EP3857068A1

EP3857068A1 - Labyrinth piston compressor

Info

Publication number: EP3857068A1
Application number: EP19783448.4A
Authority: EP
Inventors: Alexandre Voser; Reiner Schulz; Sandro BRUNNER
Original assignee: Burckhardt Compression AG
Current assignee: Burckhardt Compression AG
Priority date: 2018-09-24
Filing date: 2019-09-24
Publication date: 2021-08-04
Also published as: WO2020064781A1; JP2022502596A; US20210404454A1; KR20210063407A; CN113302398A

Abstract

The labyrinth piston compressor (1) comprises a cylinder (10), a piston (20) located in the cylinder (10), and a piston rod (24), the piston rod (24) extending in a longitudinal direction (L) and being connected to the piston (20), the piston (20) being movable back and forth inside the cylinder (10) in the longitudinal direction (L), the cylinder (10) having a first cylinder cover (11), an inlet valve (90) and an outlet valve (91) being located in the first cylinder cover (11), and the inlet valve (90) and the outlet valve (91) being symmetrical with respect to a plane of symmetry (S) running along the piston rod (24) in the longitudinal direction (L).

Description

LABYRINTH PISTON COMPRESSOR

description

The invention relates to a labyrinth piston compressor.

State of the art

Liquid natural gas, also known as "liquefied natural gas" or "LNG" for short, is natural gas that has cooled to a temperature of at least - 160 ° C, and at these depths

Temperatures takes a liquid state of matter. The

Document WO 2009/1 12479A1 discloses a piston compressor for supplying natural gas fuel, this natural gas fuel being obtained by compressing exhaust gas that is emitted from the liquid natural gas by means of the piston compressor. Such a piston compressor, which is very well-proven per se, allows the evaporation gas of the liquid natural gas, which usually has a temperature of about-160 ° C. at a pressure of usually 1 bar, to one

preferably compress variable end pressure in the range between 100 bar and 500 bar, preferably to a final pressure in the range between 210 bar and 350 bar. Such a piston compressor has the advantage that natural gas can be drawn in and then compressed in a wide temperature range of preferably between - 160 ° C to + 100 ° C. Such a piston compressor is capable, for example an input fluid having a temperature of - 160 ° C to a compressed fluid having a temperature of -40 ° C to

condense. In this application, there is a temperature difference in the range of 120 ° C between the inlet and outlet of the piston compressor. To date, it is a major technical challenge to have an inexpensive piston compressor, especially one

To form a labyrinth piston compressor, which is suitable for compressing a fluid that has a high temperature difference between the input fluid and the output fluid.

Presentation of the invention

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.

This object is achieved with a labyrinth piston compressor having the features of claim 1. The dependent claims 2 to 15 relate to further advantageous configurations.

The task is solved in particular with a

A labyrinth piston compressor comprising a cylinder, a piston arranged in the cylinder and a piston rod, the piston rod extending in a longitudinal direction and being connected to the piston, and the piston being movable back and forth within the cylinder in the longitudinal direction, the cylinder having a first cylinder cover comprises, wherein an inlet valve and an outlet valve are arranged in the first cylinder cover, and wherein the inlet valve and the outlet valve are arranged symmetrically with respect to a plane of symmetry running in the longitudinal direction along the piston rod. A labyrinth piston compressor includes a piston and one

Cylinder, wherein at least the piston and the cylinder wall of the cylinder is formed a labyrinth seal. The labyrinth seal is a non-contact seal. The sealing effect is based on the extension of the flow path through the gap to be sealed, as a result of which the flow resistance is significantly increased. The path extension is achieved by means of a surface structure of the piston and possibly also of the cylinder wall. The surface of the piston preferably has a plurality of circumferential depressions which are spaced apart from one another in the longitudinal direction of the piston. With this non-contact construction, absolute tightness is not possible. For this purpose, the labyrinth piston compressor comprising the labyrinth seal has the advantage that the labyrinth seal is made contactless because the piston and the cylinder wall do not touch each other, and therefore no lubrication between the piston and the cylinder wall is required. Such a labyrinth piston compressor allows a so-called oil-free compression of a fluid because there is none for the compression of the fluid

Lubricant, especially no oil is required. The piston of such a labyrinth piston compressor has no sealing rings, since the labyrinth seal effects a seal.

