EP3857065B1 - Compresseur à piston et son procédé de fonctionnement - Google Patents

Compresseur à piston et son procédé de fonctionnement Download PDF

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Publication number
EP3857065B1
EP3857065B1 EP19786900.1A EP19786900A EP3857065B1 EP 3857065 B1 EP3857065 B1 EP 3857065B1 EP 19786900 A EP19786900 A EP 19786900A EP 3857065 B1 EP3857065 B1 EP 3857065B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
piston
fluid
longitudinal direction
support arms
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.)
Active
Application number
EP19786900.1A
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German (de)
English (en)
Other versions
EP3857065A1 (fr
Inventor
Alexandre Voser
Reiner Schulz
Sandro BRUNNER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Burckhardt Compression AG
Original Assignee
Burckhardt Compression AG
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Publication date
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Publication of EP3857065A1 publication Critical patent/EP3857065A1/fr
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Classifications

    • 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
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
    • F04B15/08—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure the liquids having low boiling points
    • 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
    • F04B5/00—Machines or pumps with differential-surface pistons
    • F04B5/02—Machines or pumps with differential-surface pistons with double-acting pistons
    • 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
    • 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
    • F04B53/14—Pistons, piston-rods or piston-rod 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
    • 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
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/144—Adaptation of piston-rods
    • F04B53/146—Piston-rod guiding arrangements
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or 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
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/20—Other positive-displacement pumps
    • F04B19/22—Other positive-displacement pumps of reciprocating-piston type
    • 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
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
    • F04B15/08—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure the liquids having low boiling points
    • F04B2015/081—Liquefied gases
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
    • 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
    • F04B9/042—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 cams

Definitions

  • the invention relates to a piston compressor and a method for operating a piston compressor.
  • Liquid natural gas also referred to as “liquefied natural gas” or “LNG” for short, is natural gas that has been cooled to a temperature of at least -160 °C and that assumes a liquid state of aggregation at these low temperatures.
  • the pamphlet WO 2009/112479A1 discloses a reciprocating compressor for supplying natural gas fuel, the natural gas fuel being obtained by compressing exhaust gas discharged from liquid natural gas using the reciprocating compressor.
  • Such a piston compressor which has been tried and tested in itself, allows the exhaust gas of the liquid natural gas, which usually has a temperature of about -160° C.
  • Such a piston compressor has the advantage that natural gas in a wide temperature range of preferably between -160 °C and +100 °C and can then be compressed.
  • Such a piston compressor is, for example, able to compress an input fluid at a temperature of -160° C. to a compressed fluid at a temperature of -40° C. In this application, there is a temperature difference of around 120 °C between the inlet and outlet of the piston compressor. To date, it has been a major technical challenge to create an inexpensive piston compressor, in particular a labyrinth piston compressor, which is suitable for compressing a fluid which has a high temperature difference between the input fluid and the output fluid.
  • the object of the invention is to design a piston compressor which, despite the high temperature difference between the inlet and outlet, is suitable for compressing a fluid and which is economically advantageous.
  • a piston compressor comprising a cylinder and a piston arranged therein, a carrier housing with a crosshead mounted in the carrier housing, a spacer which connects the cylinder with the carrier housing, and a piston rod running in a longitudinal direction, which connects the crosshead with the Piston connects, with the spacer a
  • a plurality of support arms the support arms being connected to and supporting the cylinder.
  • a piston compressor comprising a cylinder and a piston arranged therein, a carrier housing with a crosshead mounted in the carrier housing, a spacer which connects the cylinder to the carrier housing, and a piston rod running in a longitudinal direction, which connects the crosshead with the piston, the spacer comprising a plurality of longitudinally extending support arms, the support arms being individually connected to the cylinder toward the cylinder.
  • the object is further achieved in particular with a method for operating a piston compressor comprising a cylinder and a piston arranged therein, a support housing with a crosshead mounted in the support housing, a spacer which connects the cylinder to the support housing, and a piston rod running in a longitudinal direction, which connects the crosshead to the piston, wherein thermal energy due to a thermal difference existing between the cylinder and the support housing is exchanged via a plurality of support arms.
  • the object is further achieved in particular with a method for operating a piston compressor comprising a cylinder and a piston arranged therein, a support housing with a crosshead mounted in the support housing, a spacer which connects the cylinder to the support housing, and a piston rod running in a longitudinal direction, which connects the crosshead to the piston, the spacer comprising a plurality of longitudinally extending support arms, the support arms for Cylinders are each individually connected to the cylinder via attachment points, so that thermal energy caused by a between the Attachment points applied heat difference is not exchanged directly in the circumferential direction to the longitudinal direction between the attachment points, but via the longitudinally extending support arms.
  • a labyrinth piston compressor comprises a piston and a cylinder, a labyrinth seal being formed at least for the piston and the cylinder wall of the cylinder.
  • the labyrinth seal is a non-contact seal.
  • the sealing effect is based on the lengthening of the flow path through the gap to be sealed, which significantly increases the flow resistance.
  • the lengthening of the travel is achieved by a surface structure of the piston and possibly also the cylinder wall.
