Piston compressor system

Abstract

The invention relates to a piston compressor system for compressing a gas, comprising a drive motor and a piston compressor (1), which comprises at least one cylinder (6), at least one piston (5), which is respectively supported in a respective cylinder (6) of a respective cylinder housing (8), such that a respective piston (5) and a respective cylinder (6) delimit a compression chamber (29) for compressing a gas, at least one mechanical device (40), with which the at least one piston (5) is in mechanical action connection for the reciprocating movement of the at least one piston (5), and at least one lubrication chamber (44), in which the at least one mechanical device (40) is at least partially arranged and with which the at least one mechanical device (40) can be lubricated with a lubricant, wherein the piston compressor (1) comprises at least one diaphragm (34) and fluidically separates a respective lubrication chamber (44) from a respective compression chamber (29) by means of the at least one diaphragm (34).

Description

Technical Field

[0001] The present invention relates to a reciprocating compressor system according to the preamble of claim 1. Background Technology

[0002] Piston compressors are used in various technical applications to compress gases. In a piston compressor, a piston performs a reciprocating motion. The piston is supported in a cylinder. An inlet valve is used to introduce gas into the compression chamber, and an outlet valve is used to discharge gas from the compression chamber. The compression chamber is defined by the surface of the cylinder head at the end opposite the piston. The inlet and outlet valves are usually integrated into the cylinder head. The reciprocating motion of the piston is achieved by a mechanical device. This mechanical device is constructed, for example, as a crank-driven mechanism with a crankshaft and connecting rod, or as a roller shoe with working rollers and a drive shaft with at least one cam. This mechanical device is arranged in a lubrication chamber. The lubrication chamber is loaded with a lubricant, such as lubricating oil, to lubricate the moving parts of the mechanical device. This mechanical device is driven, for example, by an electric motor. The piston performs a reciprocating motion between the top dead center (TDC) and bottom dead center (BDC) of the piston, and the volume difference of the compression chamber between the TDC and BDC defines the stroke volume. The clearance volume (Totvolumen) of the compression chamber is the volume of the compression chamber at the top dead center of the piston.

[0003] Certain technical applications involving compressed gases require the supply of compressed gases with high purity. The seal between the cylinder and the piston with piston rings is not a complete gap seal, allowing lubricant to enter the compression chamber of the reciprocating compressor from the lubrication chamber, thus contaminating the compressed gas. To prevent this undesirable and unavoidable contamination of the compressed gas, it is known to create an additional space between the compression chamber and / or the space with the piston and the lubrication chamber, and to provide, for example, a suction device for this space. However, this is disadvantageously very complex, resulting in high manufacturing costs and large structural space for the reciprocating compressor. Furthermore, diaphragm compressors are also known, but these have a small delivery volume per unit volume of structural space.

[0004] EP 0 541 482 B1 illustrates a reciprocating compressor for oil-free gas compression, having at least one cylinder and a piston guided therein, the piston having at least one slit, so-called trapping piston ring disposed in an annular groove on the piston, the piston ring defining a pressure-loaded space of the annular groove in the compression chamber by its outer peripheral surface opposite to the inner surface of the cylinder, and from the outer peripheral surface having two radially parallel limiting interfaces, wherein the face facing the compression chamber extends over a portion of the radial ring width, wherein the piston ring is slidably guided by its two parallel limiting interfaces on corresponding faces of the annular groove, wherein the remaining face of the piston ring facing the compression chamber, originating from the outer peripheral surface facing the inner surface of the cylinder, is configured as a wedge-shaped face, the wedge-shaped face extending to the limiting interface at an angle of 5° to 15° to a line parallel to the limiting interface facing the compression chamber.

[0005] DE 2020699 A1 discloses an immersion piston compressor having a single-stage or multi-stage piston and / or cylinder, wherein at least one bellows is generally arranged as at least one diaphragm between each piston and the crankcase. The bellows, secured to the rest of the immersion piston compressor by means of an intermediate piece, disadvantageously cannot ensure a completely sealed isolation between the crankcase and the compression chamber, and the assembly and disassembly of the bellows are inconvenient. Summary of the Invention

[0006] A reciprocating compressor system for compressing gases according to the invention includes a drive motor for the reciprocating compressor, the reciprocating compressor comprising at least one cylinder, at least one piston, at least one mechanical device, and at least one lubrication chamber. The at least one piston is supported in each of the cylinder housings, such that each piston and each cylinder define a compression chamber for compressing the gas. The at least one piston is mechanically operatively connected to the at least one mechanical device for reciprocating motion of the at least one piston. The at least one mechanical device is at least partially arranged in the at least one lubrication chamber and is lubricated in the at least one lubrication chamber by means of a lubricant. The reciprocating compressor of the reciprocating compressor system includes at least one diaphragm, which fluidly and tightly separates each lubrication chamber from each compression chamber by means of the at least one diaphragm. Advantageously, the fluid-sealed and tight isolation of each lubrication chamber from each compression chamber by means of the at least one diaphragm prevents contamination of the gas to be compressed in the compression chamber by the lubricating oil in the lubrication chamber.

[0007] In another embodiment, each diaphragm is divided, particularly radially, into an inner diaphragm space and an outer diaphragm space by a cylinder, a piston, and preferably a flange portion. The gas to be compressed escaping from the compression chamber at the gap seal between the piston guide and the piston thus reaches only the outer diaphragm space. Lubricating oil from the lubrication chamber at the sliding bearing of the piston rod thus reaches only the inner diaphragm space. Advantageously, this eliminates the possibility of lubricating oil being carried into the compression chamber, and additionally, the compressed gas in the outer diaphragm space can be vented to the surrounding environment or supplied again to the inlet valve for reuse of leaks at the gap seal between the piston and the piston guide on the cylinder. The cylinder portion space is preferably arranged between each piston and the lubrication chamber. The piston rod is arranged in the inner diaphragm space and is contaminated with lubricating oil. Due to the fixed fluid seals at the two axial ends of the diaphragm, the inner diaphragm space and the outer diaphragm space are fluid-sealed and tightly isolated.

[0008] In one supplementary embodiment, the reciprocating compressor system includes two sub-reciprocating compressors, each with one piston and one cylinder, forming a two-stage reciprocating compressor system. The outlet valve of the first sub-reciprocating compressor is connected to the inlet valve of the second sub-reciprocating compressor via a connecting pressure line. A reciprocating compressor system with two reciprocating compressors can achieve significantly higher compression pressures, such as 300 bar, than a reciprocating compressor system with only one sub-reciprocating compressor.

[0009] In another variation, a heat exchanger is installed or integrated into the connecting pressure line to cool the gas compressed by the first piston compressor, which is guided through the connecting pressure line. This prevents the compressed gas from reaching excessively high temperatures, such as less than 150°C, at the outlet valve and discharge passage of the second piston compressor, thus avoiding damage to the piston compressor system. The compressed gas is heated during compression at the first piston compressor and then cooled in the heat exchanger before being introduced into the second piston compressor, ensuring that excessively high temperatures do not occur in the compressed gas after it exits the second piston compressor.

[0010] In another configuration, the reciprocating compressor system includes a lubrication system having at least one lubricating oil line, a lubricating oil container, and a lubricating oil delivery device for lubricating the at least one mechanical device arranged in the lubrication chamber. Preferably, a heat exchanger is installed or integrated into the lubrication system for cooling the lubricating oil guided through the lubricating oil line. Thus, cooling the lubricating oil by means of the heat exchanger prevents the lubricating oil from neutralizing, thereby avoiding high temperatures in the lubrication chamber and the internal space of the diaphragm lubricated by the lubricating oil. The lubricating oil not only lubricates the lubrication chamber and the internal space of the diaphragm but also cools them.

[0011] Preferably, the reciprocating compressor system includes a container with the gas to be compressed and / or a container with the compressed gas.

