EP3812582A1 - Piston compressor and method for operating the same - Google Patents
Piston compressor and method for operating the same Download PDFInfo
- Publication number
- EP3812582A1 EP3812582A1 EP19204408.9A EP19204408A EP3812582A1 EP 3812582 A1 EP3812582 A1 EP 3812582A1 EP 19204408 A EP19204408 A EP 19204408A EP 3812582 A1 EP3812582 A1 EP 3812582A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- piston rod
- magnetic bearing
- longitudinal direction
- packing seal
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
- 238000000034 method Methods 0.000 title claims description 13
- 238000012856 packing Methods 0.000 claims abstract description 48
- 238000001816 cooling Methods 0.000 claims description 13
- 238000007789 sealing Methods 0.000 claims description 13
- 238000006073 displacement reaction Methods 0.000 claims description 10
- 239000002826 coolant Substances 0.000 claims description 2
- 230000005484 gravity Effects 0.000 description 6
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 239000000110 cooling liquid Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000002655 kraft paper Substances 0.000 description 1
- 238000011017 operating method Methods 0.000 description 1
Images
Classifications
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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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
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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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
- F04B39/0022—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons piston rods
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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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
- F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
- F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
- F04B39/042—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod sealing being provided on the piston
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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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/121—Casings
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/122—Cylinder block
-
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
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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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/08—Cooling; Heating; Preventing freezing
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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
- F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
- F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/50—Bearings
- F05B2240/51—Bearings magnetic
- F05B2240/515—Bearings magnetic electromagnetic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/57—Seals
Definitions
- the invention relates to a reciprocating compressor and a method for operating the same.
- WO2014 / 139565A1 discloses a reciprocating compressor with a horizontally extending cylinder in which a reciprocating piston is arranged in the horizontal direction.
- This piston compressor has the disadvantage that the sealing rings are subject to relatively great wear and tear, and that the piston compressor can only be operated at a relatively low speed.
- the object of the invention is to design a more advantageous piston compressor which preferably has a piston that can move in the horizontal direction.
- a piston compressor for compressing a gas comprising a cylinder running essentially in the horizontal direction and comprising a piston, a piston rod, a packing seal, a cross head and a drive, the piston being arranged movably in a longitudinal direction within the cylinder is, wherein the piston is connected to the crosshead via a piston rod, wherein a packing seal is arranged between the piston and the crosshead, through which the piston rod extends, and wherein the crosshead is driven by the drive, wherein between the piston and the crosshead also a controllable magnetic bearing is arranged, wherein the magnetic bearing can bring about a magnetic force on the piston rod at least perpendicular to the longitudinal direction, and wherein a control device controls the magnetic force caused by the magnetic bearing on the piston rod.
- the object is further achieved in particular with a method for operating a reciprocating compressor comprising a piston which is moved back and forth in a longitudinal direction within a cylinder, the longitudinal direction running essentially in the horizontal direction, the piston being driven via a piston rod, wherein a controllable, at least perpendicular to the A magnetic force acting in the longitudinal direction is exerted on the piston rod and thereby a relief force is brought about on the piston via the piston rod, the magnetic force being controlled as a function of a state variable.
- the piston compressor according to the invention for compressing a gas comprises a controllable magnetic bearing which is arranged between a piston and a cross head of the piston compressor, a piston rod connecting the piston to the cross head, the piston rod running through the magnetic magnetic bearing, and the magnetic bearing at least perpendicular to the In the direction of extension of the piston rod, a controllable, magnetic force of attraction exerts on the piston rod in order to preferably bring about a vertically upwardly directed force on the piston rod.
- the controllable magnetic bearing is preferably designed as a radial bearing. However, the magnetic bearing could also be designed in such a way that the magnetic force only acts in one direction or in one dimension, preferably in the direction opposite to gravity.
- the piston compressor comprises at least one cylinder as well as a piston arranged to be movable back and forth within the cylinder, the cylinder interior and thus also the movement of the piston preferably running in the horizontal direction or essentially in the horizontal direction, such a piston compressor also being a horizontal piston compressor referred to as. It is known to provide pistons movable in the horizontal direction with a so-called guide ring which rests on the inner surface of the cylinder.
- the attractive force exerted on the piston rod by the magnetic bearing at least in the vertical direction and / or that exerted on the piston rod is that the bearing force of a piston supported on the inner surface of the cylinder is reduced, or that the piston or the guide ring no longer touches the inner surface of the cylinder, so that the piston or the guide ring of the piston either only has a reduced bearing force the inner surface of the cylinder rests, and particularly advantageously moves back and forth within the cylinder without touching the inner surface of the cylinder.
- the piston of the piston compressor according to the invention is particularly advantageously designed as a labyrinth piston, such a labyrinth piston, as is known per se, having a labyrinth structure on its surface which serves to seal between the piston and the inner surface of the cylinder.
- the attractive force brought about by the magnetic bearing on the piston rod is preferably controlled in such a way that the piston moving back and forth does not touch the inner surface of the cylinder along the entire stroke.
- the piston compression according to the invention is, however, also suitable for pistons with piston rings and, if necessary, additionally having guide rings.
- the piston compressor according to the invention also has the advantage that it can be operated with a higher number of revolutions or with a higher mean piston speed, since the piston or the guide ring is either the inner wall of the cylinder no longer touched at all, or only rests on the inner wall of the cylinder with reduced contact force.
- Such an operation at a higher speed of rotation is particularly advantageous in a piston compressor with a so-called dry-running piston, i.e. a labyrinth piston, or a piston with self-lubricating sealing rings, i.e. a piston whose piston or sealing rings are not oil-lubricated, which is also called a unlubricated piston is called.
