CN115812124A - multi-stage compressor - Google Patents

Abstract

A multi-stage compressor for compressing a fluid, the compressor comprising: two or more cylinders, each cylinder having a compression chamber and a piston, such that fluid in each of the compression chambers can be compressed by the associated piston; the cylinders are connected in series such that fluid entering the inlet of the compressor can be compressed to a first pressure in the compression chamber of a first cylinder and then into the compression chamber of a second cylinder where the compressed fluid is compressed to a second higher pressure and then exits from the outlet of the compressor; wherein each piston is driven by the same crank pin of the compressor. Furthermore, a method for compressing a fluid, and a system comprising the multi-stage compressor are disclosed.

Description

multi-stage compressor

The invention relates to a multi-stage compressor for compressing fluid, the compressor comprising:

two or more cylinders, each cylinder having a compression chamber and a piston such that fluid in each of these compression chambers can be compressed by the associated piston;

The cylinders are connected in series so that fluid entering the inlet of the compressor can be compressed to a first pressure in the compression chamber of the first cylinder and then enter the compression chamber of the second cylinder where the compressed fluid is compressed to The second higher pressure, then the fluid exits the outlet of the compressor.

A multi-stage compressor is known, for example, from US 2151825, the cylinders of which are driven one by one by the shaft of a standard crankshaft.

A compressor for generating pressure is known, for example, from WO 07036972 A1, which discloses a hydraulic machine, advantageously for obtaining pressurized hydraulic fluid, with radial cylinders, improved bearings in the crankshaft , that is, the radial cylinders of the machine are fixed to its crankcase, where the corresponding connecting rods are coupled with the crankshaft through improved rolling friction bearings to reduce working parts, simplify machining and assembly processes, thereby improving the mechanical performance of the machine and prolonging its service life.

A first aspect of the invention relates to a multi-stage compressor according to the opening paragraph, wherein each piston is driven by the same crankpin of the compressor.

In this way, since the pistons are driven by the same crankpin, each piston does not need its own crankpin, so a multistage compressor can be made more compact in the axial direction of the compressor, i.e. in the direction in which the crankpin extends. compact.

A multi-stage compressor can be understood as a compressor in which fluid is compressed to a first pressure in a compression chamber of a first cylinder, and then the compressed fluid enters at least a compression chamber of a second cylinder, where the compressed The fluid is compressed even further to a second higher pressure. The compression chamber of each cylinder may define a compression stage of a multi-stage compressor. A multi-stage compressor may comprise more than two stages and/or more than two cylinders with compression chambers. The fluid entering the compressor inlet may be pre-compressed, ie the fluid entering the inlet may already be compressed. That is, the fluid entering the compressor inlet may be at a pressure above atmospheric pressure. For example, the fluid entering the inlet may be at the following pressures above atmospheric pressure: 1 bar, 2 bar, 3 bar, 4 bar, 5 bar, 6 bar, 7 bar, 8 bar, 9 bar, 10 bar, 11 bar, 12 bar bar, 13 bar, 14 bar, 15 bar, 16 bar, 17 bar, 18 bar, 19 bar, 20 bar, 21 bar, 22 bar, 23 bar, 24 bar, 25 bar or more. This can help create fluid that is compressed to even higher pressures by the compressor.

The fluid may be any suitable fluid, liquid and/or gas. The fluid may be a compressible fluid.

The crankpin may extend in the axial direction and/or in the radial direction of the compressor. A crankpin is rotatable about an axis of rotation to drive the piston. The crank pin may be positioned at a distance from the axis of rotation. The crank pin may be positioned at a distance in radial direction from the axis of rotation. There may be a distance from the central axis of the crankpin to the axis of rotation. The axis of rotation may lie outside the periphery of the crankpin. The axis of rotation and the axial direction may be parallel. A crankpin may be attached to a rotatable crankshaft. The crankshaft may extend outside of the compressor housing. The crankshaft may extend in an axial direction of the compressor. The crankshaft may extend beyond the housing of the compressor. The crankshaft of the compressor may be configured such that a drive unit and/or a crankshaft of another compressor may be coupled thereto. The axis of rotation may be concentric with the crankshaft. The radial direction may extend perpendicular to the axis of rotation. The crankpin may be cylindrical, having a length extending in an axial direction and a crankpin diameter extending perpendicular to the axial direction. The crankpin may be positioned a distance "D" from the axis of rotation to the central axis and/or periphery of the crankpin of at least 0.1, 0.25, 0.5, 1, 2, 3, 4, 5 or more crankpin radii. The outer periphery of the crankpin may overlap the axis of rotation when viewed in a direction parallel to the axis of rotation. The outer diameter of the crankpin may be equal to or greater than the maximum diameter of at least one and/or two, and/or three, and/or four, and/or five, and/or six or more pistons of the compressor Outer diameter. The outer diameter of the crankpin may be equal to or greater than the largest diameter of all pistons of the compressor. The diameter of the crank pin can be equal to or greater than 1.1 times, 1.2 times, 1.3 times, 1.4 times, 1.5 times, 1.6 times, 1.7 times, 1.8 times, 1.9 times, 2 times the maximum outer diameter of the compressor piston. This may allow shorter pistons to be used, and/or may reduce the lever arm acting on the crank pin and thus potentially the axis of rotation and/or crankshaft. Reducing the lever arm reduces the amount of torque required to drive the compressor, thereby reducing compressor power consumption and increasing efficiency. At least one, two, three, four, five, six or more pistons may have a substantially constant outer diameter and/or a constant outer diameter. Substantially constant outer diameter and/or constant outer diameter may be understood as substantially the same and/or the same outer diameter along the length of the piston(s).

At least one, two, three, four, five, six or more pistons may have different piston lengths "L". The sliding shoes may be substantially identical or identical to each other. The retaining rings may be substantially identical or identical to each other. The same sliding shoe and/or the same retaining ring may facilitate the stroke length being defined by the piston length of the associated piston, especially when the pistons are driven by the same crank pin and/or crank pin bearing. The length "L" of the piston may be a length extending in a radial direction. The length of the piston may extend from the top surface of the top end of the piston to the bottom surface of the bottom end of the piston. The diameter of the piston may extend normal to its length. The length of the piston may alternatively be denoted as piston length. The stroke length of a piston may be defined as the distance a piston travels in an associated cylinder and/or compression chamber while the compressor is operating. Additionally or alternatively, the stroke length may be the distance traveled by the top and/or bottom end of the piston between the bottom-most point of the stroke and the top-most point of the stroke. Additionally or alternatively, the stroke length may be the distance traveled by the top and/or bottom end of the piston between bottom dead center and top dead center.

The term "associated" may be understood as being linked to or directly working with, potentially in contact with. For example, a cylinder may have an associated piston and an associated compression chamber in which the associated piston works. Similarly, the cylinder and/or piston may have associated seals, such as rod seals, for sealing between the piston and the cylinder.

The cylinder can be positioned about the axis of rotation. The cylinder may extend in a radial direction away from the axis of rotation. Compression chambers may be located within associated cylinders. A compression chamber may be a hollow space within a cylinder in which fluid is compressed. The hollow space may occupy a small fraction of the total volume of the cylinder. The hollow space may be cylindrical. The compressor may comprise at least 3, 4, 5 or 6 or more cylinders. Compressors can include 2, 3, 4, 5 or 6 cylinders. If there are more than two cylinders, fluid may successively enter the compression chamber(s) of the additional cylinder(s) and be compressed to successively higher pressures.

The piston can be cylindrical and/or disc-shaped. In operation, the pistons can move up and down in the combustion chamber and/or cylinder and/or substantially, substantially only, or only in the radial direction of the compressor and/or in the axial direction of the corresponding piston, Or only or substantially only in the axial direction of the corresponding piston. In operation, the piston can swing up and down within the combustion chamber and/or cylinder. The diameter or outer diameter or maximum outer diameter "d" of the piston may be smaller than or equal to the diameter or inner diameter of the associated combustion chamber. Potentially during compressor operation and/or when stopped, there may be some clearance between the inner wall of the compression chamber and the outer circumference of the associated piston. The piston is spaced by a predetermined clearance from the inner wall of the compression chamber, potentially during operation of the compressor and/or at rest. The gap may surround the entire periphery of the associated piston. The piston may extend in a radial direction. The piston may comprise and/or consist of a solid material. The piston may comprise and/or consist of a hollow material. Hollow materials can be lighter than solid materials, thereby improving the efficiency of the compressor because the inertia of the piston can be reduced and less mass must move to compress the fluid. The piston may be made of metal, metal alloys such as brass, steel, aluminum or aluminum alloys, bronze and/or combinations thereof. The piston can be made of steel with an aluminum core.

The inlet of the compressor can be understood as the inlet pipe for the fluid to enter the compressor. The inlet may enter into the compression chamber of the first cylinder of the compressor, ie into the first stage of the compressor. An inlet may be understood as an entry point for fluid to enter the compressor. Fluid may enter the compression chamber of the first cylinder of the compressor, ie the first compression stage of the compressor, through the inlet. The inlet may include a check valve as described herein for preventing fluid from the compression chamber from flowing out of the chamber through the inlet. The inlet and outlet of the compressor may be located on the same side of the compressor. This can provide easy access to entry and exit.

The outlet of the compressor can be understood as the outlet duct for the fluid to leave the compressor. The outlet may leave the compression chamber of the last cylinder of the compressor, ie the last stage of the compressor. An outlet may be understood as an exit point for fluid to exit the compressor. Fluid may leave the compression chamber of the last cylinder of the compressor, ie the last compression stage of the compressor, through the outlet. The outlet may include a check valve as described herein to prevent fluid from entering the chamber from outside the compression chamber through the outlet.

The crankpin may be positioned at a distance from the crankshaft, ie such that there is a distance between the outer periphery of the crankpin and the outer periphery of the crankshaft. The crankpin may be located at a point located radially from the axis of rotation of the crankshaft. The crankpin may extend parallel to the crankshaft. One or more bearings, such as roller bearings and/or slider bearings, may be attached and/or mounted on the crank pin. Two roller bearings can be mounted on the crank pin. The crankpin may be a separate component from the crankshaft. The crank pin may comprise, consist of, and/or be coated with a slider bearing material such as metal, metal alloy, or polymer, such as brass, steel, aluminum or aluminum alloys, bronze, PTFE, and/or combinations thereof.