The labyrinth 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 ejected has a large temperature difference of

for example 100 ° C to 120 ° C or more. Of the

Piston compressor according to the invention is designed in such a way that the temperature differences present do not result in any significant thermal stresses or no significant distortion in components of the piston compressor, or in that the

Piston compressor is designed such that an expansion of components caused due to the temperature difference present of the piston compressor takes place in such a way that the individual components are hardly displaced relative to each other due to the temperature difference, which is particularly important for a labyrinth piston compressor since the gap between the outer peripheral surface of the

Labyrinth piston and the inner surface of the cylinder facing the outer peripheral surface is particularly small. The according to the invention

The labyrinth piston compressor can preferably be operated safely and reliably regardless of the temperature differences present. 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 gives 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 as it flows through the exhaust valve

Leaves cylinder interior immediately, so that the piston compressor has an extremely small or no gas dead space or harmful space within which a temperature transfer between the fluid and piston compressor could take place, so that the piston compressor has relatively few contact surfaces that could exchange heat with the fluid. The piston compressor according to the invention thus preferably has, with the exception of the absolutely necessary

Contact surfaces of the inflow of the fluid to be compressed

Compressing the fluid to be compressed and ejecting the compressed fluid, preferably negligibly little or no additional contact areas and contact points between the piston compressor and the delivered fluid, which is a

Heat transfer between fluid and piston compressor limited.

In addition, the cylinder and / or the piston of the piston compressor advantageously consists 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. Has the relatively high thermal conductivity the consequence that a temperature equilibrium is established in the components of the piston compressor during its operation

Temperature differences are much smaller than that

Temperature differences between the inflowing and the

compressed, flowing fluid. The cylinder and the piston are particularly advantageously made of the same material.

The intake valve and the exhaust valve are also in the cylinder

preferably arranged symmetrically with respect to a plane of symmetry running along a center line of the cylinder. The consequence of this is that during operation of the piston compressor in the region of the plane of symmetry an average temperature will arise which lies between the temperature of the inflowing fluid and the temperature of the outflowing fluid, which reduces the maximum possible temperature differences occurring in the cylinder.

In a further advantageous embodiment, a flange or hose, which is arranged at the inlet valve or outlet valve and is used for supplying or discharging the fluid, has a small contact area with respect to the cylinder, which in turn reduces heat transfer between the flange or hose and the cylinder.

The piston compressor comprises a carrier housing in which

preferably a crankshaft and at least one crosshead is arranged. The piston compressor according to the invention comprises one

Spacer, which is connected to the carrier housing and the cylinder, on the one hand to hold the cylinder in a defined position with respect to the carrier housing, and on the other hand any

Reduce temperature flow between cylinder and carrier housing. In a particularly advantageous embodiment, the spacer is connected to the cylinder at those areas at which the

Average temperature or essentially the average temperature is present. This has the consequence that the on during the operation of the piston compressor Spacers occurring between the cylinder and carrier housing

Temperature differences are kept within limits, the spacer preferably being arranged in such a way that it has a heat distribution that is symmetrical to the plane of symmetry, with the result that there is little or no distortion of the spacer due to the temperatures applied to the spacer. Thus, during operation of the piston compressor, there is in particular no or a negligibly small asymmetrical thermal expansion or

Deformation but advantageously at most one thermal expansion or deformation taking place symmetrically to the plane of symmetry due to the temperature present, this effect occurring in particular on the cylinder, on the piston and on the spacer. Therefore, the piston rod running between the carrier housing and the cylinder does not experience any deformation.

In an advantageous embodiment, the cylinder and / or the piston consists of aluminum or an aluminum alloy, a very good heat-conducting metal. The very good heat conduction has the advantage that during the continuous operation of the

Piston compressor very quickly sets an average temperature or an average operating temperature of the individual components of the compressor, and thereby temperature peaks can be avoided.

The piston compressor according to the invention has the advantage that, in a preferred embodiment, it requires relatively few parts and that the movable parts can be selected to be relatively low in mass.

This also gives the advantage that the invention

Piston compressor can be operated at a high speed of, for example, up to 1800 revolutions per minute.

The piston compressor according to the invention is explained in detail below using exemplary embodiments. Brief description of the drawings

The drawings used to explain the exemplary embodiments show:

Fig. 1 shows a longitudinal section through a piston compressor along the

Section line A-A;

2 shows a detailed view of the piston compressor according to FIG. 1,

especially the cylinder and the piston;

3 shows a detailed view of the arrangement of the valve in the cylinder;

4 shows a side view of the cylinder with a spacer;

5 shows a further side view of the cylinder with a spacer;

Fig. 6 shows a longitudinal section through the cylinder with pistons along the

Section line A-A;

7 shows a further longitudinal section through the cylinder with piston along the section line B-B;

8 is a side view of the piston compressor;

Fig. 9 the piston compressor in an insert configuration.

