• 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 support ring (11), it is provided that the sealing element (8) only over a part of the radial height of the sealing element (8) abuts axially on the support ring (11) to reduce the contact surface (25) between the sealing element (8) and support ring (11) in the radial direction.
    公开号:AT514335A4
    申请号:T504492013
    申请日:2013-07-10
    公开日:2014-12-15
    发明作者:Christian Hold；Alexander Loedl；Alexander Jandl；Tino Dr Lindner-Silwester；Matthias Dr Kornfeld
    申请人:Hoerbiger Kompressortech Hold；
    IPC主号:
    专利说明:

    827 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 sealing 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, this may lead to a leakage of sealing medium between the sealing element and piston rod, mainly due to the sealing medium film adhering to the surface of the reciprocating piston rod and thus transported from the seal and stripped at the opposite stroke of the piston rod. Since the sealing element is made of a tribologically favorable material, usually made of a plastic, it can in 2/151
    827 AT
    Operation due to the effective pressure differences 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 problem is addressed in sealing elements for larger diameter piston rods, e.g. 5 diameter greater 50mm, tightened, as the sealing elements are characterized soft. 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 sealing element abuts only axially over a part of the radial height of the sealing element on the support ring in order to reduce the contact area between the sealing element and the support ring in the radial direction. Due to the reduced contact surface between the support ring and sealing element, the effective surface pressure between the two components is increased, whereby a reliable Abis seal against the acting high pressure of the sealing medium is effected on this surface by a lifting of the sealing element is prevented by the support ring. Thereby, the sealing medium leakage can be effectively reduced by the sealing arrangement.
    The contact surface can be produced in different ways, wherein the different structural features can also be used in combination. For example, may be 20 provided in the first end face of a sealing element and / or in the sealing element facing end face of the support ring a gradation. Or it may be provided as a step a recess in the first end face of the sealing element or a recess in the facing end face of the support ring.
    It is advantageous if the recess is provided in the radially central region of the sealing element 25, because then the contact surface is formed in the radially outer region of the sealing element, which is favorable in terms of deformation of the sealing element and thus for the sealing effect. For this purpose, the recess may also extend from the radially central region of the sealing element to a draw-in surface which connects the sealing surface to the first end face, which leads to a contact surface only in the radially outer region. If the sealing element is designed to be radially widened radially inward, a sufficient length of the feed surface can be ensured, whereby wear on the sealing surface does not impair the function of the sealing element.
    Likewise, it is possible for the production of the contact surface, to provide a gradation of a widening of the sealing element and on the support ring on the sealing element facing 3/152 '
    827 AT
    End face in the region of the broadening to provide a recess. For the deformation of the sealing element and for its sealing effect, it is particularly advantageous if the contact surface is formed in the radially outer region of the first end face of the sealing element. For this purpose, it can be provided that a gap is formed radially inward between the sealing element and the support ring.
    If a recess is provided in the support ring, which connects the annular gap between the seal assembly and piston rod with the space between the support ring and sealing element, it is ensured that the high pressure of the sealing medium can not form in the space between the support ring and sealing element, resulting in unfavorable deformation of the Could lead sealing element and would be detrimental to the sealing effect.
    With a by a spring element axially biased spring ring which bears axially against a second end face of the sealing element, a defined position of the sealing element in the sealing arrangement can be ensured, whereby the sealing arrangement or the compressor can be safely raised.
    An undesirable radial expansion of the sealing element during operation of the compressor can be prevented if an axial shoulder is provided on the support ring and / or on the spring ring, which rests against the radially outer peripheral surface of the sealing element, whereby the radial expansion is blocked.
    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 to 4. It shows
    1 shows a sealing arrangement according to the invention,
    2 and 3 each show a detailed view of a sealing element of a device according to the invention
    Sealing arrangement and
    4 shows a view of a spring ring.
