• 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:
    Multi-stage piston compressor (1) and method for idle control of a multi-stage piston compressor (1) with a last compressor stage (5) and at least one of these last compressor stage (5) upstream compressor stage (4) with an associated cylinder chamber (10), wherein during the idle phase at least one Flow cross-section from the associated cylinder chamber (10) to the suction chamber (7) and / or the pressure chamber (13) and / or an additional volume (26) of the at least one upstream compressor stage (4) is opened, wherein with open flow cross section of the at least one upstream compressor stage ( 4), by the dimensioning of a damaged volume (23, 25) of the last compressor stage (5) of the final pressure reached by the compression of this last compressor stage (5) is reduced.
    公开号:AT516091A1
    申请号:T50452/2014
    申请日:2014-06-30
    公开日:2016-02-15
    发明作者:
    申请人:Hoerbiger Kompressortech Hold；
    IPC主号:
    专利说明:

    Idle control for multi-stage reciprocating compressors
    The subject invention relates to a multi-stage piston compressor and a method for idle control of a multi-stage piston compressor with a last compressor stage and at least one, this last compressor stage upstream compressor stage with an associated cylinder chamber, wherein during the idle phase at least one flow cross-section from the associated cylinder chamber to the suction chamber and / or pressure chamber and / or is opened to an additional volume of the at least one upstream compressor stage. Commercial vehicles, such as trucks, buses, construction machinery or rail vehicles, usually have compressed air actuated brakes on the supply of compressed air usually a compressor is provided. This is for example driven by the drive of the vehicle, or, as usual in rail vehicles, by a separate electric motor. Especially in reciprocating compressors high demands are made in terms of highest possible performance despite compact design. Similarly, in compressors often provide an idle control, especially in compressors which are also driven when just no medium to be compacted is needed. As an idle control Abhebeeinrichtungen can be used, which keep the valve element of the mammal valve for a certain period of time forcibly open. The Abhebeeinrichtung, or the actuator therefor, is usually arranged on the cylinder head and has one or more lift-off fingers, which are pressed against the valve element of the mammal valve to lift it from the valve seat and thus keep it open.
    For realizing idle control in two-stage compressors, e.g. the two cylinders of the first and second stages are connected at idle via a separate overflow channel.
    This prevents that compressed medium from the second compressor stage is conveyed into the adjoining pressure line, since no pressure is built up in the second compressor stage which is sufficient to open the pressure valve of the second compressor stage. In full load operation, this overflow is in both cylinders with shut-off piston, sliding louvers o.ä. locked.
    However, this in turn results in a number of disadvantages, such as an increased space requirement, since the separate overflow and the associated shut-off piston or sliding blades must be arranged in the cylinder. Because of this space problem, the flow cross sections in the overflow are relatively small and thus the flow resistance is high, resulting in an unnecessarily high power consumption during the idle phase. For single-stage reciprocating compressors, for example, DE 43 21 013 B4 shows an idle control in which an additional space connected to the compression space of the reciprocating compressor is used. In the course of conversion to idle the additional room is opened by pressing an additional valve. Due to the thus significantly enlarged dead space only an idling pressure is reached during the compression stroke, which is not sufficient to open the pressure valve of the compressor.
    The above-mentioned disadvantages can also be found in this arrangement, since in turn a corresponding actuating mechanism is necessary for operating the additional valve which leads to an increased space requirement. Furthermore, it must not be disregarded that the use of actuators brings the need for moving parts, which in turn mean wear and associated maintenance or carry a certain risk of failure in itself.
    The object of the present invention is therefore to realize a reliable idling control for multi-stage reciprocating compressors, which has the least possible number of actuating mechanisms.
    This object is achieved by the device according to the invention and the method according to the invention in that, when the flow cross-section of the at least one upstream compressor stage is dimensioned, the dimensioning of a damaged volume of the last compressor stage reduces the final pressure reached by the compression of this last compressor stage.