Basically, the same parts are the same in the drawings

Provide reference numerals.

Ways of Carrying Out the Invention

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 with a bearing part 63a arranged therein, the crosshead 63 being drivable via a crankshaft 61 and a connecting rod 62, and comprising a spacer 40 with a support section 41, wherein the spacer 40 connects the cylinder 10 to the carrier housing 60 and, as in FIG. 1 shown, carries the cylinder 10 with the piston compressor 1 arranged upright. The piston compressor 1 comprises a piston rod 24, which connects the cross head 63 to the piston 20 and drives the piston 20. The piston compressor 1 has a longitudinal axis L which extends in the center of the piston rod 24 along the piston rod 24. The cylinder 10 comprises a first cylinder cover 11, a second cylinder cover 12 and one arranged in between

Cylinder jacket 13. The first cylinder cover 11 comprises one

Inlet valve receiving opening 1 1a and one

Exhaust valve receiving opening 11b, in which an intake valve 90 and an exhaust valve 91 are arranged. In addition, one flange 14 is connected to the opening 1 1a, 1 1b, the flange 14 serving for supplying or discharging a fluid between outside the cylinder 10 and an interior 10a of the cylinder 10. Fluids can

for example via a hose 15 connected to the respective flange 14. The second cylinder cover 12 likewise comprises an inlet valve receiving opening 12a and an outlet valve receiving opening 12b with an inlet valve 90 and an outlet valve 91 arranged therein. The second cylinder cover 12 has a central section 12h having a passage opening 12g, in which the piston rod 24 is arranged to be movable in its direction L.

The cylinder 10 or the piston 20 is designed to be double-acting, in which the piston 20 delimits a first cylinder interior 10a and a second cylinder interior 10b. In another

Embodiment could be dispensed with the cylinder jacket 13 in that the first and second cylinder covers 11, 12 are made longer in the longitudinal direction L.

In the longitudinal direction L, a first, a second and a third stuffing box chamber 50, 51.52 are arranged downstream of the central section 12h. The spacer 40 has a spacer interior 40a, in which an oil wiping pack 55, only shown schematically comprising preferably a guide is arranged which the

Piston rod 24 encloses. In addition, 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 cross head 63, so that the cross head 63, the piston rod 24 connected to the cross head 63 and the piston 20 connected to the piston rod 24 in

Longitudinal direction L can move back and forth. The sliding surface for the crosshead is preferably lubricated, preferably with oil, this lubrication not being shown in detail.

The cylinder 10 and / or the piston 20, and preferably also the carrier housing 60 and the crosshead 63, consist of a metal with a thermal conductivity in the range of preferably between 100 and 300 (W / m · K), preferably of aluminum or one

Aluminum alloy. Advantageously, the cylinder 10 and the piston 20, and preferably also the carrier housing 60 and the

Cross head 63, made of the same material, so that they have the same properties with regard to thermal expansion.

FIG. 2 shows a detailed view of the piston compressor 1 according to FIG. 1, essentially the cylinder 10, the piston 20, the flanges 14 and the inlet and outlet valves 90, 91. In one possible embodiment, the cylinder 10 and the piston 20 are designed to be single-acting , for example, an inlet valve 90 and an outlet valve 91 are arranged only in the first cylinder cover 11. However, as shown in FIG. 2, the cylinder 10 and the piston 20 are particularly advantageously configured to be double-acting, with a first cylinder interior 10a, a second cylinder interior 10b and two inlet valves 90 and two

Exhaust valves 91. According to the invention, an intake valve 90 and an exhaust valve 91 are thus arranged at least in the first cylinder cover 11 or in the second cylinder cover 12, and preferably, as shown in FIG. 2, an intake valve 90 and two in each of the two cylinder covers 11, 12 an outlet valve 91 is arranged. In the respective cylinder cover 11, 12, the inlet valve 90 and the outlet valve 91 are preferably symmetrical with respect to one in the longitudinal direction L along the piston rod 24

extending symmetry plane S arranged. Preferably, both intake valves 90 and both exhaust valves 91 are arranged on the same side of cylinder 10 as shown in FIG. 2, that is, as shown in FIG. 2, both on the left and both on the right of the