    In Fig. 1 is a sealing arrangement 1 according to the invention for sealing an axially reciprocating piston rod 3 of a reciprocating compressor against a pressure difference to be sealed pd - pat of a working medium of the compressor, 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 the moving piston rod 3. 4/153 '
    827 AT
    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 blade 6 are arranged axially adjacent to each other and radially spaced from the piston rod 3, to prevent the piston rod 3 from rubbing against the chamber discs 4, 5 and the cutting disc 6, and to a mobility of the To allow piston rod 3 transversely to the lifting movement (indicated by the double arrow). The orientations "axial" and "radial" are based on the orientation of the piston rod 3, ie axially in the direction of the longitudinal axis of the piston rod 3 and radially transversely thereto. In the simplest case, the cutting disc 6 but also be omitted. However, other embodiments, e.g. with T-shaped cutting discs or an L-shaped disc and a cylindrical disc, conceivable. On a chamber disk 5, a flange can also be provided radially on the outside, by means of which the sealing arrangement 1, e.g. distributed over the circumference arranged screws, can be attached to the housing part 2. The chamber discs 4, 5, and optionally the cutting disc 6 or other discs, can be held together in a known manner by means not shown, through bolts. By this arrangement arises between the L-shaped chamber discs 4, 5, optionally the cutting disc 6, and the piston rod 3 has a recess 10 in which two sealing elements 8 are arranged axially spaced.
    The sealing elements 8 are axially against support rings 11 and the support rings 11 are axially on the axial boundary wall of the recess 10, here at the radial leg of the chamber disk 4, 5, at. The support rings 11 prevent a possible by the high, acting on the sealing element 8 pressure inline extrusion of the sealing element 8 in the annular gap between chamber disc 4, 5 and piston rod. 3
    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 ρ0π, which is greater than the pressure to be sealed pd, 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 pressure of the working medium, so that poN > pd. The sealing medium acts radially outward and axially on the sealing elements 8, which are thus pressed radially inwardly against the piston rod 3 and axially against the support rings 11 and together with these against 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.
    The sealing element 8 is designed as a one-piece, circumferentially uncut sealing ring and is by the acting pressure poi | the supplied into the recess 10, pressurized sealing medium axially against the support ring 11 and together with the -4- 5/15
    827 AT
    Support ring 11 against the axial boundary wall of the recess 10, so here against the radial leg of the L-shaped chamber discs 4, 5, pressed. The sealing element 8 is radially outwardly spaced from the chamber discs 4, 5, that is arranged by the axial limbs of the chamber disc 4, 5, and is radially inward with a extending in the axial direction 5 sealing surface 12 on the piston rod 3 at.
    At the support ring 11 opposite axial end face of the sealing element 8, a spring ring 9 may rest against which a spring element 14 acts in the axial direction to axially bias the sealing element 8 against the boundary wall of the recess 10. The spring element 14 can between the spring ring 9 and an axial stop in the 10 sealing arrangement 1, hierz.B. the blade 6, be arranged. The spring element 14 is e.g. executed in the form of several, distributed over the circumference coil springs. Thus, the position of the sealing element 8 is defined at standstill of the reciprocating compressor to allow a controlled startup of the reciprocating compressor. The spring ring 9 can also rest over a shoulder on the radially outer circumferential surface of the sealing element 8, 15 set the radial position of the spring ring 9. The spring ring 9 is preferably as a rigid, undivided, e.g. metallic, executed ring, as will be described below with reference to Figure 4 for an advantageous embodiment in detail.
    In Figure 2, a sealing element 8 is shown in combination with the support ring 11 in an advantageous embodiment enlarged. The support ring 11 may radially outside a axial, the Dichtele-20 ment 8 facing shoulder 28, over which the support ring 11 radially abuts the sealing element 8, to prevent the support ring 11, which is typically made of a metal, radially shifts and may get in contact with the piston rod 3.