The crankpin and/or one or more bearings on the crankpin may be positioned such that the axis of rotation of the crankshaft has a distance from the central axis and/or periphery of the crankpin, potentially at least 0.1, 0.25, 0.5, 1, 2, 3, 4, 5 or larger crankpin radii. The periphery of the crankpin and/or bearing(s) on the crankpin may overlap the axis of rotation. This can reduce the length of the lever arm acting on the crankpin and/or on the axis of rotation of the crankshaft. Additionally or alternatively, the outer diameter of the crankpin and/or bearing(s) may be equal to or greater than at least one and/or two, and/or three, and/or four, and/or five of the compressor The maximum outside diameter of one, and/or six or more pistons. Additionally or alternatively, the outer diameter of the crankpin and/or bearing(s) may be equal to or greater than the largest diameter of all pistons of the compressor. Additionally or alternatively, the outer diameter of the crankpin and/or bearing(s) may be equal to or greater than 1.1, 1.2, 1.3, 1.4, 1.5, 1.6, 1.7 times the maximum outer diameter of the compressor piston , 1.8 times, 1.9 times, 2 times. This may allow the use of shorter pistons, and/or may reduce the length of the lever arm acting on the crank pin and thus potentially the axis of rotation and/or the crankshaft. Reducing the length of the lever arm reduces the amount of torque required to drive the compressor, thereby reducing compressor power consumption and increasing efficiency. The one or more bearings on the crankpin may alternatively be denoted crankpin bearing(s). The crankpin bearing(s) can drive the pistons of the compressor. The crankpin bearing may be an axial-radial bearing, such as an axial-radial roller bearing.

A lever arm can also be expressed as a moment arm. The length of the lever arm acting on the crank pin and/or the axis of rotation may be equal to or less than 200%, 190%, 180%, 170%, 160%, 150%, 140% of the minimum and/or maximum stroke length of the compressor piston , 130%, 120%, 110%, 100%, 90%, 80%, 70%, 65%, 60%, 55%, 50%, 45%, 40%, 35%, 30%, 25%, 20 %, 19%, 18%, 17%, 16%, 15%, 14%, 13%, 12%, 11%, 10%, 9%, 8%, 7%, 6%, or 5%. Additionally or alternatively, the length of the lever arm acting on the crank pin and/or the axis of rotation may be equal to or less than 90%, 80%, 70%, 60%, or less than the piston length of the shortest and/or longest piston of the compressor. 55%, 50%, 45%, 40%, 35%, 30%, 25%, 20%, 19%, 18%, 17%, 16%, 15%, 14%, 13%, 12%, 11% , 10%, 9%, 8%, 7%, 6% or 5%. The outer diameter of the crankpin and/or crankpin bearing(s) may be equal to or greater than 1.1 times, 1.2 times, 1.3 times, 1.4 times, 1.5 times, 1.6 times the minimum and/or maximum stroke length of each piston of the compressor times, 1.7 times, 1.8 times, 1.9 times, 2 times, 2.1 times, 2.2 times, 2.3 times, 2.4 times, 2.5 times, 2.6 times, 2.7 times, 2.8 times, 2.9 times, 3 times, 3.1 times, 3.2 times, 3.3 times, 3.4 times, 3.5 times, 3.6 times, 3.7 times, 3.8 times, 3.9 times, 4 times, 4.1 times, 4.2 times, 4.3 times, 4.4 times, 4.5 times, 4.6 times, 4.7 times, 4.8 times, 4.9 times , or 5 times. The outer diameter of the crankpin and/or crankpin bearing(s) may be equal to or greater than 0.1, 0.2, 0.3, 0.4, 0.5, 0.6 times the piston length of the shortest and/or longest piston of the compressor , 0.7 times, 0.8 times, 0.9 times, 1 times, 1.1 times, 1.2 times, 1.3 times, 1.4 times, 1.5 times, 1.6 times, 1.7 times, 1.8 times, 1.9 times, 2 times. The technical features in this paragraph can provide a shorter lever arm with the advantages mentioned above.

The crankshaft may be supported in the compressor housing by one or more crankshaft bearings (eg, slider bearings and/or roller bearings described herein). A crankshaft may include at least two interconnected shafts. Each shaft may be supported in the compressor housing by one or more crankshaft bearings (eg, slide bearings and/or roller bearings described herein). At least two shafts may be concentric with each other and/or with the axis of rotation. At least two shafts may have equal length and/or diameter. At least two shafts may have different lengths. At least one of the at least two shafts may be configured to engage with a drive unit for driving the compressor. At least one of the at least two shafts may be a drive shaft for driving the compressor. A crank pin may be positioned between two of the at least two shafts. The crankpin may be mounted eccentrically to at least two shafts. The crank pin may interconnect two of the at least two shafts. The crankpin may interconnect the two shafts by clamping to them. A crank pin may be clamped and fastened to a respective end of each of the at least two interconnected shafts by a bolt clamping mechanism to interconnect the two shafts. A crank pin may be clamped at respective ends of the crank pin and secured to respective ends of each of the two shafts. The crankpin and at least two shafts may be in one piece. The crankpin and at least two shafts may be machined from one piece to form a continuous unit.

The compressor may be electrically driven by an electric drive unit powered eg by batteries, solar, wind, wave, nuclear, thermal, preferably sustainable energy. Additionally and/or alternatively, the compressor may be driven by a fossil fuel powered drive unit.

A piston may extend beyond its associated compression chamber and/or cylinder towards the axis of rotation. The overall length of the piston in radial direction may be longer than the overall length of the associated compression chamber in radial direction. A piston at top dead center (TDC), ie at the apex of its stroke, may extend beyond its associated cylinder toward the axis of rotation. The piston may extend away from and beyond its associated compression chamber and/or cylinder in a direction facing the crankpin. A piston at top dead center may extend away from and beyond its associated compression chamber and/or cylinder in a direction facing the crankpin. Each cylinder and/or piston may include a linear seal (such as a piston seal and/or a rod seal) for sealing between the associated piston and cylinder. One or more cylinders may include one or more rod seals for sealing against the piston. The piston may be an associated piston of the cylinder. For example, the first cylinder and/or the cylinder base of the first cylinder may include one or more rod seals for sealing on the associated piston of the first cylinder; and/or the second cylinder and/or the The cylinder base may include one or more rod seals for sealing on an associated piston of the second cylinder; and/or the third cylinder and/or the cylinder base of the third cylinder may include one or more rod seals, for sealing on the associated piston of the third cylinder; and/or the fourth cylinder and/or the cylinder base of the fourth cylinder may include one or more rod seals for sealing on the associated piston of the fourth cylinder and/or the fifth cylinder and/or the cylinder base of the fifth cylinder may include one or more rod seals for sealing on the associated piston of the fifth cylinder; and/or the sixth cylinder and/or the sixth cylinder The cylinder base of the cylinder may include one or more rod seals for sealing on the associated piston of the sixth cylinder, and so on. The piston may include one or more linear seals, such as piston rings and/or shaft seals. The seals may be hydraulic seals and/or pneumatic seals. The cylinder and/or piston may include a combination of hydraulic and/or pneumatic seals. Linear seals can be positioned circumferentially in the cylinder or on the piston. Linear seals may be positioned in the circumference of the cylinder and/or compression chamber and/or on the circumference of the piston. A linear seal may be positioned in the cylinder and/or compression chamber adjacent to the end of the piston at bottom dead center. The end at bottom dead center of the piston may be positioned in the cylinder and/or compression chamber at a distance from the cylinder base and/or bottom of the associated compression chamber. A linear seal may be mounted circumferentially on a portion of the piston located within the cylinder and/or compression chamber.

One or more, or all of the pistons may not include any seals, such as piston rings or piston seals, potentially attached to and/or mounted on the pistons. In an embodiment, no seals are attached or installed on one or more or all of the pistons. Such seals are typically positioned between the outer diameter of the piston and the inner wall of the associated compression chamber to provide a seal therebetween. The movement of the piston is configured such that the piston does not contact the inner wall of the associated compression chamber during operation and/or at rest, and seals such as rod seals and/or shaft seals are provided (which are located in the cylinder housing to provide a seal between the pistons seal with the associated compression chamber) prevents the piston from contacting and/or wears and/or damages the inner walls of the compression chamber, and ensures that the compression chamber has an adequate seal, especially to the crank housing, which may allow the omission of a seal on the piston components, such as piston seals and/or piston ring(s). Additionally or alternatively, the compressor, and/or one or more pistons, and/or one or more cylinders, and/or one or more compression chambers, and/or one or more sliding shoes, and/or crankpin and/or one or more bearings located on the crankpin, and/or one or more guide grooves and/or one or more guide elements, and/or one or more rod seals contained in the cylinder base The member may be configured such that, in operation and/or at rest, the or each piston does not contact or substantially contact, or is configured not to contact or substantially contact the inner wall of the associated compression chamber. Additionally or alternatively, the compressor, and/or one or more pistons, and/or one or more cylinders, and/or one or more compression chambers, and/or one or more sliding shoes, and/or crankpin and/or one or more bearings located on the crankpin, and/or one or more guide grooves and/or one or more guide elements, and/or one or more rod seals contained in the cylinder base The components may be configured such that in operation the or each piston moves only or substantially only, or is configured to move only or substantially only in the radial direction of the compressor. Thereby, frictional losses of the piston(s) moving in the compression chamber(s) may be reduced and/or prevented, whereby the efficiency of the compressor may be increased. This may also reduce wear on the inner wall(s) of the compression chamber(s) and/or the peripheral, potentially peripheral surface of the piston(s), thereby extending the service intervals and/or life of the compressor.

"Periphery" may be understood as the outer limit and/or edge of an object. Similarly, "peripheral surface" may be understood as the outer and/or outermost surface of an object. The periphery of the object may substantially coincide or coincide with the diameter and/or outer diameter and/or outermost diameter of the object.

Two or more cylinders may be positioned radially about the axis of rotation. The two or more cylinders can be radial cylinders. Two or more cylinders may be equally spaced about the axis of rotation. Two or more cylinders may be spaced equidistantly in the radial direction from the axis of rotation.