- the controllable magnetic bearing can either be used as a supporting bearing, by which the piston is held without touching the inner surface of the cylinder, or it can be used as a relief bearing, through which the force exerted by the piston on the inner surface of the cylinder is reduced, whereby the In this case, the piston touches the inner wall.
- the magnetic bearing is arranged at a predetermined point in the horizontal reciprocating compressor, whereas the position of the center of gravity of the piston changes continuously during operation due to the back and forth movement, so that the length of the piston rod between the magnetic magnetic bearing and the center of gravity changes during operation the lever arm formed by the piston is constantly changing.
- a control device provided for supplying power to the magnetic bearing is therefore advantageously designed such that the magnetic force caused by the magnetic magnetic bearing on the piston rod is controlled depending on the position of the piston or depending on the length of the aforementioned lever arm.
- at least one force acting in the vertical direction is exerted on the piston rod.
- the magnetic bearing is particularly advantageously designed as a radial bearing that, perpendicular to the longitudinal direction of the piston rod, a force controllable in two dimensions can exert on the piston rod, preferably a force in the vertical direction and a force in the horizontal direction.
- a radial bearing is advantageously controlled in such a way that the piston does not touch the inner surface of the cylinder in any of its possible positions during operation, neither a lower, an upper nor a lateral inner surface of the cylinder.
- the magnetic bearing is preferably controlled as a function of a measured state variable, in particular if the piston should not touch the inner surface of the cylinder during operation, the state variable comprising at least one of the following variables: displacement path of the piston in the cylinder, displacement path of the piston rod in the direction of the piston rod, Displacement of the piston rod perpendicular to the direction of the piston rod, as well as the angle of rotation of the drive shaft.
- the distance between the piston rod and the magnetic bearing is suitable as a state variable, at least in the vertical direction, and in particular the gap width in the magnetic bearing between the piston rod and the magnetic bearing.
- a reciprocating compressor usually comprises a packing seal with sealing rings, the piston rod running through this packing seal or its sealing rings in order to seal the cylinder interior from the outside.
- the magnetic bearings are also arranged in the packing seal.
- Such a modified packing seal comprising the magnetic bearing is designed particularly advantageously as an interchangeable part.
- Such a modified packing seal particularly advantageously has the same mass as previously known packing seals without magnetic bearings, so that the modified packing seal comprising the magnetic bearing can be used for installation in existing reciprocating compressors in order to retrofit them and improve them in quality.
- the modified packing seal also includes cooling channels.
- these cooling channels are connected to a cooling circuit in order to cool the magnetic magnetic bearing and / or the packing seal.
- Fig. 1 shows a piston compressor 1 for compressing a gas, comprising a cylinder 2 running in the horizontal direction and comprising a piston 3 movable within the cylinder 2 in the direction of the cylinder 2 or in the longitudinal direction L.
- the piston compressor 1 also comprises a piston rod 16, a packing seal 12 , a magnetic magnetic bearing 13, a cross head 17 with a linear guide 18, a push rod 19 and a drive, for example a crank 20 with a drive shaft 21.
- the piston 3 is double-acting in the illustrated embodiment and comprises sealing or piston rings 4 and a guide ring 5, the piston 3 dividing the interior of the cylinder 2 into a first interior 6 and a second interior 7, these two interior spaces each having an inlet valve 8, 9 and an outlet valve 10, 11 each.
- the cylinder 2 is connected to a housing 15 via an intermediate piece 14, the packing seal 12 and the magnetic magnetic bearing 13 also being arranged in the intermediate piece.
- the magnetic magnetic bearing 13 causes a magnetic force F m on the piston rod 16 at least in the vertical direction.
- a control device 22 detects a state variable Z of the piston compressor 1, for example the displacement s (t) of the piston in the cylinder, via a signal line 24 and a sensor (not shown) 7 as a function of time, the displacement path s (t) of the piston rod 16 and / or an angle of rotation a (t) of the drive shaft 21 as a function of time.
- the control device 22 controls the current in the magnets of the magnetic bearing 13 and thereby the magnetic force caused by the magnets on the piston rod 16 via a signal line 25.
- control device 22 can be operated in a control mode in which a state variable Z is measured and the magnetic force F m is changed as a function of the state variable Z. There is no need for feedback.
- Figure 3 shows an example of such a control mode in which the course of a curve K1 is specified, the curve K1 specifying the relationship between the state variable Z, in the present case the angle of rotation ⁇ of the drive shaft 21, and the magnetic force F m to be generated as a function of the angle of rotation ⁇ .
- the lever arm formed by the center of gravity S of the piston 3 and the magnetic bearing 13 is shortest, and the magnetic force F m is greatest at the top dead center because the lever arm formed by the piston rod 16 between the center of gravity S of the piston 3 and the magnetic bearing 13 is the longest is.
- the angle of rotation ⁇ is measured with a sensor (not shown) and fed to the control device 22 via the signal line 24.
- the curve profile K1 can, for example, be specified on the basis of empirical values.
- This embodiment is particularly advantageous when, as in Figure 1 shown, a piston 3 having a guide ring 5 is used, wherein the guide ring 5 rests against the inner surface of the cylinder 2, and
- the magnetic force F m serves to reduce the bearing force of the guide ring 5 on the inner surface of the cylinder 2, in order to thereby in particular reduce wear on the guide ring 5.
- the curve K1 shown only shows the course of the magnetic force Fm as a function of the crankshaft angle ⁇ between 0 ° and 180 °.