    This makes it possible to reduce by a geometric measure, at least the flow rate during the idling phase or to prevent further promotion of the multi-stage compressor entirely. For multi-stage reciprocating compressors only a reduced number of actuating mechanisms is required. As a result, both the space required for the idle control within the compressor, as well as the technical complexity is reduced. The associated reduction in moving parts also leads to a lower probability of failure and lower maintenance.
    Advantageously, it is provided that by dimensioning the harmful volume of the last compressor stage, in the compression in the last compressor stage, a final pressure required to open a pressure valve of the last compressor stage is not reached. In this way, a conveying during the idling phase is prevented because no medium is conveyed through the corresponding pressure valve.
    Advantageously, it is further provided that the delivery of the last compressor stage is reduced by the dimensioning of the damaged volume of the last compressor stage. This means that the compressor also delivers medium during the idle phase, but a reduced flow rate. As a result, the power consumption of the compressor is reduced accordingly.
    In an advantageous variant, it is provided that, to open the flow cross section, a mammalian valve is forcibly kept open for the at least one upstream compressor stage of the reciprocating compressor. As a result, at least one actuating mechanism is less required to realize an idle control.
    Advantageously, it can be provided that a pressure valve of the at least one upstream compressor stage of the reciprocating compressor is forcibly kept open to open the flow cross-section. Again, there are the analogous advantages of forcibly keeping the mammal valve open and at least one actuation mechanism for implementing idle control can be saved.
    Furthermore, it can be advantageously provided that by an actuating mechanism, a bypass channel, which connects the suction chamber or the pressure chamber or the additional volume of the at least one upstream compressor stage with its associated cylinder chamber, is released. A corresponding multi-stage reciprocating compressor has a last compressor stage and at least one, this last compressor stage upstream compressor stage with a suction chamber, a pressure chamber and an associated cylinder chamber, wherein in the at least one upstream compressor stage, a flow cross-section is provided which the suction chamber and / or the pressure chamber and / or an additional volume of the at least one upstream compressor stage connects to the first cylinder space and is forced open for idle control of the flow cross-section with a Schadvolumen the last compressor stage is dimensioned such that when forced open flow cross section of the final pressure reached by the compression of the last compressor stage is reduced.
    It is advantageously provided that a desired intermediate pressure between the last compressor stage and the at least one upstream compressor stage of the multi-stage reciprocating compressor is achieved by adapting a stroke volume of the last compressor stage. As a result, the full-load operation without disadvantages, such as increased temperature level, poorer delivery, higher power consumption, even with appropriately sized Schadvolumen the last compressor stage.
    In a further embodiment, the dead space volume is formed by an additional damage space and the additional damage space is connected via a channel to a last cylinder space of the last compressor stage. This allows "conventional" components, such as the crank mechanism to use unchanged and to make only in the cylinder or cylinder head changes in the form of additional damage.
    The subject invention will be explained in more detail below with reference to Figures 1 and 2, which show by way of example, schematically and not by way of limitation advantageous embodiments of the invention. It shows
    1 shows a part of the cylinder and the cylinder head of a piston compressor according to the invention in a first embodiment,
    2 shows a part of the cylinder and the cylinder head of a piston compressor according to the invention in a second embodiment,
    3 shows a schematic example of the arrangement of an additional volume.
    Fig. 1 shows a part of the cylinder 2 and the cylinder head 3 of a reciprocating compressor 1 in a two-stage variant. The two-part embodiment variant of the cylinder head 3 with a cylinder head upper part 3.1 and a cylinder head lower part 3.2 is chosen only as an example. The idle control according to the invention can of course also be provided for reciprocating compressor 1 with more than two stages.
    In the following, the load operation of such a two-stage reciprocating compressor 1 will first be described.