[0012] In an additional variant, the reciprocating compressor system includes at least one pressure sensor, and more particularly multiple pressure sensors, for sensing pressure, particularly the pressure of gas, lubricating oil, and / or lubricating oil containers.

[0013] In a supplementary embodiment, the pressure of the gas in the suction line and / or pressure line and / or leak return line and / or connected pressure line and / or container with the gas to be compressed and / or container with the compressed gas can be sensed by means of the at least one pressure sensor.

[0014] In another configuration, the reciprocating compressor system includes at least one temperature sensor, and more particularly multiple temperature sensors, for sensing temperature, particularly the temperature of the gas, lubricating oil, and / or lubricating oil container.

[0015] To meet the destination, the temperature of the gas in the suction line and / or pressure line and / or leak return line and / or connecting pressure line and / or container with the gas to be compressed and / or container with the compressed gas can be sensed by means of the at least one temperature sensor.

[0016] In another variation, the reciprocating compressor system includes a control and / or regulation unit for controlling and / or regulating the reciprocating compressor system. This control and / or regulation unit is, for example, implemented as a computing unit or a computer.

[0017] In an additional embodiment, the pressure sensed by at least one pressure sensor and / or the temperature sensed by at least one temperature sensor can be transmitted to a control and / or regulation unit, and the reciprocating compressor system can be controlled and / or regulated based on the sensed pressure and / or temperature, particularly by issuing a fault message and / or performing automatic shutdown when the pressure and / or temperature exceed and / or fall below at least one limit value for pressure and / or temperature. Thus, faults or damage to the compressor system can be identified and corrective measures taken by sensing the pressure and / or temperature.

[0018] In particular, the reciprocating compressor system includes an electrolyzer for generating the gas to be compressed, especially hydrogen, and the gas can be introduced from the electrolyzer at a generation pressure, especially greater than 15 bar, into a container containing the gas to be compressed. During the electrolysis of water in the electrolyzer, the gas generated by the electrolyzer, especially hydrogen and oxygen as the gas to be compressed, has a pressure greater than 15 bar during generation and electrolysis, and this can be utilized by introducing the generated gas at the generation pressure into a container containing the gas to be compressed.

[0019] In another embodiment, the delivery capacity of the reciprocating compressor and / or reciprocating compressor system can be controlled and / or regulated by means of a control and / or regulating unit, such that the pressure of the gas to be compressed in the container is greater than, and particularly consistently greater than, a predetermined minimum pressure. The minimum pressure in the container with the gas to be compressed is, for example, between 15 bar and 50 bar. Thus, no pressure below the minimum pressure will occur in the container with the gas to be compressed, allowing the generation pressure of the gas to be compressed from the electrolyte to be used for compression in the reciprocating compressor system.

[0020] In an additional configuration, the delivery capacity of the reciprocating compressor and / or reciprocating compressor system can be controlled and / or regulated according to the electrolytic cell's production capacity using a control and / or regulation unit. Specifically, the average delivery capacity of the reciprocating compressor and / or reciprocating compressor system during synchronization substantially (especially with a deviation of less than 30%, 20%, or 10%) corresponds to the average production capacity of the electrolytic cell during synchronization. The average delivery capacity of the reciprocating compressor and / or reciprocating compressor system is controlled and / or regulated, for example, by controlling and / or regulating the rotational speed of the drive shaft. Alternatively, the average delivery capacity of the reciprocating compressor and / or reciprocating compressor system can be controlled and / or regulated by being able to change the rotational speed of the drive shaft during synchronization, preferably to zero or corresponding to the maximum rotational speed of the drive shaft. The delivery capacity of the reciprocating compressor and / or reciprocating compressor system and the production capacity of the electrolytic cell are thus coordinated with each other during synchronization, such that the production pressure of the electrolytic cell can be fully utilized for compression in the reciprocating compressor and / or reciprocating compressor system, i.e., the pressure in the container containing the gas to be compressed does not drop below, for example, the production pressure of 15 bar.

[0021] In another configuration, the reciprocating compressor system includes at least one housing for a clearance lubrication chamber.

[0022] In an additional variant, the reciprocating compressor includes an inlet valve for each compression chamber and an outlet valve for each compression chamber.

[0023] In another embodiment, a piston rod is fixed to each piston in the reciprocating compressor for mechanical connection between each mechanical device and each piston, wherein, preferably, relative movement can be performed between the piston and the piston rod in the radial direction. Advantageously, virtually no force is transmitted radially from the piston rod to the piston, resulting in less mechanical wear on the radially outer side of the piston and on the piston rings.

[0024] To suit the purpose, the piston is constructed in two parts, having a first piston assembly and a second piston assembly. The piston can thus be advantageously optimized in terms of geometry and / or materials for gas compression. For example, the first piston assembly, which is confined to the compression chamber, is constructed of a material optimized for gas compression, and the second piston assembly, on which a diaphragm and / or piston rod, particularly a stop ring for the piston rod, is indirectly or directly attached, is made of a material optimized for this connection.

[0025] In a supplementary variation, the at least one diaphragm is configured as at least one bellows.

[0026] Preferably, the stroke height of each piston between its top dead center and bottom dead center is less than 30%, 10%, 5%, or 3% of the extension dimension of the at least one diaphragm, and in particular the at least one bellows, in the longitudinal direction of the cylinder related to the stroke movement. Therefore, the diaphragm experiences minimal stretching and compression during the piston's stroke, resulting in a long service life due to minimal mechanical load.

[0027] In one additional configuration, components of the compressor system are mounted on the base frame, either indirectly or directly. Preferably, the components of the compressor system mounted on the base frame are a reciprocating compressor and / or at least one cylinder housing of a reciprocating compressor and / or a container for the gas to be compressed and / or a container with compressed gas and / or a drive motor, especially an electric motor, and / or a lubricating oil container.

[0028] Preferably, at least two cylinder housings of the compressor are connected to each other via connecting pipes.

[0029] In another variation, a throttling channel is constructed from the lubrication chamber into the diaphragm interior space to guide lubricating oil into the diaphragm interior space, and a discharge channel is constructed from the diaphragm interior space into the lubricating oil line to guide lubricating oil from the diaphragm interior space into the lubricating oil line and / or lubricating oil container. The flow cross-section of the throttling channel is smaller than that of the discharge channel; preferably, the flow cross-section of the throttling channel is smaller than 70%, 50%, 30%, or 10% of the flow cross-section of the discharge channel. This advantageously guides lubricating oil into the diaphragm interior space for lubrication and cooling of the sliding bearings of the diaphragm interior space and the piston rod.

[0030] In another variation, the first piston assembly is the one facing the compression chamber, and the second piston assembly is the one facing the mechanical device. Preferably, a first imaginary plane perpendicular to the longitudinal axis of the piston and / or cylinder and / or piston rod intersects only the first piston assembly, and a second imaginary plane perpendicular to the longitudinal axis of the piston and / or cylinder and / or piston rod intersects only the second piston assembly.

[0031] In an additional embodiment, each piston limits the compression chamber only at the first piston assembly.

[0032] In an additional variation, the first piston component and the second piston component are interconnected in a form-locking and / or force-locking and / or material-locking manner. Preferably, the first piston component and the second piston component are interconnected by a locking connection or a bayonet connection.

[0033] In a supplementary embodiment, the first piston component and the second piston component are connected to each other by a threaded connection.

[0034] In another variation, due to the geometry of the first and second piston components, an annular groove is constructed between the first and second piston components, and piston rings are arranged in the annular groove.

[0035] In another embodiment, the components of the reciprocating compressor are sealed to each other by at least one seal, and said components are cylinder housings and / or cylinder heads and / or flanges and / or housings and / or fastening elements for lubrication chambers. The two components of the reciprocating compressor come into contact with each other at contact surfaces, particularly flat contact surfaces, especially by pressure. A seal is typically not achieved between these contact surfaces of the two components of the reciprocating compressor because the components are constructed of metal and / or rigid materials. For this reason, it is necessary to seal the contact surfaces with seals to achieve, for example, a seal between the compression chamber and the external space of the diaphragm and the surrounding environment.

