.
  • a compressor which is characterized in that the counter-ring in the region of its sealing surface has a larger diameter than the sliding ring.
  • the sliding ring in the region of its sealing surface has a larger diameter than the counter ring.
  • a compressor preferred, which is characterized in that the seal ring is rotatably coupled to the drive shaft, wherein the counter-ring is rotatably coupled to a housing of the compressor. During operation of the compressor, the mating ring then remains fixed in space, while the sliding ring rotates together with and synchronously with the drive shaft in the compressor housing. The sealing surface of the sliding ring rubs on the sealing surface of the counter ring.
  • a first coupling device is provided, through which the sliding ring is rotatably coupled to the drive shaft. It is provided a second coupling means by which the counter-ring is rotatably coupled to the housing.
  • the sliding ring is rotatably mounted together with the drive shaft, wherein the counter-ring is rotatably coupled to a housing of the compressor, and wherein the counter-ring in the region of the sealing surface has a larger diameter than the sliding ring.
  • An embodiment of the compressor is preferred, which is characterized in that the sliding ring is biased with its sealing surface against the sealing surface of the mating ring.
  • a spring element is preferably provided which urges the sliding ring against the mating ring.
  • the spring element acts on the counter ring and urges it against the seal ring.
  • the bias advantageously causes an increased sealing effect in the region of the sealing surfaces, in particular with respect to the gaseous refrigerant under normal conditions.
  • the radial groove is formed to open edge to a peripheral surface of the sealing element.
  • this embodiment has very favorable lubricating and cooling properties for the sealing gap.
  • the radial groove - seen in plan view - is formed substantially rectangular.
  • the radial groove is rectangular.
  • it extends with a long side of the rectangle parallel to the radial direction, that is, has radially inward.
  • a substantially rectangular or rectangular radial groove is particularly easy to introduce into the sealing surface, in particular by sintering without mechanical processing.
  • the substantially rectangular or rectangular radial groove preferably has rounded corners, in particular two radially inwardly pointing, rounded corners on a narrow side of the rectangle, because this optimally exploits the advantages of the sintering method, with no need for mechanical reworking.
  • rounded corners are manufacturing technology in the sintering process, especially for ceramic materials, easier to produce than sharp-edged corners, especially in the radially inner region of the radial groove.
  • a bottom surface of the radial groove also passes over rounded areas in wall surfaces thereof.
  • the radial groove - seen in plan view - is formed schaufeiförmig.
  • the top view responds to a viewing direction along the axial direction on the sealing surface.
  • the shovel-shaped radial groove preferably has transverse to the radial direction curved wall surfaces.
  • the shovel-shaped radial groove opens radially outward. This indicates that a - perpendicular to Measured radial direction - width of the radial groove increases with increasing radial distance to the longitudinal axis of the drive shaft.
  • the blade shape of the radial groove supports in a particularly suitable manner a promotion of the lubricant in the radial groove to the sealing gap, ie radially inward.
  • the lubricant is deflected in particular by the curved wall surfaces, so that its tangential movement is deflected very efficiently into a radially inwardly directed movement, whereby the efficiency of the cooling and lubrication of the sealing gap is further improved.
  • the compressor which is characterized in that the radial groove extends - seen in the radial direction - up to the sealing gap. In this way, it is ensured that lubricant, which enters the radial groove, is conveyed up to the sealing gap, where it can efficiently cool and lubricate it.
  • the radial groove - in the radial direction - partially hineinerstreckt in the sealing gap.
  • the diameter of the sealing surface of that sealing element having the smaller diameter at least increased by the amount by which the radial groove in the sealing gap extends into it.
  • the sealing effect remains radial within the radial groove, although at the same time a particularly efficient delivery of the lubricant to the sealing gap and even partially into it is achieved, which increases its cooling and lubricating effect.
  • an embodiment of the compressor is preferred, which is characterized in that a plurality of radial grooves in the sealing surface is provided.
  • a plurality of radial grooves in the sealing surface is provided.
  • four, six, eight, ten or twelve radial grooves are provided, particularly preferably eight radial grooves.
  • the radial grooves are preferably - seen in the circumferential direction - arranged symmetrically distributed. This means in particular, that the radial grooves - seen in the circumferential direction - in pairs equal angular distances from each other, or that they are arranged distributed uniformly over the circumference of the sealing element.
  • a plurality of radial grooves increases the efficiency of the cooling and lubrication of the sealing gap, wherein a symmetrical arrangement on the one hand from the manufacturing point of view is advantageous and on the other hand ensures a particularly uniform cooling and lubrication along the circumferential direction.
  • Figure 1 is a schematic partial sectional view of an embodiment of a compressor
  • Figure 2a is a representation of a first embodiment of a sealing element in plan view
  • FIG. 2b shows a sectional view of the sealing element along the line A-A according to FIG. 2a), and FIG. 3 shows a view of a second exemplary embodiment of a sealing element in plan view.
