• 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 a hydraulic sealing medium barrier for sealing a piston rod of a reciprocating compressor high temperatures of the sealing medium arise and there is a risk that dirt and abrasion deposit and thus impair the function of the seal. To prevent this, a sealing arrangement (1) is proposed according to the invention, which for the circulation of sealing medium a discharge (11) for sealing medium, which is connected to the recess (10), and a circulating device (13), with the sealing medium on the Inlet and outlet (7,11) through the recess (10) is circulated.
    公开号:AT512945A4
    申请号:T50218/2012
    申请日:2012-06-04
    公开日:2013-12-15
    发明作者:
    申请人:Hoerbiger Kompressortech Hold；
    IPC主号:
    专利说明:

    820 AT
    Sealing arrangement for sealing a reciprocating piston rod of a piston 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 arranged in each case at one axial end of the recess and on the piston rod fitting are and in the sealing arrangement, a supply line for a sealing medium is provided, 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 pressure packs are used, which seal between the reciprocating piston rod of the reciprocating compressor and a stationary 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 a certain amount of leakage that 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. 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, at least reduced along the piston rod, ideally even eliminated.
    Such gaskets or seals are also normally cooled, e.g. by circulating cooling medium through the packing to indirectly cool the piston rod by cooling the packing. Of course, this causes additional design and operational costs.
    However, a seal in the form of a sealing medium barrier, in addition to an unavoidable leakage of sealing medium, but also some problems. Due to the small volume of sealing medium in the sealing medium barrier, the sealing medium is achieved through the application of heat due to the friction (due to the friction between fast reciprocating coolant).
    820 AT
    Piston rod and the sealing medium) can easily reach temperatures of up to 200 ° C and above.
    As a result, the choice of sealing media that can be used is already limited right from the start. However, the high temperatures also result in rapid thermal aging of the sealing medium, which may impair the sealing function. Due to the temperature rise, but it also leads to an increase in pressure in the seal, which may undesirably lead to increased leakage of sealing medium from the seal. In addition, due to the increased pressure, the sealing elements of the sealing medium barrier are of course also excessively stressed, which can ultimately lead to the failure of the sealing elements. In addition, hydraulic components in the standard version are only designed for temperatures of typically 80 ° C. Hydraulic components, the higher temperatures, especially such high temperatures as possible here dominate, are correspondingly expensive. In addition, these high temperatures also require sufficient cooling of the seal. Last but not least, contamination, e.g. from abrasion or process-related dirt accumulate, which may also affect the function of the seal.
    It is therefore an object of the subject invention to overcome the above problems with sealing medium barriers as a seal in a reciprocating compressor.
    This object is achieved by providing a derivative for the sealing medium is provided, which is connected to the recess and further provided a circulating device, is circulated with the sealing medium via the inlet and outlet through the recess. By the circulation of sealing medium through the recess is ensured without affecting the sealing function that the temperature of the sealing medium is held in reasonable areas, so that the associated problems, such as pressure increase in the seal, thermal aging of the sealing medium, cooling the sealing arrangement at least be significantly reduced. In addition, this also a vulnerable contamination is removed from the seal, which also disturbing deposits of dirt or abrasion can be reduced. Another significant added benefit of this revolution is to be seen in the fact that thereby the cooling of the sealing arrangement can be omitted and at the same time the piston rod is cooled directly, which was previously possible only by expensive constructions.
    The desired pressure of the sealing medium can be adjusted in a simple manner, if a pressure control unit is arranged in the discharge.
    In order to prevent a backflow of working medium of the compressor in the sealing medium container at standstill of the compressor and / or in case of failure, a first and / or a second shut-off valve may be arranged in the discharge, which may also serve for venting the seal. -2-
    If a biased check valve is arranged in the supply line, it can be prevented in a simple manner that, in the event of a fault or in the switched-off state, working medium of the compressor flows back into the sealing medium container.
    A vent line can be automatically opened or closed when the second 5 check valve is actuated by the pressure in front of the preloaded check valve. This can also be prevented that sealing medium is lost through the vent line.
    It can also be realized in a simple manner, a temperature control of the hydraulic system by a temperature sensor is provided at the discharge, which is connected to a control unit for controlling the circulation device. Thus the temperature of the sealing medium can be regulated ba / v. be limited to the top.