[0036] In another embodiment, the at least one sealing ring and / or the at least one fastening ring has any shape in a cross section perpendicular to the longitudinal axis of the cylinder, especially circular or rectangular, particularly square or elliptical.

[0037] Preferably, the component is constructed of metal, especially steel and / or aluminum.

[0038] In an additional embodiment, the at least one seal is constructed to completely surround the circumferential direction.

[0039] In an additional configuration, the at least one seal is constructed of an elastic material. Preferably, the seal's strength is measured in kN / mm². 2 The elastic modulus is less than 30, 20, 10, 5, 3 or 2.

[0040] Preferably, the at least one seal is pre-tightened by pressure.

[0041] In a supplementary variation, the at least one seal is pre-tightened in the axial direction by means of pressure (especially with a deviation of less than 30°, 20° or 10°).

[0042] In another configuration, the at least one seal is arranged at least partially, and in particular completely, in each of the recesses.

[0043] To meet the requirements, the at least one groove is constructed to completely surround the circumferential direction.

[0044] In an additional embodiment, each seal is arranged in only one groove.

[0045] In a supplementary embodiment, the at least one fastening element is constructed in a ring shape.

[0046] In another configuration, the at least one fastening element is constructed to completely surround the longitudinal axis of each cylinder in either the tangential or circumferential direction. This enables tight isolation between the at least one lubrication chamber and the at least one compression chamber.

[0047] In particular, the axial and / or radial extension dimensions of the at least one fastening element are substantially constant (especially with deviations of less than 30%, 20%, or 10%).

[0048] In another variation, each diaphragm is fixed to a fastening element as a sealing device by material locking, particularly welding and / or adhesive bonding, for tight isolation between each lubrication chamber and each compression chamber.

[0049] In a supplementary embodiment, one material locking connection between the diaphragm and the fastening element and / or between the fastening element and the piston is a welded connection, especially a welded connection produced by means of laser welding.

[0050] In another variation, the at least one seal is constructed in a ring shape.

[0051] In an additional configuration, the at least one seal is constructed in a single component, particularly a single component.

[0052] In a supplementary embodiment, the at least one seal is at least partially, and especially entirely, constructed of HPU and / or PU (polyurethane) and / or NBR (acrylonitrile-butadiene rubber) and / or FPM and / or FKM (fluororubber) and / or EPDM (ethylene propylene diene monomer) and / or silicone and / or PTFE (polytetrafluoroethylene) and / or POM (polyoxymethylene).

[0053] In a supplementary variation, at least one seal between the two components is pre-tightened by pressure due to the connection between the two components by means of a fixing element, particularly a screw and / or a bayonet connection and / or a locking connection.

[0054] Preferably, a flange is constructed between each of the cylinder housings and each of the housings for the lubrication chamber. The flange indirectly transmits forces acting on the cylinder housings, such as those due to friction between the piston and piston guide, to the housing for the lubrication chamber. As an additional component, the flange allows for a simple configuration, via a support pipe joint, of the axial extension dimension of the guide bore for the sliding bearing of the piston rod to have a sufficiently large axial extension dimension as a sliding bearing, without significantly increasing the overall axial extension dimension of the reciprocating compressor. Furthermore, the flange improves flexibility during the assembly and disassembly of the reciprocating compressor.

[0055] In another embodiment, the flange plate is form-locked and / or force-locked to each of the cylinder housings and / or the housings for the lubrication chamber. The flange plate is preferably fixed to the cylinder housing and / or the housing for the lubrication chamber by means of at least one fixing element, particularly at least one screw. For this purpose, corresponding holes with and / or without internal threads are formed in the cylinder housing and / or the housing for the lubrication chamber. The internal threads are for screwing in the external threads on the screw. Furthermore, at least one hole for guiding the screw through is also formed in the flange plate. The screw with the screw head is subjected to tensile load, such that the cylinder housing presses against the flange plate and / or the flange plate presses against the housing for the lubrication chamber for a force-locked connection. Additionally, there is preferably substantially no radial clearance and / or no radial distance between the at least one hole where the screw is arranged and the screw, thereby additionally providing a form-locked connection between the cylinder housing and the flange plate and / or between the flange plate and the housing for the lubrication chamber. Preferably, the fixing element is constructed as a bayonet connection or a rivet. Preferably, the form-locking connection between the cylinder housing and the flange plate and / or between the flange plate and the housing for the lubrication chamber is formed by form-locking geometry and corresponding form-locking geometry.

[0056] In an additional variation, the maximum radial extension dimension of the flange is greater than the maximum axial extension dimension of the flange, preferably greater than 70%, 50% or 30% of the maximum axial extension dimension of the flange.

[0057] In a supplementary configuration, the axial extension dimension of the flange plate as the flange plate thickness is essentially constant (especially with deviations of less than 30%, 20%, 10%, 5% or 1%), and the support pipe joint is preferably not considered.

[0058] In another variation, a connection channel is constructed from the internal space of the diaphragm to the surrounding environment, particularly in the flange plate, for the ambient pressure within the internal space of the diaphragm, and preferably, the reciprocating compressor and / or reciprocating compressor system does not have a throttling channel and / or a discharge channel for guiding lubricating oil from the lubricating oil circuit through the internal space of the diaphragm.

[0059] In another variant, the flange is constructed in a disc shape.

[0060] In a supplementary configuration, the cylinder housing and / or cylinder head and / or flange and / or housing for the lubrication chamber are at least partially, especially entirely, constructed of metal (especially steel and / or aluminum) and / or plastic (especially fiber-reinforced plastic).

[0061] As per the destination, the lubrication chamber is sealed.

[0062] In another embodiment, the number of corrugations in the bellows is greater than 5, 10, 30, 50, 100, or 200.

[0063] In an additional variation, the clearance volume (Totvolumen) of each compression chamber is less than 10%, 5%, 3%, or 2% of the stroke volume of each compression chamber. Advantageously, the reciprocating compressor can thus achieve high pressure of the gas to be compressed at a small piston stroke height by means of a shaft having at least one cam and a mechanical device including working rollers.

[0064] In a supplementary configuration, the at least one diaphragm, and in particular the at least one bellows, is arranged at least partially, and in particular completely, between the piston and the mechanical device in the direction of the cylinder longitudinal axis.

[0065] Preferably, in each of the compressors and / or sub-piston compressors, the internal space of the diaphragm is sealed to the external space of the diaphragm in a fluid-tight manner.

[0066] In another embodiment, the at least one diaphragm, and in particular the at least one bellows, is constructed in a substantially cylindrical shell shape, especially in the region within the at least one cylinder.

[0067] In a supplementary variation, the at least one piston is mechanically connected to a mechanical device via a piston rod.

[0068] In accordance with the destination, the at least one cylinder includes at least one cylinder head.

[0069] In an additional embodiment, the working roller comprises a cylindrical shell-shaped working roller with a central bore, and a support pin is arranged in the central bore. An annular gap is formed between the cylindrical shell-shaped working roller and the support pin, and this annular gap is lubricated with a lubricant. The axial end of the support pin is supported in a roller shoe, for example, by a sliding bearing.

[0070] In an additional embodiment, the axial extension dimension of the at least one diaphragm is greater than 5, 10, 20, or 30 times the thickness of the at least one diaphragm. Therefore, the axial extension dimension of the at least one diaphragm is significantly greater than the thickness of the diaphragm.