  • the compressor 1 which is designed for compression of a gaseous refrigerant under normal conditions and for use in a power-heat engine, has a drive shaft 3, which is rotatably mounted about an axis of rotation D for driving the compressor. In this case, only a partial section of the compressor 1 is shown above the axis of rotation D in FIG. It is a drive shaft 3 encompassing sealing means 5 is provided which has exactly two sealing elements, namely a sliding ring 7 and a counter ring 9.
  • the sliding ring 7 has a first sealing surface 1 1, wherein the counter-ring 9 has a second sealing surface 13.
  • the sliding ring 7 is pressed by a spring element 15 against the counter ring 9, so that the sealing surfaces 1 1, 13 in the region of a sealing gap 17 are close to each other.
  • the sealing gap 17 is defined by the region in which the sealing surfaces 1 1, 13 rest against each other and are pressed firmly against each other.
  • the sliding ring 7 is rotatably coupled to the drive shaft 3 and therefore rotates during operation of the compressor 1 together with this and synchronous to it about the rotation axis D. Furthermore, the slide ring 7 is sealed relative to the drive shaft 3 by a first O-ring seal 19.
  • the counter-ring 9 is rotatably coupled to a housing 21 of the compressor 1, so that it is arranged fixed in space in any case relative to the housing 21 during operation of the compressor 1 anyway. Furthermore, the counter-ring 9 is sealed relative to the housing 21 by a second O-ring seal 23.
  • the sliding ring 7 is rotatably coupled via a first coupling means, not shown, with the drive shaft 3, wherein the counter-ring 9 is rotatably coupled via a second coupling means, not shown, with the housing 21.
  • a centrifugal lubrication device 25 is provided, via which lubricant for cooling and lubrication can be fed to the sealing gap 17 in a manner known per se during operation of the compressor along an arrow P.
  • the counter-ring 9 has a larger diameter than the sliding ring 7. This makes it possible to lug the sealing surface 13 of the counter-ring 9 very smoothly with high quality and goodness, resulting in a particularly good sealing effect in the region of the sealing gap 17 is achieved.
  • the sealing surface 11 of the sliding ring 7 is not or preferably only used to a limited extent. lent their diameter larger than that of a conventional
  • At least one radial groove is introduced into the sealing surface 13 of the counter ring 9, which extends in the direction of the sealing gap 17.
  • FIG. 2a shows a first embodiment of a sealing element, in this case specifically the counter-ring 9 in plan view of the sealing surface 13.
  • the same and functionally identical elements are provided with the same reference numerals, so reference is made to the preceding description.
  • the counter ring 9 has a central bore 27, through which the drive shaft 3 extends in the assembled state.
  • the exemplary embodiment of the mating ring 9 illustrated here has eight radial grooves, of which only one is designated by the reference numeral 29 for the sake of better clarity. It can clearly be seen that the radial grooves 29, starting from a peripheral surface 31 of the counter ring 9, extend inwards and thus towards the sealing gap 17, as viewed in the radial direction.
  • the radial grooves 9 are formed in the illustrated embodiment rectangular with rounded corners 33. From the illustration according to FIG. 2 a) it is also clear that bottom surfaces 35 of the radial grooves 29 merge over curved regions in wall surfaces 37. In this case, the rectangular radial grooves 29 extend in the radial direction and are thus aligned with the axis of rotation D. It can also be seen that the eight radial grooves 29 are distributed symmetrically along the circumferential direction.
  • Figure 2b shows a sectional view of the embodiment of the counter-ring 9 according to Figure 2a) along the line A-A.
  • Identical and functionally identical elements are provided with the same reference numerals, so that reference is made to the preceding description. It is particularly clear that a depth t of the radial grooves 29 is preferably at least 5% to at most 20%, preferably at least 10% to at most 15%, particularly preferably 13% of a thickness d of the counter-ring 9.
  • Figure 3 shows a representation of a second embodiment of a sealing element, in this case specifically of the counter-ring 309 in plan view.
  • Identical and functionally identical elements are increasingly represented by the reference numbers used previously by 300, as far as the modified embodiment of the counter-ring 309 is concerned.
  • the same and functionally identical elements are denoted by identical reference numerals. Reference is made in this regard to the preceding description.
  • the mating ring 309 eight radial grooves 329 which, however, in contrast to the embodiment of the mating ring 9 according to Figure 2 - seen in plan view - are formed schaufeiförmig.
  • the radial grooves 329 have curved wall surfaces 337 transverse to the radial direction.
  • a width b namely a distance between opposite wall surfaces 337 of the radial grooves 329 becomes larger with increasing radial distance to the rotation axis D.
  • the radial grooves 329 thus open outwards to the circumferential surface 331. It is shown that the radial grooves 329 shown in FIG. 3 are particularly suitable, owing to their snow-shrouded geometry, for efficiently guiding the lubricant to the sealing gap 17.
  • the radial grooves 29, 329 effect a deflection of the lubricant impinging on the sealing surface 13 and / or the peripheral surface 31, 331 and in particular a deflection of the tangential movement of the lubricant in a radially inwardly directed movement to the sealing gap 17.
  • the radial grooves 29, 329 results in a counteraction to the rotation-induced centrifugal effect.
  • the radial grooves 29, 329 to improve the reliability of the compressor 1, to an improved heat dissipation from the region of the sealing gap 17 and to an improved tightness of the sealing device 5 at.
  • the radial grooves 29, 329 also reduce the use of material in the area of the sealing device 5.
  • the compressor 1 in particular due to the particularly flat sealing surface 13 has a sealing device 5 with increased sealing effect, at the same time efficient cooling and lubrication of the sealing gap 17 is ensured by the radial grooves 29, 329.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Compressor (AREA)
  • Mechanical Sealing (AREA)

