• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    In order to reduce the sealing medium leakage in a sealing arrangement (1) consisting of two sealing elements (8), which are pressed by a sealing medium against the piston rod (3) and against a wall (11) of a recess (1 0), it is provided that the radially inner circumferential surface (24) of at least one of the sealing elements (8) consists of a sealing surface (12) and a draw-in surface (23), to the sealing surface (12) a second, the axial end (11) of the recess (1 0) facing away from end face (21) adjoins and bezel cover ring (9) is provided, which rests at least partially radially on the radially outer peripheral surface (25) of the sealing element (8) and at least partially axially on the second end face (21) of the sealing element (8).
    公开号:AT513495A4
    申请号:T50548/2012
    申请日:2012-11-28
    公开日:2014-05-15
    发明作者:Martin Lagler；Christian Hold；Alexander Jandl；Tino Dr Lindner-Silwester；Alexander Loedl
    申请人:Hoerbiger Kompressortech Hold；
    IPC主号:
    专利说明:

    825 AT
    Sealing arrangement for sealing a reciprocating piston rod of a reciprocating compressor
    The subject invention relates to a sealing arrangement for sealing a reciprocating piston rod of a reciprocating compressor with a first and second sealing element, which are arranged axially spaced in a recess of the sealing arrangement, wherein the sealing elements with a first end face at one axial end of the recess and with a Sealing surface are arranged adjacent to the piston rod and in the sealing arrangement, a supply line is provided for a sealing medium, which is connected to the recess.
    In a reciprocating compressor, the high pressure space, e.g. the working pressure in the cylinder of the compressor, in relation to a space with low pressure, e.g. the atmospheric pressure in the crankcase of the compressor to seal along the piston rod. For this purpose, so-called sealing packs are used in known manner, which seal between the reciprocating piston rod of the reciprocating compressor and a fixed machine part, usually the compressor housing. As a rule, such a sealing packing comprises a plurality of packing rings or packing ring combinations arranged axially one behind the other. Most commonly, combinations of a radially cut and a tangentially cut packing ring are used, such as e.g. from EP 1 146 264 A2. In addition, segmented ring designs in which a packing ring is composed of a plurality of ring segments are also used, such as e.g. from US 4 350 349 A known. However, such seals are not 100% dense systems, but always have some leakage amount of the working medium of the compressor, which escapes through the seal.
    In order to reduce the problem of leakage, it has already been proposed in WO 2010/079227 A1 to use as a seal two axially spaced sealing elements, between which a sealing medium, e.g. Oil is introduced at high pressure, whereby the sealing elements are pressed to seal against intended sealing surfaces in the packing and against the piston rod. In this way, a sealing medium barrier is provided which reduces the leakage of the working medium of the compressor, e.g. Air or natural gas, along the piston rod at least reduced, ideally and even eliminated. However, leakage of the sealing medium between the sealing element and the piston rod can occur, mainly due to the sealing medium film which adheres to the surface of the reciprocating piston rod and is thus transported out of the seal and stripped off. Since the sealing element is made of a tribologically favorable material, usually made of a plastic, it can in operation due to the acting pressure differences 2/12
    825 AT and the geometry of the sealing element also come to deformations of the sealing element, which adversely affects the sealing surface or the sealing edge of the sealing element and thus increases the sealing medium leakage. This seal medium leakage should desirably be as low as possible.
    It is therefore an object of the subject invention to provide a sealing arrangement of the above type, with which the sealing medium leakage can be effectively reduced by the seal.
    This is achieved with a sealing element of a seal, in which the radially inner circumferential surface of at least one of the sealing elements and the feed surface is composed, wherein the sealing surface is followed by a second, the axial end of the recess facing away from the end face of the sealing element and further a rigid Cover ring is provided which rests at least partially radially on the radially outer circumferential surface of the sealing element and at least partially axially on the second end face of the sealing element. Characterized in that the cover ring axially and radially on the second end face of the sealing element, which adjoins the sealing surface of the sealing element, fitting, the cover ring engages actively in the deformation of the sealing edge or the forming sealing gap between the sealing element and the piston rod and supports the sealing edge. Due to the reciprocating movement of the piston rod, sealing medium is drawn into the sealing gap, as a result of which pressure builds up in the sealing gap, which will widen the sealing element radially. By the cover ring on the one hand, the sealing gap by the reciprocating movement of the piston rod and the adhering thereto sealing medium film does not open-wide, which would lead to increased sealing medium leakage through the seal. On the other hand, the cover ring also supports the sealing element against occurring Stülpmomente trying to deform the sealing element, which would also adversely affect the sealing edge or the sealing gap and also would increase the seal medium leakage through the seal.
