• 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:

    公开号:AT510171A4
    申请号:T0021311
    申请日:2011-02-17
    公开日:2012-02-15
    发明作者:Andreas Dipl Ing Brandl；Tino Dr Lindner-Silwester；Christian Hold；Christian Kernbichler
    申请人:Hoerbiger Kompressortech Hold；
    IPC主号:
    专利说明:

    «• · · ·· · • ♦ ·» * ··
    813 AT
    Seal for a reciprocating piston rod of a reciprocating compressor
    The subject invention relates to a sealing packing for a reciprocating piston rod of a reciprocating compressor, wherein in the sealing pack, a first and a second sealing element are provided, which are arranged in a barrier recess of the sealing packing and an opening into the barrier recess supply line for a Sealant is provided.
    In certain applications of compressors, such as e.g. In compressor stations in the transportation of natural gas, it is becoming increasingly important for environmental reasons (also due to increasingly stringent legislation) to minimize the leakage of the compression medium (for example natural gas) from the compressor. This leakage arises essentially along the reciprocating piston rod, which is usually sealed against the compressor housing by means of so-called well-known sealing gaskets. It would therefore have to be met by conventional gaskets high demands to meet the demands on the tightness, which is not always possible, but would at least significantly increase the cost of the seal.
    WO 2010/079227 A1 describes a gas-tight seal in a sealing pack which prevents gas leakage along the piston rod. For this purpose, a pressurized sealing medium is trapped between two sealing elements, which forms in this way a sealing medium barrier and prevents gas leakage. In addition, other sealing elements with different functions, such as e.g. a scraper ring, a packing ring or a packing ring combination or a hydraulic sealing ring can be arranged. The seal described therein is gas-tight in normal operation. In case of a malfunction, e.g. in the case of failure of the hydraulic supply of the sealing medium barrier or damage to a sealing element of the sealing medium barrier, however, the function of the seal can no longer be guaranteed, which can result in the emergency shutdown of the compressor as a result. This also means that certain extraordinary conditions can only be responded to by the forced undesired shutdown of the compressor. A damaged sealing element of the sealing medium barrier may e.g. This may also result in sealing medium being required in the cylinder or crankcase, which may also be undesirable, resulting in consequential damage to the compressor (e.g., piston, piston rod, crankshaft, connecting rod, etc.), and thus typically results in shutdown of the compressor. In particular, an over-lubrication of the cylinder should be prevented in order to avoid any consequential damage. Falls e.g. the hydraulic supply of the sealing medium barrier, the sealing function of the packing is no longer given and it can get compression medium from the cylinder in the crankcase -1- and from there into the environment, which can also lead to forced shutdown of the compressor. Due to the above-mentioned problem, the hydraulic supply can not be easily turned off in the event of a fault, so that in case of failure, the entire compressor for maintenance or damage repair must be turned off. This leads to a loss of business, which can cause great economic damage in practice.
    A further problem of WO 2010/079227 A1 is that for a reliable recovery of the sealing medium, a very complex, complicated configuration of different sealing elements and pressure and drainage lines is required, such as e.g. shown in Fig. 6 of WO 2010/079227 A1. This makes such an arrangement, and especially a retrofitting of existing compressors, consuming and therefore economically uninteresting.
    It is therefore an object of the subject invention to improve a prior art gas tight seal so that even in the event of a malfunction of a component of the seal such as e.g. the hydraulic supply or a sealing element, the function of the sealing packing can be maintained at least sufficiently and a shutdown of the compressor is avoided and the packing is still simple.
    This object is achieved in that the crankcase end of the sealing packing a scraper recess is provided in which a gas-tight scraper ring is arranged and at the cylinder-side end of the packing a sealing ring recess is provided, in which a sealing ring arrangement is arranged, wherein the barriers -Aus-recess axially between the scraper recess and sealing ring recess is arranged and in the sealing pack, a drainage line is provided, which is connected to the space between the barrier recess and the second recess. This configuration is achieved in a simple manner that in case of failure or damage of the sealing medium barrier of the gas-tight wiper ring takes over the function of the gas-tight seal and possibly controlled from the cylinder compression medium via the drainage line and can be safely removed. Thus, in case of failure, the sealing function of the packing can still be maintained. As a result, a shutdown of the compressor can be avoided, whereby the reliability of such a gasket can be significantly improved.