Plane of symmetry S. The piston compressor according to the invention is particularly suitable for compressing a fluid via the inlet valve 90

inflowing inlet fluid FE and its outlet fluid FA flowing out via outlet valve 91 have a high temperature difference of, for example, between 100 ° C. to 150 ° C. So can

for example, the inlet fluid FE, for example exhaust gas from liquid natural gas, have a temperature of −160 ° C., and the outlet fluid FA have a temperature of −40 ° C., so that they

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 region of the plane of symmetry S or the longitudinal axis L running along the piston rod 24, wherein the temperature of the cylinder 10 and the piston 20 perpendicular to the longitudinal axis L usually decreases towards the inlet valve 90 and increases towards the outlet valve 91. In the direction of the longitudinal axis L, the cylinder 10 preferably has only a small number

Temperature differences. Because the cylinder 10 and the piston 20 have an average temperature in the region 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 present in these parts or by Caused temperature differences Changes in length. In an advantageous embodiment, the cylinder 10 and / or the piston 20 are made of a highly thermally conductive material, for example aluminum, which gives the advantage that the temperature differences present during operation on the cylinder 10 and on the piston 20 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 exposed to air

Ambient temperature warmed up, what is applied to the cylinder 10

Temperature differences are further reduced, in particular if the cylinder 10 or at least the cylinder cover 11, 12 consist of a material that is a good conductor of heat.

In a piston compressor 1, a gas space is understood to mean the space between a fluid supply line 15 and the input valve 90 or the space between the output valve 91 and a fluid discharge line 16. The piston compressor 1 according to the invention has

advantageously no gas space or only a very small gas space, in that the fluid flow direction F immediately before the inlet valve 90

Fluid supply line 15 or a flange 14 is arranged, via which the fluid is supplied to the cylinder 10 from the outside, or in that a fluid discharge line 16 or a flange 14 is arranged in the fluid flow direction F immediately after the outlet valve 91, via which the fluid from the Cylinder 10 is discharged to the outside. Thus, the delivered fluid is no longer in direct heat-conducting contact with the cylinder 10 until immediately before the inlet valve 90 or immediately after the outlet valve 91. This has the consequence that the cylinder 10 is cooled to a lesser depth. In a further advantageous embodiment, at least one of the components inlet valve 90, outlet valve 91 and flange 14 are designed such that they have an increased thermal conductivity

Have cylinder cover 1 1, 12 to extract heat from the cylinder cover 1 1, 12 only to a reduced extent, due to the by

Inlet valve 90, outlet valve 91 and / or flange 14

flowing cool fluid. Figure 3 shows a detailed view of an embodiment to increase the thermal resistance. The exhaust valve 91 does not lie over the entire surface but only over part of the surface 91a on the first cylinder cover 11, which is the

Thermal resistance between outlet valve 91 and the first

Cylinder cover 1 1 increased. In the same way, that could also

Inlet valve 90 may be arranged in the first or second cylinder cover 11, 12. A further possibility for increasing the thermal resistance is, as shown in FIG. 3, that the flange 14 does not rest over the entire surface but only over the partial areas 14a on the first cylinder cover 11, which increases the thermal resistance between the flange 14 and the first cylinder cover 11. In the same way, the flange 14 could also be arranged in the second cylinder cover 12. 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 while conveying and compressing, for example, exhaust gas, the above-described increase in thermal conductivity giving the advantage that the cylinder 10 is reduced due to the flowing fluid F Mass is cooled so that the cylinder 10 has a higher during operation

Temperature and preferably also a more uniform one

Has temperature distribution, for example, the risk of

Warping of the components of the piston compressor 1 due to the temperature differences present, in particular warping of the cylinder 10, the piston 20, the piston rod 24 or the

Spacer 40 reduced. In an advantageous embodiment, 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 such that the so-called damage chamber remains as small as possible.

As shown in Figures 2 and 3, show in an advantageous

Embodiment of at least one of the two piston covers 21, 22, a protruding from the associated cylinder cover 11, 12,

in particular convex piston end face 21a, 22a, the

assigned cylinder cover 1 1, 12 a corresponding above

Cylinder cover outside 1 1c, 12c or one correspondingly receding with respect to piston end face 21a, 22a

Has cylinder inside lid l ld, 12d. When the piston 20 is in the uppermost position, the first cylinder interior 10a corresponds to the clearance, which, as can be seen from FIG. 3, is very small.

