US20090311114A1 - Multi-stage piston compressor - Google Patents
Multi-stage piston compressor Download PDFInfo
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- US20090311114A1 US20090311114A1 US12/477,272 US47727209A US2009311114A1 US 20090311114 A1 US20090311114 A1 US 20090311114A1 US 47727209 A US47727209 A US 47727209A US 2009311114 A1 US2009311114 A1 US 2009311114A1
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- piston
- stage
- cylinder units
- cylinder
- cylinder unit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B25/00—Multi-stage pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B25/00—Multi-stage pumps
- F04B25/02—Multi-stage pumps of stepped piston type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
Abstract
A multi-stage piston compressor is provided with at least two piston-cylinder units, which respectively comprise a separate linear drive for moving the piston. A control device is also provided, which is designed in a manner such that the linear drives may be controlled individually with regard to speed and stroke.
Description
- The invention relates to a multi-stage piston compressor having at least two piston-cylinder units.
- Multi-stage piston compressors are known, in order to increase the pressure of a gas in several stages. With such multi-stage compressors, the exit pressure is increased in a first stage to a first intermediate pressure by a first piston-cylinder unit. This first intermediate pressure is then increased to a yet higher pressure in the second stage by a second piston-cylinder unit. This continues in accordance with the number of applied stages. With the known piston compressors, the pistons of all piston-cylinder units are driven via a common crank drive, which fixedly sets the stroke of the piston. Moreover, the diameter of the individual cylinders is selected differently, depending on the pressure ratio between the individual stages, i.e. the inner diameter of the cylinders reduces from stage to stage, since the volume of the gas decreases with each pressure increase. The known multi-stage piston compressors, on account of their mechanical design, are therefore set to certain stage pressure ratios, as well as a certain total volume flow and a certain total pressure. Variations are only possible in a restricted manner, by different valve control. For this reason, it is problematic to apply such piston compressors where different compressions or pressures and different volume flows are to be realized with one and the same machine.
- It is therefore an object of the invention to improve a multi-stage piston compressor, to the extent that the pressure and volume flow may be varied in a simple manner with one and the same machine.
- The multi-stage piston compressor according to the invention comprises at least two piston-cylinder units, i.e. it is designed at least in a two-stage manner. Correspondingly more piston-cylinder units are provided, in the case that more stages are envisaged. Thereby, at least one piston-cylinder unit is provided for each stage. According to the invention, each piston-cylinder unit is provided in each case with a separate linear drive for moving the piston. This means that the piston of the first piston-cylinder unit, i.e. of the first stage, is moved via a separate linear drive, and the piston of the second piston-cylinder unit, i.e. of the second stage, is driven by an individual separate linear drive. Thus one provides a separate linear drive for moving the piston for each stage, i.e. for each piston-cylinder unit which forms a stage. This means that here, one makes do without a common drive crank shaft and thus a mechanical coupling of the movement of the pistons of the individual piston-cylinder units. A synchronization or coupling of the movement of the individual pistons of the piston-cylinder unit, according to the invention, is effected in a purely control-technological manner by controlling the linear drives.
- For this, according to the invention, a control device is provided, which is designed in a manner such that the linear drives may be controlled by the control device in an individual manner with regard to the speed and stroke. This means that the control device is designed such that it may activate the linear drives of the individual piston-cylinder units independently of one another, i.e. the stroke of the piston and also the movement speed of the piston may be separately controlled or set for each linear drive. Moreover, the starting point in time and the end point in time of the piston movement may be separately set for each piston-cylinder unit, and be changed as the case may be, by the control device suitably activating the respective associated linear drive of the piston-cylinder unit, i.e., by the control device beginning and stopping the piston movement.
- One may set the multi-stage piston compressor to different delivery powers and pressures in a flexible manner due to the fact that one forgoes the mechanical movement coupling of the individual pistons. Thus, for example, the speed of the pistons may be varied, if a reduced volume flow is desired. Thereby, the stroke and speed of all pistons does not need to be increased or reduced to the same extent, but rather it is possible due to the inventive independent control of the drives, to vary the stroke and the speed of the individual pistons of the different stages independently of one another. In particular, it is possible to change the displacement volume by changing the stroke, for example of the second stage, in dependence on the pressure increase, which takes place in the first stage.