    The sealing element 8 abuts with a radially inner, axially extending sealing surface 12 on the piston rod 3, against which it is pressed at high pressure (poi |). This results in high friction loads, which the sealing element 8 has to 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 polyetheretherketone (PEEK) or polyphenylene sulphide (PPS) materials. On the sealing element 8 act by the pressure poi | the sealing medium 30 forces that press the sealing element 8 against the support ring 11 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. 6/155 '
    827 AT
    To the sealing surface 12 is axially adjacent to the sealing surface 12 at an angle α inclined feed surface 21, which connects the sealing surface 12 with the support ring 11 facing the first end face 26 of the sealing element 8. Likewise, the sealing surface 12 is adjoined by a wiping surface 22 which is inclined relative to the sealing surface 12 by an angle β. The edge between sealing surface 12 and the stripping surface 22 forms the sealing edge 23. For a favorable operation of the sealing element 8, that is to say for low frictional forces or friction losses and a small sealing medium leakage, it has proven to be advantageous if the angle of the draw-in surface 21 a <4 °, but greater than zero, and the angle of the scraping surface 22 ß>. 75 °, whereby angles greater than 90 ° are conceivable, is selected. Likewise, it is advantageous if the axial length of the sealing surface 12 is smaller than the axial length of the feed surface 21, wherein the feed surface 21 for reasons of wear and the sealing surface 12 for the purpose of good management of the sealing element 8 each require a sufficient length.
    Due to the forces acting on the sealing element 8 by the acting pressure p0H and the geometry of the sealing element 8 but also cogging moments Ms arise, 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. Therefore, it is advantageous if the sealing element 8 is made sufficiently rigid in order to reduce the bulging of the sealing element 8. For this purpose, it may be provided that the first end face 26 axially opposite second end face 24 of the sealing element 8, on which the spring ring 9 abuts, is arranged axially in front of the sealing edge 23. As a result, the sealing element 8 is axially widened in the radially outer region, which increases the rigidity of the sealing element 8.
    Due to the deformations of the sealing element 8 in operation, it can also happen that the high pressure poN "creeps" into the axial contact surface 25 between the support element 11 and sealing element 8, whereby the contact between the support member 11 and sealing element 8 is weakened, which ultimately lead to it can, that the sealing element 8 lifts completely from the support ring 11, which would open a leakage path for the sealing medium and the sealing effect of the sealing arrangement 1 would be destroyed. To prevent this, the sealing element 8 is only partially, so only over part of the radial height of the sealing element 8, axially on the support ring 11 at. Sealing element 8 and support ring 11 are axially against each other and thereby overlap in the radial direction. This overlapping area is reduced by the axial engagement in sections in order to form a reduced contact area between support element 11 and sealing element 8. Sealing element 8 and support ring 11 are consequently axially separated over part of the radial overlap between the sealing element 8 and the support ring 11. The reduced contact surface 25 leads through the acting
    827 AT
    Pressure Pen to an increased surface pressure at the contact surface 25, whereby the "creeping" of the high pressure p0n can be prevented in the contact surface 25. For the deformation of the sealing element 8, it is more favorable if the contact surface 25 in the radially outer region of the sealing element 8, ie in the region of the outer peripheral surface 33, is formed. The contact surface 25 is preferably provided in the region of the radially outer half, advantageously in the region of the radially outer third, of the radial height of the sealing element 8. Preferably, the contact surface 25 is reduced to 50 to 10% of the radial height of the sealing element 8 for a secure seal.
    The sections axial separation between sealing element 8 and support ring 11 can of course be realized in a variety of ways. On the one hand, as shown in FIG. 2, it is conceivable to have a step in the first end face 26 of the sealing element 8, as here in the form of a recess 27, e.g. in the form of a back turn, provide. The gradation or recess 27 is preferably provided in the radially central region of the sealing element 8 in order not to shorten the feed surface 21 axially. However, the recess 27 in the first end face 26 but could also reach to the feed surface 21. It is also possible that on the support ring 11 on the sealing element 8 facing end face 32 radially inwardly a recess 29, e.g. in the form of a recess (as indicated by dashed lines in FIG. 2), or that the sealing element 8 is axially shortened at the first end face 26 between the recess 27 and the feed face 21, e.g. is turned off (as indicated by dashed lines in Figure 2). Thus, the forming contact surface 25 would be further reduced and between the support ring 11 and sealing element 8 in the region of the feed surface 21 and an axial gap 30 arise.