    An L-shaped cover ring is simple and can be advantageously made compact. For low frictional forces or frictional losses and small sealing medium leaks, it has been found to be particularly advantageous if the cover ring bears axially on the sealing element at a part of the radial height of the sealing element, preferably at least 35% to at most 85% of the radial height, or the sealing surface extends over a maximum of 50% of the axial width of the sealing element, or the feed surface is inclined relative to the sealing surface by a maximum of 4 °, or the second end face of the sealing element is inclined relative to the sealing surface by at least 75 °, or the cover ring at least 25% to maximum 100% of the axial width of the radially outer circumferential surface of the Dichtele-3/12
    825 AT ment is attached to this. Especially advantageous is a sealing element-cover ring combination that meets all, or at least several of the above features.
    In order to avoid deformation of the sealing element caused by extrusion of the sealing element into the gap between the chamber disc and the piston rod, a support ring is advantageously arranged between the axial end of the recess and the sealing element, on which the sealing element is arranged axially adjacent.
    Most preferably, the support ring bears radially on the outside on an axial shoulder facing the sealing element. In this way it can be prevented that the support ring touches the piston rod. The subject invention will be explained in more detail below with reference to schematic, non-limiting and advantageous embodiments of the invention facing Figures 1 and 2. It shows
    1 is a sealing arrangement according to the invention and
    2 shows a detailed view of a sealing element of a sealing arrangement according to the invention. FIG. 1 shows a sealing arrangement 1 according to the invention for sealing an axially reciprocating piston rod 3 of a reciprocating compressor against a pressure difference pd-pa to be sealed, a working medium, e.g. the difference of cylinder pressure pd and pressure in the crankcase pat, shown. The sealing arrangement 1 is arranged in a stationary housing part 2 of the compressor and seals between this housing part 2 and 20 of the moving piston rod 3.
    In the example shown, the sealing arrangement 1 comprises two L-shaped chamber disks 4, 5, which are separated axially by a separating disk 6 in the exemplary embodiment shown. The L-shaped chamber discs 4, 5 and the cutting disc 6 are arranged axially adjacent to each other and radially spaced from the piston rod 3, to prevent the piston rod 25 from rubbing against the chamber discs 4, 5 or the separating disc 6 and around one Mobility of the piston rod 3 transverse to the stroke movement (indicated by the double arrow) to allow. In the simplest case, the cutting disc 6 but also be omitted. However, other embodiments, e.g. with T-shaped cutting discs, conceivable. On a chamber disc 5, a flange can be provided radially outward, with-30 tels the sealing assembly 1 can be attached to the housing part 2. The chamber discs 4, 5 and optionally the cutting disc 6 can be held together in a known manner by a continuous bolt. By this arrangement, between the L-shaped chamber discs 4, 5, optionally the cutting disc 6 and the piston rod 3, two recesses 10, in each of which a sealing element 8 is arranged. 4.12
    825 AT
    In principle, however, only one sealing element could be provided in one of the recesses 10 or the sealing elements 8 could also be designed differently. The sealing element 8 is designed as a one-piece, uncircular in the circumferential direction sealing ring and is by the effective pressure of a supplied into the recess 10, pressurized sealing medium respectively at the axial ends 11 of the recess 10, ie at the radial limbs of the L-shaped chamber discs. 4 , 5, pressed (the orientations "axial" and "radial" are based on the orientation of the piston rod 3). The sealing elements 8 are spaced apart radially from the chamber discs 4, 5, that is to say from the axial limbs of the chamber discs 4, 5, and bear against the piston rod 3 radially inwards with a sealing surface 12 extending in the axial direction. On the sealing elements 8 is located radially and axially a rigid, undivided, e.g. metallic, cover ring 9, as will be explained below with reference to Figure 2 in detail.
    Between the cover ring 9 and an axial stop in the seal 1, here e.g. the cutting disc 6, may also be a spring element 14, e.g. a plurality of circumferentially distributed coil springs, be arranged, which biases the cover ring 9 and thus the sealing element 8 axially in the direction of the axial end 11 of the recess 10. The two sealing elements 8 are consequently pushed apart by the spring element 14. This can be ensured, especially at standstill, a defined position of the sealing element 8, whereby the seal 1 and the compressor can be safely started.