[0071] In an additional embodiment, the diaphragm is made of metal and / or plastic. Preferably, the plastic construction of the diaphragm is an elastomer. The diaphragm is flexible to withstand the reciprocating motion of the piston. Preferably, the diaphragm consists of multiple layers, particularly layers made of different materials such as metal and / or plastic. A layer, for example a thin layer made of metal such as aluminum foil, reduces the permeation of substances through the diaphragm. The diaphragm has a very small permeability coefficient, especially for lubricants. Q = P * F * t * Δp / d. Where Q is the amount of gas or vapor passing through a layer of area F and thickness d in time t, when the pressure difference of the permeate before and after the layer is Δp. The oxygen permeability of the diaphragm (in cm⁻¹) is... 3 / m 2 The hydrogen permeability of the membrane (in *d*bar) is preferably less than 30, 10, 1, or 0.1. 3 / m 2 (Using *d*bar as the unit) preferably less than 50, 10, 1 or 0.2.

[0072] In another embodiment, the cylinder has a longitudinal axis. The longitudinal axis of the cylinder corresponds to the direction of movement of the piston supported in the cylinder.

[0073] To meet the requirements, the mechanical device consists of a roller shoe with working rollers and a drive shaft with cams.

[0074] In another embodiment, the mechanical device consists of a crankshaft and a connecting rod that serves as a piston rod.

[0075] In an additional variant, the reciprocating compressor includes an electric motor for driving the reciprocating compressor. For example, the electric motor drives a drive shaft with cams and / or a crankshaft.

[0076] The pressure that can be generated by a reciprocating compressor is in the range of 100 bar to 1000 bar. Attached Figure Description

[0077] The embodiments of the present invention will now be described in more detail with reference to the accompanying drawings. Figure 1 Cross-section of a reciprocating compressor used for compressing gases. Figure 2 According to the working rollers and drive shaft with roller shoes Figure 1 AA section, Figure 3 :according to Figure 1 An enlarged partial cross-section of a piston compressor. Figure 4 :according to Figure 1 Another enlarged section of the cross-section of the piston compressor. Figure 5 The cross-section of a reciprocating compressor for compressing gases, which has two cylinder housings, and Figure 6 A greatly simplified schematic diagram of a compressor system. Detailed Implementation

[0078] exist Figure 1 The diagram shows a cross-section of a reciprocating compressor 1 for compressing gas according to a first embodiment. The reciprocating compressor 1 is used to compress gas, such as hydrogen or air, under high pressure. The pressure that the reciprocating compressor 1 can generate is, for example, between 100 bar and 1000 bar.

[0079] The reciprocating compressor 1 includes a drive shaft 2 with two cams 3, which rotates about a rotation axis 26. The drive shaft 2 is driven by an electric motor (not shown). The rotation axis 26 is located at... Figure 1 Within the drawing plane and perpendicular to Figure 2 The drawing plane is shown. Piston 5 is supported in cylinder 6, specifically in piston guide 7 of cylinder 6 formed by cylinder housing 8. A completely circumferential annular groove 15 is constructed on the radially outer side of piston 5. A piston ring 16 is arranged in each annular groove 15. Piston 5 is constructed in two parts, having a first piston component 5a and a second piston component 5b. Compression chamber 29 is limited only by the first piston component 5a. The maximum axial extension dimension of the second piston component 5b is significantly larger than the maximum extension dimension of the first piston component 5a, for example, the maximum axial extension dimension of the second piston component 5b is greater than 2, 3, or 5 times the maximum extension dimension of the first piston component 5a. The annular groove 15 with piston ring 16 is constructed in the second piston component 5b and between the first piston component 5a and the second piston component 5b. Optionally, at least one annular groove 15 and at least one piston ring 16 (not shown) may also be constructed in the first piston component 5a. The first piston component 5a is form-locked and / or force-locked to the second piston component 5b, particularly by screwing a bolt 86 or pipe fitting 86 with external threads constructed on the first piston component 5a into a hole 87 with internal threads in the second piston component 5b, as a threaded connection 88. In contrast to the threaded connection 88... Figure 3The connection may also include bayonet connections, locking connections, or material locking connections, such as welded connections or adhesive connections (not shown), for the connection between the first and second piston components 5a, 5b. The compression chamber 29 is defined by the cylinder housing 8 with cylinder head 17 and the piston 5 (i.e., the first piston component 5a). The end 18 of the cylinder head 17 defines the compression chamber 29 and does not function as a surface part of the cylinder 6 that is involved in its function and / or construction. An inlet passage 22 with an inlet valve 19 and a outlet passage 24 with an outlet valve 20 lead into the compression chamber 29. Gas flows into the compression chamber 29 through the inlet passage 22 with an inlet opening 21, and gas under high pressure flows out of the compression chamber 29 through the outlet passage 24 with an outlet opening 23. The inlet valve 19, for example a check valve, is configured such that only gas flows into the compression chamber 29, while the outlet valve 20, for example a check valve, is configured such that only gas flows out of the compression chamber 29. The volume of the compression chamber 29 changes due to the reciprocating stroke of the piston 5. The piston 5 is indirectly supported on the drive shaft 2 by means of the piston rod 14. The piston 5 and the piston rod 14 are coaxially and / or concentrically oriented. A roller shoe 9 with working rollers 10 is fixed to the end of the piston rod 14. The working rollers 10 can rotate here, and their axis of rotation 25 is located at... Figure 1 The drawing plane shown is in and perpendicular to Figure 2 The drawing plane. The drive shaft 2 having at least one cam 3 has a shaft-rolling surface 4, and the working roller 10 has a roller-rolling surface 11.

[0080] The roller-rolling surface 11 of the working roller 10 rolls at the contact surface 12 on the shaft-rolling surface 4 of the drive shaft 2, which has two cams 3. The roller shoe 9 is supported in a roller shoe bearing formed by the cylinder housing 8, which acts as a sliding bearing. A spring 27, i.e., a coil spring 27, acts as an elastic element 28 (clamped between the flange plate 43 and the roller shoe 9), applying pressure to the roller shoe 9 so that the roller-rolling surface 11 of the working roller 10 is always in contact with the shaft-rolling surface 4 of the drive shaft 2. The spring 27, as the elastic element 28, is positioned on the roller shoe 9 and the flange plate 43, so that the flange plate 43 serves to support the elastic element 28. The roller shoe 9, piston rod 14, and piston 5 thus perform a reciprocating stroke together. The working roller 10 is supported in the roller shoe 9 by means of a sliding bearing 13. The roller shoe 9 with the working roller 10 and the drive shaft 2 with the cams 3 thus function as a mechanical device 40 to generate the reciprocating motion of the piston 5.

[0081] Inlet valve 19 and outlet valve 20 are mounted or integrated in cylinder head 17. Cylinder head 17 is a component of cylinder 6 or cylinder housing 8. Cylinder head 17 is fixed to cylinder 6 by fixing element 38 as screw 39, and therefore also fixed to cylinder housing 8. A portion of surface 18 of cylinder head 17 forms surface 18 or end 18 of limiting compression chamber 29. Inlet valve 19 includes valve piston 30, elastic element 35 as spring 36, and support element 37 for spring 36. In the closed position, valve piston 30 is fluid-tightly positioned on valve seal seat 32 that surrounds it completely in the tangential direction. Figure 1 The outlet valve 20 similarly includes a valve piston 31 for the outlet valve 20, an elastic element 35 as a spring 36, and a support element 37 for the spring 36. Figure 1 The spring 36 of the outlet valve 20 rests on the valve seat 33 in the closed position of the outlet valve 20. The valve seat 32 for the inlet valve 19 and the valve seat 33 for the outlet valve 20 are configured here to correspond to the geometry constructed on the cylinder head 17. The inlet valve 19 and the outlet valve 20 are pneumatically actuated with valve pistons 30 and 31. Due to the pressure change in the compression chamber 29 during the reciprocating motion of the piston 5, the inlet valve 19 opens and the outlet valve 20 closes during the increase in volume of the compression chamber 29, and vice versa during the decrease in volume of the compression chamber 29 during the reciprocating motion of the piston 5.