    For reasons of wear, it is advantageous if the feed surface 21 has a certain axial length. In order to ensure this, the sealing element 8 in the radially inner region, in particular at the transition between the first end face 26 and the feed surface 21, can also be made widened axially. In the first end face 26 an axially projecting step is thus provided in this area, as shown in Figure 3. In this case, it would also be possible to dispense with the recess 27 in order to achieve a gradation for the reduced contact surface 25. However, the recess 27 can preferably be used to locally make the sealing element 8 selectively more flexible or stiffer in order to influence the deformation of the sealing element 8. For this purpose, the recess 29 on the support ring 11 can be made deeper to still hold the contact surface 25 in the radially outer region of the sealing element 8. Likewise, a gap 30 between support ring 11 and sealing element 8 may be provided radially inwardly in this embodiment.
    Due to the deformation of the sealing element 8 during operation, it may happen that the gap 30 is closed, that is to say that the sealing element 8 rests axially radially on the support ring 11. 8/157
    827 AT
    To prevent it, e.g. formed by a due to manufacturing imperfections of the contact surface leakage of sealing medium, an overpressure (p0n) in the space between the support ring 11 and sealing element 8 forms, which would have a negative impact on the deformation of the sealing element 8 and thus on the sealing effect, in the support ring 11 a Recess 31 may be provided, which connects this resulting space between the support ring 11 and sealing element 8 with the prevailing compression pressure pa (cylinder side) or with atmospheric pressure pat (crankcase side). This ensures that in this room always a lower pressure than the pressure poi | the sealing medium acts to counteract an everting of the sealing element 8. Likewise, such a recess 31 in a configuration without gap 30, e.g. as described with reference to Figure 2, be provided.
    Likewise, it has been found that the sealing element 8 can expand radially during operation, in particular during repeated start / stop operation of the compressor, at start / stop of the Dichtmediumversorgungssystems or during startup when the sealing element 8 15 must first retract, which of course also the Would increase sealant leakage. In order to prevent this, provision can be made for the support ring 11 and / or the spring ring 9 to rest radially on the outside of the sealing element 8, e.g. via a corresponding axial shoulder on the support ring 11 or on the spring ring 9. The support ring 11 and / or the spring ring 9, which are both undivided rings and e.g. are made of metal, lock so that the sealing element 8 ge-20 gene radial expansion.
    An advantageous embodiment of the spring ring 9 is shown in Figure 4. On the spring ring 9 distributed over the circumference, radially and axially protruding from the spring ring 9 extensions 40 are provided, in each of which a blind bore 41 is arranged for receiving one end of a spring. 9/158 '
    权利要求:
    Claims (13)
    [1]
    8. A sealing arrangement for sealing a reciprocating piston rod (3) of a piston compressor with a first and second sealing element (8), which are arranged axially spaced in a recess (10) of the sealing arrangement (1), wherein the sealing elements ( 8) with a first end face (26) abut axially on a support ring (11) and abut with a sealing surface (12) on the piston rod (3) and in the sealing arrangement (1) a supply line (7) is provided for a sealing medium, the is connected to the recess (10), characterized in that the sealing element (8) only over part of the radial height of the sealing element (8) axially against the support ring (11) to the contact surface (25) between the sealing element (8) and Reduce support ring (11) in the radial direction.
    [2]
    2. Sealing arrangement according to claim 1, characterized in that in the first end face (26) of a sealing element (8) and / or in the sealing element (8) facing end face (32) of the support ring (11) is provided a gradation.
    [3]
    3. Sealing arrangement according to claim 2, characterized in that a recess (27) in the first end face (26) of the sealing element (8) or a recess (29) in the facing end face (32) of the support ring (11) is provided as gradation ,
    [4]
    4. Sealing arrangement according to claim 3, characterized in that the recess (27) in the sealing element (8) in the radially central region of the sealing element (8) is provided.