The compressor may include cooling passages for cooling the cylinders and/or the compression chamber. Each cylinder may include one or more cooling passages for cooling the cylinder and/or the compression chamber. The one or more cooling passages may be interconnected by one or more cooling tubes extending between the cylinders. The one or more cooling tubes may extend outside the cylinder. The one or more cooling channels and the one or more cooling pipes may form a cooling circuit for cooling the cylinder. Each cylinder may include at least one cooling channel with a first flow direction and at least one cooling channel with a second flow direction. The second flow direction may be opposite to the first flow direction. In this way, a circulating flow of cooling medium can be provided. The two cooling channels of each cylinder can be interconnected with the two cooling channels of the previous and/or subsequent cylinder, wherein each cooling channel of each cylinder is connected to the immediately preceding and/or immediately following via a corresponding cooling pipe. The corresponding cooling channels of the subsequent cylinders are interconnected. In the cylinder defining the first or last compression stage, the at least one cooling passage flowing in the first direction and the at least one cooling passage flowing in the second direction may be interconnected to form a loop such that the cooling medium fluid may circulate through through the corresponding cylinder and to the previous cylinder.

In an embodiment, the multistage compressor further comprises at least one supply compressor for supplying compressed fluid at a pressure above atmospheric pressure to the compression chamber of the first cylinder and/or to the inlet of the multistage compressor, wherein the supply compressor And the piston is driven by the same crankshaft as the piston of the multi-stage compressor. In a development of the previous embodiment, the at least one supply compressor is driven by the same crank pin as the pistons of the multi-stage compressor.

The supply compressor may be a reciprocating compressor and/or a diaphragm compressor, and/or a piston compressor. The multi-stage compressor may comprise two, three, four, five or more supply compressors each supplying compressed fluid at a pressure above atmospheric pressure to the compression chamber of the first cylinder. One or more supply compressors may be mounted and/or positioned on and/or in and/or within the multi-stage compressor. One or more supply compressors may be at least partially positioned and/or mounted and/or housed within the compressor housing. One or more supply compressors can operate in parallel. One or more supply compressors may be positioned outside the multi-stage compressor housing. One or more supply compressors may be positioned circumferentially about the same crankshaft that drives the pistons. One or more supply compressors may be positioned outside the multi-stage compressor housing, circumferentially around the same crankshaft. Each of the one or more supply compressors may be driven by the same second crankpin. The second crank pin may be located outside the multi-stage compressor housing, potentially on the same crankshaft that drives each piston.

One or more supply compressors may be positioned within the periphery of the multi-stage compressor. One or more supply compressors may be located at least partially within or within the multi-stage compressor housing. One or more supply compressors may be attached to respective valve tubes and/or cooling tubes. One or more supply compressors may be positioned between adjacent cylinders of the multi-stage compressor, potentially in the space between adjacent cylinders. One or more or each supply compressor (potentially a respective outlet of each supply compressor) may be connected to the compression chamber of the first cylinder, potentially via a respective supply duct. Each supply compressor may potentially be connected to the inlet of the compression chamber of the first cylinder by a respective associated supply duct. One or more supply pipes may flow into a common pipe and/or manifold before flowing into the compression chamber of the first cylinder.

Testing has shown that including such a supply compressor to compress the air provides an appropriate amount of compressed air to the compression chamber of the first cylinder with minimal noise from the supply compressor and minimal impact on the drive unit driving the multi-stage compressor. The same results are expected for other gases and fluids. In an embodiment, a separate independent sliding shoe for engaging the crank pin is attached to the bottom end of each piston.

In this way, the compressor can be quickly assembled since no connecting rods are required. This can increase the efficiency of the compressor because less energy can be lost overcoming the inertia of the moving parts and/or friction between the moving parts. In addition, the movement of each piston can remain independent, which improves compressor design options and adaptability. The bottom end of the piston may be the end opposite the top end of the piston. The tip of the piston may be positioned within the associated compression chamber. The top surface of the piston tip can compress fluid in an associated compression chamber. The bottom end of the piston may be the end of the piston closest to and/or facing the crank pin and/or the axis of rotation. Each sliding shoe may be mounted on the bottom end of an associated piston. Each sliding shoe may be mounted at the bottom end of the associated piston. Each sliding shoe may be attached to the associated piston via a connecting shaft extending through the bottom end of the associated piston and at least a portion of the associated sliding shoe. Each sliding shoe is detachable from its associated piston. The sliding shoe can be a separate part, ie independent parts not connected to each other. Each sliding shoe may engage a crankpin and/or a crankpin bearing attached to the crankpin. The sliding shoe and/or the sliding surface of the sliding shoe engaging or engaging the crankpin and/or crankpin bearing may comprise a sliding body bearing material such as a metal, metal alloy or polymer such as brass, steel, aluminum or an aluminum alloy , bronze, PTFE and/or combinations thereof), and/or coated with and/or consisted of. The sliding surface may be shaped to form fit with the crankpin and/or a crankpin bearing attached to the crankpin. The sliding surface may be arcuate and/or shaped as part of the circumference of a circle. The sliding surface of the sliding shoe may be the lower and/or bottom surface of the sliding shoe, and/or the surface facing the crankpin and/or crankpin bearing. The sliding surface of the sliding shoe may be the surface on which the sliding shoe slides on the crank pin and/or the crank pin bearing. One or more or each sliding shoe may include a sliding surface for engaging the crankpin and/or a crankpin bearing attached thereto. The sliding shoe sliding surface may be a part of the sliding shoe for engaging a crankpin and/or a crankpin bearing attached to the crankpin.

At least one crankpin bearing for engaging the sliding shoe may be mounted on the crankpin. The crankpin bearings may be round. A crankpin bearing may be positioned between the crankpin and the sliding shoe. The crank pin bearing may be a plain bearing (also known as a sliding bearing or plain bearing), or may be a roller bearing, or any other suitable bearing. A sliding shoe may engage the outer surface of the crankpin bearing. A roller bearing can be understood as a bearing with an inner ring and an outer ring with rolling elements between the inner ring and the outer ring. In the case of roller bearings, the outer surface of the bearing may be the outer surface of the outer ring of the bearing. In the case of roller bearings, the surface of the inner ring of the bearing may be attached to the crank pin. A sliding shoe can be attached to and associated with a piston.

In a development of the previous embodiment, each sliding shoe is rotatably attached to the bottom end of the associated piston.

Having an individual rotating sliding shoe for each piston can provide a high degree of freedom of choice in design, since the engagement of each sliding shoe with the crank pin and thus the movement of each piston can be customized for each piston. The sliding shoe may be rotatably attached to the bottom end of the associated piston via a bearing such as a slider bearing, roller bearing or any other suitable bearing. The sliding shoe and/or piston may comprise at least one bearing and/or bearing surface for supporting the connecting shaft and allowing relative rotational movement of the associated sliding shoe and piston. The bearing surface may be a sliding body bearing surface. The bearings may be sliding body bearings (also referred to as slide bearings), roller bearings or the like. Each piston may include a slide or roller bearing in the bottom end of the piston for supporting the associated connecting shaft. Each sliding shoe may comprise at least one slider bearing and/or roller bearing through which the associated connecting shaft extends. At least a portion of the sliding shoe through which the associated connecting shaft extends may comprise a sliding body bearing material such as metal, metal alloy or polymer such as brass, steel, aluminum or aluminum alloy, bronze, PTFE and/or combinations thereof, And/or consist of and/or be coated with it, so that the sliding shoe itself can constitute a sliding body bearing for supporting the associated connecting shaft. The connecting shaft may extend through two such parts of the associated sliding shoe. The connection shaft may extend in the axial direction. The connecting shaft may be secured to the associated piston and sliding shoe by one or more circlips, pins, bolts or the like. Snap rings, pins, bolts, etc. may be positioned at opposite ends of the connecting shaft in the axial direction.

In an embodiment, the housing of the multi-stage compressor comprises at least one guide slot configured for guiding the movement of at least one guide element attached to the piston.

This may provide freedom of choice in the design of the compression chamber and associated piston diameter, as the walls of the compression chamber need not be configured to guide the piston. The compressor may comprise at least one guide slot per piston for guiding the movement of at least one guide element and/or sliding shoe attached to the associated piston. The guide groove may be offset from the piston in the axial direction. The at least one guide groove may extend in a radial direction. The at least one guide groove may extend for a length equal to the stroke length of the associated piston. The at least one guide element can be attached to the connecting shaft. The housing of the compressor may comprise at least two guide grooves per piston, which are offset in the axial direction on both sides of the piston and/or the sliding shoe. Each piston and/or sliding shoe may comprise one or more guide elements for being guided in guide grooves. Each guide element can be guided in a separate guide groove. Two guide elements can be attached to the piston and/or the sliding shoe, wherein the two guide elements are offset in the axial direction on both sides of the piston and/or the sliding shoe. Two guide elements may be attached to opposite ends of the connecting shaft in the axial direction. The movement of each piston can thus be guided. The guide element may comprise and/or consist of a metal or sliding body bearing material as described herein. The guide element may be fastened to the connecting shaft via a clamp, such as a circlip. The pistons may be guided such that the one or more pistons do not contact the inner wall of the associated compression chamber and/or such that the one or more pistons move only in radial direction. This can have advantages as described above.

The at least one guide groove and/or the at least one guide element attached to the piston may be configured such that in operation the associated piston does not contact the inner wall of the associated compression chamber and/or such that in operation the piston only moves along the Or substantially only in the radial direction of the compressor.

In an embodiment, the multistage compressor comprises one or more linear bearings configured to guide an associated one of the pistons of the multistage compressor and/or at least one guide attached to the associated piston. component movement.

Linear bearings can be plain bushes, slider bearings, roller bearings, etc. A multi-stage compressor may comprise 1, 2, 3, 4, 5, 6 or more linear bearings per piston for guiding the associated piston and/or at least Movement of a guiding element. Each linear bearing can guide a guide element attached to the associated piston. Additionally or alternatively, the guide element attached to the associated piston may comprise one or more linear bearings. Each linear bearing may be attached to slide on a journal and/or shaft in or on the compressor housing. The journal and/or the shaft may extend parallel to the associated piston and/or the direction of movement of the associated piston. The at least one guide element may comprise two linear bearings, each sliding on a journal and/or shaft attached in or on the multi-stage compressor housing.

Additionally or alternatively, multi-stage compressors may include 1, 2, 3, 4, 5, 6 or more bushing guide rods per piston configured for Guides the movement of the associated piston. The bushing guide rod(s) may be positioned and/or attached in the compressor housing and/or the cylinder housing and/or the compression chamber, potentially forming the innermost surface of the compression chamber. The innermost surface of the compression chamber may face the associated piston and potentially provide a surface for the piston to slide on. The bushing guide rod(s) may be made of bushing material. The liner guide rod(s) may extend parallel to the associated piston and/or the direction of movement of the associated piston. The bushing guide rod(s) may alternatively be denoted as bushing guide rod(s). The liner guide rod(s) may extend in the axial direction of the associated piston and may be positioned around the circumference of the associated piston.