  • the surface of the piston has a plurality of circumferential indentations spaced apart from one another in the longitudinal direction of the piston. Absolute tightness is not possible with this non-contact construction.
  • the labyrinth piston compressor comprising the labyrinth seal has the advantage that the labyrinth seal is contactless because the piston and the cylinder wall do not touch each other, and that therefore no lubrication is required between the piston and the cylinder wall.
  • Such a labyrinth piston compressor allows a so-called oil-free compression of a fluid because no lubricant, in particular no oil, is required to compress the fluid.
  • the piston of such a labyrinth piston compressor has no sealing rings since the labyrinth seal effects a seal.
  • the piston compressor according to the invention has the advantage that it can also be operated safely when the temperature of the fluid to be sucked in and the temperature of the compressed fluid to be discharged have a large temperature difference of, for example, 100° C. to 120° C. or even more.
  • the inventive piston compressor is designed such that the existing temperature differences do not result in any significant thermal stresses or any significant distortion of components of the piston compressor, or that the piston compressor is designed in such a way that an expansion of components of the piston compressor caused by the existing temperature difference takes place in such a way that the individual components expand relative to one another Due to the temperature difference can hardly be mutually shifted, so that the piston compressor can be operated safely and reliably regardless of the temperature differences.
  • the piston compressor according to the invention has the advantage that the at least one inlet valve and the at least one outlet valve are arranged in the cylinder cover, which has the advantage that a fluid to be compressed flows directly into the cylinder interior after flowing through the inlet valve, or that a compressed fluid when it leaves the cylinder interior immediately after it has flowed through the outlet valve, so that the piston compressor has an extremely small gas dead space or dead space or no dead space at all, within which a temperature transfer between the fluid and the piston compressor could take place, so that the piston compressor has relatively few contact surfaces that generate heat with the fluid could exchange .
  • the inventive piston compressor thus preferably, with the exception of the absolutely necessary contact surfaces of the inflow of the fluid to be compressed, the compression of the fluid to be compressed and the ejection of the compressed fluid ized fluids, preferably negligibly small or no additional contact surfaces and contact points between the piston compressor and the fluid being pumped, which limits heat transfer between the fluid and the piston compressor.
  • the cylinder and/or the piston of the reciprocating compressor is advantageously made of a metal with a thermal conductivity in the range between 100 and 300 (W/m K), preferably made of aluminum or an aluminum alloy.
  • the relatively high thermal conductivity means that during operation of the piston compressor, a temperature equilibrium is established in its components, the temperature differences between which are significantly smaller than the temperature differences between the inflowing fluid and the compressed, outflowing fluid.
  • the cylinder and the piston are particularly advantageously made of the same material.
  • the inlet valve and the outlet valve are preferably arranged symmetrically in the cylinder with respect to a plane of symmetry running along a center line of the cylinder.
  • a flange or hose arranged at the inlet valve or outlet valve, which is used to supply or drain off the fluid has a small contact surface with respect to the cylinder, which in turn reduces heat transfer between the flange or hose and the cylinder.
  • the flange or hose also has the advantage of
  • the piston compressor includes a support housing in which a crankshaft and at least one crosshead are preferably arranged.
  • the piston compressor according to the invention includes a spacer, which is connected to the support housing and the cylinder, on the one hand to hold the cylinder in a defined position relative to the support housing, and on the other hand to reduce any temperature flow between the cylinder and the support housing.
  • the spacer is connected to those areas with the cylinder at which the Average temperature or essentially the average temperature is applied.
  • the temperature differences that occur during operation of the piston compressor on the spacer between the cylinder and the support housing are kept within limits, with the spacer preferably being arranged in such a way that it has a heat distribution that runs symmetrically to the plane of symmetry, with the result that due to of the temperatures applied to the spacer, there is little or no distortion of the spacer.
  • the spacer preferably being arranged in such a way that it has a heat distribution that runs symmetrically to the plane of symmetry, with the result that due to of the temperatures applied to the spacer, there is little or no distortion of the spacer.
  • the cylinder and/or the piston consists of aluminum or an aluminum alloy, which is a metal that conducts heat very well.
  • the very good heat conduction in turn has the advantage that during the continuous operation of the piston compressor, a mean temperature or a mean operating temperature of the individual components of the compressor is established very quickly, and temperature peaks are thereby avoided.
  • the piston compressor according to the invention has the advantage that, in a preferred embodiment, it requires relatively few parts and that the moving parts can be chosen to be relatively low in mass.
  • FIG. 1 shows a longitudinal section through a piston compressor 1 comprising a cylinder 10 and a piston 20 arranged therein, comprising a carrier housing 60 with a crosshead 63 arranged therein with bearing part 63a, wherein the crosshead 63 can be driven via a crankshaft 61 and a connecting rod 62, and comprising a Spacer 40 with support section 41, the spacer 40 connecting the cylinder 10 to the carrier housing 60 and, as in FIG figure 1 shown, carries the cylinder 10 when the piston compressor 1 is arranged in an upright position.
  • the piston compressor 1 includes a piston rod 24 which connects the crosshead 63 to the piston 20 and drives the piston 20 .
  • the piston compressor 1 has a longitudinal axis L, which extends along the piston rod 24 in the center of the piston rod 24 .