[0082] Piston 5 is supported on piston guide 7 of cylinder 6 and performs reciprocating translational motion along the longitudinal axis 41 of cylinder 6. Mechanical device 40 is arranged in lubrication chamber 44, and lubrication chamber 44 is defined by a closed housing 45 for both mechanical device 40 and lubrication chamber 44. The closed housing 45... Figure 1 Only a portion is shown. In the lubrication chamber 44, the mechanical device 40 is lubricated with a lubricant, such as lubricating oil or fuel. Since the bearings of the moving parts are implemented as sliding bearings, lubricant is necessary. The piston compressor 1 compresses, for example, hydrogen for a fuel cell or air or oxygen for breathing in the compression chamber 29. Therefore, the gas to be compressed must not be contaminated by the lubricant from the lubrication chamber 44, not even by a very small amount. The radially outer side of the piston 5 is supported on the piston guide 7 of the cylinder 6 by piston rings 16; as a gap seal, complete and tight isolation between the lubrication chamber 44 and the compression chamber 29 containing the gas to be compressed cannot be achieved.

[0083] For this reason, the lubrication chamber 44 is tightly and completely isolated from and sealed to the compression chamber 29 by means of a diaphragm 34, which serves as a bellows 34. The bellows 34, which serves as the diaphragm 34, is constructed of metal and / or plastic. The plastic is especially an elastomer. The axial extension dimension of the diaphragm 34 is significantly greater than the thickness of the diaphragm 34. Between the cylinder housing 8 and the housing 45 for the mechanical device 40, annular and disc-shaped flange plates 43 are arranged along the longitudinal axis 41 of the cylinder 6. The flange plates 43 are used to transmit the forces acting on the cylinder housing 8 to the housing 45 for the lubrication chamber 44 and the mechanical device 40.

[0084] The lower axial end region of the diaphragm 34, which is the bellows 34, is fixed to the annular fastening element 49, which is the sealing ring 46 made of metal, by means of a locking connection 52 made of a material that serves as a welding connection 53. Figure 1 and Figure 4 The fastening element 49, serving as the sealing ring 46, is L-shaped in cross-section, comprising a first side 59 extending substantially radially 57 and a second side 60 extending substantially axially 56 in cross-section. The first side 59 forms a first ring 59 in cross-section, and the second side 60 forms a second ring 60. The welded connection 53 is preferably manufactured by laser welding. The welded connection 53 is constructed, in the tangential direction 58, completely circumferentially between the bellows 34 and the annular fastening element 49, serving as the sealing ring 46, at the axial end of the second ring 60 facing the compression chamber 29. Thus, the welded connection 53, serving as a material-locking connection 52, is fluid-tightly constructed to tightly isolate the lubrication chamber 44 from the compression chamber 29. Thus, the material-locking connection 52 also forms a sealing device 42 and a fastening device 47. The axial direction 56 is oriented along the longitudinal axis 41 of the cylinder 6. The radial direction 57 is oriented perpendicular to the longitudinal axis 41. The annular fastening element 49 extends significantly in the radial direction 57 (as a diameter) than it extends in the axial direction 56. The annular fastening element 49 is clamped and fixed between the cylinder housing 8 and the flange plate 43 by pressure at the first ring 59. Therefore, the cylinder housing 8 and the flange plate 43 form a fastening member 50 for clamping and fixing the fastening element 49 by pressure as a clamping connection force. Furthermore, due to the geometry of the fastening element 49, the cylinder housing 8, and the flange plate 43, the fastening element 49 is form-fitted onto the cylinder housing 8 and the flange plate 43, particularly in the radial direction 57 and the axial direction 56.

[0085] The flange 43 is fastened to the housing 45 of the mechanical device 40 by means of a fixing element 38, which is a screw 39. Furthermore, due to the geometry of the reciprocating compressor 1, lubricant and / or gas will flow outward in the radial direction 57 along the gap 51 and / or contact surface 51 from the spaces inside and outside the bellows 34, which serve as the inner and outer spaces of the diaphragm space 61 and the outer space of the diaphragm 62, the compression chamber 29, and the lubrication chamber 44. The gap 51 is constructed between the fastening element 49 and the flange 43, between the fastening element 49 and the cylinder housing 8, between the flange 43 and the housing 45 for the mechanical device 40 and the lubrication chamber 44, and between the cylinder head 17 and the cylinder housing 8. Figure 1 and Figure 4 For this reason, a groove 55 is constructed in the cylinder housing 8, the flange plate 43, and the housing 45, respectively. Two grooves 55 are constructed in the cylinder housing 8. A seal 54 is arranged in each groove 55. Figure 1 and Figure 4 The seal 54 and the groove 55 are constructed to completely surround the cylinder in both the tangential and circumferential directions 58. The dimensions of the seal 54 and the groove 55 are designed such that they are pre-tightened by pressure in the axial direction 56 on one side between the cylinder housing 8 and the sealing ring 46, and on the other side between the sealing ring 46 and the flange plate 43. Therefore, the axial extension dimension of the seal 54 without pre-tightening is greater than that with pre-tightening and compression. The seal 54 between the flange plate 43 and the housing 45, and the seal 54 between the cylinder head 17 and the cylinder housing 8, are also pre-tightened by pressure in the axial direction 56. Thus, the components 8, 17, 42, 45, 46, 47, and 49 of the reciprocating compressor 1 are sealed to each other by means of the resilient seal 54. Thus, the compression chamber 29, the diaphragm internal space 61, the diaphragm external space 62, and the lubrication chamber 44 are sealed relative to the surrounding environment at the contact surfaces 51 between components 8, 17, 42, 45, 46, 47, and 49. The seals 54 are made of, for example, EPDM or silicone. One seal 54 is arranged in each corresponding groove 55. At least one connection channel 102 is constructed in the flange plate 43, preferably according to… Figure 5 Two connection channels 102 extend from the diaphragm interior space 61 to the surrounding environment, thereby creating an ambient pressure within the diaphragm interior space 61 to reduce the load on the diaphragm 34. This is consistent with... Figure 6 This differs from the compressor system 65 shown, which has a throttling passage 84 and a discharge passage 85 in the flange 43. The flange 43 therefore has not only mechanical functions but also hydraulic and / or pneumatic functions.

[0086] The bellows 34 is indirectly fluid-tightly fixed to the lower end of the piston 5 (i.e., the second piston component 5b) by means of a sealing ring 46, which serves as a fastening device 47, at its axial end facing the compression chamber 29. Figure 1 and Figure 3 The diaphragm 34 is fluid-tightly connected at its upper axial end to the lower end of the sealing ring 46 by means of a sealing device 42 serving as a fastening device 47. The sealing device 42 and the fastening device 47 between the sealing ring 46 and the diaphragm 34 are formed by a material locking connection 52, particularly a welded connection 53 and / or an adhesive connection. The welded connection 53 is manufactured, for example, by laser welding. Similarly, the upper end of the sealing ring 46 is fixed to the lower end of the piston 5, i.e., the second piston component 5b. The sealing device 42 and the fastening device 47 between the sealing ring 46 and the piston 5 are formed by a material locking connection 52, particularly a welded connection 53 and / or an adhesive connection. The sealing ring 46 serves a sealing function and additionally acts as a fastening device 47 to indirectly fix the diaphragm 34 to the piston 5.

[0087] The material-locking connection 52 between the diaphragm 34 and the sealing ring 46 (which serves as a fastening device 47), and between the sealing ring 46 and the second piston component 5b, is constructed continuously in the circumferential direction 58 to provide a fluid-tight seal between the inner diaphragm space 61 and the outer diaphragm space 62. The diaphragm 34 divides the cylinder portion space, bounded by the cylinder 6, piston 5, and flange 43, into the inner diaphragm space 61 and the outer diaphragm space 62. In the inner diaphragm space 61, a mixture of lubricating oil and air exists because the lubrication chamber 44 and the inner diaphragm space 61 are not completely sealed. In the outer diaphragm space 62, compressed gas exists because the gap seal between the piston 5 and the cylinder 6 is not completely sealed. The internal space 61 of the diaphragm is fluidly and tightly isolated from the external space 62 of the diaphragm to prevent the gas to be compressed from being contaminated, especially by lubricating oil, which is caused by lubricating oil entrainment at the gap seal between the piston 5 with piston ring 16 and the cylinder 6 with piston guide 7.