- a measuring device for example a sensor 26, is provided in order to measure the position of the piston rod 16 and / or the piston 3 at least in the vertical direction.
- Figure 2 shows an embodiment which measures the position of the piston rod 16 in the vertical direction.
- the sensor 26 is arranged close to the magnetic bearing 13 or even inside the magnetic bearing 13, the sensor 26 advantageously measuring the distance D between an upper coil core 13a of the magnetic bearing 13 and the surface of the piston rod 16.
- the magnetic bearing 13 advantageously comprises at least one upper coil core 13a with a coil 13b and a lower coil core 13c with a coil 13d.
- the magnetic bearing 13 can, as in Figure 6 also be designed as a radial magnetic bearing, with a plurality of electromagnets arranged distributed in the circumferential direction, their coils 13b, 13d preferably being individually controllable, so that the direction of the magnetic force caused on the piston rod 16 by a corresponding control of the coils 13b, 13d F m can be determined.
- the control device 22 is given a setpoint value for the distance D via the setpoint input 28, the control device 22 controlling the coils 13b, 13d with current via the signal line 25 in such a way that the piston rod 16 is independent of stroke s (t) or has an essentially constant, constant distance D from the crankshaft angle ⁇ (t) with respect to the upper coil core 13a.
- the piston rod 16 acts as a magnetic armature of the two coil cores 13a, 13b.
- the magnetic bearing 13 can preferably bring about an upwardly directed force as well as a downwardly directed magnetic attraction force on the piston rod 16, so that the position of the piston rod 16 relative to the magnetic bearing 13 can be controlled particularly precisely.
- the reciprocating compressor 1 is thus advantageously operated in such a way that a controllable magnetic force F m is exerted on the piston rod 16, so that a force F m acting at least in the vertical direction, or a relief force F h , is exerted on the piston via the piston rod 16 ) is effected on the piston 3, which counteracts the force of gravity F, the magnetic force F m being controlled or changed depending on a state variable Z such as the distance D, the stroke s (t) or the angle of rotation a (t) becomes.
- the in Figure 4 The longitudinal section shown shows a packing seal 12 known per se, comprising a plurality of chamber rings 12a in which sealing rings 12b are arranged.
- the packing seal 12 comprises a fastening part 12c, to which all chamber rings 12a are fastened in a manner not shown in detail are.
- the packing seal 12 is connected to a cylinder housing 2a of a cylinder 2 via the fastening part 12c, with a piston rod 16 running through the packing seal 12.
- the cylinder housing 2a has a recess which corresponds to an outer contour 12d of the packing seal 12, so that the entire packing seal 12 can be inserted into this recess and, if necessary, the entire packing seal 12 can be replaced.
- Figure 5 shows a longitudinal section through a packing seal 12 according to the invention comprising a magnetic bearing 13.
- Figure 6 shows a section of the magnetic bearing 13, which is designed as a radial bearing and comprises eight coil cores 13a, 13c, the two opposite coil cores 13a, 13c being provided with reference numerals.
- the coil cores 13a, 13c are wound with coils 13b, 13d.
- the end face 13e of the coil core 13a facing the piston rod 16 is shown.
- the packing seal 12 according to Figure 5 comprises two chamber rings 12a in which sealing rings 12b are arranged.
- the packing seal 12 also comprises two emergency bearings 12f, 12g, each with a bearing surface 12h, 12i.
- the packing seal 12 also comprises a holder 12k for a sensor 26, a sensor 26 being arranged at least at the top, and a plurality of sensors 26 preferably being arranged at a distance from one another in the circumferential direction.
- the packing seal 12 comprises a fastening part 12c, with which preferably all in Figure 5 components shown are connected.
- the packing seal 12 has an outer contour 12d.
- the outer contour 12d of the packing seal 12 according to the invention is dimensioned similarly or identically to that in FIG Figure 4 shown, known packing seal 12, so that the packing seal 12 according to the invention can be used in existing reciprocating compressors 1 having the known packing seal 12.
- a piston compressor 1 upgraded with the packing seal 12 according to the invention is also provided with a control device 22 so that existing piston compressor 1 can also be provided with the device according to the invention or existing piston compressor 1 can be operated with the method according to the invention.
- the packing seal according to the invention comprises 12, as in FIG Figure 5 also cooling channels 12l, which for example run inside the outer jacket 12e and / or inside the coil cores 13a, 13c, the cooling channels forming part of a cooling circuit in order to cool the magnetic bearing 13 and / or the packing seal 12.
- the cooling circuit is only shown schematically, with the supply lines and the discharge lines of the cooling circuit preferably being arranged to run through the fastening part 12c in such a way that the fastening part 12c has connections 12m for the cooling circuit accessible from the outside, preferably on its end face, and that the cooling circuit inside the packing seal 12 is predefined and fully configured, so that after the packing seal 12 has been installed, only the external coolant supply from the outside needs to be connected to the fastening part 12c in order to supply the cooling circuit inside the packing seal 12 with cooling liquid.
- Figure 5 are in particular the Connection channels arranged within the emergency bearing 12g and mutually fluidly connecting the cooling channels 12l are not shown.
- a piston compressor 1 comprising a piston 3 with piston or sealing rings 4 and a guide ring 5 is shown.
- the guide ring 5 could be dispensed with.
- the piston 3 could also be designed as a labyrinth piston, this labyrinth piston preferably not touching the inner wall of the cylinder 2.