  • the cylinder 10 comprises a first cylinder cover 11, a second cylinder cover 12 and a cylinder jacket 13 arranged between them.
  • the first cylinder cover 11 comprises an intake valve receiving opening 11a and an exhaust valve receiving opening 11b, in which an intake valve 90 or an exhaust valve 91 is arranged.
  • one flange 14 each is connected to the opening 11a, 11b, the flange 14 serving to supply or discharge a fluid between the outside of the cylinder 10 and an interior space 10a of the cylinder 10 . Fluids can be supplied or discharged, for example, via a hose 15 connected to the respective flange 14 .
  • the second cylinder cover 12 also includes an intake valve receiving opening 12a and an exhaust valve receiving opening 12b with intake valve 90 or exhaust valve 91 arranged therein.
  • the cylinder 10 or the piston 20 is designed to be double-acting, in that the piston 20 delimits a first cylinder interior 10a and a second cylinder interior 10b.
  • the cylinder jacket 13 could be dispensed with by making the first and second cylinder covers 11, 12 longer in the longitudinal direction L.
  • a first, a second and a third stuffing box chamber 50, 51.52 are arranged following the middle section 12h.
  • the spacer 40 has a spacer interior 40a, in which an oil scraper packing 55, shown only schematically, is arranged, preferably comprising a guide which encloses the piston rod 24.
  • an oil screen 54 is arranged on the piston rod 24 .
  • the carrier housing 60 has a bore 60a, which forms a sliding surface for the crosshead 63, so that the crosshead 63, the piston rod 24 connected to the crosshead 63 and the piston 20 connected to the piston rod 24 can move back and forth in the longitudinal direction L.
  • the sliding surface for the crosshead is lubricated, preferably with oil, this lubrication not being shown in detail.
  • Cylinder 10 and/or piston 20, and preferably also support housing 60 and crosshead 63 are made of a metal having a thermal conductivity in the range of preferably between 100 and 300 (W/m ⁇ K), preferably aluminum or an aluminum alloy .
  • the cylinder 10 and the piston 20, and preferably also the support housing 60 and the crosshead 63 are made of the same material, so that they have the same properties with regard to thermal expansion.
  • figure 2 shows a detailed view of the piston compressor 1 according to figure 1 , essentially the cylinder 10, the piston 20, the flanges 14 and the inlet and outlet valves 90, 91.
  • the cylinder 10 and the piston 20 are designed to be single-acting, for example by only having one inlet valve in the first cylinder cover 11 90 and an outlet valve 91 is arranged.
  • the cylinder 10 and the piston 20 are particularly advantageous, as shown in figure 2 shown, double-acting, with a first cylinder interior 10a, a second cylinder interior 10b and two intake valves 90 and two exhaust valves 91.
  • an intake valve 90 is thus provided in at least the first cylinder cover 11 or the second cylinder cover 12 and an outlet valve 91, and preferably as in figure 2 shown in both cylinder covers 11,12 each have an inlet valve 90 and an outlet valve 91 arranged.
  • the inlet valve 90 and the outlet valve 91 are arranged symmetrically with respect to a plane of symmetry S running in the longitudinal direction L along the piston rod 24.
  • Both inlet valves 90 and both outlet valves 91 are preferably as in FIG figure 2 shown arranged on the same side of the cylinder 10, i.e. as in FIG figure 2 shown, both to the left and both to the right of the plane of symmetry S.
  • the piston compressor according to the invention is particularly suitable for compressing a fluid whose inlet fluid F E flowing in via the inlet valve 90 and its outlet fluid F A flowing out via the outlet valve 91 have a high temperature difference of between 100° C. and 150° C., for example.
  • the inlet fluid F E for example exhaust gas from liquid natural gas
  • the outlet fluid F A can have a temperature of -40° C., so that the temperature difference is 120° C.
  • the symmetrical arrangement of inlet valve 90 and outlet valve 91 with respect to the plane of symmetry S has the advantage that the cylinder 10 and the piston 20 assume an average temperature during operation in the area of the plane of symmetry S or the longitudinal axis L running along the piston rod 24, where the temperature of the cylinder 10 and the piston 20 perpendicular to the longitudinal axis L usually decreases towards the intake valve 90 and increases towards the exhaust valve 91 .
  • the cylinder 10 preferably has only small temperature differences.
  • the cylinder 10 and the piston 20 Due to the fact that the cylinder 10 and the piston 20 have an average temperature in the area of the longitudinal axis L during operation, the cylinder 10, the piston 20 and the piston rod 24 experience no or negligible distortion caused by temperature differences in these parts, or changes in length caused by temperature differences.
  • the cylinder 10 and/or the piston 20 consists of a material with good thermal conductivity, for example aluminum, which has the advantage that the temperature differences present at the cylinder 10 and at the piston 20 during operation are reduced.
  • the piston compressor according to the invention is advantageously operated at ambient temperature. If exhaust gas from liquid natural gas is compressed with the piston compressor according to the invention, the outer surface of the cylinder 10 is heated with air at ambient temperature, which further reduces the temperature differences present at the cylinder 10, particularly when the cylinder 10 or at least the cylinder covers 11, 12 consists of a material that conducts heat well.