- Preferably, the control device is thus designed in a manner such that the stage pressure ratio of the piston-cylinder unit may be changed by the individual control of the linear drives of the at least two piston-cylinder units. This is not possible with conventional piston compressors, which have a common crank shaft driving all pistons, since the pressure ratio and the volume ratio between the individual stages are matched to one another in a fixed manner. According to the invention, it is possible to change the stage pressure ratios of the individual stages by the mechanically independent drives of the nearest piston-cylinder units and the associated individual control. If the stage pressure ratio of a preceding stage, for example of the first stage, is increased, then accordingly, the displacement volume may be adapted by reducing the stroke in the subsequent stage, i.e., for example of the second stage. The stage pressure ratio thereby may likewise be changed by changing the stroke. Thereby, it is simultaneously possible to adapt the rates of stroke such that the individual stages, i.e. the individual piston-cylinder units, operate at the same frequency, even with a different stroke. Moreover, the dead space in the cylinder may be reduced, i.e. the volumetric losses may be reduced, by the individual control of the drives, since the upper and lower dead point may be moved to in a precise manner by the linear drive and the more precise control.
- According to a preferred embodiment, the at least two piston-cylinder units are designed in a manner such that their cylinders have differently large inner cross sections, i.e. in particular different diameters. The associated pistons thereby are adapted with regard to their cross section or diameter to the inner cross section of the cylinders. By this design, in the second stage of the compressor, which must have a lower displacement volume than the first stage due to the higher pressure, one succeeds in this reduced displacement volume not only being achieved by changing the stroke by the linear drive, but also by a constructional adaptation of the piston-cylinder unit of the second and following stages. This means that the inner cross section preferably decreases from stage to stage. The volume ratio between the individual cylinders is mechanically predefined in this manner, but it does not thereby also automatically fix the pressure ratios or stage pressure ratios at the stages, on account of the separate linear drives. Rather, these may still yet be changed by changing the stroke of the respective linear drive by suitable programming or setting of the control device. Thus, expressed simply, a coarse volume adaption is achieved by the mechanical size graduation of the cylinders, while the individual fine adaptation is achieved by the control device by the individual control of the stroke of the linear drives.
- Further preferably, the linear drives in each case comprise a rotating drive motor, in particular a servomotor, and a spindle drive, which converts the rotational movement of the drive motor into a linear movement for the piston. Sufficiently large forces may be applied onto the piston by such a drive. Furthermore, this may be controlled or regulated (controlled with a closed loop) in a precise manner with regard to its stroke and rate of travel. For this, positioning sensors may be provided on the piston, the spindle drive and/or the drive motor, in order to exactly detect the current position of the piston, and to precisely regulate the movement of the piston by control or regulation of the drive motor. The control device is accordingly designed to process the signals detected by the sensors, and to activate the drive motor while taking these signals into account. The spindle drive may be designed in a known manner, for example with a ball and screw. Preferably, the spindle drive is permanently lubricated, in particular lubricated for life, so than no continuous lubricant supply is necessary on operation. However, it is to be understood that other differently designed linear drives may also be applied, which are suitable for linearly moving a piston, and being activated individually by the control device. These in particular may also be other electrical linear drives. Thus, as the case may be, suitable gear means may be provided, in order to convert a rotating movement into a linear movement. However, the linear movement, according to the invention, is variable in stroke and speed by the control device.
- Further preferably, the piston-cylinder units are designed in a dry-running manner. Thus, one may forego lubrication on operation, which significantly simplifies the complete construction of the compressor, and permits an application where a lubricant contamination of the gas to be compressed must be avoided.
- According to a further preferred embodiment, an intermediate cooler may be arranged between two piston-cylinder units. This cools the compressed gas exiting from a first piston-cylinder unit, before it enters into the subsequent second piston-cylinder unit of the second stage of the compressor. Accordingly, such an intermediate cooler may also be arranged between a second and third, third and fourth stage etc., depending on how many stages the compressor has. Moreover, such a cooler may also be arranged at the exit side of the last stage.
- Further preferably, the piston-cylinder units in each case may be designed in a double-stroke manner, so that a delivery or compression is effected with the forward stroke as well as backward stroke.