    The two-stage reciprocating compressor 1 has at least one first compressor stage 4, referred to below as the upstream compressor stage 4, and an adjoining second compressor stage 5, referred to below as the last compressor stage 5. As the last compressor stage that compressor stage is to be seen, which is connected via a pressure line, not shown, with a consumer. The last compressor stage 5 is thus the stage after which there is no further compression. The upstream compressor stage 4 is that compressor stage to understand, via which medium is sucked by means of a suction line, not shown, from the environment of the piston compressor 1. Of course, several upstream compressor stages 4 can be considered, with only the first upstream compressor stage 4 is connected to the suction line. All others are arranged between this and the last compressor stage 5.
    Since, as already noted, a two-stage reciprocating compressor is described by way of example in the following, however, there is only one upstream compressor stage 4. The upstream compressor stage 4 is connected via a first mammal valve 6 to a first suction chamber 7 delimited by the first mammal valve 6 , The first suction chamber 7 is connected to the suction line, not shown, with the environment of the piston compressor 1 or with an upstream filter, which is also not shown. About this suction line and subsequently on the first suction chamber 7, the reciprocating compressor 1 can suck to be compressed medium. In load operation, the first compressor valve 6 is opened by the downward movement of the piston 8 of the upstream compressor stage 4 and the resulting pressure difference between the first suction chamber 7 and, the upstream compressor stage 4 associated cylinder chamber 10 and medium to be compressed via suction channels 9 in the associated cylinder chamber 10 promoted the upstream compressor stage 4.
    After reaching the bottom dead center of the piston 8 of the upstream compressor stage 4, the sucked medium is compressed by the following upward movement of the piston 8 and closed by the rising pressure, the first mammal valve 6 of the upstream compressor stage 4 again. Due to, by the upward movement of the piston 8, increasing pressure in the associated cylinder chamber 10 of the upstream compressor stage 4, the first pressure valve 11 is opened. The medium thus compressed flows through corresponding pressure channels 12 into the adjoining first pressure chamber 13, and subsequently to the suction chamber 14 of the last compressor stage 5. During the upward movement of the piston 8 of the upstream compressor stage 4, the piston 18 of the last compressor stage 5 moves downward in, for example, oppositely moved pistons 8 and 18. In this way, the medium is conveyed via the suction chamber 14 of the last compressor stage 5, via the suction channels 15 and via the opening mammal valve 16 of the last compressor stage 5 into the last cylinder chamber 17 of the last compressor stage 5. Has reached by the downward movement, the piston 18 of the last compressor stage 5 its bottom dead center, the medium is further compressed in the course of the subsequent upward movement of the piston 18 of the last compressor stage 5. In this case, the mammal valve 16 of the last compressor stage 5 is closed by the rising pressure. Via a pressure valve 19 or via corresponding pressure channels 20, the second compressor stage is connected to the second pressure chamber 21. In the pressure chamber 21 is a counter-pressure. This is dependent on a consumer connected via a pressure line, not shown. For this reason, a final pressure must be achieved by the compression in the last compressor stage 5, which allows the pressure valve 19 of the last compressor stage 5 against the pressure in the second pressure chamber 21 to open.
    This is the case during load operation, due to the described two-stage compression, which is why the compressed medium via the pressure channels 20 in the pressure chamber 21 connected thereto is pushed out via the pressure valve 19 of the last compressor stage 5.
    The procedure just described in load operation results in a very analogous manner for piston compressors, which have a more than two-stage compression. The compression is continued in further subsequent upstream compression stages 4 and conveyed via the pressure valve 19 of the last compressor stage 5, the medium in the corresponding pressure chamber 21. For the idle control according to the invention, for example, a lifting device 22 is provided for positively opening the first mammal valve 6.
    The lift-off device 22 is embodied in the exemplary embodiment illustrated in FIG. 1 as a lift-off finger with stepped piston for the valve element 6.1 of the first mammal valve 6 of the upstream compressor stage 4. The actuation of the lifting device 22 takes place in this case via a pressure line 22.1 via which a corresponding actuating pressure is applied. As a result, the lifting device is moved against the force exerted by the spring 22.2 force in the direction of the first mammal valve 6 and thereby pushes the valve element 6.1 of the first mammal valve 6 from its valve seat 6.2. Of course, other variants of the lifting device 22 are possible, wherein preferably a possible space-saving variant is sought.