Additionally or alternatively, a multi-stage compressor may include 1, 2, 3, 4, 5, 6 or more guide rollers configured to guide movement of an associated piston. The guide rollers may be positioned and/or attached and/or seated and/or installed in the multi-stage compressor housing and/or the cylinder housing. Guide rollers may rollably guide the movement of the associated piston. The guide roller(s) may be positioned along the axial direction of the associated piston and may be positioned around the circumference of the associated piston.

In an embodiment, the compression chamber of at least a first cylinder of the two or more cylinders is connected to the compression chamber of a second cylinder by at least one check valve to prevent fluid from the compression chamber of the second cylinder from flowing to the first cylinder. The compression chamber of a cylinder.

In this way, fluid can flow from the compression chamber of a given cylinder to the compression chamber of the immediately following cylinder, that is, from the first compression stage of a multi-stage compressor to the next compression stage, and flow from a given compression chamber to the next compression stage can be prevented. The compression chamber of the cylinder of the previous compression stage. This may reduce the complexity of the compressor construction as only a single flow channel with check valves between the compression chambers of the two cylinders may be required. The compression chamber of a cylinder can be connected to the compression chamber of the immediately following and/or immediately preceding cylinder via at least one non-return valve. The compression chambers of the cylinders may be connected by check valves, preventing fluid from the compression chamber of a given cylinder from flowing to the compression chamber of the immediately preceding cylinder. The at least one check valve may prevent fluid flow from a given cylinder to an immediately preceding cylinder. A check valve may be provided between each compression chamber and the compression chamber of the cylinder immediately following and/or the cylinder immediately preceding it. The at least one non-return valve can also be denoted as a shut-off valve. The at least one check valve may be spring loaded. The at least one check valve may be a ball stop valve, a diaphragm stop valve, a swing stop valve or any other suitable valve. The compression chamber of the last cylinder (ie the last compression stage) may be connected to the outlet of the compressor. The compression chamber of the last cylinder can be connected to the outlet of the compressor by at least one check valve. The inlet of the compressor may be connected to the compression chamber of the first cylinder, ie the first compression stage of the compressor, via at least one check valve. In this way, compressed fluid can be sequentially passed from the inlet through the compression chambers of successive cylinders to and out of the outlet, and fluid from the outlet can be prevented from flowing through previous compression chambers of previous cylinders. Check valves can be located on the outside of two or more cylinders. The check valve may be located in a valve housing which can be attached and detached from the cylinder and/or cylinder housing and/or compressor and/or compressor housing.

In an embodiment, the at least one check valve is located external to the two or more cylinders, within a valve conduit, such that fluid flowing from the compression chamber of at least a first cylinder to the compression chamber of a second cylinder flows through the valve conduit and The at least one check valve.

The term "outside of two or more cylinders" throughout this disclosure may be understood as not being located in or within the cylinders and/or cylinder housings of the two or more cylinders.

In this way, the design of the compressor (in particular the cylinder and the cylinder housing) has a high degree of freedom of choice, since the connection of the compression chamber and the non-return valve can be provided separately from the cylinder and/or the cylinder housing and/or outside it . The valve tube may form part of the compression chamber. The compression chamber may comprise at least a portion of the valve tube. The valve tube may include the tube volume for fluid to flow through both sides of the check valve. The compression chamber may comprise the tube volume of the valve tube. The compression chamber can be connected directly to the tube volume. The valve tube may be a cylindrical tube. The or a valve tube may extend between a given cylinder and the immediately following or preceding cylinder. A valve duct may be arranged between each compression chamber and the compression chamber of the cylinder immediately following and/or the cylinder immediately preceding it. One or more, potentially all, of the valve tubes may be located within the outer perimeter of the compressor and/or cylinder and/or cylinder housing. One or more, potentially all, valve tubes may be located closer to the center and/or axis of rotation of the compressor than to the outermost portion of the cylinder(s) and/or cylinder housing(s). Said outermost part of the cylinder(s) and/or cylinder housing(s) is potentially the center and/or axis of rotation of the cylinder(s) and/or cylinder housing(s) away from the compressor furthest part. The at least one check valve may be positioned within the valve tube midway along the length of the valve tube extending between a given cylinder and an immediately following cylinder. The valve tube may include an inlet port and an outlet port. The valve tube may have a valve tube length extending between an inlet end of the valve tube and an outlet end of the valve tube. One or more, potentially all, valve tubes may be straight or substantially straight. The term "straight" may be understood as a tube extending only or substantially only in one direction. One or more, or all, of the valve tubes may extend substantially or between the outer side wall of a given cylinder and/or cylinder housing and the outer side wall of the immediately following or immediately preceding cylinder and/or cylinder housing . The valve tube may extend substantially straight and/or straight between said respective outer side walls. One, or one or more, or each, or all valve tubes may extend straight and/or substantially straight between the immediately following and/or immediately preceding the cylinder and/or the outer side wall of the cylinder housing extended. The at least one check valve prevents fluid from flowing in a direction from the outlet end to the inlet end of the valve tube. The first tube volume may be the tube volume extending from the inlet end of the valve tube to the check valve. The second tube volume may be the tube volume extending from the check valve to the outlet end of the valve tube. At least one compression chamber may comprise the first tube volume. The check valve may be positioned closer to the inlet end of the valve tube than to the outlet end of the valve tube. The check valve may be positioned less than 1/100, 1/75, 1/50, 1/40, 1/30, 1/25, 1/20, 1/15 of the valve tube length from the inlet end of the valve tube , 1/10, 1/9, 1/8, 1/7, 1/6, 1/5, 1/4, 1/3. The at least one check valve may be positioned inside the valve tube equidistant from the inlet and outlet ports. The valve tube may comprise sealing elements at its inlet and/or outlet end for sealing against the housing of the cylinder. The inlet and/or outlet ends of the valve tube may be rounded and/or spherical. The cylinder housing may comprise an opening corresponding to the shape of the inlet and/or outlet end of the valve tube to receive the inlet and/or outlet end. In this way, the valve tube can be easily attached to and removed from the housing of the compressor cylinder. The valve tube may include a first valve tube portion and a second valve tube portion. The first valve tube part and the second valve tube part can be detached from each other, so that the valve tube can be disassembled into a disassembled state in which the first valve tube part and the second valve tube part are disconnected. The first valve part and the second valve part may be attached to each other in an assembled state where the first valve tube and the second valve tube are connected. The first valve tube part and the second valve tube part may be attached to each other via threads. The first valve tube portion may include threads mating with threads on the second valve tube portion to assemble and detach the first valve tube portion and the second valve tube portion. Each of the first valve tube portion and the second valve tube portion may constitute one half of the valve tube. In the assembled state, the sealing element can be arranged between the first valve tube part and the second valve tube part. The valve tube can be cooled by a cooling device. A cooling device for cooling the valve tube, such as a cooling jacket, may be attached to the valve tube. A cooling device may be provided around the valve tube. A cooling jacket can be connected to one or more cooling tubes. The cooling tubes can be connected to one or more cooling channels. A cooling jacket may be connected to one or more cooling channels. In this way, the cooling jacket can be part of the cooling circuit of the compressor and can cool both the two or more cylinders and the valve tubes. The cooling jacket and the connected valve lines and/or the connected cooling channels can form a cooling circuit separate from the cooling circuit for cooling the cylinder. In the disassembled state of the valve tube, the at least one non-return valve can be exposed. The at least one non-return valve can be accommodated in the first and/or in the second valve line. The at least one check valve may be detachably attachable to the first and/or second valve tube portion. The at least one non-return valve can be screwed into the first or the second valve tube part. Check valves may be positioned at the inlet end of the valve tube(s) and the outlet end of the valve tube(s). The volume between the check valves at the inlet and outlet ends of the valve tube(s) may be considered the tube volume. This provides a buffer for the compressed fluid between the compression chambers.

One or more cooling tubes may extend between the cylinders, parallel to the valve tubes.

In a development of the previous embodiment, the valve tube(s) are removably attached between the two cylinders.

This can provide a compressor that is easy to maintain and/or adapt to different usage situations, as the valve tubes can be quickly and easily replaced or swapped out for different versions, such as higher rated check valves for higher pressure applications.

The valve tube(s) may be removably attached to the cylinder by press fit, clip in, snap lock and/or threaded connection. The valve tube(s) may be removably attached such that the valve tube(s) may be removed by hand (ie, without the use of tools). The inlet and/or outlet ends of the valve tube may be removably attachable in the cylinder.

In an embodiment, the at least one compression chamber comprises the first tube volume of the valve tube.

In an embodiment, the valve tube(s) extend between a given cylinder and the immediately following cylinder.

In an embodiment, the valve tube(s) are arranged between each compression chamber and the compression chamber of the cylinder immediately following and/or immediately preceding it.

In an embodiment, one or more, potentially all, valve tubes are substantially straight.

In an embodiment, one or more, potentially all, valve tubes are located within the outer perimeter of the compressor and/or cylinder and/or cylinder housing.

In an embodiment, one or more, potentially all, valve tubes are positioned closer to the center of the crankpin and/or the axis of rotation about which the crankpin rotates than to the outermost portion of the cylinder and/or cylinder housing.

In an embodiment, one or more of the valve tube(s) is straight and/or substantially between the immediately following and/or immediately preceding the cylinder and/or the outer side wall of the cylinder housing Extend straight.

In an embodiment, one or more pistons have different diameters.

In this way, the compressor can be customized for a particular use case, since the piston and/or cylinder diameter can be selected for the compressor to deliver a desired pressure output from a given pressure input.

In an embodiment, for at least one cylinder, the cylinder housing, including the associated compression chamber, of a given cylinder is detachable and attachable from the compressor.

In this way, the compressor can be easily maintained and/or adapted to specific use cases, since the cylinder housing can be quickly exchanged or exchanged for a different cylinder housing with, for example, a compression chamber of a different diameter, in order for the compressor to provide the required pressure output.