    In order to enable a safe switching of the sealing medium barrier, a spring element is preferably arranged in the barrier recess, which axially presses apart the first and the second sealing element. Thus, the position of the sealing elements is fixed at rest and it is ensured that the sealing elements when switching on the hydrau- -2- • · * ···· «I ·
    The supply of the sealing medium barrier can be pressed axially against the boundary of the barrier recess 813.
    The degradation of the cylinder-side high pressure can preferably be divided into a plurality of sealing ring assemblies by a further sealing ring recess is provided at the cylinder-side end of the packing, in which a further sealing ring assembly is arranged. Thus, the requirement for a single seal arrangement can be reduced.
    Advantageously, a rigid sealing ring is arranged in a second sealing ring recess for reducing the dynamic pressure peaks of the cylinder-side pressure.
    In order to increase the reliability of the packing further, it may be provided to arrange a further sealing element in one of the sealing ring recesses. Thus, a failure of a sealing element of the sealing medium barrier can be compensated.
    A particularly simple construction of the sealing packing results when a barrier recess and / or a scraper recess and / or a sealing ring recess is arranged in a chamber disk.
    The subject invention will be explained in more detail below with reference to Figures 1 and 2, which show non-limiting, advantageous embodiments of the invention. It shows
    Fig. 1 shows a preferred embodiment of a sealing package and Fig. 2 shows a further embodiment of the sealing medium barrier.
    In an advantageous embodiment according to FIG. 1, the gas-tight seal according to the invention comprises a sealing packing 1 with a number of chamber disks 3,4, 5, 7, 9, 10, in which partly sealing elements of different function are arranged. The chamber discs 3, 4, 5, 7, 9, 10 can be connected to each other in a known manner by means of through bolts. This packing 1 is used in a well-known manner in the (not shown here) housing of a compressor, wherein a first chamber disc 3 is designed as a flange, by means of which the packing 1 can be secured in the housing, e.g. by means of distributed over the circumference screws. In this case, the sealing packing 1 seals between a cylinder-side space Z, with high pressure, and a crankcase-side space K, as a rule with atmospheric pressure. "Sealing" here means to prevent the compression medium, such as e.g. Natural gas, from the cylinder-side space Z, e.g. along the piston rod 2, enters the crankcase side space K and thus an undesirable leakage of compression medium would be present. -3- • ··· ·· * · «ft
    813 AT • m · · · ··· ·· »et • · * · * · ···« • * * * · · · · · · ·
    In a barrier chamber disk 5, two sealing elements 11, axially spaced from one another, are arranged in a barrier recess 12 for this purpose. Of course, each sealing element 11 may equivalently also be arranged in a separate barrier chamber disk 5a, 5b instead of a common barrier chamber disk 5, as shown in FIG. In this case, the barrier recess 12 would be formed of two interconnected recesses 12a, 12b in the respective barrier chamber discs 5a, 5b. Of course, another separating disk could also be arranged between the two barrier chamber disks 5a, 5b in FIG. 2, as long as the two recesses 12a, 12b are hydraulically connected to form the barrier recess 12.
    In the barrier recess 12 opens a hydraulic supply line 13, via the sealing medium, e.g. Oil is supplied under pressure. Due to the pressure of the sealing medium, the sealing elements 11 are both axially against the adjacent chamber discs 4, 6 (as in Fig. 1) and against the axial boundary of the barrier chamber disc 5, 5a, 5b (as in Fig. 2), as well pressed radially against the piston rod 2 inside. Thus, a sealing medium barrier 14 is formed, which prevents a flow of compression medium along the piston rod 2.
    The sealing elements 11 can also be axially prestressed by a spring element 27 (see FIG. 2) in that the two sealing elements 11 are pressed apart axially by the spring element 27 and against the axial boundary of the barrier recess 12. In this way, a safe switching of the sealing medium barrier 14 can be achieved, since the position of the sealing elements 11 is fixed in this way.