- According to a particular embodiment of the invention, a switch-over valve is arranged on the exit side of at least a first piston-cylinder unit, by which valve the exit-side flow path may be switched between a subsequent second piston-cylinder unit and an exit conduit, preferably an exit conduit for several piston-cylinder units. This switch-over valve may also be actuated via the control device or, however, may be manually actuatable. Such a switch-over valve permits the piston compressor according to the invention to be converted from a multi-stage operation into a multi-flow operation, in which the individual piston-cylinder units of the several stages are not arranged in series, but are operated connected in parallel. Such an application may then be preferred if a larger volume flow is desired, with a lower pressure ratio between the entry pressure and the exit pressure of the compressor. It may also be possible, depending on the number of stages or piston-cylinder units in the piston compressor, not to connect all piston-cylinder units in parallel, but only individual ones. Moreover, by the use of such a switch-over valve, it is also possible to completely switch off individual piston-cylinder units. Thus, for example, with a three-stage piston compressor, the switch-over valve, which is arranged on the exit side of the second stage, i.e. of the second piston-cylinder unit, may be switched over such that the flow path no longer leads to the third piston-cylinder unit, but the flow is deflected directly into the exit conduit of the piston compressor. Then, for the thus separated or disconnected piston-cylinder unit, the linear drive is not set into operation at all by the control device. The efficiency of the compressor in such an operating mode may be increased in this manner, since the power loss may be reduced.
- The control device is preferably designed as a memory-programmable control, at which certain exit parameters, in particular desired pressure and delivery volume, may be set. Moreover, the control device may be designed such that it processes the signals of different sensors and controls the linear drives of the individual stages or piston-cylinder units, while taking into account these parameters detected by the sensors. These may be, for example, pressure sensors or temperature sensors, which are arranged at the entry side and exit side of the compressor and/or between the individual stages of the compressor, in order to monitor the operating condition. The pressure signals and/or temperature signals may then, for example, be taken into account by the control device, in order to control the stroke and speed of the linear drives, such that desired defined pressure values or pressure ratios may be achieved by the compressor. Relatively or additionally, a monitoring of the volume flow in a corresponding manner would also be possible.
- The foregoing summary, as well as the following detailed description of the invention, will be better understood when read in conjunction with the appended drawings. For the purpose of illustrating the invention, there are shown in the drawings embodiments which are presently preferred. It should be understood, however, that the invention is not limited to the precise arrangements and instrumentalities shown. In the drawings:
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FIG. 1 is a schematic, perspective view of a three-stage piston compressor according to one embodiment of the present invention; -
FIG. 2 is a schematic, perspective view of a three-stage piston compressor according to a second embodiment of the invention; -
FIG. 3 a schematic connection diagram of the compressor according toFIG. 2 ; and -
FIG. 4 a schematic, perspective, sectional view of a cylinder usable in piston compressors of the present invention. - The piston compressor shown in
FIG. 1 is designed in a three-stage manner and accordingly comprises three piston-cylinder units cylinder units FIG. 4 , consist in each case of acylinder 8 which is cylindrical in cross section and of apiston 10 which is linearly movable therein. Thepiston 10 is connected to apiston rod 12. Thecylinder 8 in a known manner comprises inlet valves and outlet valves, which may be designed as spring-biased check valves, which are suitably connected to the entry conduits and exit conduits. - According to the invention, each piston-
cylinder unit linear drive cylinder unit 2 comprises alinear drive 14 which is connected to thepiston rod 12 of thepiston cylinder unit 2, in order to move itspiston 10 linearly in the inside of thecylinder 8. Correspondingly, the piston-cylinder unit 4 is connected to its ownlinear drive 16, which moves thepiston 10 of the second piston-cylinder unit 4. The third piston-cylinder unit 6 has its ownlinear drive 18, which moves thepiston 10 of the piston-cylinder unit 6 in itscylinder 8. - The linear drives 14, 16, 18 are designed as spindle drives, which are driven respectively by a
servomotor servomotor 20 is assigned to thelinear drive 14, theservomotor 22 to thelinear drive 16, and theservomotor 24 to thelinear drive 18. In this regard, each piston-cylinder unit pistons 10 may be moved in a very precise manner via thelinear drives - The
servomotors linear drives electrical leads 26 to thecontrol device 28, which activates or regulates thelinear drives servomotors - An electronic coupling of the drives of the piston-