The cylinder housing can be detached and attached to the cylinder base. The cylinder base may include linear seals, such as piston seals and/or rod seals, for sealing between the associated piston and cylinder. At least one, two, three, four, five, six or more of the cylinder bases may include a linear seal, such as a rod seal, for sealing between the associated piston and cylinder. The height to which the rod seal extends in the radial direction of the compressor may be equal to or less than 1/2, 9/20, 2/5, 7/20, 3/10, 1/4, 1 of the stroke length of the associated piston /5, 3/20, 1/10, 1/20. The height of the rod seal may extend parallel to the length of the associated piston. Rod seals may alternatively be denoted shaft seals. One or more, potentially all, of the cylinder bases may be attached, potentially detachably attached, to the compressor housing.

When the compressor is stopped and/or in operation, one or more pistons may only contact, or substantially only contact, an associated linear seal, such as a rod seal. The associated linear seal may be incorporated in the base of the associated cylinder and/or constituted by the associated cylinder. When the compressor is stopped and/or in operation, the two or more pistons may only contact, or substantially only contact, associated linear seals contained in the cylinder base and/or constituted by the cylinder. When the compressor is stopped and/or in operation, all pistons may substantially only contact, or only contact, associated linear seals, such as rod seals. The associated linear seal is potentially incorporated in the cylinder base and/or constituted by the cylinder.

Experiments have shown that rod and/or shaft seals located in the cylinder housing perform better at higher pressures than seals located on the piston. This may be due to the fact that rod and/or shaft seals located in the cylinder housing have a greater available seal in both the radial and axial directions of the piston compared to seals such as piston rings located on the piston. space. This can provide greater choice in the size, material and/or shape of the seal. This may help to achieve reduced friction and/or improved sealing during operation of the compressor.

In an embodiment, the compression chambers of one or more cylinders have different diameters.

In this way, the compressor can be customized and/or configured for a particular use case, since the compression chamber diameter can be selected for the compressor to deliver a desired pressure output from a given pressure input.

Each compression chamber of more than two cylinders may have a different diameter. The diameter of the piston may correspond to the diameter of the corresponding compression chamber.

In an embodiment, each sliding shoe is fastened to the crankpin by a separate associated annular retaining ring surrounding the circumference of the crankpin.

In this way, the engagement of the sliding shoe and the crank pin can be ensured, since the sliding shoe can be held on the crank pin. Furthermore, this can increase the freedom of choice in the design of the compressor (including cylinders, compression chambers, pistons, sliding shoes, etc.), because the retaining rings can be configured and designed independently.

The term "separately" may be understood as not forming part of another component, ie being a distinct part itself.

Additionally or alternatively, the retaining ring may surround the circumference of a retaining ring bearing mounted on the crank pin. The retaining ring may grip the circumference of the crank pin and/or the circumference of a retaining ring bearing mounted on the crank pin. The retaining ring may directly contact the circumference of the crankpin. The retaining ring may sit on a retaining ring bearing mounted on the crank pin. The retaining ring bearing may be a slide bearing or a roller bearing as described herein. A retaining ring may be secured to the crankpin between two bearings on the crankpin. Each or one or more of the sliding shoes may include a recess or opening for receiving a retaining ring. A recess or opening for receiving the retaining ring may be located in and/or extend through the sliding surface. A retaining ring may be attached in the opening of the associated sliding shoe. The retaining ring may extend through the opening of the associated sliding shoe. The retaining ring is detachable from the associated sliding shoe. The retaining ring may be connected to the associated sliding shoe via one or more bolts, screws, clamps, pins and/or snap rings. The retaining ring may be rigidly attached to the sliding shoe, ie such that relative movement of the associated retaining ring and sliding shoe is prevented. The retaining ring can comprise, consist of and/or be covered with the same material as the crank pin and/or the sliding shoe. Each sliding shoe may include threaded holes for receiving bolts or screws to secure the associated retaining ring to the sliding shoe. Each retaining ring may include through holes for receiving bolts or screws. Each retaining ring may include threaded through holes for receiving bolts or screws. The retaining ring may comprise, consist of and/or be coated with a slider bearing material such as metal, metal alloy or polymer such as brass, steel, aluminum or aluminum alloys, bronze, PTFE and/or combinations thereof. Additionally or alternatively, the retaining ring bearing may be two or more retaining ring bearings. The retainer ring bearing(s) may be separate from the one or more crankpin bearings. The retaining ring bearing(s) may be located between two bearings mounted on the crankpin (ie crankpin bearings). The retainer ring bearing(s) may have a smaller outer diameter than the crankpin bearing(s). The retaining rings may abut each other. In this way, the compressor can be made more compact. By making the retaining rings out of bearing material, the friction between the retaining rings can be reduced, thereby increasing the efficiency of the compressor. Furthermore, the retaining rings abutting against each other can ensure that the retaining rings cannot move axially on the retaining ring bearing(s) and/or the crank pin and can further increase the stability of the piston movement. These retaining rings may be positioned between two crankpin bearings, abutting the two bearings. In other words, the retaining ring can be sandwiched between two crank bearings. This can help to further ensure that the retaining ring does not move axially on the crankpin and/or retaining ring bearing(s) and further improve the stability of the piston movement. The use of an axial-radial bearing as the crankpin bearing reduces the friction of movement of the retaining ring sandwiched between the crankpin bearings.

In a development of the previous embodiment, the retaining ring is positioned on a bearing mounted on the crankpin.

In this way, energy lost to friction between moving parts can be reduced since the bearings can reduce friction between the retaining ring and the crankpin.

In an embodiment, the retaining ring(s) surrounds the circumference of the retaining ring bearing mounted on the crankpin.

In an embodiment, the retaining ring clamps the circumference of the retaining ring bearing.

In an embodiment, the retaining ring is fastened to the crankpin between two bearings mounted on the crankpin.

In an embodiment, one or more of the sliding shoes includes a recess or opening for receiving the retaining ring.

In a modification of the previous embodiment, the recess or opening for receiving the retaining ring is located in the sliding surface of the one or more sliding shoes and/or extends through the sliding surface to engage the crank pin and/or the crank pin Bearing engaged.

In an embodiment, the compressor is configured such that, in operation and/or at rest, at least one or each piston does not substantially contact the inner wall of the associated compression chamber.

In an embodiment, the compressor is configured such that in operation at least one or each piston moves only or substantially only in a radial direction of the compressor.

In an embodiment, the at least one guide groove and/or the at least one guide element attached to the piston is configured such that in operation the associated piston does not contact the inner wall of the associated compression chamber, and/or such that in operation , the piston moves only or substantially only in the radial direction of the compressor.

In an embodiment, the first cylinder includes one or more associated rod seals for sealing on an associated piston of the first cylinder.

In an embodiment, the cylinder base of the first cylinder includes an associated rod seal for sealing between the first cylinder and its associated piston.

In an embodiment, the rod seal has a height extending in the radial direction of the compressor that is equal to or less than 1/2 the stroke length of the associated piston.

In an embodiment, the associated piston of the first cylinder substantially only contacts the associated rod seal of the first cylinder when the compressor is stopped and/or in operation.

In an embodiment, the piston does not include any seals, such as piston rings or piston seals, that might be attached to and/or mounted on the piston.

In an embodiment, the outer diameter of the crankpin and/or the crankpin bearing(s) provided on the crankpin is at least 1.1 times the minimum and/or maximum stroke length of each piston.

In an embodiment, the length of the lever arm acting on the axis of rotation about which the crankpin rotates is equal to or less than 200% of the minimum and/or maximum stroke length of each piston.

In an embodiment, the compressor comprises a rotatable crankshaft comprising at least two interconnected separate shafts extending parallel to the crank pin, wherein the crank pin is clamped to the at least two by a detachable clamping mechanism. A corresponding end of each of the interconnected shafts is used to interconnect the two shafts.

In this way, the compressor can be easily disassembled since the crankpin and the crankshaft can be disassembled from each other. This can improve serviceability. Furthermore, this may allow the compressor to be adapted to different usage situations by interchanging components.

In an additional or alternative embodiment, at least one sliding shoe is rotatably attached to the associated piston via a connecting shaft extending through the sliding shoe and the associated piston, wherein the at least one guide groove is configured to The guided at least one guide element is attached to the connection shaft.

In this way, the drive and movement of the piston can be guided and secured by at least one guide element in at least one guide groove.

The maximum size of the compressor can be equal to or less than 5m, 4.5m, 4m, 3.5m, 3m, 2.5m, 2m, 1.9m, 1.8m, 1.7m, 1.6m, 1.5m, 1.4m, 1.3m , 1.2m, 1.1m, 1m, 0.9m, 0.8m, 0.7m, 0.6m, 0.5m, 0.4m, 0.3m, 0.2m, or 0.1m. The maximum dimension may be the maximum dimension of the compressor extending in the radial direction of the compressor or in the axial direction of the compressor.

A second aspect of the invention relates to a method for compressing a fluid in a multi-stage compressor comprising:

two or more cylinders, each cylinder having a compression chamber and a piston such that the fluid in each compression chamber is compressed by the associated piston;

The cylinders are connected in series such that fluid entering the inlet of the compressor is compressed to a first pressure in the compression chamber of the first cylinder and then enters the compression chamber of the second cylinder where the compressed fluid is compressed to the first pressure. two higher pressures; and

Each of these pistons is driven by the same crankpin of the compressor.

If there are more than two cylinders, fluid successively enters the compression chamber(s) of the additional cylinder(s) and is compressed to successively higher pressures before exiting from the outlet of the compressor.

In an embodiment, the multistage compressor further comprises at least one supply compressor for supplying compressed fluid at a pressure above atmospheric pressure to the compression chamber of the first cylinder, wherein the supply compressor and the piston are connected to the piston of the multistage compressor Driven by the same crankshaft, potentially the same crankpin.

In a third aspect, the invention relates to a system for compressing a fluid comprising:

- a multi-stage compressor according to the first aspect of the invention; and

- A second compressor configured to provide fluid at a pressure above atmospheric pressure to the inlet of the multi-stage compressor and/or the compression chamber of the first cylinder.

In an embodiment, the second compressor is a static or stationary compressor.

A static or stationary compressor may be understood as a compressor that is placed and/or mounted and/or fixed to a certain location and has to be dismantled and/or dismounted in order to move from said location. The second compressor may be a compressor supplying a compressed air system and/or an air line and/or air line system such as may be used in workshops, factories and/or industrial plants.

In an embodiment, the second compressor is formed by and/or is part of a multi-stage compressor.