    The illustrated valves 6, 11, 16 and 19 are shown by way of example and not limitation with concentric valve elements 6.1, 11.1, 16.1 and 19.1 with the corresponding valve seats 6.2, 11.2, 16.2 and 19.2 and the valve springs 6.3,11.3, 16.3 and 19.3. Of course, other designs, such as multi-valve valves, juxtaposed valves or the like are conceivable. Of course, the first mammalian valve 6 need not necessarily be kept open. The keeping open of the pressure valve 11 of the upstream compressor stage 4 is conceivable.
    In general, it is only necessary that during the idle phase, at least one flow cross-section from the associated cylinder chamber 10 to the suction chamber 7, or to the pressure chamber 13 or to an additional damage chamber of the upstream compressor stage 4 is opened, of course, several of these possibilities come simultaneously into consideration. This flow cross section can be formed for example by the suction channels 9 or through the pressure channels 12, wherein the corresponding valve elements are lifted inevitably.
    For example, it can also be provided that by an actuating mechanism, such as a piston 27, a bypass channel 29, which connects the suction chamber 7 or the pressure chamber 13 or an additional volume 26 of the upstream compressor stage 4 with its associated cylinder chamber 10 is released. In this case, the bypass channel 29 corresponds to the above-mentioned flow cross-section.
    3 shows a merely schematic example of the arrangement of a corresponding additional volume 26. As already stated, the additional volume 26 is connected via a bypass channel 29 to the cylinder chamber 10 of the upstream compressor stage 4. As an actuating mechanism, for releasing the bypass channel 29, a piston 27 is shown, which, for example, can be actuated via a pressure line 28, for example.
    Of course, such an additional volume need not necessarily be arranged inside the piston compressor, but may also be provided outside the piston compressor in the form of an external chamber or the like. Also, the described embodiment of the actuating mechanism is chosen only by way of example.
    When the cross-section or bypass channel 29 of the upstream compressor stage 4 is open, the dimensioning of a damaged volume 23 of another subsequent compressor stage 5 reduces the final pressure reached by the compression of this further subsequent compressor stage 5 since none or only a small pre-compression takes place in the upstream compressor stage 4 , As a result, a final pressure required to open the pressure valve 19 of the further compressor stage 5 is not reached or the delivery rate of the further compressor stage 5 is reduced.
    Termination pressure is the pressure which is reached within a cylinder space 10 or 17 when the associated piston 8 or 18 has reached its top dead center or the highest possible pressure that can be reached in a compressor stage.
    Subsequently, in a non-limiting example, that variant is described in which the mammalian valve 6 of the first compressor stage is forcibly opened and in this way a corresponding flow cross-section is released.
    In the course of the idling phase, the valve element 6.1 of the first mammal valve 6 of the upstream compressor stage 4 is forcibly lifted from its valve seat 6.2 by means of the lifting device 22 and the mammal valve thus forcibly kept open.
    During the upward movement of the piston 8 of the upstream compressor stage 4, the medium in the associated cylinder chamber 10 is not, or hardly compacted, since the first mammalian valve 6 remains forcibly opened. On the one hand sets via a valve spring 11.3 on the valve seat 11.2 depressed valve element 11.1 of the first pressure valve 11 the medium a corresponding resistance, on the other hand, a low pressure is built up when pushing back on the mammalian valve 6 of the upstream compressor stage 4, which the pressure valve 11 to Start of idle control opens at short notice. The pressure thus prevailing in the pressure chamber 13 of the upstream compressor stage 4 subsequently ensures a state of equilibrium between pressure in the associated cylinder chamber 10 and pressure in the pressure chamber 13, which is why the first pressure valve 11 subsequently also remains closed. The medium is therefore pushed back over the forcibly opened mammal valve 6 in the first suction chamber 7 connected thereto. For the two-stage reciprocating compressor partially shown in Fig. 1, a correspondingly sized Schadvolumen 23 of the last compressor stage 5 is provided in the last compressor stage 5. The damaged volume 23 is that volume which is formed by the space within the cylinder space 17, which is not swept by a displacement surface, that is from a surface of the piston 18 of the last compressor stage 5. If the piston 18 of the piston compressor 1, as shown in Fig. 1, in its uppermost position, ie the top dead center, so in the last cylinder chamber 17 and in the cylinder head 3 remaining volume above the piston 18 forms the Schadvolumen 23. Such Arrangement of the damaged volume 23 is not necessarily provided. It is also conceivable that the damaged volume 23 is formed by an additional damage space 25.