cylinder units control device 28. Compared to a mechanical coupling, as is achieved with conventional piston compressors via the common crank shaft, this electronic coupling has the advantage that the coupling is variable and may be changed in thecontrol device 28 according to different control programs or regulation programs. Thus, the stroke and rate of travel of each individuallinear drive control device 28. This means that the pistons of each piston-cylinder unit - The first piston-
cylinder unit 2 comprises agas inlet 30. Theexit opening 32 of the first piston-cylinder unit 2 is connected via aconduit 33 to the entry opening 34 of the second piston-cylinder unit 4. Theexit opening 36 of the second piston-cylinder unit 4 is connected via aconduit 37 to the entry opening 38 of the third piston-cylinder unit 6. Theexit opening 40 of the third piston-cylinder unit is connected to apressure conduit 42, which forms the exit conduit of the compressor. In this manner, the gas entering intogas inlet 30 is compressed in three stages in the piston-cylinder units cylinder units cylinder unit 4, which forms the second stage of the compressor, has a smaller cross section, i.e., a smaller inner diameter of thecylinder 8 and a smaller diameter of the associatedpiston 10, than with the first piston-cylinder unit 2. Correspondingly, the cross section of the third piston-cylinder unit 6 is once again smaller than that of the second piston-cylinder unit 4. These size changes preferably correspond to the ratio of the pressure increase from stage to stage, i.e., from piston-cylinder unit 2 to piston-cylinder unit 4, or from piston-cylinder unit 4 to piston-cylinder unit 6. Since the stage pressure ratio is variable with the system according to the invention, the size graduation in cross section of the piston-cylinder units respective piston 10 via the individuallinear drive piston 10 according to the invention is specifically not predefined, but is variable via the associatedlinear drive - The
control device 28 is preferably designed as a memory-programmable control device and comprises a display andinput device 44, which, for example, consists of a suitable keyboard and a display or of a touch-sensitive display. Alternatively or additionally, one may provide interfaces to computer systems. Alternatively, thecontrol device 28 may also be integrated into a computer system, and theconduits 26 connected via suitable interfaces. Furthermore, thecontrol device 28 may yet process different sensor signals as are explained byFIG. 3 . Moreover, it may obtain position signals from thelinear drives servomotors piston 10 in thecylinder 12 for each piston-cylinder unit - It is possible to move the
piston 10 in a very precise manner in thecylinder 12 by thelinear drives piston 10 may be moved further toward the axial end wall of thecylinder 12 than with conventional systems, ideally almost completely up to the end wall. The volumetric efficiency of the system may be increased thereby. Moreover, the rate of travel of thepiston 10 may be precisely set and controlled or regulated by thecontrol device 28. Thereby, the rate of travel is preferably selected to be slower, preferably slower than 2 m/s, further preferably below 1 m/s. This leads to lower vibrations and to a low wear of the system. - Certain nominal values may be set on the compressor via the
control device 28, in particular the desired exit pressure at the exit opening 40 of the third piston-cylinder unit 6. A desired volume flow may also be preset. Thecontrol device 28, depending on these variables, individually activates the threelinear drives servomotors pistons 10 of the piston-cylinder units cylinder unit gas inlet 30 and the exit opening 32 of the first piston-cylinder unit 2, the pressure difference between theentry opening 34 and the exit opening 36 of the second piston-cylinder unit 4, and the pressure difference between theentry opening 38 and the exit opening 40 of the third piston-cylinder unit 6, may be individually set by the control device by a change of the stroke of the associatedpiston 10 by a suitable regulation of thelinear drive control device 28, in order to ensure that all three piston-cylinder units cylinder units control unit 28. - With the embodiment shown in
FIG. 1 , switch-overvalves conduits cylinder unit 2 and the second piston-cylinder unit 4, as well as between the second piston-cylinder unit 4 and the third piston-cylinder unit 6. This permits individual stages of the compressor to be completely disconnected. Thus, the switch-overvalve 46 may switch the flow path at the exit side of the first piston-cylinder unit 2 between theentry opening 34 and the second piston-cylinder unit 4 and an exit conduit 50. The exit conduit 50 in the shown example is connected to thepressure conduit 42, but it is also conceivable for thepressure conduit 42 and the exit conduit 50 to be designed as a common exit conduit. If the switch-overvalve 46 is switched such that the flow path runs to the entry opening 34 of the second piston-cylinder unit 4, the gas compressed in the first stage is thus led to the second piston-cylinder unit 4 as a second stage, in order to be further compressed there. If the switch-overvalve 46 is switched to the exit conduit 50, the gas exiting from theexit opening 32 is no longer led to the second piston-cylinder unit 4, but directly into thepressure conduit 42. The compression with this setting is then effected only by the first piston-cylinder unit 2, and the second piston-cylinder unit 4 and the third piston-cylinder unit 6 are thus disconnected. In that case, the associated drives in the form ofservomotors valve 48 functions in the same manner. If this is switched such that the flow on the exit side of theexit opening 36 is led into the exit conduit 50, then gas is no longer led to the entry opening 38 of the third piston-cylinder unit 6, and this is set out of function. The compressor in this condition operates as a two-stage compressor with the piston-cylinder units - The switch-over