Abstract
Der Kolbenverdichter (1) zum Verdichten eines Gases umfasst einen in Wesentlichen in horizontaler Richtung verlaufenden Zylinder (2) und umfasst einen Kolben (3), eine Kolbenstange (16), eine Packungsdichtung (12), einen Kreuzkopf (17) sowie einen Antrieb (21), wobei der Kolben (3) in einer Längsrichtung (L) beweglich innerhalb des Zylinders (2) angeordnet ist, wobei der Kolben (3) über eine Kolbenstange (16) mit dem Kreuzkopf (17) verbunden ist, wobei zwischen dem Kolben (3) und dem Kreuzkopf (17) eine Packungsdichtung (12) angeordnet ist, durch welche die Kolbenstange (16) verläuft, und wobei der Kreuzkopf (17) durch den Antrieb (21) angetrieben ist, wobei zwischen dem Kolben (3) und dem Kreuzkopf (17) zudem ein ansteuerbares Magnetlager (13) angeordnet ist, wobei das Magnetlager (13) zumindest senkrecht zur Längsrichtung (L) eine magnetische Kraft (Fm) auf die Kolbenstange (16) bewirken kann, und wobei eine Ansteuervorrichtung (22) die vom Magnetlager (13) auf die Kolbenstange (16) bewirkte magnetische Kraft (Fm) ansteuert. The piston compressor (1) for compressing a gas comprises a cylinder (2) running essentially in the horizontal direction and comprises a piston (3), a piston rod (16), a packing seal (12), a cross head (17) and a drive ( 21), the piston (3) being movably arranged in a longitudinal direction (L) within the cylinder (2), the piston (3) being connected to the cross head (17) via a piston rod (16), with between the piston (3) and the cross head (17) a packing seal (12) is arranged through which the piston rod (16) extends, and wherein the cross head (17) is driven by the drive (21), with between the piston (3) and a controllable magnetic bearing (13) is also arranged on the crosshead (17), the magnetic bearing (13) being able to exert a magnetic force (F m ) on the piston rod (16) at least perpendicular to the longitudinal direction (L), and wherein a control device (22 ) from the magnetic bearing (13) to the piston rod (16 ) caused magnetic force (F m ) controls.
Description
Die Erfindung betrifft einen Kolbenverdichter sowie ein Verfahren zum Betrieb desselben.The invention relates to a reciprocating compressor and a method for operating the same.
Das Dokument
Aufgabe der Erfindung ist es einen vorteilhafteren Kolbenverdichter auszubilden, der vorzugsweise einen in horizontaler Richtung beweglichen Kolben aufweist.The object of the invention is to design a more advantageous piston compressor which preferably has a piston that can move in the horizontal direction.
Diese Aufgabe wird gelöst mit einem Kolbenverdichtung aufweisend die Merkmale von Anspruch 1. Die abhängigen Ansprüche 2 bis 6 betreffen weitere vorteilhafte Ausgestaltungen. Die Aufgabe wird weiter gelöst mit einem Verfahren aufweisend die Merkmale von Anspruch 7.die abhängigen Ansprüche 8 bis 13 betreffen weitere vorteilhafte Verfahrensschritte.This object is achieved with a piston compression having the features of
Die Aufgabe wird insbesondere gelöst mit einem Kolbenverdichter zum Verdichten eines Gases, umfassend einen in Wesentlichen in horizontaler Richtung verlaufenden Zylinder sowie umfassend einen Kolben, eine Kolbenstange, eine Packungsdichtung, einen Kreuzkopf sowie einen Antrieb, wobei der Kolben in einer Längsrichtung beweglich innerhalb des Zylinders angeordnet ist, wobei der Kolben über eine Kolbenstange mit dem Kreuzkopf verbunden ist, wobei zwischen dem Kolben und dem Kreuzkopf eine Packungsdichtung angeordnet ist, durch welche die Kolbenstange verläuft, und wobei der Kreuzkopf durch den Antrieb angetrieben ist, wobei zwischen dem Kolben und dem Kreuzkopf zudem ein ansteuerbares Magnetlager angeordnet ist, wobei das Magnetlager zumindest senkrecht zur Längsrichtung eine magnetische Kraft auf die Kolbenstange bewirken kann, und wobei eine Ansteuervorrichtung die vom Magnetlager auf die Kolbenstange bewirkte magnetische Kraft ansteuert.
Die Aufgabe wird weiter insbesondere gelöst mit einem Verfahren zum Betrieb eines Kolbenverdichters umfassend einen Kolben, der in einer Längsrichtung innerhalb eines Zylinders hin und her bewegt wird, wobei die Längsrichtung im Wesentlichen in horizontaler Richtung verläuft, wobei der Kolben über eine Kolbenstange angetrieben wird, wobei eine ansteuerbare, zumindest senkrecht zur Längsrichtung wirkende, magnetische Kraft auf die Kolbenstange ausgeübt wird und dadurch über die Kolbenstange eine Entlastungskraft auf den Kolben bewirkt wird, wobei die magnetische Kraft in Abhängigkeit einer Zustandsgrösse angesteuert wird.The object is achieved in particular with a piston compressor for compressing a gas, comprising a cylinder running essentially in the horizontal direction and comprising a piston, a piston rod, a packing seal, a cross head and a drive, the piston being arranged movably in a longitudinal direction within the cylinder is, wherein the piston is connected to the crosshead via a piston rod, wherein a packing seal is arranged between the piston and the crosshead, through which the piston rod extends, and wherein the crosshead is driven by the drive, wherein between the piston and the crosshead also a controllable magnetic bearing is arranged, wherein the magnetic bearing can bring about a magnetic force on the piston rod at least perpendicular to the longitudinal direction, and wherein a control device controls the magnetic force caused by the magnetic bearing on the piston rod.