[0088] The upper sealing ring 46, serving as a fastening device 47, also constitutes a fastening ring 47 for securing the diaphragm 34 to the piston 5. The sealing ring 46 has a sleeve-shaped or cylindrical shell-shaped extension 63 that extends into a recess on the second piston component 5b. Figure 3At the end of the piston rod 14 facing the piston 5, the piston rod 14 is configured to have a small axial extension dimension and a large radial diameter, such that a stop ring 64 is formed on the piston rod 14. The stop ring 64 is preferably constructed as a single piece with the rest of the piston rod 14. The axial end of the sleeve-shaped extension 63 of the fastening element 63 facing the compression chamber 29 rests on the stop ring 64, which is fully constructed in the circumferential direction 58. Thus, the tension in the piston rod 14 can be indirectly transmitted from the piston rod 14 to the piston 5 via the fastening element 49, which serves as a sealing ring 46 and a fastening device 47, in a form-locking manner, and conversely, via the axial end of the sleeve-shaped extension 63, which is pressed against the lower side and axial end of the stop ring 64 facing the lubrication chamber 44 by pressure. Furthermore, the axial end of the piston rod 14 is positioned on the piston 5, i.e., the second piston component 5b, so that pressure in the piston rod 14 can be transmitted from the piston rod 14 to the piston 5 by means of pressure transmission between the axial end of the piston rod 14 and the piston 5, and vice versa. The geometry of the piston rod 14 with the stop ring 64 and the geometry of the notch on the piston 5, i.e., the second piston component 5b, are constructed such that, in the radial direction 57, there is a gap or radial distance between the piston rod 14, especially the stop ring 64, and the piston 5 and the sealing ring 46 on the other hand. The piston 5 and the piston rod 14 are independent components. Therefore, relative movement can occur between the piston rod 14 and the piston 5 in the radial direction 57. Therefore, within this radial gap or radial distance, no force can be transmitted between the piston 5 and the piston rod 14 in a form-locking manner, thereby reducing the load applied to the piston 5 with radial force. This advantageously reduces mechanical wear between the piston guide 7 on the cylinder 6 and the piston 5 with the piston ring 16.

[0089] In the radial direction 57, an optional guide ring 89 is constructed between the second ring 60 of the lower sealing ring 46 and the piston rod 14. A guide hole 90 is constructed in the flange plate 43, such that the flange plate 43 is annularly constructed. In the guide hole 90, the piston rod 14 is supported as a sliding bearing. Furthermore, on the flange plate 43, which is subjected to pressure due to the cylinder housing 8 and the housing 45, a cylindrical cover-shaped support pipe joint 105 is constructed on the lower side of the flange plate 43. Figure 1 The guide hole 90 is used to enlarge its axial extension dimension. The radially inner side of the support tube joint 105 also forms a sliding bearing for the piston rod 14. The support tube joint 105 is arranged within the elastic element 28, preferably with at least 50% or 90% of its axial extension dimension arranged within the elastic element 28. Similarly, a guide hole 90 is also constructed in the guide ring 89 as a sliding bearing for the piston rod 14. A friction-reducing and / or locally harder coating (e.g., a DLC coating as a diamond-like carbon coating) can be applied to the outer side of the piston rod 14 and / or to the sliding bearing at the guide hole 90 to reduce friction and mechanical wear.

[0090] The axial extension dimension of the piston rod 14 is significantly greater than the sum of the axial extension dimensions of at least one guide hole 90. Preferably, the axial extension dimension of the piston rod 14 is greater than 2, 3, or 5 times the sum of the axial extension dimensions of at least one guide hole 90, wherein the sum may also have only one addend. The cylindrical shell-shaped guide holes 90 in the flange 43 and guide ring 89 have only a small gap or a radial distance of a few micrometers (e.g., 0 to 50 micrometers) between the radially outer side of the piston rod 14 and the radially inner side of the guide hole 90 in the radial direction 57. The guide ring 89 may also be configured and function as a piston rod seal 89; for example, the guide ring may be made of plastic rather than metal. This sliding bearing of the piston rod 14 at the guide hole 90 is lubricated with lubricating oil carried from the lubrication chamber 44 due to the gap or radial distance. The axial end region of the guide hole 90 is conically constructed to avoid increased mechanical wear at sharp edges. Furthermore, the guide hole 90 is substantially (e.g., with a deviation of less than 5°, 3°, or 1°) oriented at a right angle to the disc flange 43, that is, at a right angle to the imaginary plane unfolded by the disc flange 43. The guide hole 90 in the flange 43 is used to guide the piston rod 14. Due to the small gap or radial distance between the piston rod 14 and the guide hole 90 in the flange 43, very little leakage occurs from the lubrication chamber 44 to the diaphragm interior space 61 (and vice versa), so the flange 43 also assumes the sealing function between the diaphragm interior space 61 and the lubrication chamber 44.

[0091] The cylinder head 17 is constructed with a centering geometry 91 as a centering protrusion 93 for orientation in the radial direction 57. The cylinder housing 8 is constructed with a mating centering geometry 92 as a centering recess 94. The radially outer side 91 of the centering protrusion 93 thus forms a convex curved centering geometry 91. The radially inner side 92 at the centering recess 94 forms a concave curved mating centering geometry 92. The centering geometry 91 and the mating centering geometry 92 are substantially parallel to each other (especially with a deviation of less than 5°, 3°, or 1°) and oriented parallel to the longitudinal axis 41 of the cylinder 6 and the piston rod 14. The centering geometry 91 and the mating centering geometry 92 are constructed to completely surround each other in the tangential direction 58 or the circumferential direction 58. The centering geometry 91 and the mating centering geometry 92 are in contact with each other in a completely surrounding manner, that is, the centering geometry 91 fits against the contact surface of the mating centering geometry 92. Thus, cylinder head 17 is aligned with cylinder 6 and cylinder housing 8, and vice versa.

[0092] The cylinder housing 8 is centered relative to the flange plate 43 by means of centering geometry 91 and mating centering geometry 92, and similarly, the reverse is also true. For this purpose, a centering protrusion 93 is formed in the axial end region of the cylinder housing 8. The radially outer side 92 of the centering protrusion 93 forms the mating centering geometry 92. A large centering recess 94 is formed on the flange plate 43, such that the remaining surrounding ring of the limiting centering recess 94 forms the centering geometry 91 on the radially inner side 91.

[0093] The housing 45 is centered relative to the flange 43 by centering geometry 91 and mating centering geometry 92, and similarly, the reverse. For this purpose, a centering protrusion 93 is formed in the axial end region of the housing 45. The radially inner side 91 of the centering protrusion 93 forms the centering geometry 91. A large centering recess 94 is formed on the flange 43, such that the remaining limiting centering recess 94, forming a ring that completely surrounds the housing 45 in the circumferential or tangential direction 58, acts as a centering ring on the radially outer side 92, forming the mating centering geometry 92. Therefore, the flange 43 indirectly serves to center the cylinder housing 8 relative to the housing 45 for the lubrication chamber 44 and the mechanical device 40.

[0094] Furthermore, on the cylinder housing 8, the centering geometry 91 is configured as the radial inner side of the centering recess 93 ( Figure 4 The sealing ring 46 and the fastening ring 47, which serve as fastening elements 49, form a mating alignment geometry 92 on their radially outer sides for orienting the fastening element 49 relative to the cylinder housing 8 in the radial direction 57.