  • a gas space is understood to be the space between a fluid supply line 15 and the inlet valve 90 or the space between the outlet valve 91 and a fluid outlet line 16.
  • the piston compressor 1 according to the invention advantageously has no or very little gas space, in that the fluid supply line 15 or a flange 14, via which the fluid is supplied from the outside to the cylinder 10, is arranged immediately in front of the inlet valve 90 in the direction of fluid flow F, or in that Fluid flow direction F immediately after the outlet valve 91, a fluid discharge line 16 leading to the outside or a flange 14 is arranged, via which the fluid is discharged from the cylinder 10 to the outside.
  • the pumped fluid is no longer in direct thermally conductive contact with the cylinder 10 until immediately before the inlet valve 90 or immediately after the outlet valve 91.
  • the cylinder 10 is cooled to a lesser extent.
  • At least one of the components intake valve 90, exhaust valve 91 and flange 14 are designed in such a way that they have an increased thermal resistance to the cylinder cover 11, 12 in order to extract heat from the cylinder cover 11,12 only to a reduced extent, due to the cool fluid flowing through the inlet valve 90, the outlet valve 91 and/or the flange 14.
  • figure 3 shows a detailed view of an embodiment for increasing the thermal resistance.
  • the exhaust valve 91 is not in full contact with the first cylinder cover 11 but rather only partially over the partial surfaces 91a, which increases the heat conduction resistance between the exhaust valve 91 and the first cylinder cover 11 .
  • the inlet valve 90 could also be arranged in the first or second cylinder cover 11, 12 in the same way.
  • FIG. 3 Another way to increase the thermal resistance is as in figure 3 shown in the fact that the flange 14 does not rest over the entire surface but only over part of the surface via the partial surfaces 14a on the first cylinder cover 11, which increases the thermal resistance between the flange 14 and the first cylinder cover 11.
  • the flange 14 could also be arranged in the second cylinder cover 12 in the same way.
  • the piston compressor 1 according to the invention is advantageously operated at ambient temperature, so that the cylinder 10 is heated by the ambient air during the conveying and compressing of, for example, exhaust gas, the increase in thermal conductivity described above having the advantage that the cylinder 10, due to the fluid F flowing through, has a reduced mass is cooled, so that the cylinder 10 has a higher temperature during operation and preferably also a more uniform temperature distribution, which, for example, increases the risk of the components of the piston compressor 1 warping due to the temperature differences present, in particular a warping of the cylinder 10, the piston 20, the Piston rod 24 or the spacer 40 is reduced.
  • the inside of the first or second cylinder cover 11, 12 and the outer surface of the first or second piston cover 21, 22 are mutually adapted in such a way that the dead space remains as small as possible.
  • At least one of the two piston covers 21, 22 has a piston end face 21a, 22a that protrudes towards the associated cylinder cover 11, 12, and in particular is convex, with the associated cylinder cover 11, 12 having a correspondingly protruding cylinder cover outer side 11c, 12c or a cylinder cover inner side 11d, 12d receding correspondingly with respect to the piston end face 21a, 22a.
  • the first cylinder interior 10a corresponds to the dead space when the piston 20 is in the uppermost position figure 3 evident, is very small.
  • first cylinder cover 11 and/or the second cylinder cover 12 could have an end face running perpendicularly to the longitudinal axis L, in which the inlet valve 90 and the outlet valve 91 are arranged.
  • the first cylinder cover 11 and/or second cylinder cover 12 are particularly advantageous, however, as shown in FIG figure 2 shown designed such that the inlet valve 90 and the outlet valve 91 are arranged with respect to the plane of symmetry S inclined running in the cylinder cover 11,12. This enables valves 90, 91 to be used with a larger diameter, which reduces their flow resistance.
  • the Figures 4 and 5 show the same cylinder 10 as in figure 2 , but not in one section but in two different side views.
  • the cylinder 10 includes the first cylinder cover 11, the cylinder jacket 13 and the second cylinder cover 12. In the cylinder covers 11,12 the flanges 14 are arranged.
  • the cylinder 10 is firmly connected to the carrier housing 60 via a spacer 40 and is arranged at a distance from the carrier housing 60 .
  • the spacer 40 comprises two support arms 42, 43 arranged symmetrically with respect to the plane of symmetry S.
  • Each of the two attachment points 12e, 12f is preferably configured identically in the circumferential direction and, as in figure 4 shown, in the circumferential direction has a width C in the range of preferably between 10° and 30°.
  • FIG 4 the course of the section line BB and the course of the plane of symmetry S are also shown.
  • FIG 5 the course of the section line AA and the course of the second plane of symmetry S 2 are also shown.
  • the attachment points 12e, 12f preferably run as shown in figure 4 shown with the attachment point 12f, substantially perpendicular to the plane of symmetry S and are arranged symmetrically to the plane of symmetry S running.
  • Point S 3 shows the intersection of attachment point 12f with plane of symmetry S.
  • Attachment point 12f preferably runs symmetrically with respect to point S 3 or symmetrically with respect to plane of symmetry S.