The object is further achieved in particular with a method for operating a reciprocating compressor comprising a piston which is moved back and forth in a longitudinal direction within a cylinder, the longitudinal direction running essentially in the horizontal direction, the piston being driven via a piston rod, wherein a controllable, at least perpendicular to the A magnetic force acting in the longitudinal direction is exerted on the piston rod and thereby a relief force is brought about on the piston via the piston rod, the magnetic force being controlled as a function of a state variable.
Der erfindungsgemässe Kolbenverdichter zum Verdichten eines Gases umfasst ein ansteuerbares Magnetlager, welches zwischen einem Kolben und einem Kreuzkopf des Kolbenverdichters angeordnet ist, wobei eine Kolbenstange den Kolben mit dem Kreuzkopf verbindet, wobei die Kolbenstange durch das magnetische Magnetlager verläuft, und wobei das Magnetlager zumindest senkrecht zur Verlaufsrichtung der Kolbenstange eine ansteuerbare, magnetische Anziehungskraft auf die Kolbenstange ausübt, um vorzugsweise eine vertikal nach oben gerichtete Kraft auf die Kolbenstange zu bewirken. Das ansteuerbare Magnetlager ist vorzugsweise als Radiallager ausgestaltet. Das Magnetlager könnte jedoch auch derart ausgestaltet sein, dass die Magnetkraft nur in einer Richtung bzw. in einer Dimension wirkt, vorzugsweise in zur Schwerkraft entgegengesetzten Richtung. Der Kolbenverdichter umfasst zumindest einen Zylinder sowie jeweils einen innerhalb des Zylinders hin- und her beweglich angeordneten Kolben, wobei der Zylinderinnenraum und somit auch die Bewegung des Kolbens vorzugsweise in horizontaler Richtung oder im Wesentlichen in horizontaler Richtung verläuft, wobei ein derartiger Kolbenverdichter auch als horizontaler Kolbenverdichter bezeichnet wird. Es ist bekannt in horizontaler Richtung bewegliche Kolben mit einem sogenannten Führungsring zu versehen, welcher an der Innenoberfläche des Zylinders aufliegt. Die vom Magnetlager zumindest in vertikaler Richtung auf die Kolbenstange ausgeübte Anziehungskraft und/oder die auf die Kolbenstange ausgeübte Abstossungskraft hat zur Folge, dass die Auflagekraft eines an der Innenoberfläche des Zylinders abgestützten Kolbens reduziert wird, oder dass der Kolben bzw. der Führungsring die Innenoberfläche des Zylinders nicht mehr berührt, sodass der Kolben bzw. der Führungsring des Kolbens entweder nur mit reduzierter Auflagekraft an der Innenoberfläche des Zylinders aufliegt, und besonders vorteilhaft sich ohne eine Berührung der Innenoberfläche des Zylinders innerhalb des Zylinders hin und her bewegt. Falls ein Kolben einen Führungsring aufweist, so ergibt sich aus der Verwendung des Magnetlagers der Vorteil, dass die Auflagekraft des Führungsrings an der Innenoberfläche und dadurch der Verschleiss des Führungsrings reduziert wird, sodass der Führungsring eine höhere Standzeit bzw. eine höhere Lebensdauer aufweist, bis dieser zu ersetzen ist. Besonders vorteilhaft ist der Kolben des erfindungsgemässen Kolbenverdichters als ein Labyrinthkolben ausgestaltet, wobei ein solcher Labyrinthkolben, wie an sich bekannt, an dessen Oberfläche eine Labyrinthstruktur aufweist, welche zur Abdichtung zwischen Kolben und Innenoberfläche des Zylinders dient. Die vom Magnetlager auf die Kolbenstange bewirkte Anziehungskraft wird dabei vorzugsweise derart angesteuert, dass der sich hin und her bewegende Kolben entlang des gesamten Hubweges die Innenoberfläche des Zylinders nicht berührt. Der erfindungsgemässe Kolbenverdichtung ist jedoch auch für Kolben mit Kolbenringen und gegebenenfalls zusätzlich aufweisend Führungsringe geeignet.The piston compressor according to the invention for compressing a gas comprises a controllable magnetic bearing which is arranged between a piston and a cross head of the piston compressor, a piston rod connecting the piston to the cross head, the piston rod running through the magnetic magnetic bearing, and the magnetic bearing at least perpendicular to the In the direction of extension of the piston rod, a controllable, magnetic force of attraction exerts on the piston rod in order to preferably bring about a vertically upwardly directed force on the piston rod. The controllable magnetic bearing is preferably designed as a radial bearing. However, the magnetic bearing could also be designed in such a way that the magnetic force only acts in one direction or in one dimension, preferably in the direction opposite to gravity. The piston compressor comprises at least one cylinder as well as a piston arranged to be movable back and forth within the cylinder, the cylinder interior and thus also the movement of the piston preferably running in the horizontal direction or essentially in the horizontal direction, such a piston compressor also being a horizontal piston compressor referred to as. It is known to provide pistons movable in the horizontal direction with a so-called guide ring which rests on the inner surface of the cylinder. The attractive force exerted on the piston rod by the magnetic bearing at least in the vertical direction and / or that exerted on the piston rod The effect of the repulsive force is that the bearing force of a piston supported on the inner surface of the cylinder is reduced, or that the piston or the guide ring no longer touches the inner surface of the cylinder, so that the piston or the guide ring of the piston either only has a reduced bearing force the inner surface of the cylinder rests, and particularly advantageously moves back and forth within the cylinder without touching the inner surface of the cylinder. If a piston has a guide ring, the use of the magnetic bearing has the advantage that the bearing force of the guide ring on the inner surface and thus the wear on the guide ring is reduced, so that the guide ring has a longer service life or a longer service life until it is to be replaced. The piston of the piston compressor according to the invention is particularly advantageously designed as a labyrinth piston, such a labyrinth piston, as is known per se, having a labyrinth structure on its surface which serves to seal between the piston and the inner surface of the cylinder. The attractive force brought about by the magnetic bearing on the piston rod is preferably controlled in such a way that the piston moving back and forth does not touch the inner surface of the cylinder along the entire stroke. The piston compression according to the invention is, however, also suitable for pistons with piston rings and, if necessary, additionally having guide rings.