    In the sealing arrangement 1, a supply line 7 is further provided, which is connected to the recess 10 and via which a sealing medium, such. an oil, under a pressure ροΝ, which is greater than the pressure to be sealed pd, or in certain embodiments at least greater than the suction pressure of the compressor, can be supplied into the recess 10. In the case of a dynamically changing working pressure pd, of course, p0H > pd, max, or the pressure of the sealing medium is dynamically adapted to the working fluid pressure, so that p0H > pd. The sealing medium acts radially outward and axially on the sealing elements 8 and the cover rings 9, which are thus pressed radially inwardly to the piston rod 3 and axially to the chamber discs 4, 5 and thus seal. This creates a sealing medium barrier, which prevents leakage of the gaseous working medium of the compressor to be sealed along the piston rod 3.
    2, a sealing element 8 is shown enlarged in an advantageous embodiment. In addition, an optional support ring 13 is arranged in FIG. 2 between the sealing element 8 and the axial end 11 of the recess 10, against which the sealing element 8 abuts axially with a first end face 20. The support ring 13 abuts axially against the chamber disk 4. As already described above for Fig.1, the support ring 13 may also be omitted, whereby the sealing element 8 with the 5/12
    825 AT first end face 20 axially directly at the axial end 11 of the recess 10, so here on the chamber disk 4, would rest.
    The sealing element 8 has a radially inner peripheral surface 24, which is composed of a sealing surface 12 and an adjoining feed surface 23. The sealing surface 12 is provided on the first end face 20 facing away from the axial end of the sealing element 8. The feed surface 23 is inclined at an angle α relative to the sealing surface 12 and preferably connects the sealing surface 12 with the first end face 20. The first end face 20 opposite the second axial end face 21 of the sealing element 8 is arranged at an angle ß relative to the sealing surface 12 inclined and preferably connects to the sealing surface 12. The edge between the sealing surface 12 and the second end face 21 forms the sealing edge 22.
    The sealing element 8 thus rests only on the small sealing surface 12 on the piston rod 3, against which it is pressed at high pressure (p0ii). This results in high frictional loads, which the sealing element 8 must withstand for a sufficiently long time. The sealing element 8 is therefore preferably made of a tribologically favorable, but at the same time mechanically high-strength and temperature-stable material, preferably plastic, such as. modified PEEK or PPS materials. On the sealing element 8 and the cover ring 9 act thereby by the pressure ροΝ the sealing medium forces that presses the sealing element 8 against the chamber disc 4 and the support ring 13 and with the sealing surface 12 against the piston rod 3. As a result, frictional forces of a few hundred Newtons, typically between 100 N and 250 N, and friction losses of a few hundred W, typically between 500 W and 1000 W, can occur at a sealing medium pressure p0H of approximately 50 bar between sealing element 8 and piston rod 3. Due to these forces and the geometry of the sealing element 8 but also impact torque Ms act on the sealing element 8, trying to deform the sealing element 8. In particular, the very small sealing surface 12 and the sealing edge 22 is very sensitive to it and such Stülpmomente Ms may interfere with the contact between the piston rod 3 and the sealing surface 12, whereby the sealing medium leakage would rise. In order to reduce or prevent this, the cover ring 9 is provided, which bears axially on the front second end face 21 of the sealing element 8, which adjoins the sealing surface 12 and the sealing edge 22 thus supports against deformation, so that they do not or only slightly deform. For this purpose, the cover ring 9 is partly on the height hd on the sealing element 8, wherein the height hd is advantageously at least 35% to 85% of the height hr of the sealing element 8.
    Likewise, it has been found that the sealing element 8 can expand radially during operation, in particular at repeated start / stop operation of the compressor, at start / stop of the sealing medium supply system or during start-up operation, when the sealing element only 6/12
    825 AT, which of course would also increase the Dichtmediumleackage. To prevent this, the cover ring 9 covers the sealing element 8 in the axial direction also on the radially outer peripheral surface 25. For this purpose, the cover ring 9 is along a length ld on the outer peripheral surface 25, wherein the length ld advantageously at least 25% to 100% 5 is the width bra of the sealing element 8 on the outer peripheral surface 25. This results in an L-shaped cross section of the cover ring 9. For a favorable operation of the sealing element 8, ie for low frictional forces or friction losses and a small sealing medium leakage, it has further proved to be advantageous if the angle a <4 °, but larger Zero, and the angle β> 75 °, wherein also angles greater than 10 90 ° are conceivable, is selected. Likewise, it is advantageous if the length ls the
    Sealing surface 12 is at most 50% of the width bri of the sealing element 8 on the inner peripheral surface 24.