  • cylinder 10 points during operation of piston compressor 1 in the area of the plane of symmetry S or in the area of point S 3 has an average temperature, with the same temperature being present at both attachment points 12e, 12f due to the symmetrical arrangement, or cylinder 10 having the same temperature, so that the first support arm 42 and the second support arm 43 are also at the two attachment points 12e, 12f have the same temperature.
  • the symmetrical design of the cylinder 10 and the flanges 14 attached to the cylinder 10, as well as the symmetrical arrangement of the two fastening points 12e, 12f, and the symmetrically designed support arms 42, 43 of the spacer 40 result in the advantage that the support arms 42, 43 on the two Fastening points 12e, 12f have the same temperature, so that no mutual thermal distortion occurs on the two support arms 42, 43.
  • the input fluid F E and the output fluid F A can have a significant temperature difference, so that the corresponding flanges 14 and also the cylinder 10 and possibly the piston 20 can have a temperature difference in the direction C, which at most can lead to a distortion of the cylinder or a Distortion of its components, particularly in direction C, could result.
  • the spacer 40 is U-shaped, comprising a first support arm 42 and a second support arm 43.
  • the spacer 40 could also have more support arms, for example four, six or eight, which are connected to the second cylinder cover 12, and which preferably are arranged symmetrically with respect to the plane of symmetry S.
  • the second gland chamber 51 and the third gland chamber 52 and the spacer cover 53 are not shown.
  • figure 6 shows essentially the cylinder 10 and the piston 20 without the flanges 14 in a section along section line AA.
  • figure 7 shows essentially the cylinder 10 and the piston 20 without the flanges 14 in a section along section line BB.
  • the cylinder 10 comprises at least three parts, the first cylinder cover 11, the second cylinder cover 12 and a preferably tubular cylinder jacket 13, the cylinder jacket 13 being arranged between the first cylinder cover 11 and the second cylinder cover 13.
  • the piston 20 comprises at least three parts, a first piston cover 21, a second piston cover 22 and a piston skirt 23 arranged between the first and second piston cover 21, 22.
  • This layered structure of the cylinder and/or piston enables particularly favorable maintenance because maintenance is only those parts that could show considerable wear are to be replaced, for example the cylinder jacket 13 and the piston jacket 23.
  • the piston jacket 23 has at least partially a labyrinth-shaped outer surface 23a, so that the piston compressor 1 is designed as a labyrinth piston compressor.
  • At least one sealing ring is arranged on the piston jacket 23, with the piston jacket 23 preferably having at least one circumferential groove in which the sealing ring is arranged, so that the piston compressor 1 is configured as a ring-sealed piston compressor 1 .
  • the second cylinder cover 12 has attachment points 12e, 12f, preferably arranged on its outer edge 12i, to which the support arms 42, 43 are attached via an attachment means, not shown, preferably a screw.
  • the attachment points 12e, 12f are preferably arranged mutually symmetrically to the plane of symmetry S.
  • At least one of the two piston covers 21, 22 has a piston end face 21a, 22a that protrudes towards the associated cylinder cover 11, 12, and in particular is convex, with the associated cylinder cover 11, 12 having a correspondingly protruding outer side 11c, 12c of the cylinder cover or one with respect to the Piston end face 21a, 22a has a correspondingly receding cylinder cover inner side lld, 12d, as is the case, for example, in figure 2 is shown.
  • the second cylinder cover 12 has in its center a passage opening 12g running in the longitudinal direction L, along which the piston rod 24 runs, at least one stuffing box chamber 50 preferably being arranged in the longitudinal direction L downstream of the passage opening 12g, outside of the cylinder cover 12, and preferably a plurality of Stuffing box chambers are arranged.
  • At least one of the inlet valve 90, outlet valve 91 and flange 14 does not bear against the first or second cylinder cover 11, 12 with the entire possible surface, but rather only bears on part of the surface, i.e. with part of the possible total surface, on the first or second cylinder cover 11,12 to increase the thermal resistance between intake valve 90, exhaust valve 91, flange 14 and the first or second cylinder cover 11,12.
  • FIG 8 shows the piston compressor 1 in a side view.
  • This comprises two cylinders 10 with pistons 20 arranged therein, each piston 20 being connected to the carrier housing 60 via a spacer 40, and each piston rod 24 being driven by a common crankshaft 61.
  • An oil collecting pan 64 is arranged below the carrier housing 60 .
  • the piston compressor 1 can also have only one single cylinder 10 with piston 20, or a plurality of cylinders 10 with corresponding piston 20, for example between three to ten cylinders 10 comprise.
  • FIG 9 shows a compressor unit 80 comprising a piston compressor 1, an electric motor 81, a supply manifold 85, which is connected to the fluid supply line 15, and a discharge manifold 86, which is connected to the fluid discharge line 16.
  • the fluid supply line 15 and the fluid discharge line 16 are preferably designed to be elastic in order to compensate for temperature-related expansions, with these lines 15, 16 consisting of a metal mesh, for example.