[0095] Therefore, centering geometry 91 and mating centering geometry 92 are formed on components 8, 17, 42, 45, 46, 47, and 49 for centering as a form-locking mechanism for the radial orientation of components 8, 17, 42, 45, 46, 47, and 49 relative to each other. Thus, the term "centering" means, in particular, the radial orientation of components 8, 17, 42, 45, 46, 47, and 49 relative to each other. Centering geometry 91 and mating centering geometry 92 may also be formed by at least one centering pin and at least one mating centering hole, wherein at least one centering pin is arranged in at least one mating centering hole (not shown).

[0096] The axial extension dimension 48 of the bellows 34 along the longitudinal axis 41, i.e., the area of ​​the piston 5's stroke movement between top dead center and bottom dead center, is significantly larger than the stroke height of the piston 5, which is the difference between the top dead center and bottom dead center. The extension dimension 48 is, for example, 100 mm to 150 mm, and the stroke height of the piston 5 is preferably 10 mm, but at most 50 mm. Figure 1In this drawing, due to drawing requirements, the extension dimension 48 and the stroke height of the piston 5 are not drawn to scale. Therefore, the mechanical load on the deformation of the diaphragm 34 is relatively small, as only a small deformation occurs per unit length of the extension dimension 48. Thus, the diaphragm 34 can be constructed not only as a bellows 34 in the relevant area with the extension dimension 48, but also as a simple diaphragm without folds. Because the deformation of the diaphragm 34 in the relevant area with the extension dimension 48 is small, the service life of the diaphragm 34 corresponds at least to the service life of the rest of the reciprocating compressor 1. Due to the small stroke height of the piston 5 and the large extension dimension 48 of the diaphragm 34, the axial extension dimension of the piston guide 7 is significantly smaller than the axial extension dimension of the cylinder housing 8. The diaphragm 34 is completely disposed within the cylinder housing 8. For example, the axial extension dimension of the piston guide 7 is less than 70%, 50%, 30%, or 10% of the axial extension dimension of the cylinder housing 8. The piston rod 14 should be implemented to resist bending, for example, by means that the axial extension dimension of the piston rod 14 is at least 5, 10, or 15 times larger than the diameter of the piston rod 14 outside the stop ring 64. The diameter of the piston rod 14 outside the stop ring 64 is, for example, less than 10 mm, such as 9 mm or 8 mm. The diameters of the piston 5 and the piston guide 7 are, for example, between 10 mm and 50 mm, preferably between 20 mm and 40 mm.

[0097] Figure 6 A compressor system 65 having the aforementioned reciprocating compressor 1 is shown. Figure 6 In the illustrated embodiment, the compressor system 65 includes a reciprocating compressor 1 with two sub-piston compressors 1, i.e., similar to... Figure 5 The illustrated embodiment has two cylinders 6, two pistons 5, and two compression chambers 29, and these two sub-piston compressors 1 share a common drive shaft 2 and a common lubrication chamber 44. Therefore, compressor 1 may include at least one sub-piston compressor 1. This sub-piston compressor 1 has only one cylinder 6 and one piston 5. The common drive shaft 2 is driven by a drive motor 120, particularly an electric motor 120, via a connecting shaft (not shown). The pressure in the lubrication chamber 44 is sensed and monitored by a pressure sensor 113. The temperature in the lubrication chamber 44 is sensed and monitored by a temperature sensor 119.

[0098] Figure 6The reciprocating compressor 1 is shown in a very simplified and schematic manner. The compressor system 65 includes a container 66 containing the gas to be compressed, a container 67 containing the compressed gas, and a lubricating oil container 81. The gas to be compressed is supplied to the first sub-reciprocating compressor 1 via a suction line 68, and the gas compressed by the first sub-reciprocating compressor 1 is supplied to the inlet valve 19 of the second sub-reciprocating compressor 1 via a connecting pressure line 106. The gas pressure in the connecting pressure line 106 is monitored and sensed by a pressure sensor 112. The gas temperature in the connecting pressure line 106 is monitored and sensed by a temperature sensor 117. A heat exchanger 107 is installed or integrated in the connecting pressure line 106, such that the connecting pressure line 106 is cooled by the gas compressed in the first sub-reciprocating compressor 1 by means of heat dissipation to the surrounding environment. Preferably, a blower (not shown) is installed in the heat exchanger 107 for actively guiding ambient air through the heat exchanger 107. This forms a two-stage reciprocating compressor 1. Gas compressed by the second sub-piston compressor 1 is supplied to container 67 via pressure line 69. The diaphragm external space 62 of each sub-piston compressor 1 is fluidly connected to suction line 68 via leakage return line 70, and thus also fluidly connected to inlet valve 19 and inlet passage 22 of the first sub-piston compressor 1, and simultaneously fluidly connected to container 66. Leakage return line 70 passes through leakage port 103 in cylinder housing 8 (… Figure 5 The piston guide 7 on cylinder 6 is connected to the external space 62 of the diaphragm. The gap seal between the piston guide 7 on cylinder 6 and the piston 5 with piston ring 16 is not completely sealed, allowing the gas to be compressed to reach the external space 62 of the diaphragm. This leakage of the gas to be compressed is then supplied to the suction line 68, i.e., reused, rather than being discharged unused into the surrounding environment. The throttling section 71, as a narrowing point, restricts the volumetric flow of the leaked gas guided through the leak return line 70. The pressure sensor 74, particularly located in the leak return line before the throttling section 71 along the flow direction, monitors the pressure in the leak return line 70 and preferably in the external space 62 of the diaphragm. The temperature sensor 116 monitors the temperature in the leak return line 70. The pressure sensor 72 monitors and senses the temperature in the suction line 68. The temperature sensor 114 monitors and senses the pressure in the suction line 68. The pressure sensor 73 monitors and senses the pressure in the pressure line 69. The temperature sensor 115 monitors and senses the temperature in the pressure line 69. The temperature of the compressed gas in the pressure line 69 should be between 120°C and 150°C, which is achieved in particular by the heat exchanger 107.

[0099] The shut-off mechanism 75, especially the valve 75, can reduce or even completely cut off the flow of compressed gas from container 66 to the first sub-piston compressor 1. The shut-off mechanism 76 (especially the valve 76) in the pressure line 69 can reduce or even completely cut off the flow of compressed gas from the second sub-piston compressor 1 to container 67. The lubrication chamber 44 of the piston compressor 1 is sealed relative to the surrounding environment, and lubricating oil in the lubricating oil container 81 is delivered from the lubricating oil container 81 to the lubrication chamber 44 by the delivery device 79, especially the gear pump 80, through the lubricating oil line 77. A throttling channel 84 with a small flow cross-section is formed from the lubrication chamber 44 to the internal space 61 of each diaphragm. A discharge channel 85 with a significantly larger flow cross-section than the throttling channel 84 is formed from the internal space 61 of each diaphragm to the lubricating oil line 78. The flow cross-section of the discharge channel 85 is, for example, at least 2, 3, or 5 times larger than the flow cross-section of the throttling channel 84. Lubricating oil, guided from the lubrication chamber 44 to the internal spaces 61 of the two diaphragms via two throttling channels 84, is then guided back to the lubricating oil container 81 via two discharge channels 85 and lubricating oil lines 78. This creates a lubricating oil circulation that lubricates and cools not only the mechanical components 40 in the lubrication chamber 44 but also the internal spaces 61 of the diaphragms. As the lubricating oil is guided to the outside of the reciprocating compressor 1 during the lubricating oil circulation, it can also dissipate additional heat to the surrounding environment, for example, through lubricating oil lines 77, 78 and the lubricating oil container 81. Furthermore, an additional heat exchanger 108 (preferably with a blower for ambient air) is installed or integrated into the lubricating oil circulation as an oil cooler. The pressure in the lubricating oil chamber 44 is greater than the ambient pressure, for example, 2 to 5 bar. Due to the discharge valve 83 connecting the lubricating oil container 81 to the surrounding environment, there is an ambient pressure of approximately 1 bar in the lubricating oil container 81. As a safety measure, the pressure in the lubricating oil container 81 is monitored by a pressure sensor 82. Pressure sensors 72, 73, 74, 82, 112, and 113 are connected to the control and / or regulation unit 109 via data lines (not shown). This control and / or regulation unit detects the pressure measured by the pressure sensors 72, 73, 74, 82, 112, and 113 and the temperature measured by the temperature sensors 114, 115, 116, 117, 118, and 119, and can trigger a fault alarm and / or shut down the compressor system 65 based on the measured pressure and / or temperature. Pressure sensors 72, 73, 74, 82, 112, and 113 and / or temperature sensors 114, 115, 116, 117, 118, and 119 may also include, additionally and / or exclusively, a display device for visually displaying the pressure and / or temperature. With the aid of the visual pressure display, the user of the compressor system 65 can also manually monitor whether the pressure is normal. With the aid of the visual temperature display, the user of the compressor system 65 can also manually monitor whether the temperature is normal.The lubrication chamber 44 and the diaphragm interior space 61 are therefore lubricated and cooled by the lubrication system 104 of the compressor system 65.