In one possible embodiment, the first cylinder cover 11 and / or the second cylinder cover 12 could have an end surface running perpendicular to the longitudinal axis L, in which the inlet valve 90 and the outlet valve 91 are arranged. However, the first cylinder cover 11 and / or the second cylinder cover 12 are particularly advantageously configured, as shown in FIG. 2, such that the inlet valve 90 and the

Exhaust valve 91 are arranged inclined in the cylinder cover 11, 12 with respect to the plane of symmetry S. This enables valves 90, 91 with a larger diameter to be used, which reduces their flow resistance.

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 comprises 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 over a

Spacer 40 firmly connected to the carrier housing 60 and

spaced apart with respect to the carrier housing 60. Of the

In the exemplary embodiment shown, spacer 40 comprises two support arms 42, 43 arranged symmetrically with respect to the plane of symmetry S, and the second cylinder cover 12 comprises two fastening points 12e, 12f, which are each firmly connected to a support arm 42, 43. Each of the two fastening points 12e, 12f is preferably configured identically in the circumferential direction and, as shown in FIG

Circumferential direction a width C in the range of preferably between 10 ° to 30 °. In Figure 4, the course of the section line B-B and the course of the plane of symmetry S is shown. FIG. 5 also shows the course of the section line A-A and the course of the second plane of symmetry S2. The attachment points 12e, 12f preferably run, as shown in FIG. 4 with the attachment point 12f, essentially perpendicular to the plane of symmetry S and are symmetrical to the

Plane of symmetry S arranged. The point S ₃ shows the

Intersection of the attachment point 12f with the plane of symmetry S. The attachment point 12f preferably runs symmetrically with respect to the point S ₃ or symmetrically with respect to the plane of symmetry S. As already described, the cylinder 10 points during operation of the piston compressor 1 in the area of the plane of symmetry S or in the area of the Point S _{3 has} an average temperature, the same temperature being present at both fastening points 12e, 12f due to the symmetrical arrangement, or the cylinder 10 having the same temperature, so that the first support arm 42 and the second support arm 43 at the two fastening points 12e, 12f the same

Have temperature. The symmetrical design of the cylinder 10 and the flanges 14 fastened 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 there is no mutual thermal distortion on the two support arms 42, 43. As already described, the input fluid FE and the output fluid FA can have a considerable temperature difference, so that the corresponding flanges 14 and also the cylinder 10 and possibly the piston 20 in the direction of travel C one

Difference in temperature, which could possibly lead to a warping of the cylinder or a warping of its components, in particular in the direction C. However, such a delay has no or negligible influence on the point S3 or on the support arms 42, 43, so that the cylinder 10 through the

Spacer 40 is held in a defined position during the operation of the piston compressor 1. It is particularly important that the piston rod 24 also passes through the passage opening 12g of the second valve cover 12 in the region of the plane of symmetry S, a region of the valve cover 12 which also has an average temperature, so that there is no or only one between the passage opening 12g and the piston rod 24 very little thermal distortion should occur.

5, the spacer 40 is U-shaped, comprising a first support arm 42 and a second support arm 43. However, the spacer 40 could also have more support arms, for example four, six or eight, which are connected to the second cylinder cover 12

are connected, and which are preferably arranged symmetrically with respect to the plane of symmetry S. In order to enable a better representation, the second stuffing box chamber 51 and the third stuffing box chamber 52 are not shown in FIG.

Figure 6 essentially shows the cylinder 10 and the piston 20 without the flanges 14 in a section along the section line A-A. FIG. 7 essentially shows the cylinder 10 and the piston 20 without the

Flanges 14 in a section along the 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 jacket 23 arranged between the first and second piston covers 21, 22. This layer structure of the cylinder and / or piston enables particularly favorable maintenance because only for maintenance purposes replace those parts that could show considerable wear, for example the cylinder jacket 13 and the piston jacket 23.

Advantageously, the piston skirt 23 at least partially has a labyrinth-shaped outer surface 23a, so that the piston compressor 1 is designed as a labyrinth piston compressor. In a further advantageous embodiment, instead of the labyrinth-shaped one

Outside surface 23a, at least one sealing ring is arranged on the piston jacket 23, 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 designed as a ring-sealed piston compressor 1.