    The support ring 13 can radially outside have an axial, the sealing element 8 facing shoulder 26, via which the support ring 13 bears radially on the sealing element 8 to prevent 15 that the support ring 13, which is typically made of a metal, in contact with the Piston rod 3 can get advised. In this case, the cover ring 9 is preferably along a length ld of at least 25% to 75% of the width bra of the sealing element 8 on the outer peripheral surface 25 in order to make room for the shoulder 26. The support ring 13 prevents known manner that the sealing element 8 is extruded due to the acting pressure difference in the gap 20 between chamber disk 4 and piston rod 3, which could adversely affect the function of the sealing element 8. 7/12
    权利要求:
    Claims (9)
    [1]
    A sealing arrangement for sealing a reciprocating piston rod (3) of a reciprocating compressor with a first and second sealing element (8) which are arranged axially spaced in a recess 5 (10) of the sealing arrangement (1) the sealing elements (8) are arranged with a first end face (20) on one axial end (11) of the recess (10) and with a sealing surface (12) on the piston rod (3) and in the sealing arrangement (1) a feed line ( 7) is provided for a sealing medium, which is connected to the recess (10), characterized in that the radially inward-10 the peripheral surface (24) at least one of the sealing elements (8) from the sealing surface (12) and a feed surface (23) that a second, the axial end (11) of the recess (10) facing away from the end surface (21) connects to the sealing surface (12) and that a rigid cover ring (9) is provided which at least partially radially to the radia L outer peripheral surface (25) of the sealing element (8) and at least partially axially against the second end-15 surface (21) of the sealing element (8).
    [2]
    2. Sealing arrangement according to claim 1, characterized in that the cover ring (9) is L-shaped.
    [3]
    3. Sealing arrangement according to claim 1, characterized in that the cover ring (9) on a part (hd) of the radial height (hr) of the sealing element (8), preferably at least 20 35% to a maximum of 85% of the radial height (hr) , abuts axially on the sealing element (8).
    [4]
    4. Sealing arrangement according to claim 1, characterized in that extending the sealing surface (12) over a length (ls) of at most 50% of the axial width (bri) of the radially inner peripheral surface (24) of the sealing element (8).
    [5]
    5. Sealing arrangement according to claim 1, characterized in that the feed surface 25 (23) relative to the sealing surface (12) is inclined by a maximum of 4 °.
    [6]
    6. Sealing arrangement according to claim 1, characterized in that the second end face (21) of the sealing element (8) relative to the sealing surface (12) is inclined by at least 75 °.
    [7]
    7. Sealing arrangement according to claim 1, characterized in that the cover ring (9) 30 at least 25% to a maximum of 100% of the axial width (bra) of the radially outer peripheral surface (25) of the sealing element (8) abuts against this. 8/12 825 AT
    [8]
    8. Sealing arrangement according to one of claims 1 to 6, characterized in that between the axial end (11) of the recess (10) and the sealing element (8), a support ring (13) is arranged, on which the sealing element (8) axially adjacent is arranged.