Abstract

L'invention concerne un compresseur (1) pour une machine de cogénération, adapté pour comprimer un fluide frigorigène sous forme gazeuse en conditions normales, comprenant un arbre d'entraînement (3) et un dispositif d'étanchéité (5) entourant l'arbre d'entraînement (3) et comportant deux éléments d'étanchéité, à savoir une bague coulissante (7) et une contre-bague (9, 309), lesquelles sont placées de manière étanche l'une contre l'autre avec chacune une surface d'étanchéité (11, 13, 313) de manière à former un espace étanche (17) entre les surfaces d'étanchéité (11, 13, 313). Selon l'invention, un système de lubrification à force centrifuge (25) est prévu pour lubrifier le dispositif d'étanchéité (5). Le compresseur (1) est caractérisé en ce qu'un des éléments d'étanchéité (7, 9, 309) comporte un diamètre plus grand au niveau des surfaces d'étanchéité (11, 13, 313) que l'autre élément d'étanchéité (7, 9, 309), l'élément d'étanchéité (7, 9, 309) de plus grand diamètre comportant dans sa surface d'étanchéité (11, 13, 313) au moins une rainure radiale (29, 329) qui s'étend en direction de l'espace étanche (17).
PCT/EP2014/075716 2013-12-20 2014-11-26 Compresseur pour machine de cogénération WO2015090881A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112014005773.8T DE112014005773A5 (de) 2013-12-20 2014-11-26 Kompressor für eine Kraft-Wärme-Maschine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013114629.5 2013-12-20
DE102013114629 2013-12-20

Publications (1)

Publication Number Publication Date
WO2015090881A1 true WO2015090881A1 (fr) 2015-06-25

Family

ID=52014031

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2014/075716 WO2015090881A1 (fr) 2013-12-20 2014-11-26 Compresseur pour machine de cogénération

Country Status (2)

Country Link
DE (1) DE112014005773A5 (fr)
WO (1) WO2015090881A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015217448A1 (de) * 2015-09-11 2017-03-16 Magna Powertrain Bad Homburg GmbH Kompressor mit Axiallager
CN110573774A (zh) * 2017-05-19 2019-12-13 伊格尔工业股份有限公司 滑动部件

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1024319A2 (fr) * 1999-01-27 2000-08-02 FEODOR BURGMANN DICHTUNGSWERKE GmbH & Co. Garniture mécanique d'étanchéité pour compresseur frigorifique de véhicule autombile utilisant du CO2 comme fluide frigorigène
WO2001011276A1 (fr) 1999-08-06 2001-02-15 Luk Fahrzeug-Hydraulik Gmbh & Co.Kg Compresseur au co¿2?
US20090096175A1 (en) * 2007-10-11 2009-04-16 Kaco Gmbh & Co. Kg Seal Arrangement, Especially for High Pressure Applications, Preferably for Use In CO2 Compressors
WO2010049077A1 (fr) * 2008-10-31 2010-05-06 Kaco Gmbh + Co. Kg Garniture mécanique d'étanchéité
DE102010024289A1 (de) * 2010-04-23 2011-10-27 Carl Freudenberg Kg Gleitringdichtung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1024319A2 (fr) * 1999-01-27 2000-08-02 FEODOR BURGMANN DICHTUNGSWERKE GmbH & Co. Garniture mécanique d'étanchéité pour compresseur frigorifique de véhicule autombile utilisant du CO2 comme fluide frigorigène
WO2001011276A1 (fr) 1999-08-06 2001-02-15 Luk Fahrzeug-Hydraulik Gmbh & Co.Kg Compresseur au co¿2?
US20090096175A1 (en) * 2007-10-11 2009-04-16 Kaco Gmbh & Co. Kg Seal Arrangement, Especially for High Pressure Applications, Preferably for Use In CO2 Compressors
DE102007050349A1 (de) * 2007-10-11 2009-04-23 Kaco Gmbh + Co. Kg Dichtungsanordnung, insbesondere für den Hochdruckbereich, vorzugsweise für den Einsatz bei CO2-Kompressoren
WO2010049077A1 (fr) * 2008-10-31 2010-05-06 Kaco Gmbh + Co. Kg Garniture mécanique d'étanchéité
DE102010024289A1 (de) * 2010-04-23 2011-10-27 Carl Freudenberg Kg Gleitringdichtung

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015217448A1 (de) * 2015-09-11 2017-03-16 Magna Powertrain Bad Homburg GmbH Kompressor mit Axiallager
CN110573774A (zh) * 2017-05-19 2019-12-13 伊格尔工业股份有限公司 滑动部件
CN110573774B (zh) * 2017-05-19 2022-06-17 伊格尔工业股份有限公司 滑动部件

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