In an embodiment, the system further comprises one or more components selected from: a gas filter and/or a fluid filter and/or a cooling device and/or a cooling fluid tank and/or a power supply and/or a generator, and /or a drive unit for driving the multi-stage compressor, and/or a compressed fluid tank, wherein, in given cases, the multi-stage compressor is connected to a fluid tank for supplying compressed fluid to the compressed fluid tank.

The compressed fluid tank may be a compressed liquid tank or a compressed gas tank, such as an air tank. The gas filter can be a carbon filter (clean air).

The cooling device may be a cryogenic cooling device (also referred to as a cryogenic cooler). The electrical generator may be used to provide power to a given application, such as a drive unit for driving a multi-stage compressor, and/or other external applications. The generator may be powered by sustainable energy sources such as solar, wind, hydro and/or surplus energy, etc. This can contribute to sustainability and reduction of CO2 emissions (CO2 neutralization) especially when the generator is driven by energy from the aforementioned sources. The system may also optionally include a container in which to place one or more components of the system. In one embodiment, the generator is a compressed air driven generator. The generator may be driven by compressed air from a tank of compressed air supplied by the multi-stage compressor, and/or directly from the multi-stage compressor.

In an embodiment, the multi-stage compressor is a portable compressor. In an embodiment, the second compressor is a multi-stage compressor according to the first aspect of the invention.

In an embodiment, the second compressor is a supply compressor for supplying compressed fluid at a pressure above atmospheric pressure to the compression chamber of the first cylinder, wherein the supply compressor and the pistons are driven by the same crankshaft as the pistons of the multi-stage compressor , potentially the same crankpin drive.

In an embodiment, the multi-stage compressor and the second compressor are powered by the same drive unit.

A crankshaft of the multi-stage compressor and a crankshaft of the second compressor may be coupled together to transmit driving force between the compressors. Two, three, four, five or more compressors can be powered by the same drive unit. The crankshafts of two, three, four, five or more compressors can be coupled together. Additionally or alternatively, the multi-stage compressor and the second, third, fourth, fifth or more compressors may share a common crankshaft. Two, three, four, five or more compressors according to the invention can be connected in series or in parallel. An additional compressor (potentially a multi-stage compressor according to the first aspect of the invention) may be connected to each compressor connected in parallel, or to the first of compressors connected in series. A single additional compressor may provide fluid at a pressure above atmospheric pressure to the inlet of the associated compressor(s).

In a fourth aspect, the invention relates to the use of a multi-stage compressor according to the first aspect of the invention and/or a system according to the third aspect of the invention for energy storage.

In an embodiment, the energy storage is a compressed fluid energy storage.

The fluid may be air, water, fossil fuels, such as fossil fuel gases, and/or liquids. Compressors can be used to fill compressed air tanks with compressed air for inflating tires, powering air rifles, filling gas tanks (such as oxygen or other gas tanks), powering generators to generate electricity, powering machinery Providing power, powering air motors such as in vehicles, workshops, factories, industrial plants, etc. Additionally or alternatively, a compressor may be used to provide compressed fluid, such as water, for industrial applications, such as cutting different materials with compressed fluid, powering generators to generate electricity, driving machinery.

In an embodiment, the invention relates to the use of a multi-stage compressor according to the first aspect of the invention and/or a system according to the third aspect of the invention for storing compressed fluid to drive an electrical generator.

In an embodiment, the invention relates to the use of a multi-stage compressor according to the first aspect of the invention and/or a system according to the third aspect of the invention for compressed gas storage, potentially compressed air storage.

In an embodiment, the invention relates to the use of a multi-stage compressor according to the first aspect of the invention and/or a system according to the third aspect of the invention for compressing a fluid.

In an embodiment, the invention relates to the use of a multi-stage compressor according to the first aspect of the invention, wherein the multi-stage compressor is connected to a second compressor.

In one embodiment, the second compressor provides fluid at a pressure above atmospheric pressure to the inlet of the multi-stage compressor.

In one embodiment, the second compressor is a static or stationary compressor installation.

In a development of the previous embodiment, static or stationary compressor implementations are installed in gas stations, workshops, garages or buildings.

In an embodiment, the invention relates to the use of a multi-stage compressor according to the first aspect of the invention and/or a system according to the third aspect of the invention for charging an air driven gun, rifle, bow or the like.

In an embodiment, the invention relates to a multi-stage compressor according to the first aspect of the invention and/or a system according to the third aspect of the invention for energizing hydraulic or pneumatic dampers, springs, suspension systems etc. the use of.

In an embodiment, the invention relates to a multi-stage compressor according to the first aspect of the invention and/or a system according to the third aspect of the invention for filling fluid tanks or air tanks, tyres, inflatables, inflatable devices and other uses.

Those skilled in the art will appreciate that any one or more of the above aspects and embodiments of the present disclosure may be combined with any one or more of the other aspects and embodiments thereof.

In the following, non-limiting exemplary embodiments will be described in more detail with reference to the accompanying drawings, in which:

Figure 1 shows a perspective view of the front side of an assembled multi-stage compressor,

Figure 2 shows a perspective view of the rear side of the compressor of Figure 1,

Figure 3 shows a side view of the compressor of Figure 2,

Figure 4 shows a sectional view along the line A-A of the compressor of Figure 3,

Figure 5 shows a partially exploded view of the compressor of Figure 1,

Figure 6 shows an enlarged detailed view of the crankpin, piston and sliding shoe assembly of the compressor of Figure 5, and

Figure 7 shows an exploded view of the crankpin and piston assembly seen in Figure 6,

Figure 8 shows a multi-stage compressor with an alternative embodiment of cooling tubes and cooling jackets,

Figure 9 shows an embodiment of a multi-stage compressor comprising a supply compressor,

Figure 10 shows a section through the multi-stage compressor of Figure 10 corresponding to the section shown in Figure 4,

Figure 11 shows a close-up cross-section of the supply compressor of Figure 10,

Figure 12 shows an alternative piston movement guide,

Figure 13 shows a second alternative piston movement guide, and

Figure 14 shows a third alternative piston movement guide.

Starting with FIG. 1 , a multistage compressor 1 according to the invention is shown seen from the front. The compressor 1 comprises three cylinders 2 a , 2 b , 2 c each having a cylinder housing 22 . These cylinders are interconnected by a valve tube 7 which in this embodiment has a cooling jacket 71 for cooling the valve tube 7 attached thereto. A cooling line 26 for cooling the cylinders 2 a , 2 b , 2 c runs parallel to the valve line 7 . Cooling ducts 26 connect cooling passages (not shown) in the cylinder housing 22 to allow a flow of cooling medium for cooling the cylinders 2a, 2b, 2c to flow through the compressor 1 . The compressor 1 further comprises an inlet 12 for fluid entering the first cylinder of the compressor 1 and an outlet 13 for leaving the last cylinder of the compressor 1 . The fluid supplied to the inlet 12 of the compressor 1 may be pressurized or pre-compressed, so that the fluid compressed in the first cylinder 2a is already pressurized before being compressed in this cylinder. For example, the fluid supplied to the inlet may be pressurized to 8 bar as in this example. The compressor further has a crankshaft 6 comprising two interconnected individual shafts 61 . One of the shafts 61 is configured to be connected to a drive unit for driving the compressor 61 (i.e. to rotate the crank pin 5), and the other shaft 61 exiting from the rear side of the compressor is optionally configured to be connected to a second compressor and drives the second compressor.

Turning to FIG. 2 , where the compressor 1 is viewed from the rear side, it is seen that the guide element 33 for guiding the movement of the piston 3 is guided in the guide groove 15 . As can be seen in FIGS. 1 and 2 , most of the components of the compressor 1 , such as the compressor housing 11 , the cylinder housing 22 , the inlet 12 , the outlet 13 and the shielding plate 17 , are interconnected to each other via bolts 16 . This allows easy assembly/disassembly as well as maintenance and exchange of components for different use cases. In FIG. 3 , the compressor 1 is seen from the side, where it can be seen that the two interconnected shafts 61 of the crankshaft 6 are concentric and extend an equal length from the compressor housing 11 .

Turning to FIG. 4 , there is shown a cross-sectional view of the compressor 1 along line A-A of FIG. 3 , where the sliding shoes have been removed. Here, the compression chambers 21 and the associated cylindrical pistons 3 in the cylinders 2a, 2b, 2c can be seen. The cylinders 2a, 2b, 2c are positioned around the axis of rotation RA and extend in a radial direction away from the axis of rotation RA. The compression chambers 21 located inside the cylinders have different diameters and the associated piston 3 has a corresponding diameter, ie the diameter of the piston 3 corresponds to the diameter of the associated compression chamber 21 . In this way, the compressor 1 is tailored to deliver fluid at a given input pressure into the inlet 12 of FIG. 1 out of the outlet 13 of FIG. 1 at a certain output pressure.

When the crankshaft 6 is driven and thereby rotated, the crankpin 5 rotates about the axis of rotation RA, whereby the piston 3 is driven into and out of an associated compression chamber 21 to compress the fluid therein. As seen more clearly in FIG. 6 , the drive in and out of the piston 3 is through the sliding shoe 4 with the crankpin bearing 51 mounted on the crankpin 5 and the retaining ring 42 around the circumference of the retaining ring bearing 44 on the crankpin 5 joined to achieve. As the crankpin 5 then rotates about the axis of rotation RA according to its relative position to the piston, the crankpin pushes the piston 3 into the relevant compression through the sliding shoe 4 (which engages the crankpin bearing 51 and is connected to the piston 3 via the connecting shaft 43). chamber, or by a separate retaining ring 42 (which is attached to the associated sliding shoe 4 and is fastened to the crankpin 5 by surrounding the circumference of the crankpin 5 and a retaining ring bearing 44 mounted on the crankpin 5). 3 Pull out the associated compression chamber 21. It can also be seen how the compression chamber 21 of a cylinder 2 a , 2 b , 2 c is connected to the compression chamber of the immediately following cylinder via a non-return valve 72 . The respective chambers are connected by a non-return valve 72 to prevent fluid flow from the compression chamber 21 of a given cylinder 2a, 2b, 2c to the compression chamber of the cylinder immediately preceding it. In the illustrated embodiment, the check valves 72 are located in cylindrical valve tubes 7 comprising tube volumes for fluid to flow through both sides of the check valves 72 . Thus, in the embodiment shown, fluid can enter the compression chamber 21 of the first cylinder 2 a (where it is compressed by the associated piston 3 ), then flow through the flow channel 28 and through the stop in the valve tube 7 . The return valve 72 thus enters the compression chamber 21 of the second cylinder 2b (where the fluid is further compressed by the associated piston 3 ) and flows through the next flow channel 28 and the check valve 72 in the valve tube 7 to enter the compression Chamber 21 is in the third cylinder 2c (where the fluid is further compressed by the associated piston 3 ) and flows through the outlet 13 of the compressor 1 . The spherical inlet end 73 and outlet end 74 of the valve tube each comprise a sealing element and are press fit into the cylinder housing 22 of the cylinder 2a, 2b, 2c.