    [9]
    9. Sealing arrangement according to claim 8, characterized in that the support ring (9) 5 radially outside a the sealing element (8) facing the axial shoulder (26) which is arranged radially outwardly on the sealing element (8) fitting. 12.9
    类似技术:
    公开号 | 公开日 | 专利标题
    EP2376819B2|2017-10-11|Sealing arrangement for sealing a piston rod of a reciprocating compressor
    AT513495B1|2014-05-15|Sealing arrangement for sealing a reciprocating piston rod of a reciprocating compressor
    EP2078887B1|2011-02-23|Gas-proof piston ring assembly
    EP2489907B1|2016-03-23|Seal for a moving piston rod of a piston compressor
    EP2360400B1|2013-04-03|Stripping assembly and compressor with such a stripping assembly
    AT505550B1|2009-02-15|MULTIPLE PACKING RING
    DE60007513T2|2004-11-11|SHAFT SEAL
    AT514335B1|2014-12-15|Sealing arrangement for sealing a reciprocating piston rod of a reciprocating compressor
    AT505293B1|2008-12-15|PACKING RING COMBINATION
    AT513836B1|2014-08-15|Compressor with and method for flushing the compressor housing with purge gas
    DE202018102291U1|2018-08-02|sealing unit
    DE112015001071T5|2016-12-08|oil control ring
    DE102016013638B4|2019-05-02|Sealing arrangement and its use
    AT504522B1|2008-06-15|Sealing arrangement for sealing a housing part relative to a moving part with two sealing rings and a protective ring useful in compressor technology ensures uniform sealing ring wear combined with good sealing action
    DE102020106646B3|2020-11-26|Seal arrangement and its use
    DE4491133B4|2004-04-01|Uniformly compressible gland seal
    DE102018108655A1|2018-11-15|Piston assembly for a slave cylinder with encompassing seal
    EP2131079B1|2012-08-15|Radial shaft sealing system
    DE102016005035A1|2017-11-02|Sealing ring, sealing arrangement with the sealing ring and use of sealing ring and seal assembly
    DE102014223606A1|2015-06-18|Slave cylinder housing and release device with cooling channel
    EP2151610A1|2010-02-10|Rotary shaft lip seals with swellable excluder lips
    AT504864A1|2008-08-15|CUTTED PACK RING
    同族专利:
    公开号 | 公开日
    JP2014105876A|2014-06-09|
    CN103850914A|2014-06-11|
    AT513495B1|2014-05-15|
    EP2738430A1|2014-06-04|
    US20140145403A1|2014-05-29|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2853020A|1955-08-10|1958-09-23|Fuller Co|Shaft seal|
    DE1425523A1|1962-04-25|1969-05-29|Nat Res Dev|Shaft seal|
    WO2007124830A1|2006-04-28|2007-11-08|Andritz Ag|Sealing arrangement|
    AT510171A4|2011-02-17|2012-02-15|Hoerbiger Kompressortech Hold|SEALING PACK FOR A ROLLING PISTON ROD OF A PISTON COMPRESSOR|
    GB2185542B|1985-07-13|1988-05-25|Crane Packing Ltd|Gas tight seal|
    AT507564B1|2009-01-12|2010-06-15|Hoerbiger Kompressortech Hold|SEAL ASSEMBLY FOR SEALING A PISTON ROD OF A PISTON COMPRESSOR|
    AT508782B1|2010-02-15|2011-04-15|Hoerbiger Kompressortech Hold|CIRCUIT ARRANGEMENT AND COMPRESSOR WITH SUCH A CUT-OFF ARRANGEMENT|
    AT514335B1|2013-07-10|2014-12-15|Hoerbiger Kompressortech Hold|Sealing arrangement for sealing a reciprocating piston rod of a reciprocating compressor|CN106704586B|2017-02-28|2018-04-10|中冶华天南京工程技术有限公司|For changing the sealing device of sealing ring tankful rate|
    JP6993103B2|2017-04-28|2022-01-13|Nok株式会社|Ring dust strip and sealing device|
    US11255319B2|2019-03-09|2022-02-22|Neo Mechanics Limited|Shaft-cylinder assembly for high temperature operation|
    DE102019206215A1|2019-04-30|2020-11-05|Technische Universität Dresden|Seal arrangement for reciprocating compressors|
    CN113257614A|2021-04-25|2021-08-13|西安交通大学|Vacuum arc-extinguishing chamber capable of being used in high-pressure environment|
    法律状态:
    2018-07-15| MM01| Lapse because of not paying annual fees|Effective date: 20171128 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50548/2012A|AT513495B1|2012-11-28|2012-11-28|Sealing arrangement for sealing a reciprocating piston rod of a reciprocating compressor|ATA50548/2012A| AT513495B1|2012-11-28|2012-11-28|Sealing arrangement for sealing a reciprocating piston rod of a reciprocating compressor|
    EP13189256.4A| EP2738430A1|2012-11-28|2013-10-18|Sealing assembly for sealing a reciprocating piston rod of a reciprocating compressor|
    US14/088,578| US20140145403A1|2012-11-28|2013-11-25|Seal Arrangement for Sealing a Reciprocating Piston Rod of a Piston Compressor|
    CN201310612706.9A| CN103850914A|2012-11-28|2013-11-27|Seal Arrangement for Sealing a Reciprocating Piston Rod of a Piston Compressor|
    JP2013246081A| JP2014105876A|2012-11-28|2013-11-28|Seal device for sealing reciprocation piston rod of piston compressor|
    [返回顶部]