    At the crank box side end K of the packing 1, a stripping chamber disc 4 is further provided, here between the first chamber disc 3 and the barrier chamber disc 5 or one of the barrier chamber disc 5a. In the stripping chamber disc 4, a gas-tight scraper ring 16, at least in the direction of the crankcase, in the form of a scraper recess 15, here two gas-tight scraper rings 16 lying one behind the other, are arranged. In this context, "gas-tight" means that there are no defined gas leakage paths in the axial or radial direction on the scraper ring 16, apart from unavoidable production-related imperfections (such as manufacturing deviations, roughness, etc.). Such a gas-tight wiper ring is e.g. from the Austrian patent application A 216/2010 known.
    At the cylinder-side end Z of the sealing packing 1, a conventional sealing ring arrangement 18 known per se is arranged in at least one sealing ring chamber disk 9 in a sealing ring recess 17, such as e.g. a segmented sealing ring according to EP 2 056 003 A1, or a sealing ring combination known per se, e.g. from an axially connected one another lying radially and tangentially cut sealing ring. In the sealing ring recess 17 may further be provided a rigid support ring 19 to which the sealing ring assembly 18 may abut axially.
    In this minimal configuration of the sealing packing 1, ie with a sealing medium barrier 14, a crank box side K, gas-tight wiper ring 16 in a wiper recess 15 and a cylinder-side Z seal assembly 18 in a sealing ring recess 17, the function of the sealing packing 1 is maintained even if the hydraulic supply of the sealing medium barrier 14 fails, as explained below.
    In normal operation, pressurized sealing medium is fed into the barrier recess 12 via the hydraulic feed line 13. The two sealing elements 11 are pressed against the axial boundaries of the barrier recess 12 and against the piston rod 2, whereby a gas-tight sealing medium barrier 14 is formed. The sealing elements 11 should preferably be designed so that as little as possible sealing medium from the sealing medium barrier 14, e.g. along the surface of the piston rod 2, is lost. However, due to the reciprocation of the piston rod 2, some sealing medium adhering to the piston rod surface will always be conveyed through the sealing medium barrier 14. However, this practically unavoidable sealing medium leakage should advantageously be as low as possible, which is possible by a corresponding design of the sealing elements 11. The sealing medium leakage is K crankcase side K stripped by the scraper ring 16 of the piston rod 2, so that leakage of sealing medium from the packing 1 in the crankcase can be largely prevented. The stripped sealing medium can be removed via a drainage line 20, which is connected to the space between the sealing medium barrier 14 and the scraper ring 16, and, if appropriate, the sealing medium supply or a sealing medium reservoir can be recirculated via corresponding lines. At the sealing ring arrangement 18 at the cylinder-side end Z of the sealing packing 1, the cylinder-side high pressure lying above the suction pressure is reduced, so that the necessary pressure of the hydraulic supply into the sealing medium barrier 14 can be reduced.
    If the hydraulic supply of the sealing medium barrier 14 fails or is switched off (see below), then the high cylinder-side pressure on the sealing ring arrangement 18 lying above the suction pressure is reduced. The gas-tight wiper ring 16 then also assumes the seal in the direction of the crankcase and any compression medium leakage, e.g. Natural gas, is discharged via the drainage line 20 and e.g. flared. This prevents that compression medium undesirably enters the crankcase and can escape uncontrollably from there into the environment. Thus, the seal pack 1 can continue to be used in the event of an error, at least until the next maintenance
    813 AT • · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · An interim shutdown of the compressor, however, is no longer necessary.
    When a sealing member 11 of the sealing medium barrier 14 becomes leaking, e.g. due to excessive wear or other damage, so this can be determined by the greatly increasing flow rate of sealing medium, as increasingly density medium is lost through the sealing medium barrier 14. In this case, the hydraulic supply of the sealing medium barrier 14 can be easily turned off without significantly affecting the function of the sealing packing 1.
    The function of the sealing packing 1 can be improved by arranging further elements. As shown in Fig. 1, e.g. be provided further sealing ring assemblies or sealing elements.
    Thus, a second sealing ring arrangement 25, e.g. as illustrated, an uncut seal ring, or third seal ring assembly 22, e.g. As shown, a segmented sealing ring according to EP 2 056 003 A1, be provided again combined with a support ring 26. At such a sealing ring assembly 22, 25, the cylinder-side pressure is partially reduced, so that the reduction of the cylinder-side pressure advantageous to a plurality of sealing ring assemblies 18, 22, 25 can be divided. In the case of an uncut seal this degradation of the dynamic pressure peaks of the cylinder-side pressure takes place.