valves valves exit openings valves entry openings cylinder units cylinder units servomotor valves -
FIG. 2 now shows an arrangement, which corresponds essentially to the arrangement according toFIG. 1 . There, the three piston-cylinder units pistons 10 act with the forward stroke as well as with the return stroke. Moreover, in each case,intermediate coolers cylinder units cylinder unit 6. Theintermediate cooler 52 is arranged in theconduit 33 between the piston-cylinder units intermediate cooler 44 in theconduit 37 between the piston-cylinder units cylinder unit 6. The intermediate coolers may be designed in a manner known per se as air coolers or water coolers. Due to the double-stroke construction, the first piston-cylinder unit comprises twoentry openings 58 connected to thegas inlet 30, and correspondingly twoexit openings 32 which are connected to theconduit 33 and theintermediate cooler 52 arranged in this. Theconduit 33 then leads to twoentry openings 34 of the second piston-cylinder unit 4. The second piston-cylinder unit 4 correspondingly comprises twoexit openings 36 which are connected to theconduit 37 and theintermediate cooler 54 situated in this. Theconduit 37 at the exit side of theintermediate cooler 54, leads to the twoentry openings 38 of the third piston-cylinder unit 6. The third piston-cylinder unit 6 correspondingly comprises twoexit openings 40, which lead to theintermediate cooler 56, which is connected at the exit side to thepressure conduit 42. The manner of functioning of the piston compressor according toFIG. 2 otherwise corresponds to the manner of functioning of the piston compressor according toFIG. 1 , which is described above, only that it operates in a double-stroke manner. It is to be understood that the switch-overvalves FIG. 2 and arranged in theconduits intermediate coolers 50 and 54. -
FIG. 3 once again schematically shows the flow paths with a piston compressor according toFIG. 2 . For simplification, the size differences between the piston-cylinder units FIG. 3 . The intermediate coolers are also not represented inFIG. 3 , wherein it is to be understood that a double-stroke, three-stage compressor, as is shown inFIG. 2 , may also be designed without an intermediate cooler. Alternatively, it would also be possible to provide suitable intermediate coolers with the compressor according toFIG. 1 . - It is additionally shown in
FIG. 3 , that a multitude of temperature sensors T and pressure sensors P are provided in the system. These temperature and pressure sensors are provided on the entry side and the exit side of the piston-cylinder units gas inlet 30, in theconduit 33, theconduit 37, as well as thepressure conduit 42. Moreover, temperature sensors are yet provided at each exit of the piston-cylinder units piston 10 may be detected independently of the temperature of the gas compressed with the return stroke of thepiston 10. The exit signals of the temperature sensors T and the pressure sensors P are likewise led to thecontrol device 28 via suitable signal leads or other suitable signal transmission paths, and the control device takes these into account as actual values when regulating thelinear drives servomotors intermediate coolers control device 28, for example by adapting the fan rotational speed of the coolers. Thus the cooling power may be adapted to the detected actual values of the temperature at the exit side of theindividual stages - Apart from the already mentioned advantages, the piston-
cylinder units - It will be appreciated by those skilled in the art that changes could be made to the embodiments described above without departing from the broad inventive concept thereof. It is understood, therefore, that this invention is not limited to the particular embodiments disclosed, but it is intended to cover modifications within the spirit and scope of the present invention as defined by the appended claims.
Claims (8)
1. A multi-stage piston compressor comprising at least two piston-cylinder units (2, 4, 6), each of the units having a separate linear drive (14, 16, 18) for moving the piston, and a control device (28) designed such that the linear drives (14, 16, 18) are controllable individually in speed and stroke.
2. The multi-stage piston compressor according to claim 1 , wherein the control device (28) is designed such that a stage pressure ratio of the piston-cylinder units (2, 4, 6) may be changed by the individual control of the linear drives (14, 16, 18) of the at least two piston-cylinder units (2, 4, 6).
3. The multi-stage piston compressor according to claim 1 , wherein the at least two piston-cylinder units (2, 4, 6) are designed such that cylinders (12) of the respective piston-cylinder units have differently large inner cross sections.
4. The multi-stage piston compressor according to claim 1 , wherein the linear drives (14, 16, 18) have respective rotating drive motors (20, 22, 24) and respective spindle drives, which convert a rotational movement of the drive motor (20, 22, 24) into a linear movement for respective pistons (10).