  • the piston compressor 1 comprises a cylinder 10 and a piston 20 arranged therein, a support housing 60 with a crosshead 63 mounted in the support housing 60, a spacer 40 which connects the cylinder 10 to the support housing 60, and a longitudinal axis L extending piston rod 24 connecting the crosshead 63 to the piston 20, the spacer 40 comprising a plurality of support arms 42,43, the support arms 42,43 being connected to the cylinder 10 and supporting it.
  • the cylinder 10 advantageously comprises a plurality of fastening points 12e, 12f which are arranged mutually symmetrically with respect to the longitudinal axis L and to which the support arms 42, 43 are fastened.
  • the piston compressor has a plane of symmetry S running in the longitudinal direction L along the piston rod 24, with the attachment points 12e, 12f and the support arms 42, 43 being arranged symmetrically with respect to the plane of symmetry S.
  • the spacer 40 is U-shaped, with two support arms 42, 43 running in the longitudinal direction L, the cylinder 10 having two attachment points 12e, 12f, to which the support arms 42, 43 are attached.
  • each attachment point 12e, 12f in Circumferential direction of the cylinder 10 has a width C in the range between 10 ° and 30 °.
  • the cylinder 10 advantageously includes an intake valve 90 and an exhaust valve 91, the intake valve 90 and the exhaust valve 91 being arranged mutually symmetrically with respect to the plane of symmetry S.
  • the cylinder 10 advantageously comprises a first cylinder cover 11 and a second cylinder cover 12, with both the first and the second cylinder cover 11, 12 comprising an inlet valve 90 and an outlet valve 91, so that the cylinder 10 and the piston 20 are double-acting.
  • a plurality of cylinders 10 with pistons 20 arranged therein are advantageously arranged at a distance from one another on the carrier housing 60 and are connected to the carrier housing 60 via a separate spacer 40 in each case.
  • Each piston 20 is advantageously assigned a piston rod 24, with the carrier housing 60 being designed as a monoblock, and the monoblock having a number of bores corresponding to the number of piston rods 24, in each of which a crosshead 63 is displaceably mounted, with each piston 20 having a Piston rod 20 is connected to the associated crosshead 63.
  • the monobloc and the crosshead 62 are made of a metal with a thermal conductivity in the range 100 to 300 (W/m ⁇ K), preferably aluminum or an aluminum alloy.
  • the cylinder 10 and/or the piston 20 is made of a metal having a thermal conductivity in the range between 100 and 300 (W/m ⁇ K), preferably aluminum or an aluminum alloy.
  • the piston compressor 1 comprises a cylinder 10 and a piston 20 arranged therein, a support housing 60 with a crosshead 63 mounted in the support housing 60, a spacer 40 which connects the cylinder 10 to the support housing 60, and a piston rod 24 running in a longitudinal direction L, which the Connecting the crosshead 63 to the piston 20 is advantageously operated in such a way that heat energy, caused by a heat difference between the cylinder 10 and the carrier housing 60, is exchanged via a plurality of support arms 42, 43.
  • An inlet fluid F E is advantageously supplied to the cylinder 10 via an inlet valve 90, and the fluid in the cylinder 10 is expelled from the cylinder 10 via an outlet valve 91 as an outlet fluid F A , the inlet valve 90 and the outlet valve 91 being symmetrical with respect to a are arranged along the longitudinal direction L of the piston rod 24 running plane of symmetry S, so that the cylinder 10 is heated to an average temperature during the delivery of the fluid in the area of the plane of symmetry S, which is between the temperature of the inlet fluid F E and the outlet fluid F A , wherein the support arms 42, 43 are connected to the cylinder 10 in the area of the plane of symmetry S via attachment points 12e, 12f.
  • the two center points S 3 between the attachment points 12e, 12f are advantageously brought to essentially the same temperature while the fluid is being conveyed.
  • the piston rod 24 runs in the area of the plane of symmetry S, and while the fluid is being conveyed, it is tempered to essentially the same temperature as the attachment points 12e, 12f.
  • the piston compressor 1 shown comprises a cylinder 10 and a piston 20 arranged therein, a support housing 60 with a crosshead 63 mounted in the support housing 60, a spacer 40 which connects the cylinder 10 to the support housing 60, and a piston rod 24 running in a longitudinal direction L, which connects the crosshead 63 to the piston 20, the spacer 40 comprising a plurality of support arms 42,43 running in the longitudinal direction L, the support arms 42,43 towards the cylinder 10 being individually connected to the cylinder 10.
  • the cylinder 10 has a plurality of attachment points 12e, 12f, with one support arm 42, 43 being attached to each attachment point 12e, 12f.
  • the attachment points 12e, 12f are arranged mutually symmetrically with respect to the longitudinal direction L.
  • the compressor according to the invention can be designed as a labyrinth piston compressor or as a compressor comprising at least one piston with sealing rings.
  • the method for operating a piston compressor 1 comprises a cylinder 10 and a piston 20 arranged therein, a support housing 60 with a crosshead 63 mounted in the support housing 60, a spacer 40 which connects the cylinder 10 to the support housing 60, and a longitudinal axis L running piston rod 24, which connects the crosshead 63 to the piston 20, the spacer 40 comprising a plurality of support arms 42,43 running in the longitudinal direction L, the support arms 42,43 towards the cylinder 10 each individually via fastening points 12e, 12f with the Cylinder 10 are connected, so that thermal energy, caused by a heat difference between the attachment points 12e, 12f, is not exchanged directly in the circumferential direction to the longitudinal direction L between the attachment points 12e, 12f, but is exchanged via the support arms 42, 43 running in the longitudinal direction L.