    In one of the sealing ring chamber discs 7, 9, 10, a further sealing element 23, e.g. a sealing element 11 as used in the sealing medium barrier 14 may be provided. This sealing element 23 can serve to take over its function in the event of a failure of the cylinder-side sealing element 11 of the sealing medium barrier 14. In this case, the sealing medium barrier 14 would be formed between the crank-side sealing element 11 and the sealing element 23, whereby a further safety function can be realized.
    Separate disks 6, 8 could also be arranged, if required, between individual sealing ring chamber disks 3, 4, 5, 5a, 5b, 7, 9, 10, e.g. to ensure easy assembly of the packing 1.
    It is of course also conceivable to use two or more adjacent chamber discs, e.g. the stripping chamber disk 4 and the barrier chamber disk 5a or the third -6- »*« ··· ···
    813 AT • * · · I ··· ·· · # · • · * · · · · · «
    Sealing ring chamber disc 7 and the barrier chamber disc 5b to perform as a single chamber disc. -7-
    权利要求:
    Claims (8)
    [1]
    ·· tl · • I t * · «* · · · ·« «* * • · · · · · · * * 1. Gas-tight sealing packing for a reciprocating piston rod (2) of a piston compressor in which a first and a second sealing element (11) are provided in the sealing packing (1), which are arranged in a barrier recess (12) of the sealing packing (1) and have a feed line (13) opening into the barrier recess (12) ) is provided for a sealing medium, characterized in that at the crankcase end (K) of the sealing packing (1) a stripping recess (15) is provided, in which a gas-tight wiper ring (16) is arranged and at the cylinder-side end (Z) of A sealing ring recess (17) is provided in which a sealing ring arrangement (18) is arranged, wherein the barrier recess (14) is arranged axially between the stripping recess (15) and sealing ring recess (17) and in that a drainage line (20 ) is provided, which is connected to the space between the barrier recess (14) and stripping recess (15).
    [2]
    2. Gas-tight sealing packing according to claim 1, characterized in that in the barrier recess (14) has a spring element (27) is arranged, which axially compresses the first and the second sealing element (11).
    [3]
    3. Gas-tight sealing packing according to claim 1 or 2, characterized in that at the cylinder-side end (Z) of the sealing packing (1), a further sealing ring recess is provided, in which a further sealing ring arrangement is arranged.
    [4]
    4. Gas-tight sealing packing according to claim 3, characterized in that in a second sealing ring recess (24) has a second sealing ring arrangement, preferably an uncut sealing ring (25) is arranged.
    [5]
    5. Gas-tight sealing packing according to claim 3 or 4, characterized in that in a third sealing ring recess (21), a third sealing ring arrangement (22) is arranged.
    [6]
    6. Gas-tight sealing packing according to one of claims 1 to 5, characterized in that in one of the further sealing ring recesses (21,24), a further sealing element (23) is arranged.
    [7]
    7. Gas-tight sealing packing according to one of claims 1 to 6, characterized in that the barrier recess (14) and / or the stripping recess (15) and / or a sealing ring recess (17, 21, 24) in a chamber disk (4, 5, 7, 9, 10).
    [8]
    -8th-
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    法律状态:
    2020-10-15| MM01| Lapse because of not paying annual fees|Effective date: 20200217 |
    优先权:
    申请号 | 申请日 | 专利标题
    AT0021311A|AT510171B1|2011-02-17|2011-02-17|SEALING PACK FOR A ROLLING PISTON ROD OF A PISTON COMPRESSOR|AT0021311A| AT510171B1|2011-02-17|2011-02-17|SEALING PACK FOR A ROLLING PISTON ROD OF A PISTON COMPRESSOR|
    EP12151403.8A| EP2489907B1|2011-02-17|2012-01-17|Seal for a moving piston rod of a piston compressor|
    CN201210017190.9A| CN102644754B|2011-02-17|2012-01-19|Sealing system for reciprocating piston rod of reciprocating compressor|
    US13/396,176| US20120211945A1|2011-02-17|2012-02-14|Sealing packing for a reciprocating piston rod of a reciprocating compressor|
    JP2012032043A| JP6073064B2|2011-02-17|2012-02-16|Seal packing for piston rod that performs reciprocating motion of piston compressor|
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