    The damaged volume 23 of the last compressor stage 5 is dimensioned such that a certain maximum pressure ratio can not be exceeded. The pressure valve 19 of the last compressor stage 5, for example, remains closed because, as already mentioned, a required final pressure for opening the pressure valve 19 of the last compressor stage 5 is not reached. "For example," because this is the case in particular when a, the last compressor stage downstream pressure line, which is not shown in detail, also remains pressurized during idle operation. In this case, the pressure valve 19 can not be opened against the pressure applied there.
    Of course, that case is also conceivable in which this, the last compressor stage downstream pressure line is not pressurized during idling operation. In this case, the flow rate of the further compressor stage 5 is reduced by the corresponding dimensioning of the damaged volume 23 of the further compressor stage 5.
    Thus, although the piston compressor promotes during the idle phase, but at much lower pressures and thus at much lower power consumption.
    The special dimensioning of the damaged volume 23 is achieved in the variant shown in FIG. 1 by a corresponding piston support of the piston 18 of the last compressor stage 5. This means that despite reaching the top dead center, above the piston 18, a relatively large space in the last cylinder chamber 17 remains uncoated by the piston 18, as shown in Fig. 1. This space forms the corresponding damaged volume 23.
    Accordingly, an idle control is generally realized that during the idle phase, a flow cross-section of at least one, the last compressor stage 5 upstream compressor stage 4 is forcibly kept open and by dimensioning a Schadvolumens 23 of the last compressor stage 5, in the compression in the last compressor stage 5, a required to open a pressure valve 19 of the last compressor stage 5 final pressure or the flow rate of the last compressor stage 5 is reduced, depending on whether the last compressor stage 5 subsequent pressure line also remains pressurized during idle operation or not. The corresponding dimensioning of the damaged volume 23 is usefully provided in reciprocating compressors 1 with more than two stages only in the last compressor stage 5. The steps in front of it would be "pressure-free" due to the correspondingly lifted mammal valves. As a result, the piston compressor 1 is operated with the lowest possible resistance.
    In such a dimensioning of the damaged volume 23 of the last compressor stage 5, it is advantageous that a stroke volume of the last compressor stage 5 is adapted to achieve a desired intermediate pressure between the last compressor stage 5 and the at least one upstream compressor stage 4 of the multi-stage piston compressor 1.
    The intermediate pressure is the pressure which occurs during the previously described load operation between two compressor stages, for example between the last compressor stage 5 and the immediately upstream compressor stage 4, or between individual upstream compressor stages 4, if it is a compressor with more than two compression stages trades, stops.
    An intermediate pressure which unfavorably results as a result of the described dimensioning of the harmful volume has a number of disadvantages, such as increased temperature level, increased power consumption, unfavorable mechanical loads and the like.
    If, as shown by way of example in FIG. 1, a two-stage reciprocating compressor 1, the mammalian valve 6 of the upstream compressor stage 4 of the two-stage reciprocating compressor 1 is forcibly kept open and the damaged volume 23 of the last compressor stage 5 of the two-stage reciprocating compressor 1 is dimensioned such that the pressure valve 19 the last compressor stage 5 remains closed.
    The reason for this is that valve element 6.1 of the mammal valve 6 of the upstream compressor stage 4, the last compressor stage 5 does not supply any precompressed medium, as in load operation, due to the valve element 6.1 forcedly lifted from its valve seat 6.2.