    The pressure of the sealing medium can also be regulated by providing at the discharge a pressure sensor which is connected to a control unit for controlling the circulation device. This can be set by appropriate setpoint specifications in a simple manner different sealing medium pressures. 15 To two modes of operation, e.g. Standstill and normal operation to be able to adjust, a changeover valve may be provided in the derivative, which acts on a first pressure limiting valve or a second pressure relief valve, wherein a higher switching pressure than for the second pressure relief valve is set for the first pressure relief valve. In this way, e.g. at standstill of the compressor, a higher sealing medium pressure can be adjusted in 20 of the sealing arrangement to safely prevent leakage of working medium of the compressor by the sealing arrangement.
    Any existing cooling system of the sealing arrangement can be used in a simple manner, if in the supply line branches off a cooling line, which is connected to a cooling system of the sealing arrangement. Thus, the sealing arrangement and indirectly also the Kol-25 rod can be additionally cooled by the sealing medium, but at the same time external additional units can be saved for circulating a separate cooling medium.
    The subject invention will be explained in more detail below with reference to the exemplary, schematic and non-limiting Figures 1 to 6. FIG. 1 shows a sealing arrangement according to the invention with circulation of the sealing medium, FIG.
    2 is a hydraulic diagram of the circulation of the sealing medium,
    3 shows a hydraulic scheme with constant volume flow,
    4 shows a hydraulic diagram with temperature-controlled volume flow,
    5 shows a hydraulic diagram with pressure-controlled volume flow and FIG. 6 shows a hydraulic diagram for two sealing arrangements. -3-
    Hi 820 ΑΤ
    In Fig. 1 is a known sealing arrangement 1 for sealing an axially reciprocating piston rod 3 of a reciprocating compressor against a sealed Drude pd a working medium, e.g. the cylinder pressure, shown. The sealing arrangement 1 is located in a fixed housing part 2 of the compressor, such as e.g. the compressor housing 5, and seals between this housing part 2 and the moving piston rod 3. The sealing arrangement 1 is e.g. as well known in the preassembled state in the housing part 2 is inserted and fixed, e.g. by means of a number of screws distributed over the circumference. In the example shown, the sealing arrangement 1 comprises two L-shaped chamber disks 4, 5, which in the exemplary embodiment shown are separated axially by a separating disk 6. Of course, other embodiments, e.g. with T-shaped cutting discs, conceivable. On a chamber disk 5, a flange can also be provided radially on the outside, by means of which the sealing arrangement 1 can be fastened 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 15 is formed between the L-shaped chamber discs 4, 5, optionally the cutting disc 6 and the piston rod 3, a recess 10. In this recess 10, a first and second sealing element 8, 9 are arranged, wherein the sealing elements 8,9 through the acting pressure of a in the recess 10 via a supply line 7 supplied sealing medium respectively at the axial ends of the recess 10, so the radial limbs of the L-shaped 20 chamber discs 4, 5, abut and are arranged axially separated from each other (the orientations "axially" and "radial" are based on the orientation of the piston rod 3). The first and second sealing element 8, 9 are arranged radially on the outside of the chamber disks 4, 5, that is, on the axial limbs of the chamber disks 4, 5, and lie radially inward on the sealing surface on the piston rod 3. The sealing medium, e.g. an oil 25 is supplied to the recess 10 under a pressure Poii greater than the pressure pd to be sealed. The sealing medium is thus enclosed by the sealing elements 8, Θ in the recess 10 and acts radially outward and axially on the sealing elements 8, 9, which thus pressed by the pressure poii radially inwardly to the piston rod 3 and axially to the chamber discs 4.5 be and thus seal. This creates a sealing medium barrier which prevents leakage of the gaseous working medium of the compressor to be sealed.
    As sealing elements 8, 9, either known hydraulic sealing rings, such as e.g. a lip sealing ring or a compact sealing ring, with a sealing lip resting against the piston rod 3, or else well-known rigid, cut or segmented packing rings or packing ring combinations, such as e.g. a combination of a radially and tangentially cut packing ring can be used. As is known, hydraulic sealing rings can also be designed in such a way that sealing medium which is at a stroke * 4
    820 AT is pressed through the sealing lip, is "sucked back" by the sealing lip during the counter-stroke, so that in total no or only a slight leakage of sealing medium through the hydraulic sealing ring is produced. When using packing rings or packing ring combinations usually causes a slight leakage of sealing medium 5 through the seal, but which is usually not a problem.