  • the inlet fluid FE is preferably supplied at a temperature in the range between -162° C and -40° C
  • the outlet fluid FA is preferably heated by the compression by a temperature difference in the range between 100°C and 150°C.
  • the attachment points 12e, 12f in the area of the plane of symmetry S each have a center point S 3 which during the Conveying the fluid are essentially tempered to the same temperature.
  • the spacer 40 is U-shaped, with a support section 41 and two support arms 42, 43 running in the longitudinal direction L, with thermal energy being exchanged between the cylinder 10 and the support housing 60 via the support arms 42, 43 and the support section 41.
  • each attachment point (12e, 12f) has a width C in the range between 10° and 30° in the circumferential direction of the cylinder 10, with each attachment point 12e, 12f being arranged symmetrically to the center point S 3 , so that the respective support arm 42,43 along the attachment point 12e, 12f heat energy is transferred in the circumferential direction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Claims (15)

  1. Compresseur à piston (1) comprenant un cylindre (10) ainsi qu'un piston (20) disposé dans celui-ci, un boîtier de support (60) avec une crosse de piston (63) logée dans le boîtier de support (60), une entretoise (40) qui relie le cylindre (10) au boîtier de support (60), ainsi qu'une tige de piston (24) s'étendant dans une direction longitudinale (L), qui relie la crosse de piston (63) au piston (20), l'entretoise (40) comprenant une pluralité de bras de support (42, 43) s'étendant dans la direction longitudinale (L), caractérisée en ce que les bras de support (42, 43) sont reliés chacun individuellement au cylindre (10) en direction du cylindre (10).
  2. Le compresseur à piston selon la revendication 1, caractérisé en ce que le cylindre (10) présente une pluralité de points de fixation (12e, 12f), et en ce qu'un bras de support (42, 43) est fixé à chaque point de fixation (12e, 12f) .
  3. Le compresseur à piston selon la revendication 2, caractérisé en ce que les points de fixation (12e, 12f) sont disposés de manière mutuellement symétrique par rapport à la direction longitudinale (L).
  4. Le compresseur à piston selon la revendication 3, caractérisé en ce que le cylindre (10) présente un plan de symétrie (S) s'étendant dans la direction longitudinale (L) le long de la tige de piston (24), et en ce que les points de fixation (12e, 12f) ainsi que les bras d'appui (42, 43) sont disposés symétriquement par rapport au plan de symétrie (S) .
  5. Le compresseur à piston selon l'une des revendications précédentes, caractérisé en ce que l'entretoise (40) est réalisée en forme de U, avec deux bras de support (42, 43) s'étendant dans la direction longitudinale (L), et en ce que le cylindre (10) présente deux points de fixation (12e, 12f) sur lesquels sont fixés les bras d'appui (42, 43).
  6. Le compresseur à piston selon l'une des revendications 2 à 5, caractérisé en ce que chaque point de fixation (12e, 12f) a une largeur (C) comprise entre 10° et 30° dans la direction circonférentielle du cylindre (10).
  7. Le compresseur à piston selon l'une des revendications 4 à 6, caractérisé en ce que le cylindre (10) comprend une soupape d'entrée (90) ainsi qu'une soupape de sortie (91), et en ce que la soupape d'entrée (90) ainsi que la soupape de sortie (91) sont disposées de manière mutuellement symétrique par rapport au plan de symétrie (S).
  8. Le compresseur à piston selon la revendication 7, caractérisé en ce que le cylindre (10) comprend un premier couvercle de cylindre (11) ainsi qu'un deuxième couvercle de cylindre (12), et en ce qu'aussi bien le premier que le deuxième couvercle de cylindre (11, 12) comprennent une soupape d'entrée (90) ainsi qu'une soupape de sortie (91), de sorte que le cylindre (10) et le piston (20) sont configurés à double effet.
  9. Le compresseur à piston selon l'une des revendications précédentes, caractérisé en ce qu'une pluralité de cylindres (10) avec des pistons (20) disposés à l'intérieur sont mutuellement disposés à distance sur le boîtier de support (60) et sont reliés chacun au boîtier de support (60) par une entretoise (40) séparée.
  10. Le compresseur à piston selon la revendication 8, caractérisé en ce qu'une tige de piston (24) est associée à chaque piston (20), en ce que le boîtier de support (60) est conçu comme un monobloc, et en ce que le monobloc présente un nombre de perçages correspondant au nombre de tiges de piston (24), dans chacun desquels une crosse de piston (63) est logée de manière déplaçable, chaque piston (20) étant relié à la crosse de piston (63) associée par l'intermédiaire d'une tige de piston (20) respective.