    This results in a corresponding compression only in the last compressor stage 5. The achieved by the sole compression in the last stage compressor 5 final pressure is not sufficient to the pressure valve 19 of the last compressor stage 5 against the pressure in the pressure chamber 21 and the adjoining, raise the pressure line, not shown.
    In this way, can be prevented by the combination of a forced open mammal valve 6 of the upstream compressor stage 4 with a corresponding dimensioning of the Schadvolumens 23 of the last compressor stage 5 conveying into the pressure chamber 21 of the compressor, if the subsequent pressure line is pressurized.
    2 likewise shows, by way of example only, a part of the cylinder 2 and of the cylinder head 3 of a reciprocating compressor 1 in a two-stage variant embodiment. In contrast to the piston compressor 1 shown in FIG. 1, the dead space volume 23 is formed by an additional damage space 25. The fact that this additional damage space 25 is arranged in the cylinder 2 is shown only by way of example in FIG. The additional damage space 25 could just as well be arranged in the cylinder head 3 or outside of the piston compressor 1. This additional damage space 25 is connected to the last cylinder chamber 17 of the last compressor stage 5 via at least one channel 24.
    The operation of idling control is identical to that described for Fig. 1. The difference is that the piston support of the piston 18 of the last compressor stage 5, that of a conventional piston shelter of a reciprocating compressor without, as already described, idle control corresponds. This means that the piston 18 when reaching its top dead center has swept over the largest possible part of the cylinder chamber 17 without colliding with a part of the cylinder head 3 or parts of the mammal valve 16 of the last compressor stage 5, as is also exemplified in FIG ,
    In the course of the upward movement of the piston 18 of the last compressor stage 5, the compressed medium is pushed over the at least one channel 24 into the additional damage space 25. As a result, no pressure is again reached in idling operation, which is sufficient to lift the pressure valve 19 of the last compressor stage 5 against the pressure in the pressure chamber 21 and the adjoining, not shown, pressure line.
    In turn, the combination of a forcibly opened mammal valve 6 of the upstream compressor stage 4 with a corresponding dimensioning of the harmful volume 23 of the last compressor stage 5 or the additional damage chamber 25 prevents it from being conveyed into the pressure chamber 21 of the compressor.
    The advantage of this embodiment is that "conventional" components, such as the crank mechanism can be used unchanged and only in the cylinder or cylinder head changes in the form of additional damage space must be made. The number of different components is reduced to a more economical level.
    By the described device or the described method, a reliable idle control for multi-stage piston compressor 1 is realized, with only a minimum possible number of actuating mechanisms, for example, only in the form of the lifting device 22, are necessary.
    权利要求:
    Claims (14)
    [1]
    1. A method for idle control of a multi-stage piston compressor (1) having a last compressor stage (5) and at least one, this last compressor stage (5) upstream compressor stage (4) with an associated cylinder chamber (10), wherein during the idle phase, at least one flow cross-section of associated cylinder space (10) to the suction chamber (7) and / or to the pressure chamber (13) and / or an additional volume (26) of the at least one upstream compressor stage (4) is opened, characterized in that when the flow cross-section of the at least one upstream compressor stage (4), by the dimensioning of a damaged volume (23, 25) of the last compressor stage (5) of the final pressure reached by the compression of this last compressor stage (5) is reduced.
    [2]
    2. The method according to claim 1, characterized in that by the dimensioning of the Schadvolumens (23, 25) of the last compressor stage (5), in the compression in the last compressor stage (5), for opening a pressure valve (19) of the last compressor stage ( 5) required final pressure is not reached.
    [3]
    3. The method according to claim 1, characterized in that by the dimensioning of the harmful volume (23, 25) of the last compressor stage (5), the delivery rate of the last compressor stage (5) is reduced.
    [4]
    4. The method according to claim one of claims 1 to 3, characterized in that for opening the flow cross-section a mammalian valve (6) of the at least one upstream compressor stage (4) of the reciprocating compressor (1) is forcibly kept open.