The second cylinder cover 12 has, preferably arranged on its outer edge 12i, fastening points 12e, 12f at which the

Support arms 42, 43 are fastened via a fastening means, not shown, preferably a screw. The fastening points 12e, 12f are preferably arranged mutually symmetrically to the plane of symmetry S.

In an advantageous embodiment, at least one of the two piston covers 21, 22 points toward the associated cylinder cover 11, 12 protruding, in particular convex, piston end face 21a, 22a, the associated cylinder cover 11, 12 having a correspondingly protruding cylinder cover outer side 11c, 12c or a cylinder cover inner side 11d, 12d correspondingly receding with respect to piston end surface 21a, 22a, as is the case, for example, in FIG. 2 is shown.

The second cylinder cover 12 has an in in the center

Passage opening 12g running in the longitudinal direction L, along which the piston rod 24 extends, preferably at least one stuffing box chamber 50 and preferably a plurality of stuffing box chambers being arranged in the longitudinal direction L following the passage opening 12g, outside the cylinder cover 12.

In an advantageous embodiment of the piston compressor, at least one of inlet valve 90, outlet valve 91 and flange 14 does not lie on the first or second with the entire possible area

Cylinder cover 1 1, 12, but only partially, that is with a part of the possible total area, on the first or second

Cylinder cover 1 1, 12 to the thermal resistance between

Intake valve 90, exhaust valve 91, flange 14 and first or second cylinder cover 11, 12 to increase.

Figure 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. Below the carrier housing 60, an oil drip pan 64 is arranged. In another advantageous

In one embodiment, the piston compressor 1 can also have only a single cylinder 10 with pistons 20, or a plurality of cylinders 10 with a corresponding piston 20, for example between three to ten cylinders 10.

FIG. 9 shows a compressor unit 80 comprising one

Piston compressor 1, an electric motor 81, a feed manifold 85, which is connected to the fluid supply line 15, and one

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 configured to be elastic in order to prevent temperature-related expansions

compensate, these lines 15, 16 consisting for example of a metal braid.

In an advantageous embodiment, the piston compressor 1 comprises a cylinder 10 and a piston 20 arranged therein

Carrier housing 60 with a cross head 63 mounted in the carrier housing 60, a spacer 40 which connects the cylinder 10 with the

Carrier housing 60 connects, and one in a longitudinal direction L

extending piston rod 24, which connects 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 and supporting the cylinder 10. The cylinder 10 advantageously comprises a plurality of fastening points 12e, 12f arranged symmetrically with respect to the longitudinal axis L, 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, the fastening points 12e, 12f and the support arms 42, 43 being arranged symmetrically with respect to the plane of symmetry S. Advantageously, the spacer 40 is U-shaped, with two support arms 42, 43 running in the longitudinal direction L, the cylinder 10 being two

Has attachment points 12e, 12f to which the support arms 42,43 are attached. Each fastening point 12e, 12f advantageously has a width C in the circumferential direction of the cylinder 10 in the range between 10 ° and has 30 °. The cylinder 10 advantageously includes a

Inlet valve 90 and an outlet valve 91, wherein the inlet valve 90 and the outlet valve 91 are mutually symmetrical with respect to the

Plane of symmetry S are arranged. The cylinder 10 advantageously comprises a first cylinder cover 11 and a second one

Cylinder cover 12, both the first and the second

Cylinder cover 11, 12 includes an inlet valve 90 and an outlet valve 91, so that the cylinder 10 and the piston 20 are designed to be double-acting. A plurality of cylinders 10 with pistons 20 arranged therein are advantageously spaced apart from one another

Carrier housing 60 are arranged and each have a separate

Spacers 40 are connected to the carrier housing 60.

A piston rod 24 is advantageously assigned to each piston 20, the carrier housing 60 being designed as a monoblock, and the monoblock having a number of bores corresponding to the number of piston rods 45, in which a crosshead 63 is slidably mounted, each piston 20 having one Piston rod 20 with the

associated crosshead 63 is connected. The monoblock and the crosshead 62 are 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 cylinder 10 and / or the piston 20 preferably consists of a metal with a thermal conductivity in the range between 100 and 300 (W / m · K), preferably of aluminum or one

Aluminum alloy.