    Of course, the sealing arrangement 1 could also be constructed differently or consist of other and / or additional components, such as e.g. in WO 2010/079227 A1 or AT 510171 A1 described in detail.
    With the recess 10, a discharge 11 is now connected, can be derived via the sealing medium from the 1 o recess 10. The discharge line 11 is preferably, but not necessarily, arranged diametrically opposite the mouth of the supply line 7 into the recess 10 in order to achieve a good flow through the recess 10. Of course, a plurality of leads 7 and / or leads 11 could be provided. Thus, sealing medium can be circulated through the recess 10, as explained with reference to the Fig.2 nä-15 ha-. Via a circulation device, here e.g. a circulation pump 13, the sealing assembly 1, a sealing medium flow V is supplied via the supply line 7 and discharged via the discharge line 11. The circulation of the sealing medium via a sealing medium container 14 from which sucks the circulation pump 13 and in which the sealing medium is recycled. The pressure required for the sealing ρ0 · ι is set via a pressure control unit 12.
    By the circulation of sealing medium through the sealing arrangement 1 or through the recess 10 on the one hand ensures that the temperature of the sealing medium does not rise too high. In addition, this also causes a direct cooling of the piston rod 3, since the piston rod 3 is surrounded by the sealing medium. This results in a considerable additional benefit when it is possible to dispense with costly cooling of the sealing arrangement 1 due to the direct cooling of the piston rod 3. Likewise, any contamination from the recess 10 can be flushed out by the circulation or deposits of process-related abrasion or dirt in the recess 10 can be prevented. In a further embodiment variant, the sealing arrangement 1 could additionally be cooled by means of a cooling-sealing medium flow VK branched off from the sealing medium flow V, which is supplied via a cooling line 16 to the sealing arrangement 1, as shown in dashed lines in FIG. For this purpose, before or after the sealing arrangement 1, a device 15 for regulating the cooling-sealing medium flow VK could also be provided, such as e.g. a Druckregeleinrich- device or flow control device. This could be a possibly existing -5-
    I
    820 AT cooling system of the sealing arrangement 1 are used, but the provided external units for circulating a separate cooling medium can be saved. This can be of particular interest when retrofitting an existing compressor.
    In the embodiment according to FIG. 3, the circulation takes place with a constant sealing medium Fw. The pressure p0ii required for the sealing is transmitted via the pressure regulating unit 12, here e.g. adjustable pressure relief valve, set. Such a sealing arrangement 1 is e.g. operated with a pressure ροη = 30-250 bar and a sealing medium flow of 300VTag to 15001 / day.
    In addition, in the return line to the sealing medium container 14, a first shut-off valve 18, such as, for example, may be provided. a pilot-operated check valve or as here a hydraulically controlled ball valve, be provided to prevent the back flow of gas into the Dichtmediumbehäiter 14 in case of failure. For this purpose, the shut-off valve 18 is connected via a control line, e.g. as from here on the derivation 11, driven. If no pressure ρ <, "is present in the discharge line 11, then the shut-off valve 18 closes automatically. On the shut-off valve 18 15 can also be dispensed with, since the pressure control unit 12 can take over this Funkticxi also. The pressure control unit 12 closes automatically at very low pressures and prevents the influx of gas leakage into the sealing medium container 14.
    Similarly, a bleed line 19 could also be provided in the drain 11, in which a second shut-off valve 20, such as e.g. as here a lockable check valve or a hydraulically controlled ball valve, can be arranged. For this purpose, the second shut-off valve 20 is connected via a control line, e.g. as from here on the supply line 7, driven. If there is no pressure po # in the supply line 7, the second shut-off valve 20 opens to remove the leakage gas. The gas venting pressure is preferably less than 4bar. The vent line 19 may be e.g. may be simply vented to the outside, but may be connected, for example with torch · 25 lines to flare the leakage gas.