    [5]
    5. Sealing arrangement according to claim 3, characterized in that the recess (27) in the sealing element (8) from the radially central region of the sealing element (8) to a feed surface (21), the sealing surface (12) with the first end face ( 26) connects, extends.
    [6]
    6. Sealing arrangement according to claim 3, characterized in that the sealing element (8) is designed radially widened radially inward.
    [7]
    7. Sealing arrangement according to claim 2, characterized in that as grading a widening of the sealing element (8) is provided and on the support ring (11) on the sealing element (8) facing end face (32) in the region of the broadening a recess (26) is. -9- 10/15 827 AT
    [8]
    8. Sealing arrangement according to one of claims 1 to 7, characterized in that the contact surface (25) in the radially outer region of the first end face (26) of the sealing element (8) is formed.
    [9]
    9. Sealing arrangement according to one of claims 1 to 8, characterized in that 5 radially inwardly between the sealing element (8) and support ring (11), a gap (30) is formed.
    [10]
    10. Sealing arrangement according to one of claims 1 to 9, characterized in that in the support ring (11) has a recess (31) is provided which the annular gap between the sealing arrangement (1) and piston rod (3) with the space between the support ring (11) and Sealing element (8) connects.
    [11]
    11. Sealing arrangement according to one of claims 1 to 5 or 7 to 10, characterized in that the sealing element (8) is designed to be widened radially inwardly radially.
    [12]
    12. Sealing arrangement according to one of claims 1 to 11, characterized in that by a spring element (14) axially prestressed spring ring (9) is provided, which rests axially on a second end face (24) of the sealing element (8).
    [13]
    13. Sealing arrangement according to one of claims 1 to 12, characterized in that on the support ring (11) and / or on the spring ring (9) an axial shoulder (28) is provided, which on the radially outer peripheral surface (33) of the sealing element (8 ) is present. -10- 11/15
    类似技术:
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    同族专利:
    公开号 | 公开日
    AT514335B1|2014-12-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE1425523A1|1962-04-25|1969-05-29|Nat Res Dev|Shaft seal|
    US4350349A|1981-02-12|1982-09-21|Harry A. Robertson, Jr.|Rod packing|
    GB2185542A|1985-07-13|1987-07-22|Crane Packing Ltd|Gas tight seal|
    EP1146264A2|2000-04-10|2001-10-17|Hoerbiger Kompressortechnik Services GmbH|Sealing ring combination|
    WO2007124830A1|2006-04-28|2007-11-08|Andritz Ag|Sealing arrangement|
    WO2010079227A1|2009-01-12|2010-07-15|Hoerbiger Kompressortechnik Holding Gmbh|Sealing arrangement for sealing a piston rod of a reciprocating compressor|DE102016118728A1|2016-10-04|2018-04-05|Stasskol Gmbh|Sealing device, compressor with a sealing device and method for sealing a piston rod|
    WO2020221679A1|2019-04-30|2020-11-05|Technische Universität Dresden|Sealing assembly for piston compressors|
    AT513495B1|2012-11-28|2014-05-15|Hoerbiger Kompressortech Hold|Sealing arrangement for sealing a reciprocating piston rod of a reciprocating compressor|
    WO2018037135A1|2016-08-26|2018-03-01|Burckhardt Compression Ag|Oil wiper packing|
    法律状态:
    2019-03-15| MM01| Lapse because of not paying annual fees|Effective date: 20180710 |
    优先权:
    申请号 | 申请日 | 专利标题
    AT504492013A|AT514335B1|2013-07-10|2013-07-10|Sealing arrangement for sealing a reciprocating piston rod of a reciprocating compressor|AT504492013A| AT514335B1|2013-07-10|2013-07-10|Sealing arrangement for sealing a reciprocating piston rod of a reciprocating compressor|
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