The piston compressor 1 comprising a cylinder 10 and a piston 20 arranged therein, a carrier housing 60 with a

Carrier housing 60 mounted crosshead 63, a spacer 40, which connects the cylinder 10 to the carrier housing 60, and a piston rod 24 extending in a longitudinal direction L, which the

Cross head 63 connects to the piston 20, is advantageously such operated that heat energy, due to a heat difference present between the cylinder 10 and the carrier housing 60, is exchanged via a plurality of support arms 42, 43. An inlet fluid FE is advantageously supplied to the cylinder 10 via an inlet valve 90

and the fluid in the cylinder 10 is discharged from the cylinder 10 through an exhaust valve 91 as an exit fluid FA

ejected, the intake valve 90 and the exhaust valve 91 symmetrical with respect to one along the longitudinal direction L of

Piston rod 24 extending plane of symmetry S are arranged so that the cylinder 10 during the delivery of the fluid in the region of the

The plane of symmetry S is heated to an average temperature which lies between the temperature of the inlet fluid FE and the outlet fluid FA, the support arms 42, 43 being connected to the cylinder 10 in the region of the plane of symmetry S via fastening points 12e, 12f.

Advantageously, the two center points S3 between the

Attachment points 12e, 12f during the delivery of the fluid in the

Mainly tempered to the same temperature. The piston rod 45 advantageously runs in the region of the plane of symmetry S, and this is tempered to substantially the same temperature as the attachment points 12e, 12f while the fluid is being conveyed.

The piston compressor 1 shown in FIG. 1 comprises a cylinder 10 and a piston 20 arranged therein, a carrier housing 60 with a cross head 63 mounted in the carrier housing 60, a spacer 40 which connects the cylinder 10 to the carrier housing 60, and one in a longitudinal direction L. extending piston rod 24, which connects the crosshead 63 to the piston 20, the spacer 40 comprising a plurality of longitudinally extending support arms 42, 43, the support arms 42, 43 being individually connected to the cylinder 10 toward the cylinder 10. The cylinder 10 has a plurality of fastening points 12e, 12f, one supporting arm 42, 43 being fastened to one fastening point 12e, 12f.

The attachment points 12e, 12f are mutually symmetrical with respect to the longitudinal direction L.

The compressor according to the invention can also have at least one piston as a labyrinth piston compressor or as a compressor

Sealing rings are designed.

The method for operating a piston compressor 1 comprises a cylinder 10 and a piston 20 arranged therein, a carrier housing 60 with a crosshead 63 mounted in the carrier housing 60, one

Spacer 40, which connects the cylinder 10 to the carrier 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 each individually via fastening points 12e, 12f with the cylinder 10

are connected, so that thermal energy, due to a heat difference between the fastening points 12e, 12f, is not exchanged directly in the circumferential direction to the longitudinal direction L between the fastening points 12e, 12f, but is exchanged via the support arms 42, 43 running in the longitudinal direction L.

In the process, the inlet fluid FE is preferably supplied with a

Temperature in the range between - 162 ° C and -40 ° C, and the outlet fluid FA is preferably compressed by one

Temperature difference in the range between 100 ° C and 150 ° C warmed.

In the method, the attachment points 12e, 12f each have a center point S3 in the region of the plane of symmetry S, which during the Conveying the fluid can be tempered to substantially the same temperature.

In the process, the spacer 40 is U-shaped, with a support section 41 and two support arms 42, 43 running in the longitudinal direction L, with the support arms 42, 43 and

Support section 41 thermal energy is exchanged between the cylinder 10 and the carrier housing 60.

In the process, each fastening point (12e, 12f) points in

The circumferential direction of the cylinder 10 has a width C in the range between 10 ° and 30 °, each fastening point 12e, 12f being arranged symmetrically to the center point S3, so that heat energy is transmitted in the circumferential direction from the respective support arm 42, 43 along the fastening point 12e, 12f.

Claims

PATENT CLAIMS

1. labyrinth piston compressor (1) comprising a cylinder (10), a piston (20) arranged in the cylinder (10), and a piston rod (24), the piston rod (24) extending in a longitudinal direction (L) and with the piston (20) is connected, and wherein the piston (20) inside the cylinder (10) is movable back and forth in the longitudinal direction (L), characterized in that the cylinder (10) comprises a first cylinder cover (1 1) that in the first

Cylinder cover (1 1) an inlet valve (90) and an outlet valve (91) are arranged, and that the inlet valve (90) and that

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).