    Furthermore, in the supply line 7, a biased check valve 21 may be provided to close the supply line 7 at a certain pressure pQä. The preloaded check valve 21 preferably has two functions. First, it prevents that in case of failure or in the off state working fluid of the compressor flows back into the sealing medium container 30 -30. Second, it can be used to generate upon actuation of the hydraulic unit, a pressure in the control line of the check valve 20, which branches in the flow direction before the check valve 21 from the supply line 7, which actuates the check valve 20, so closes before the sealing medium to the check valve 20th can get. If the shut-off valve 20 were not closed, sealing medium would escape through the open vent line 19. Therefore, it is advantageous that the check valve 21 is biased. In Störfail, so if there is no more pressure in the supply line 7, opens * β ~ Bl
    the check valve 20 then automatically again and the leakage gas can be removed via the vent line 19 again, as in conventional packages. As activation pressure for the check valve 21, a pressure of about 5 bar can preferably be set. Due to the circulation of the sealing medium, no separate venting of the 5 sealing medium lines is required in normal operation.
    The advantage of this design is that the seal is controlled only via the hydraulic pressure poH, whereby a very robust and simple seal can be realized.
    Likewise, of course, other suitable components such as e.g. Manometer, temperature displays, filters, etc., be provided, as shown in Fig.3 Darge-10.
    The embodiment of Figure 4 differs from Figure 2 essentially in that now no constant sealing medium flow Fw is provided, but the sealing medium flow V is temperature controlled. For this purpose, a temperature sensor 22 is provided at the discharge line 11, which supplies the current temperature T of the sealing medium exiting the sealing arrangement 15 to a control unit 23, which in turn drives the circulation pump 13 to a certain preset temperature of the sealing medium, e.g. Tmax = 80 ° C, to be maintained. As a shut-off valve 20 here comes a hydraulically controlled ball valve, e.g. is controlled by the pressure in front of the biased check valve 21, for use and the vent line 19 is provided here after the pressure control unit 12. 20 Instead of a temperature control, a pressure control can be provided, as shown in Figure 5. For this purpose, in the discharge line 11, a throttling device 26, such as e.g. an aperture, arranged and e.g. in the derivative 11, the current pressure of the sealing medium measured by a pressure sensor 25 and fed to a control unit 23. The control unit 23 controls the circulation pump 13 so that a predetermined pressure p0n in the sealing arrangement 1 is achieved.
    6 shows an embodiment in which two sealing arrangements 1 are supplied with a hydraulic unit, whereby, of course, more than two sealing arrangements 1 could also be operated by a hydraulic unit. Here is a Hydrauiikaggregat 30, with all components necessary for the hydraulic supply, and a hydraulic control block 30 31, with all necessary for the operation of hydraulic components provided. The special feature here is that can be switched via a switching valve 32 between a normal operation and a standstill operation. Switching can be done manually or automatically. Depending on the position, a first pressure limiting valve 33 and a second pressure limiting valve 34 are acted upon by the switching valve 32, wherein the first pressure limiting valve 33 has a higher switching pressure, e.g. 250bar, as the -7-
    820 AT second pressure relief valve 34, z. 150bar. Thus, depending on the position of the changeover valve 32, the pressure poi1 can be set. In normal operation, ie when the compressor is running, the low pressure poii is set. If the compressor is switched off, it can switch to standstill mode and thus to the higher pressure be switched to safely prevent 5 that working medium of the compressor is pressed into the sealing assembly 1. In fact, at standstill, in rare cases, e.g. if the pressure valve of the compressor is leaking, an increase in pressure will occur in the compressor cylinder (up to the final pressure of the compressor). At standstill of the compressor can now, for. the pressure of the sealing medium to compressor final pressure (or above) can be adjusted to prevent that the working medium is pressed into the sealing assembly 1. in the discharge lines 11 also flow measuring units 35 are arranged here. Instead of the flow measuring units 35 and pressure switch could be provided. In order to prevent a backflow of sealing medium between the sealing arrangements, non-return valves can also be built in front of the flow measuring units 35 or pressure switches. Likewise, a pressure switch 36 may be provided in the supply line in order to trigger pressure-dependent actions, for example in order to stop energizing the drive motor of the circulating pump 13 in the event of a malfunction.