Der erfindungsgemässe Kolbenverdichteter weist zudem den Vorteil auf, dass dieser mit einer höheren Drehungszahl beziehungsweise mit einer höheren mittleren Kolbengeschwindigkeit betreibbar ist, da der Kolben bzw. der Führungsring die Zylinderinnenwand entweder gar nicht mehr berührt, oder nur noch mit reduzierter Auflagekraft an der Zylinderinnenwand anliegt. Ein derartiger Betrieb mit höherer Umdrehungszahl ist insbesondere vorteilhaft bei einem Kolbenkompressor mit einem sogenannten trocken laufenden Kolben, das heisst einem Labyrinthkolben, oder einem Kolben mit selbstschmierenden Dichtungsringen, das heisst einem Kolben, dessen Kolben- bzw. Dichtungsringe nicht ölgeschmiert sind, was auch als ein ungeschmierter Kolben bezeichnet wird. Das ansteuerbare Magnetlager kann entweder als tragendes Lager verwendet werden, durch welches der Kolben ohne eine Berührung der Innenoberfläche des Zylinders gehalten wird, oder es kann als Entlastungslager verwendet werden, durch welches die vom Kolben auf die Innenoberfläche des Zylinders bewirkte Kraft reduziert wird, wobei der Kolben in diesem Fall die Innenwand berührt.The piston compressor according to the invention also has the advantage that it can be operated with a higher number of revolutions or with a higher mean piston speed, since the piston or the guide ring is either the inner wall of the cylinder no longer touched at all, or only rests on the inner wall of the cylinder with reduced contact force. Such an operation at a higher speed of rotation is particularly advantageous in a piston compressor with a so-called dry-running piston, i.e. a labyrinth piston, or a piston with self-lubricating sealing rings, i.e. a piston whose piston or sealing rings are not oil-lubricated, which is also called a unlubricated piston is called. The controllable magnetic bearing can either be used as a supporting bearing, by which the piston is held without touching the inner surface of the cylinder, or it can be used as a relief bearing, through which the force exerted by the piston on the inner surface of the cylinder is reduced, whereby the In this case, the piston touches the inner wall.
Das Magnetlager ist an einer vorgegebenen Stelle im horizontalen Kolbenverdichter angeordnet, wogegen sich die Lage des Schwerpunkts des Kolben durch die Hin- und Herbewegung während des Betriebs ständig verändert, sodass sich während des Betriebs die Länge des durch die Kolbenstange zwischen dem magnetischen Magnetlager und dem Schwerpunkt des Kolbens gebildeten Hebelarms ständig verändert. Eine zur Stromversorgung des Magnetlagers vorgesehene Ansteuervorrichtung ist daher vorteilhafterweise derart ausgestaltet, dass die vom magnetischen Magnetlager auf die Kolbenstange bewirkte magnetische Kraft in Abhängigkeit der Stellung des Kolbens beziehungsweise in Abhängigkeit der Länge des vorhin genannten Hebelarms angesteuert verändert wird. Vorteilhafterweise wird zumindest eine in vertikaler Richtung wirkende Kraft auf die Kolbenstange ausgeübt. Besonders vorteilhaft ist das Magnetlager als Radiallager ausgestaltet, das, senkrecht zur Längsrichtung der Kolbenstange, eine in zwei Dimensionen ansteuerbare Kraft auf die Kolbenstange ausüben kann, vorzugsweise eine Kraft in vertikaler Richtung und eine Kraft in horizontaler Richtung. Vorteilhafterweise wird ein solches Radiallager derart angesteuert, dass der Kolben während dem Betrieb in jeder seiner möglichen Stellungen die Innenoberfläche des Zylinders nicht berührt, weder eine untere noch eine obere noch eine seitliche Innenfläche des Zylinders.The magnetic bearing is arranged at a predetermined point in the horizontal reciprocating compressor, whereas the position of the center of gravity of the piston changes continuously during operation due to the back and forth movement, so that the length of the piston rod between the magnetic magnetic bearing and the center of gravity changes during operation the lever arm formed by the piston is constantly changing. A control device provided for supplying power to the magnetic bearing is therefore advantageously designed such that the magnetic force caused by the magnetic magnetic bearing on the piston rod is controlled depending on the position of the piston or depending on the length of the aforementioned lever arm. Advantageously, at least one force acting in the vertical direction is exerted on the piston rod. The magnetic bearing is particularly advantageously designed as a radial bearing that, perpendicular to the longitudinal direction of the piston rod, a force controllable in two dimensions can exert on the piston rod, preferably a force in the vertical direction and a force in the horizontal direction. Such a radial bearing is advantageously controlled in such a way that the piston does not touch the inner surface of the cylinder in any of its possible positions during operation, neither a lower, an upper nor a lateral inner surface of the cylinder.