    [5]
    5. The method according to claim one of claims 1 to 3, characterized in that for opening the flow cross-section, a pressure valve (11) of the at least one upstream compressor stage (4) of the reciprocating compressor (1) is forcibly kept open.
    [6]
    6. The method according to claim one of claims 1 to 3, characterized in that by an actuating mechanism, a bypass channel, which the suction chamber (7) or the pressure chamber (13) or the additional volume (26) of the at least one upstream compressor stage (4) associated cylinder space (10) connects, is released.
    [7]
    7. The method according to claim one of claims 1 to 6, characterized in that by adjusting a stroke volume of the last compressor stage (5) a ge desired intermediate pressure between the last compressor stage (5) and the at least one upstream compressor stage (4) of the multi-stage piston compressor (1) is achieved.
    [8]
    8. Multistage reciprocating compressor (1) having a last compressor stage (5) and at least one of these last compressor stage (5) upstream compressor stage (4) with a suction chamber (7), a pressure chamber (13) and an associated cylinder chamber (10), wherein in the at least one upstream compressor stage (4) is provided a flow cross-section which connects the suction chamber (7) and / or the pressure chamber (13) and / or an additional volume (26) of the at least one upstream compressor stage (4) with the cylinder chamber (10) , And for an idle control of the flow cross section is forcibly opened, characterized in that a Schadvolumen (23, 25) of the last compressor stage (5) is dimensioned such that when forced open flow cross section of the final pressure reached by the compression of the last compressor stage (5) is.
    [9]
    9. Multi-stage piston compressor (1) according to claim 8, characterized in that a pressure valve (19) of the last compressor stage (5) closed or the delivery rate of the last compressor stage (5) is reduced.
    [10]
    10. Multi-stage reciprocating compressor (1) according to Ansprunch 8 or 9, characterized in that a lifting device (22) for a mammalian valve (6) of the at least one upstream compressor stage (4) is provided for positively opening the flow cross-section.
    [11]
    11. Multi-stage reciprocating compressor (1) according to Ansprunch 8 or 9, characterized in that a lifting device (22) for a pressure valve (11) of the at least one upstream compressor stage (4) is provided for positively opening the Srömungsquerschnittes.
    [12]
    12. Multi-stage reciprocating compressor (1) according to Ansprunch 8 or 9, characterized in that a bypass channel is provided which the suction chamber (7) or the pressure chamber (13) or the additional volume (26) of the at least one upstream compressor stage (4) associated cylinder space (10) and the bypass channel has an actuating mechanism for opening or closing.
    [13]
    13. Multi-stage piston compressor (1) according to one of claims 8 to 12, characterized in that the dead space volume (23) by an additional damage space (25) is formed and the additional damage space (25) via a channel (24) with a last cylinder space (17 ) of the last compressor stage (5) is connected.
    [14]
    14. Multi-stage reciprocating compressor (1) according to one of claims 8 to 13, characterized in that a stroke volume of the last compressor stage (5) to achieve a desired intermediate pressure between the last compressor stage (5) and the at least one upstream compressor stage (4) of the multi-stage Piston compressor (1) is adjusted.
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    同族专利:
    公开号 | 公开日
    DE102015007815A1|2015-12-31|
    AT516091B1|2018-05-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE102009053133A1|2009-11-05|2011-05-12|Voith Patent Gmbh|Piston compressor with idling valve|
    DE4321013C5|1993-06-24|2014-07-17|Wabco Gmbh|gas compressor|DE102015225065A1|2015-12-14|2017-06-14|Voith Patent Gmbh|Cylinder head for multi-stage reciprocating compressor|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50452/2014A|AT516091B1|2014-06-30|2014-06-30|Idle control for multi-stage reciprocating compressors|ATA50452/2014A| AT516091B1|2014-06-30|2014-06-30|Idle control for multi-stage reciprocating compressors|
    DE102015007815.1A| DE102015007815A1|2014-06-30|2015-06-18|Idle control for multi-stage reciprocating compressors|
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