The compressor and its components are configured such that in operation the piston 3 moves substantially only in the radial direction of the compressor 1 and in the axial direction of the corresponding piston 3 in the compression chamber 21 .

In FIG. 4 it can also be seen that a separate annular retaining ring 42 surrounds the circumference of a retaining ring bearing 44 mounted on the crank pin 5 . The retaining ring 42 is attached to the associated sliding shoe 4 via bolts 16 which extend through the sliding shoe 4 (best seen in FIG. 7 ) and into bolt holes 45 of the associated retaining ring 42 . For demonstration purposes, the axis of rotation RA is shown in Figures 4 and 6, where it can be seen that the crankpin 5 is positioned such that the distance from the periphery of the crankpin 5 to the axis of rotation RA is 0.3 crankpin radius. Furthermore, it can be seen that the cylinders 2a, 2b, 2c comprise rod seals 24 for sealing on their associated pistons. When the compressor is stopped and in operation, the associated piston 3 of each cylinder 2a, 2b, 2c substantially only contacts the associated rod seal 24 of each cylinder. The piston 3 also does not include any seals, such as piston rings or piston seals attached to and/or mounted on the piston 3 .

Turning to FIG. 5 , which shows a partially exploded view of the compressor 1 , the manner in which the compressor 1 can be assembled and disassembled and how components can be swapped or replaced becomes clear. The valve tube 7 comprises a first valve tube part 7a and a second valve tube part 7b, which are detachable from each other as shown. The valve tube parts 7a, 7b are attached to each other via threads where a check valve 72 is seated and screwed into the first valve tube part 7a. A crankshaft bearing 62 for supporting the crankshaft 6 in the compressor housing 11 is considered to be positioned on the shaft 61 of the crankshaft 6 . It can also be seen that the cylinder housing 22 including the associated compression chamber 21 of a given cylinder 2 a , 2 b , 2 c is detachable and attachable from the compressor 1 , more particularly the cylinder base 27 .

Figure 6 shows an enlarged detail view of the crankpin, piston and sliding shoe assembly of the compressor. Each sliding shoe 4 is rotatably attached to the associated piston 3 via a connecting shaft 43 extending through the bottom end of the associated piston 3 and both parts of the associated sliding shoe 4 . Each piston 3 comprises a slider bearing 46 positioned in the bottom end of the piston 3 for supporting the associated connecting shaft. Each piston 3 has a length "L" extending in a radial direction from the top surface of the piston top end to the bottom surface of the bottom end. The sliding shoe 4 is made of bronze, whereby the sliding shoe 4 itself can constitute a sliding body bearing for supporting the associated connecting shaft 46 . The connecting shaft 43 extends in the axial direction and is fastened to the associated piston 3 and sliding shoe 4 by two snap springs 45 located at opposite ends of the connecting shaft 43 in the axial direction. Two guide elements 33 are also attached to opposite ends of the connecting shaft 43 in the axial direction and are fastened to the connecting shaft by means of snap springs 45 . The distance D from the center axis CA ( FIG. 6 ) of the crankpin 5 to the axis of rotation RA is about 1 crankpin radius. Mounted on the crank pin 5 are two crank pin bearings 51 which engage the sliding shoes 4 .

As best seen in FIG. 7 , the sliding shoe 4 includes a sliding surface 41 shaped to form fit with the crankpin bearing 51 for engagement with the crankpin bearing 51 . The sliding surface 41 further has openings 47 for receiving retaining rings 42 fastened therein by bolts 16 extending through the associated sliding shoes 4 and into bolt holes 48 .

FIG. 8 shows an alternative embodiment of cooling tube 26 and cooling jacket 71 . In this embodiment, some cooling pipes 26 connected to the cooling passages (not shown) in the cylinders 2a, 2b, 2c are connected with the cooling jacket 71 and enter into the cooling jacket 71, so that the valve pipe 7 and the fluid therein can be cooled. In this way, the cooling jacket 71 forms part of the cooling circuit of the cylinders 2a, 2b, 2c, wherein both the valve tubes and the cylinders 2a, 2b, 2c can be cooled.

In the illustrated embodiment, the compressor housing 11 , the cylinder housing 22 , the valve tube 7 , the cooling jacket 71 , the cooling tube 26 and the shroud 17 are made of aluminum. Cylinder base 27, connecting shaft 43, crank pin 5, crankshaft 6, clamping mechanism 63 are made of steel, wherein piston 3 is made of steel with aluminum core. The sliding shoe 4 is made of bronze, wherein the retaining ring 42 and the guide element 45 are made of a combination of bronze and steel.

Turning now to FIGS. 9 and 10 , there is shown an embodiment of a multi-stage compressor 1 further comprising three supply compressors 8 for supplying compressed fluid at a pressure above atmospheric pressure to the first stage via inlet 12 . Compression chamber 21 of a cylinder 2a. Identical or similar components have been given the same reference numerals as in FIGS. 1 to 8 . The supply compressor 8 (located within the periphery of the multi-stage compressor 1 ) and the piston 3 are driven by the same crankshaft 6 and crankpin 5 . As the crank pin 5 rotates it drives the supply compressor arm 81 which in turn actuates the spring loaded piston assembly 82 inside the supply compressor 8 where fluid is compressed to about 8 bar and exits the outlet 83 through the corresponding supply compressor A pipe (not shown) enters the inlet of the compressor 1 and the compression chamber 21 of the first cylinder 2a. The multi-stage compressor 1 then compresses the fluid as described above. A supply compressor 8 positioned circumferentially around the crankshaft 6 and crankpin 5 and partly within the multi-stage compressor housing 2 operates in parallel. Additionally or alternatively, one or more supply compressors 8 may be positioned outside the multi-stage compressor housing 2 , circumferentially around the same crankshaft 6 , 61 extending outwardly from the compressor housing 2 . Each of the one or more supply compressors may here potentially be driven by the same second crankpin. FIG. 11 shows an enlarged section through the supply compressor 8 .

In the example shown in FIGS. 1 to 11 , the movement of the piston 3 is guided by the guide groove 15 and the guide element 3 attached to the piston 4 and is configured such that in operation and at rest the associated piston 3 does not touch is associated with the inner wall of the compression chamber 21 and is such that in operation the piston 3 moves only or substantially only in the radial direction of the compressor 1 . However, the movement of the piston 3 can be directed in other ways, as shown for example in FIGS. 12-14 .

Figure 12 shows the piston 3 and the guide element 33 comprising two linear bearings 9 in the form of sliding bushes, each sliding along a journal 91 in the form of a shaft. The journal 91 can be attached in or on the multi-stage compressor housing 2 .

Additionally or alternatively, the multi-stage compressor 1 may comprise a plurality of bush guide rods 92 per piston 3 , in this case three, as seen in FIG. 13 , configured to guide Associated piston 3 movement. A bushing guide rod 92 may be positioned and attached within the cylinder housing 22 and compression chamber 21 to form the innermost surface of the compression chamber 21 facing the associated piston 3 and potentially providing a surface for the piston 3 to slide on. The bush guide rod 92 extends parallel to the associated piston 3 and the direction of movement of the piston 3 .

Additionally or alternatively, as shown in FIG. 13 , the multistage compressor 1 may have a plurality of guide rollers 93 , six in the case shown, configured to guide the movement of the associated piston 3 . Guide rollers 93 are positioned and attached in the multi-stage compressor housing 2 and the cylinder housing 2 such that they can rollingly guide the movement of the associated piston 3 . The guide rollers 93 are positioned along the axial direction of the associated piston 3 and around the circumference of the associated piston 3 .

The multi-stage compressor may further form part of a system comprising gas filters, fluid filters, cooling means (such as cryocoolers), cooling fluid tank, power supply, generator, drive unit for driving the multi-stage compressor . A compressed fluid tank, wherein, in given cases, a multi-stage compressor is connected to the compressed fluid tank to supply compressed fluid to the compressed fluid tank. The generator can provide power to a given application, such as a drive unit for driving a multi-stage compressor, and other external applications. The generator may be powered by sustainable energy sources such as solar, wind, hydro and/or surplus energy, etc. The system may also include a container in which to place one or more components of the system. The generator may be, for example, a compressed air driven generator driven by compressed air from a compressed fluid or air tank supplied by the multistage compressor, and/or may be directly driven by the multistage compressor when power is required for other external applications .

list of reference signs

1 multi-stage compressor

11 Compressor housing

12 entrance

13 exits

14 cooling tube

15 guide groove

16 bolts

17 shutter

2a, 2b, 2c cylinder

21 Compression chamber

22 cylinder housing

24 rod seal

25 cooling channels

26 cooling tube

27 Cylinder base

28 flow channels

3 pistons

31 Piston tip

32 Piston Bottom

33 Guide element

4 sliding hoof

41 sliding surfaces

42 retaining ring

43 connecting shaft

44 retaining ring bearing

45 circlip

46 bearings

47 openings

48 bolt holes

5 crankpin

51 Crank pin bearing

6 crankshaft

61 individual axes

62 crankshaft bearing

63 clamping mechanism

7 valve tube

7a First valve tube part

7b Second valve pipe part

71 cooling jacket

72 check valve

73 Valve Tube Inlet Port

74 Valve Tube Outlet Port

8 supply compressor

81 Supply the actuator arm for the compressor

82 Piston assembly for supply compressor

83 outlet for supply compressor

9 Linear bearings

91 Journal

92 Bushing Guide Rod

93 Guide rollers

RA axis of rotation

CA Central axis of the crankpin

D Distance from crank pin to axis of rotation

d Piston diameter

L Piston length

Claims (55)