Das Magnetlager wird vorzugsweise in Abhängigkeit einer gemessenen Zustandsgrösse angesteuert, insbesondere wenn der Kolben während dem Betrieb die Innenoberfläche des Zylinders nicht berührt soll, wobei die Zustandsgrösse zumindest eine der nachfolgenden Grössen umfasst: Verschiebeweg des Kolbens im Zylinder, Verschiebeweg der Kolbenstange in Verlaufsrichtung der Kolbenstange, Verschiebeweg der Kolbenstange senkrecht zur Verlaufsrichtung der Kolbenstange, sowie Drehwinkel der Antriebswelle. In einer weiteren vorteilhaften Ausgestaltung ist als Zustandsgrösse der Abstand der Kolbenstange bezüglich dem Magnetlager geeignet, zumindest in vertikaler Richtung, und insbesondere die Spaltbreite im Magnetlager zwischen Kolbenstange und Magnetlager.The magnetic bearing is preferably controlled as a function of a measured state variable, in particular if the piston should not touch the inner surface of the cylinder during operation, the state variable comprising at least one of the following variables: displacement path of the piston in the cylinder, displacement path of the piston rod in the direction of the piston rod, Displacement of the piston rod perpendicular to the direction of the piston rod, as well as the angle of rotation of the drive shaft. In a further advantageous embodiment, the distance between the piston rod and the magnetic bearing is suitable as a state variable, at least in the vertical direction, and in particular the gap width in the magnetic bearing between the piston rod and the magnetic bearing.
Ein Kolbenkompressor umfasst üblicherweise eine Packungsdichtung mit Dichtungsringen, wobei die Kolbenstange durch diese Packungsdichtung bzw. deren Dichtungsringe verläuft, um den Zylinderinnenraum gegen Aussen abzudichten. In einer besonders vorteilhaften Ausgestaltung sind in der Packungsdichtung nebst den Dichtungsringen zudem noch das Magnetlager angeordnet. Eine solche, modifizierte Packungsdichtung umfassend das Magnetlager ist besonders vorteilhaft als ein Austauschteil ausgestaltet. Besonders vorteilhaft weist eine solche modifizierte Packungsdichtung dieselben Masse auf wie bisher bekannte Packungsdichtungen ohne Magnetlager, sodass die modifizierte Packungsdichtung umfassend das Magnetlager zum Einbau in bestehende Kolbenkompressoren verwendet werden kann, um diese nachzurüsten und qualitativ zu verbessern.A reciprocating compressor usually comprises a packing seal with sealing rings, the piston rod running through this packing seal or its sealing rings in order to seal the cylinder interior from the outside. In a particularly advantageous embodiment, in addition to the sealing rings, the magnetic bearings are also arranged in the packing seal. Such a modified packing seal comprising the magnetic bearing is designed particularly advantageously as an interchangeable part. Such a modified packing seal particularly advantageously has the same mass as previously known packing seals without magnetic bearings, so that the modified packing seal comprising the magnetic bearing can be used for installation in existing reciprocating compressors in order to retrofit them and improve them in quality.
In einer weiteren, vorteilhaften Ausgestaltung umfasst die modifizierte Packungsdichtung zudem noch Kühlkanäle. Bei einer im Kolbenkompressor montierten, modifizierten Packungsdichtung sind diese Kühlkanäle mit einem Kühlkreislauf verbunden, um das magnetische Magnetlager und/oder die Packungsdichtung zu kühlen.In a further, advantageous embodiment, the modified packing seal also includes cooling channels. In the case of a modified packing seal installed in the reciprocating compressor, these cooling channels are connected to a cooling circuit in order to cool the magnetic magnetic bearing and / or the packing seal.
Die zur Erläuterung der Ausführungsbeispiele verwendeten Zeichnungen zeigen:
- Fig. 1
- einen schematisch vereinfachten Längsschnitt durch einen Kolbenverdichter;
- Fig. 2
- schematisch eine Regelungsvorrichtung;
- Fig. 3
- ein beispielhafter Verlauf der magnetischen Kraft in Funktion einer Zustandsgrösse, nämlich des Drehwinkels einer Antriebswelle;
- Fig. 4
- einen Längsschnitt durch eine bekannte Packungsdichtung;
- Fig. 5
- einen Längsschnitt durch eine Packungsdichtung gemäss der Erfindung;
- Fig. 6
- ein radiales Magnetlager.
- Fig. 1
- a schematically simplified longitudinal section through a reciprocating compressor;
- Fig. 2
- schematically a control device;
- Fig. 3
- an exemplary curve of the magnetic force as a function of a state variable, namely the angle of rotation of a drive shaft;
- Fig. 4
- a longitudinal section through a known packing seal;
- Fig. 5
- a longitudinal section through a packing seal according to the invention;
- Fig. 6
- a radial magnetic bearing.
Grundsätzlich sind in den Zeichnungen gleiche Teile mit gleichen Bezugszeichen versehen.In principle, the same parts are provided with the same reference symbols in the drawings.
Die Ansteuervorrichtung 22 kann in einer einfachen Ausführungsform in einem Ansteuermodus betrieben werden, bei welchem eine Zustandsgrösse Z gemessen wird, und die magnetische Kraft Fm in Funktion der Zustandsgrösse Z verändert wird. Dabei kann auf eine Rückkoppelung verzichtet werden.
In einer weiteren vorteilhaften Ausgestaltung ist eine Messvorrichtung, beispielsweise ein Sensor 26 vorgesehen, um die Lage der Kolbenstange 16 und/oder des Kolbens 3 zumindest in vertikaler Richtung zu messen.