5. The multi-stage piston compressor according to claim 1 , wherein the piston-cylinder units (2, 4, 6) are designed as dry-running.
6. The multi-stage piston compressor according to claim 1 , further comprising respective intermediate coolers (52, 54, 56) arranged between the at least two piston-cylinder units (2, 4, 6).
7. The multi-stage piston compressor according to claim 1 , wherein the piston-cylinder units (2, 4, 6) are designed respectively as double-stroke.
8. The multi-stage piston compressor according to claim 1 , further comprising a switch-over valve (46, 48) arranged on an exit side of at least one of the first piston-cylinder units (2, 4), wherein the switch-over valve located at an exit-side flow path may be switched between a subsequent second piston-cylinder unit (4, 6) and an exit conduit (50).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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EP08010771.7 | 2008-06-13 | ||
EP08010771.7A EP2133568B1 (en) | 2008-06-13 | 2008-06-13 | Multi-stage piston compressor |
Publications (1)
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US20090311114A1 true US20090311114A1 (en) | 2009-12-17 |
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Family Applications (1)
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US12/477,272 Abandoned US20090311114A1 (en) | 2008-06-13 | 2009-06-03 | Multi-stage piston compressor |
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US (1) | US20090311114A1 (en) |
EP (1) | EP2133568B1 (en) |
ES (1) | ES2478629T3 (en) |
PL (1) | PL2133568T3 (en) |
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2008
- 2008-06-13 EP EP08010771.7A patent/EP2133568B1/en not_active Not-in-force
- 2008-06-13 PL PL08010771T patent/PL2133568T3/en unknown
- 2008-06-13 ES ES08010771.7T patent/ES2478629T3/en active Active
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2009
- 2009-06-03 US US12/477,272 patent/US20090311114A1/en not_active Abandoned
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Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
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US20150361970A1 (en) * | 2013-02-04 | 2015-12-17 | Parker-Hannifin Corporation ("Parker") | Gas compressor |
US20150322934A1 (en) * | 2014-05-09 | 2015-11-12 | Westinghouse Air Brake Technologies Corporation | "Compressor Cooled By a Temperature Controlled Fan" |
US9951763B2 (en) * | 2014-05-09 | 2018-04-24 | Westinghouse Air Brake Technologies Corporation | Compressor cooled by a temperature controlled fan |
CN107061223A (en) * | 2017-06-15 | 2017-08-18 | 西安交通大学 | A kind of helicopter compresses preparation facilities with high pressure oxygen level Four |
EP3502470A1 (en) * | 2017-12-21 | 2019-06-26 | Haskel International, LLC | Electric driven gas booster |
US11519402B2 (en) | 2017-12-21 | 2022-12-06 | Haskel International, Llc | Electric driven gas booster |
KR20190138742A (en) * | 2018-06-06 | 2019-12-16 | 가부시키가이샤 고베 세이코쇼 | Compression device |
US11085429B2 (en) | 2018-06-06 | 2021-08-10 | Kobe Steel, Ltd. | Compression device |
KR102302946B1 (en) * | 2018-06-06 | 2021-09-17 | 가부시키가이샤 고베 세이코쇼 | Compression device |
CN110566441A (en) * | 2018-06-06 | 2019-12-13 | 株式会社神户制钢所 | Compression device |
DE102020126696A1 (en) | 2020-10-12 | 2022-04-14 | Mehrer Compression GmbH | Compressor for compressing gases |
US20220170456A1 (en) * | 2020-11-30 | 2022-06-02 | Fluke Corporation | Multi-stage electric gas pump |
US11905943B2 (en) * | 2020-11-30 | 2024-02-20 | Fluke Corporation | Multi-stage electric gas pump |
Also Published As
Publication number | Publication date |
---|---|
EP2133568B1 (en) | 2014-04-30 |
ES2478629T3 (en) | 2014-07-22 |
PL2133568T3 (en) | 2014-09-30 |
EP2133568A1 (en) | 2009-12-16 |
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Legal Events
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AS | Assignment |
Owner name: J.P. SAUER & SOHN MASCHINENBAU GMBH, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SCHULZ, HARALD;TITTEL, ROLAND;REEL/FRAME:022772/0323 Effective date: 20090528 |
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AS | Assignment |
Owner name: BORSIG COMPRESSOR PARTS GMBH, GERMANY Free format text: NUNC PRO TUNC ASSIGNMENT;ASSIGNOR:J.P. SAUER & SOHN MASCHINENBAU GMBH;REEL/FRAME:027564/0626 Effective date: 20111206 |
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