  11. Procédé de fonctionnement d'un compresseur à piston (1) comprenant un cylindre (10) ainsi qu'un piston (20) disposé dans celui-ci, un boîtier de support (60) avec une crosse de piston (63) logée dans le boîtier de support (60), une entretoise (40) qui relie le cylindre (10) au boîtier de support (60), ainsi qu'une tige de piston (24) s'étendant dans une direction longitudinale (L), qui relie la crosse de piston (63) au piston (20), l'entretoise (40) comprenant une pluralité de bras de support (42,43), caractérisé en ce que les bras de support (42, 43) sont reliés au cylindre (10), chacun individuellement, par l'intermédiaire de points de fixation (12e, 12f), de sorte que l'énergie thermique, due à une différence thermique appliquée entre les points de fixation (12e, 12f), n'est pas échangée directement dans la direction circonférentielle par rapport à la direction longitudinale (L) entre les points de fixation (12e, 12f), mais par l'intermédiaire des bras de support (42, 43) s'étendant dans la direction longitudinale (L).
  12. Le procédé selon la revendication 11, caractérisé en ce qu'un fluide d'entrée (FE) est amené au cylindre (10) par une soupape d'entrée (90), et en ce que le fluide se trouvant dans le cylindre (10) est expulsé du cylindre (10) par une soupape de sortie (91) sous forme d'un fluide de sortie (FA), la soupape d'entrée (90) et la soupape de sortie (91) étant disposées symétriquement par rapport à un plan de symétrie (S) s'étendant le long de la direction longitudinale (L) de la tige de piston (24), de sorte que le cylindre (10) est chauffé pendant le transport du fluide dans la zone du plan de symétrie (S) à une température moyenne qui se situe entre la température du fluide d'entrée (FE) et du fluide de sortie (FA), et en ce que les bras de support (42, 43) sont reliés au cylindre (10) dans la zone du plan de symétrie (S) par des points de fixation (12e, 12f).
  13. Le procédé selon la revendication 12, caractérisé en ce que le fluide d'entrée (FE) est fourni à une température comprise entre -162°C et -40°C, et en ce que le fluide de sortie (FA) est chauffé par la compression d'une différence de température comprise entre 100°C et 150°C.
  14. Le procédé selon la revendication 12 ou 13, caractérisé en ce que les points de fixation (12e, 12f) présentent chacun un point central S3 dans la zone du plan de symétrie (S), lesquels sont tempérés sensiblement à la même température pendant le transport du fluide.
  15. Le procédé selon l'une des revendications 11 à 14, caractérisé en ce que l'entretoise (40) est réalisée en forme de U, avec une section de support (41) ainsi que deux bras de support (42, 43) s'étendant dans la direction longitudinale (L), en ce que de l'énergie thermique est échangée entre le cylindre (10) et le boîtier de support (60) par l'intermédiaire des bras de support (42, 43) et de la section de support (41).
EP19786900.1A 2018-09-24 2019-09-25 Compresseur à piston et son procédé de fonctionnement Active EP3857065B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP18196409 2018-09-24
PCT/EP2019/075775 WO2020064782A1 (fr) 2018-09-24 2019-09-25 Compresseur à piston et son procédé de fonctionnement

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EP3857065A1 EP3857065A1 (fr) 2021-08-04
EP3857065B1 true EP3857065B1 (fr) 2022-07-27

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US (1) US20210388824A1 (fr)
EP (1) EP3857065B1 (fr)
JP (1) JP7483696B2 (fr)
KR (1) KR20220055448A (fr)
CN (1) CN113330213B (fr)
WO (1) WO2020064782A1 (fr)

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EP3762638B1 (fr) * 2018-03-08 2022-03-02 Burckhardt Compression AG Soupape à plaque ainsi que son procédé de fonctionnement

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US2695132A (en) * 1948-06-25 1954-11-23 Joy Mfg Co Compressor
FR1030140A (fr) * 1950-12-27 1953-06-10 Eugene Dumont Ets Pompe à double effet
US3398693A (en) * 1966-08-01 1968-08-27 Danken Inc Concrete pumping apparatus
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CA1140515A (fr) * 1978-12-04 1983-02-01 Byron L. Brucken Compresseur a plateau oscillant
US4576557A (en) * 1983-06-15 1986-03-18 Union Carbide Corporation Cryogenic liquid pump
JPS6130700U (ja) * 1984-07-27 1986-02-24 株式会社新潟鐵工所 流体荷役装置
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EP2296962B1 (fr) 2008-03-10 2011-11-16 Burckhardt Compression AG Procédé et dispositif de production de combustible gaz naturel
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ITCO20120028A1 (it) * 2012-05-16 2013-11-17 Nuovo Pignone Srl Attuatore elettromagnetico per un compressore alternativo
JP5969318B2 (ja) * 2012-08-28 2016-08-17 パスカルエンジニアリング株式会社 加圧エア駆動式ピストン往復動型油圧ポンプ
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KR20220055448A (ko) 2022-05-03
CN113330213B (zh) 2023-03-14
WO2020064782A1 (fr) 2020-04-02
WO2020064782A8 (fr) 2020-08-06
JP7483696B2 (ja) 2024-05-15
CN113330213A (zh) 2021-08-31
EP3857065A1 (fr) 2021-08-04
US20210388824A1 (en) 2021-12-16
JP2022502597A (ja) 2022-01-11

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