In einem vorteilhaften Betriebsverfahren wird der Ansteuervorrichtung 22 über die Sollwertvorgabe 28 ein Sollwert für die Distanz D vorgegeben, wobei die Ansteuervorrichtung 22 die Spulen 13b, 13d derart über die Signalleitung 25 mit Strom ansteuert, der die Kolbenstange 16 unabhängig von Hub s(t) bzw. vom Kurbelwellenwinkel α(t) eine im Wesentliche gleichbleibende, konstante Distanz D bezüglich dem oberen Spulenkern 13a aufweist. Die Kolbenstange 16 wirkt dabei als magnetischer Anker der beiden Spulenkerne 13a, 13b. Vorzugsweise kann das Magnetlager 13 sowohl eine nach oben gerichtete Kraft als auch eine nach unten gerichtet magnetische Anziehungskraft auf die Kolbenstange 16 bewirken, sodass die Lage der Kolbenstange 16 relativ zum Magnetlager 13 besonders präzise ansteuerbar ist.In an advantageous operating method, the
Der Kolbenverdichters 1 wird somit vorteilhafterweise derart betrieben, dass eine ansteuerbare magnetische Kraft Fm auf die Kolbenstange 16 ausgeübt wird, sodass über die Kolbenstange 16 eine zumindest in vertikaler Richtung wirkende Kraft Fm, bzw. eine Entlastungskraft Fh, auf den Kolben (3) bewirkt wird auf den Kolben 3 bewirkt wird, welcher der Schwerkraft F entgegenwirkt, wobei die magnetische Kraft Fm abhängig von einer Zustandsgrösse Z wie beispielsweise der Distanz D, dem Hub s(t) oder dem Drehwinkel a(t) angesteuert bzw. verändert wird.The
Der in
In einer weiteren, vorteilhaften Ausgestaltung umfasst die erfindungsgemässe Packungsdichtung 12, wie in
Im Ausführungsbeispiel gemäss
Claims (15)
Priority Applications (13)
Application Number | Priority Date | Filing Date | Title |
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EP19204408.9A EP3812582A1 (en) | 2019-10-21 | 2019-10-21 | Piston compressor and method for operating the same |
CN202080073290.6A CN114787510A (en) | 2019-10-21 | 2020-10-21 | Packing seal for a piston compressor and method for operating the same |
JP2022523398A JP2023501892A (en) | 2019-10-21 | 2020-10-21 | Piston compressor and its operation method |
KR1020227017080A KR20220079997A (en) | 2019-10-21 | 2020-10-21 | Piston Compressor and How to Operate This Piston Compressor |
US17/770,839 US20220372963A1 (en) | 2019-10-21 | 2020-10-21 | Piston compressor and method for operating same |
PCT/EP2020/079673 WO2021078820A1 (en) | 2019-10-21 | 2020-10-21 | Packing seal for a piston compressor and method for operating same |
PCT/EP2020/079589 WO2021078781A1 (en) | 2019-10-21 | 2020-10-21 | Piston compressor and method for operating same |
CN202080073263.9A CN114829771A (en) | 2019-10-21 | 2020-10-21 | Piston compressor and method for operating the same |
EP20807665.3A EP4048891A1 (en) | 2019-10-21 | 2020-10-21 | Piston compressor and method for operating same |
EP20790173.7A EP4048892A1 (en) | 2019-10-21 | 2020-10-21 | Packing seal for a piston compressor and method for operating same |
JP2022523399A JP2023501893A (en) | 2019-10-21 | 2020-10-21 | Packing seal for piston compressor and method of operating piston compressor |
US17/770,832 US20220372962A1 (en) | 2019-10-21 | 2020-10-21 | Packing seal for a piston compressor and method for operating same |
KR1020227016882A KR20220079993A (en) | 2019-10-21 | 2020-10-21 | Packing Seals for Piston Compressors and How to Operate Piston Compressors |
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EP20790173.7A Pending EP4048892A1 (en) | 2019-10-21 | 2020-10-21 | Packing seal for a piston compressor and method for operating same |
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US11852108B1 (en) * | 2023-01-31 | 2023-12-26 | Innio Waukesha Gas Engines Inc. | Exhaust purge gas for compressor packing systems and methods |
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DE3805670A1 (en) * | 1988-02-24 | 1989-09-07 | Borsig Gmbh | Guide bearing for guiding a piston rod |
FR2754570A1 (en) * | 1996-10-14 | 1998-04-17 | Thome Crepelle | IMPROVEMENT ON RECISTLINE RECIPROCATING PISTON COMPRESSORS |
WO2006042866A1 (en) * | 2004-10-22 | 2006-04-27 | Burckhardt Compression Ag | Dry-running piston rod sealing arrangement, and method for sealing a piston rod using one such arrangement |
WO2014139565A1 (en) | 2013-03-13 | 2014-09-18 | Howden Thomassen Compressors Bv | Horizontal piston compressor |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11852108B1 (en) * | 2023-01-31 | 2023-12-26 | Innio Waukesha Gas Engines Inc. | Exhaust purge gas for compressor packing systems and methods |
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WO2021078781A1 (en) | 2021-04-29 |
KR20220079993A (en) | 2022-06-14 |
US20220372962A1 (en) | 2022-11-24 |
KR20220079997A (en) | 2022-06-14 |
JP2023501893A (en) | 2023-01-20 |
CN114787510A (en) | 2022-07-22 |
US20220372963A1 (en) | 2022-11-24 |
EP4048892A1 (en) | 2022-08-31 |
WO2021078820A1 (en) | 2021-04-29 |
EP4048891A1 (en) | 2022-08-31 |
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JP2023501892A (en) | 2023-01-20 |
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