1. A multi-stage compressor for compressing fluid, the compressor comprising: two or more cylinders, each cylinder having a compression chamber and a piston such that fluid in each of these compression chambers can be compressed by the associated piston; The cylinders are connected in series so that fluid entering the inlet of the compressor can be compressed to a first pressure in the compression chamber of the first cylinder and then enter the compression chamber of the second cylinder, where , the compressed fluid is compressed to a second higher pressure before the fluid exits the compressor outlet; Where each piston is driven by the same crankpin of the compressor. 2. The multi-stage compressor of claim 1, further comprising at least one supply compressor for supplying compressed fluid at a pressure above atmospheric pressure to the compression chamber of the first cylinder, wherein the supply compressor and the piston The pistons of the multi-stage compressor are driven by the same crankshaft. 3. The multi-stage compressor of claim 2, wherein the pistons of the at least one supply compressor and the multi-stage compressor are driven by the same crankpin. 4. A multi-stage compressor as claimed in any one of the preceding claims, wherein a separate independent sliding shoe for engaging the crank pin is attached to the bottom end of each piston. 5. The multi-stage compressor of claim 4, wherein each sliding shoe is rotatably attached to the bottom end of the associated piston. 6. The multi-stage compressor according to any one of the preceding claims, wherein the casing of the multi-stage compressor comprises at least one guide groove configured for guiding at least one piston attached to the piston. Movement of a guiding element. 7. A multi-stage compressor according to any one of the preceding claims, wherein the multi-stage compressor comprises one or more linear bearings configured to guide the pistons of the multi-stage compressor Movement of the associated piston and/or at least one guide element attached to the associated piston. 8. A multi-stage compressor according to any one of the preceding claims, wherein the compression chamber of at least a first cylinder of the two or more cylinders is connected to the compression chamber of a second cylinder by at least one non-return valve , to prevent fluid from the compression chamber of the second cylinder from flowing to the compression chamber of the first cylinder. 9. The multi-stage compressor of claim 8, wherein the at least one check valve is located externally of the two or more cylinders, within a valve duct, such that flow from the compression chamber of the at least first cylinder to the second The fluid of the compression chamber of the two cylinders flows through the valve pipe and the at least one check valve. 10. The multi-stage compressor of claim 9, wherein the valve tube is removably attached between two cylinders. 11. A multi-stage compressor according to claim 9 or 10, wherein at least one compression chamber comprises the first tube volume of the valve tube. 12. A multi-stage compressor as claimed in any one of claims 9 to 11 wherein the valve duct extends between a given cylinder and the immediately following cylinder. 13. A multi-stage compressor according to any one of claims 9 to 12, wherein the valve duct is arranged between each compression chamber and the cylinder immediately following and/or the cylinder immediately preceding it. between rooms. 14. A multi-stage compressor according to any one of claims 9 to 13, wherein one or more, potentially all, valve tubes are substantially straight. 15. A multi-stage compressor according to any one of claims 9 to 14, wherein one or more, potentially all valve ducts are located at the outer perimeter of the compressor and/or cylinder and/or cylinder housing Inside. 16. A multi-stage compressor as claimed in any one of claims 9 to 15, wherein one or more, potentially all valve tubes are positioned off the center of the crankpin and/or around the crankpin The rotational axis of rotation is closer than the cylinder and/or cylinder housing or the outermost part of said cylinder and/or cylinder housing. 17. A multi-stage compressor as claimed in any one of claims 9 to 16, wherein one or more of the valve ducts is in the immediately following and/or immediately preceding cylinder and/or The outer side walls of the cylinder housing extend straight and/or substantially straight between them. 18. A multi-stage compressor according to any one of the preceding claims, wherein, for at least one cylinder, a given cylinder's cylinder housing, including the associated compression chamber, is detachable and attachable to the compressor. 19. A multi-stage compressor according to any one of claims 4 to 18, wherein each sliding shoe is secured to the crankpin by a separate associated annular retaining ring surrounding the crankpin circumference. 20. The multi-stage compressor of claim 19, wherein said retaining ring surrounds the circumference of a retaining ring bearing mounted on the crankpin. 21. A multi-stage compressor according to claim 19 or 20, wherein the retaining ring clamps the circumference of the retaining ring bearing. 22. A multi-stage compressor as claimed in any one of claims 19 to 21, wherein the retaining ring is secured to the crankpin between two bearings mounted on the crankpin. 23. A multi-stage compressor as claimed in claim 4 and any one of claims 2 or 3 or claims 5 to 22, wherein one or more sliding shoes include recesses or openings for receiving retaining rings. 24. The multi-stage compressor of claim 23, wherein the recess or opening for receiving a retaining ring is located in and/or extends through the sliding surface of the one or more sliding shoes to Engage with the crankpin and/or with the crankpin bearing. 25. A multi-stage compressor according to any one of the preceding claims, wherein the compressor is configured such that, in operation and/or at rest, at least one or each piston is substantially free of associated compression inner wall of the chamber. 26. A multi-stage compressor according to any one of the preceding claims, wherein the compressor is arranged such that in operation at least one or each piston is only or substantially only in the radial direction of the compressor direction to move. 27. The multi-stage compressor according to claim 6 and any one of claims 7 to 26, wherein the at least one guide groove and/or the at least one guide element attached to the piston is configured such that in In operation, the associated piston does not contact the inner wall of the associated compression chamber, and/or is such that, in operation, the piston moves only or substantially only in the radial direction of the compressor. 28. A multi-stage compressor according to any one of the preceding claims, wherein the first cylinder includes one or more associated rod seals for sealing on an associated piston of the first cylinder. 29. The multi-stage compressor of claim 28, wherein the cylinder base of the first cylinder includes an associated rod seal for sealing between the first cylinder and its associated piston. 30. A multi-stage compressor according to claim 28 or 29, wherein the rod seal has a height extending in the radial direction of the compressor equal to or less than 1/ of the stroke length of the associated piston 2. 31. A multi-stage compressor according to any one of claims 28 to 30, wherein, when the compressor is stopped and/or in operation, the associated piston of the first cylinder substantially only contacts the first Associated rod seals for cylinders. 32. A multi-stage compressor according to any one of the preceding claims, wherein the pistons do not include any seals, such as piston rings or piston seals, potentially attached to and/or mounted on the pistons. 33. A multi-stage compressor according to any one of the preceding claims, wherein the outer diameter of the crankpin and/or a crankpin bearing provided on the crankpin is the minimum sum of each of the pistons /or at least 1.1 times the maximum stroke length. 34. A multi-stage compressor according to any one of the preceding claims, wherein the length of the lever arm acting on the axis of rotation about which the crankpin rotates is equal to or less than the minimum and/or or 200% of the maximum stroke length. 35. A method for compressing a fluid in a multi-stage compressor comprising two or more cylinders each having a compression chamber and a piston such that each of the compression chambers The fluid in is compressed by the associated piston, Wherein, these cylinders are connected in series, so that the fluid entering the inlet of the compressor is compressed to a first pressure in the compression chamber of the first cylinder, and then enters the compression chamber of the second cylinder, and the fluid is compressed in the compression chamber of the second cylinder chamber, the compressed fluid is compressed to a second higher pressure, and Where each piston is driven by the same crankpin of the compressor. 36. The method of claim 35, wherein the multi-stage compressor further comprises at least one supply compressor for supplying compressed fluid at a pressure above atmospheric pressure to the compression chamber of the first cylinder, wherein the supply The compressor and pistons are driven by the same crankshaft, potentially the same crankpin, as the multi-stage compressor's pistons. 37. A system for compressing a fluid, the system comprising: - a multi-stage compressor according to any one of claims 1 to 34; and - A second compressor configured to provide fluid at a pressure above atmospheric pressure to the inlet of the multi-stage compressor and/or the compression chamber of the first cylinder. 38. The system of claim 37, wherein the second compressor is a static or stationary compressor. 39. The system of claim 38, wherein the second compressor consists of and/or is part of the multi-stage compressor. 40. The system according to any one of claims 37 to 39, further comprising: one or more components selected from the following list: gas filter and/or fluid filter and/or cooling device and/or cooling a fluid tank and/or a power supply and/or a generator, and/or a drive unit for driving the multistage compressor, and/or a compressed fluid tank, wherein, in a given case, the multistage compressor is connected to A fluid tank to supply compressed fluid to the compressed fluid tank. 41. A system according to claim 37 or 40, wherein the second compressor is a multi-stage compressor according to any one of claims 1-34. 42. The system of any one of claims 37 to 40, wherein the second compressor is a supply compressor for supplying compressed fluid at a pressure above atmospheric pressure to the compression chamber of the first cylinder, wherein , the supply compressor and pistons are driven by the same crankshaft, potentially the same crankpin, as the pistons of the multi-stage compressor. 43. The system of any one of claims 37 to 42, wherein the multi-stage compressor and the second compressor are powered by the same drive unit. 44. Use of a multi-stage compressor according to any one of claims 1 to 34 and/or a system according to any one of claims 37 to 43 for energy storage. 45. Use according to claim 44, wherein the energy storage is a compressed fluid energy storage. 46. Use of a multi-stage compressor according to any one of claims 1 to 34 and/or a system according to any one of claims 37 to 43 for storing compressed fluid to drive an electrical generator. 47. Use of a multi-stage compressor according to any one of claims 1 to 34 and/or a system according to any one of claims 37 to 43 for compressed gas storage, potentially compressed air storage. 48. Use of a multi-stage compressor according to any one of claims 1 to 34 and/or a system according to any one of claims 37 to 43 for compressing a fluid. 49. Use of a multi-stage compressor according to any one of claims 1 to 34, wherein the multi-stage compressor is connected to a second compressor. 50. The use of claim 49, wherein the second compressor provides fluid at a pressure above atmospheric pressure to the inlet of the multi-stage compressor. 51. Use according to claim 49 or 50, wherein the second compressor is a static or stationary compressor installation. 52. Use according to claim 51 , wherein the static or stationary compressor installation is installed in a petrol station, workshop, garage or building. 53. A multi-stage compressor according to any one of claims 1 to 34 and/or a system according to any one of claims 37 to 43 for charging an air driven gun, rifle, bow etc. able use. 54. A multi-stage compressor according to any one of claims 1 to 34 and/or a system according to any one of claims 37 to 43 for use with hydraulic or pneumatic dampers, springs, suspension systems etc. for recharging purposes. 55. A multi-stage compressor according to any one of claims 1 to 34 and/or a system according to any one of claims 37 to 43 for filling fluid tanks or air tanks, tires, inflatables , inflatable devices, etc.

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