2. Labyrinth piston compressor according to claim 1, characterized

characterized in that the cylinder (10) comprises a second cylinder cover (12) that also in the second cylinder cover (12)

Inlet valve (90) and an outlet valve (91) are arranged symmetrically with respect to the plane of symmetry (S) and the cylinder (10) and the piston (20) are thus designed to be double-acting.

3. Labyrinth piston compressor according to one of the preceding

Claims, characterized in that the cylinder (10) and / or the piston (20) consists of a metal with a thermal conductivity in the range between 100 and 300 (W / m K), preferably of aluminum or an aluminum alloy.

4. Labyrinth piston compressor according to one of the previous ones

Claims, characterized in that the inlet valve (90) and the outlet valve (91) are arranged inclined in the cylinder cover (1 1, 12) with respect to the plane of symmetry (S).

5. Labyrinth piston compressor according to one of the preceding

Claims, characterized in that the second cylinder cover

(12) is connected to a carrier housing (60) via a spacer (40) and by means of the spacer (40) with respect to the

Carrier housing (60) is kept spaced, and that the

Spacers (40) at least two symmetrical with respect to the

Plane of symmetry (S) arranged in the longitudinal direction (L) extending support arms (42, 43), which with the second cylinder cover

(13) are connected.

6. Labyrinth piston compressor according to claim 5, characterized

characterized in that the second cylinder cover (12) on the

Has outer edge (12i) arranged attachment points (12e, 12f) to which the support arms (42, 43) are attached, and that the

Fastening points (12e, 12f) symmetrical with respect to the

Plane of symmetry (S) are arranged, preferably substantially perpendicular to the plane of symmetry (S).

7. labyrinth piston compressor according to claim 6, characterized

characterized in that the spacer (40) is U-shaped, with two support arms (42, 43) running in the longitudinal direction (L), and that the second cylinder cover (12) has two fastening points (12e, 12f).

8. labyrinth piston compressor according to claim 6 or 7, characterized

characterized in that each attachment point (12e, 12f) in

The circumferential direction of the second cylinder cover (13) has a width (C) in the range between 10 ° and 30 °.

9. Maze piston compressor according to one of the preceding

Claims, characterized in that in the fluid flow direction (F) of a conveyed fluid immediately before the inlet valve (90) or in the fluid flow direction (F) immediately after the Outlet valve (91) an outwardly leading flange (14),

is arranged to the fluid the cylinder (10) from the outside

to supply or to discharge the fluid from the cylinder (10) to the outside.

10. Maze piston compressor according to one of the preceding

Claims, characterized in that the cylinder (10) comprises at least three parts, the first cylinder cover (11), the second cylinder cover (12) and in particular a tubular cylinder shell (13), the cylinder shell (13) between the first cylinder cover ( 1 1) and the second cylinder cover (13) is arranged.

1 1. Labyrinth piston compressor according to one of the preceding

Claims, characterized in that the piston (20) comprises at least three parts, a first piston cover (21), a second piston cover (22) and one between the first and second

Piston cover (21, 22) arranged piston jacket (23), the piston jacket (23) at least partially a labyrinthine

Has outer surface (23a).

12. Labyrinth piston compressor according to claim 1 1, characterized

characterized in that at least one of the two piston covers

(21, 22) has a, in particular convex, piston end face (21a, 22a) projecting towards the assigned cylinder cover (1 1, 12), and that the assigned cylinder cover (1 1, 12) has a correspondingly protruding cylinder cover outside (1 1c, 12c) or has an inside of the cylinder cover (l ld, 12d) correspondingly receding with respect to the piston end face (21a, 22a).

13. Maze piston compressor according to one of the preceding

Claims, characterized in that the second cylinder cover (12) in the center of a longitudinal (L)

Has passage opening (12g), along which the piston rod (24) runs, in the longitudinal direction (L) the

Passage opening (12g), at least one stuffing box chamber (50) is arranged outside the cylinder cover (12).

14. Labyrinth piston compressor according to one of the preceding

Claims, characterized in that at least one of the inlet valve (90), outlet valve (91) and flange (14) is only partially in contact with the first or second cylinder cover (1 1, 12) in order to reduce the thermal resistance between the inlet valve (90) and outlet valve (91 ),

To increase flange (14) and first or second cylinder cover (1 1, 12).

15. Labyrinth piston compressor according to one of claims 5 to 14, characterized in that a plurality of cylinders (10) with pistons (20) arranged therein on a common

Carrier housing (60) are arranged and are driven by a common crankshaft (61) arranged in the carrier housing (60).