    In a sealing arrangement 1 as described above, there is a small leakage of sealing medium through the sealing elements 8,9 and between sealing elements 8,9 and piston-20 rod. This leakage is preferably dissipate from the sealing arrangement. A leakage return of sealing medium from the sealing arrangement 1, such as e.g. described in AT 510171 A1 could be returned via a leakage line 17 from the sealing assembly 1 in the sealing medium container 14, such. shown in Fig.2. Instead of such a leakage line 17, the seal medium leakage could also be passed into the crankcase of the Kom-25 pressors. In the crankcase, an overflow can then be provided, wherein the overlap is in turn returned to the sealing medium container 14.
    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, 9), which are arranged axially spaced in a recess (10) of the sealing arrangement (1), wherein the Sealing elements (8, 9) in each case at an axial end of the recess (10) and on the piston rod (3) are arranged adjacent and in the sealing arrangement (1) a supply line (7) is provided for a sealing medium with the recess (10 ), characterized in that a discharge line (11) is provided for sealing medium, which is connected to the recess (10) and a circulation device (13) is provided, with the sealing medium via the inlet and outlet (7,11) is circulated through the recess (10).
    [2]
    2. Sealing arrangement according to claim 1, characterized in that in the discharge line (11) a pressure regulating unit (12) is arranged.
    [3]
    3. Sealing arrangement according to claim 1 or 2, characterized in that in the discharge line (11) a first and / or a second shut-off valve (18,20) is arranged.
    [4]
    4. Sealing arrangement according to one of claims 1 to 3, characterized in that in the supply line a biased check valve (21) is arranged.
    [5]
    5. Sealing arrangement according to claim 3 and 4, characterized in that the second shut-off valve (20) by the pressure in front of the biased check valve (21) is actuated.
    [6]
    6. Sealing arrangement according to one of claims 1 to 5, characterized in that at the discharge (11), a temperature sensor (22) is provided which is connected to a control unit (23) for controlling the circulation device (13).
    [7]
    7. Sealing arrangement according to one of claims 1 to 5, characterized in that at the discharge (11), a pressure sensor (25) is provided which is connected to a control unit (23) for controlling the circulation device (13)
    [8]
    8. Sealing arrangement according to one of claims 1 to 7, characterized in that in the discharge (11), a changeover valve (32) is provided, which acts on a first pressure relief valve (33) or a second pressure relief valve (34), wherein for the first pressure relief valve (33) a higher switching pressure than for the second pressure relief valve (34) is set
    [9]
    9. Sealing arrangement according to one of claims 1 to 8, characterized in that in the feed line (7) branches off a cooling line (16) which is connected to a cooling system of the sealing arrangement (1). -9-
    类似技术:
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    同族专利:
    公开号 | 公开日
    WO2013182456A1|2013-12-12|
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    US20150337960A1|2015-11-26|
    CN104364567A|2015-02-18|
    CN104364567B|2017-02-22|
    AT512945B1|2013-12-15|
    US9568101B2|2017-02-14|
    JP2015520344A|2015-07-16|
    EP2855982B1|2016-03-02|
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    法律状态:
    2021-02-15| MM01| Lapse because of not paying annual fees|Effective date: 20200604 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50218/2012A|AT512945B1|2012-06-04|2012-06-04|Sealing arrangement for sealing a reciprocating piston rod of a reciprocating compressor|ATA50218/2012A| AT512945B1|2012-06-04|2012-06-04|Sealing arrangement for sealing a reciprocating piston rod of a reciprocating compressor|
    US14/405,028| US9568101B2|2012-06-04|2013-05-29|Sealing configuration for sealing a reciprocating piston rod of a piston compressor|
    EP13725668.1A| EP2855982B1|2012-06-04|2013-05-29|Sealing assembly for sealing a reciprocating piston rod of a reciprocating compressor|
    JP2015515475A| JP2015520344A|2012-06-04|2013-05-29|Sealing device for sealing a piston rod that reciprocates in a piston compressor|
    CN201380029422.5A| CN104364567B|2012-06-04|2013-05-29|Sealing assembly for sealing a reciprocating piston rod of a reciprocating compressor|
    PCT/EP2013/061004| WO2013182456A1|2012-06-04|2013-05-29|Sealing assembly for sealing a reciprocating piston rod of a reciprocating compressor|
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