[0100] The compressor system 65 optionally includes an electrolyzer 110. In the electrolyzer 110, water is electrolyzed into hydrogen and oxygen using an electric current at the anode and cathode. The hydrogen and / or oxygen are introduced into a container 66 containing the gas to be compressed via a pressure line 111 of the electrolyzer 110; that is, the gas to be compressed is the hydrogen and / or oxygen produced in the electrolyzer 110. The electrolyzer 110 is capable of providing the gas to be compressed by the compressor system 65 at a pressure between 15 bar and 50 bar, i.e., without the need to install a compressor or delivery equipment in the pressure line 111 between the electrolyzer 110 and the container 66, the generated gas can be introduced into the container 66 at a pressure of 15 bar to 50 bar. The delivery capacity of the compressor system 65 is controlled and / or regulated by a control and / or regulation unit 109 such that the pressure in the container 66 is between 15 bar and 50 bar. Its main advantage is that the gas already generated in the electrolytic cell 110 within a pressure range of 15 to 50 bar does not need to be strongly compressed to a pressure of, for example, 300 bar in container 67, resulting in lower electric drive power required for the drive motor 120, and less heat generated during compression in compressor 1 because the compression ratio between containers 66 and 67 is smaller. For example, when the pressure in container 66 is 30 bar and the pressure in container 67 is 300 bar, the compression ratio is only 10. If the pressure in container 66 is 3 bar and the pressure in container 67 is 300 bar, the compression ratio will be 100. During the synchronization period when compressor system 65 and compressor 1 are running, the average delivery capacity (mass and / or volume) is substantially the same as and coordinated with the average production capacity (mass and / or volume) of electrolytic cell 110, so that the pressure in container 66 is always between 15 bar and 50 bar during the synchronization period. Control and / or regulation of the average delivery capacity of compressor 1 is preferably achieved by controlling and / or regulating the rotational speed of drive shaft 2. In contrast, the average delivery capacity of compressor 1 during the synchronization period can also be controlled and / or regulated by turning compressor 1 on and off (preferably in a cyclical manner) during the synchronization period.

[0101] The compressor system 65 includes a base frame 95 or base plate element 95 (preferably made of metal) for securing the main components of the compressor system 65. The base frame 95 or base plate element 95 is placed on the ground or foundation. A container 66 containing the gas to be compressed, a container 67 containing the compressed gas under high pressure, a lubricating oil container 81, and a reciprocating compressor 1 are fixed to the base frame 95 or base plate element 95. These main components 1, 66, 67, and 81 are each secured to the common base frame 95 by independent retaining elements 96. The retaining elements 96 are integral parts of the base frame 95.

[0102] exist Figure 5 In the piston compressor 1 shown, which has two pistons 5 and two cylinder housings 8, a fastening fitting 97 is fixed to each cylinder housing 8. A connection hole 99 (not shown) is formed at each end region of the fastening fitting 97. The two fastening fittings 97 are interconnected via a connecting fitting 98. A connection hole 99 (not shown) is formed at each end region of the connecting fitting 98, and these connection holes 99 are aligned with the connection holes 99 on the fastening fittings 97. A connecting device 100, serving as a screw 101 or rivet, is arranged in each of these aligned connection holes 99. Thus, the two cylinder housings 8 are connected to each other in a form-locking and preferably force-locking manner. The housing 45 for the two pistons 5 and the two cylinder housings 8 is designed according to... Figure 5 As shown, it is fixed to the base frame 95 by means of a retaining element 96. Furthermore, a connecting hole 99 is formed in the center of the connecting pipe 98, and another connecting pipe 98 (not shown) is fixed to the base frame 95 or base plate element 95 through this connecting hole 99. This reduces the mechanical load and transmitted force on the cylinder housing 8, flange plate 43, and housing 45, because the two cylinder housings 8 are firmly connected to each other due to the connecting pipe 98, thereby increasing rigidity, and additionally, the connecting pipe 98 (not shown) allows for... Figure 5 The connecting pipe 98 shown is fixed to the base frame 95 or the base plate element 95. Thus, at least one cylinder housing 8 is fixed to the base frame 95 via at least one connecting pipe 98.

[0103] Overall, the compressor system 65 according to the invention has significant advantages. The diaphragm 34, acting as a bellows 34, enables complete and tight isolation between the lubrication chamber 44 containing lubricant and the compression chamber 29. The reciprocating compressor 1 can therefore compress gases requiring high purity, such as hydrogen or oxygen. The delivery capacity of the compressor system 65 and the compressor 1 is coordinated with the production capacity of the electrolyzer 110, allowing the utilization of the pressure of the gas to be compressed generated by the electrolyzer 110. The heat exchanger 107 additionally reduces the temperature of the gas in the pressure lines 69 and the container 67, ensuring that temperatures do not exceed 120°C at the outlet valve 20 and the discharge passage 24, thus preventing damage due to high temperatures.

Claims

1. A reciprocating compressor system (65) for compressing gas, comprising a drive motor for the reciprocating compressor, the reciprocating compressor (1), the reciprocating compressor (1) comprising: - At least one cylinder (6). - At least one piston (5), said at least one piston being supported in each cylinder (6) of each cylinder housing (8), such that each piston (5) and each cylinder (6) define a compression chamber (29) for compressing gas. - At least one mechanical device (40), wherein the at least one piston (5) is mechanically connected to the at least one mechanical device for the reciprocating motion of the at least one piston (5). - At least one lubrication chamber (44), in which at least one mechanical device (40) is at least partially disposed, and in which at least one mechanical device (40) is capable of being lubricated with a lubricant. Its features are, The piston compressor (1) of the piston compressor system (65) includes at least one diaphragm (34), and the at least one diaphragm (34) fluidly and hermetically separates each lubrication chamber (44) from each compression chamber (29).

2. The reciprocating compressor system according to claim 1, Its features are, Each diaphragm (34) divides the cylinder portion space bounded by each cylinder (6), each piston (5) and preferably each flange (43) into, particularly in the radial direction (57), an inner space (61) and an outer space (62) of the diaphragm.

3. The reciprocating compressor system according to claim 2, Its features are, The reciprocating compressor system (65) includes two sub-reciprocating compressors (1) as a two-stage reciprocating compressor system (65). Each of the two sub-reciprocating compressors has a piston (5) and a cylinder (6), and the outlet valve (20) of the first sub-reciprocating compressor (1) is connected to the inlet valve (19) of the second sub-reciprocating compressor (1) via a connecting pressure line (106).

4. The reciprocating compressor system according to claim 3, Its features are, A heat exchanger (107) is installed or integrated in the connecting pressure line (106) for cooling the gas compressed by the first sub-piston compressor (1) that is guided through the connecting pressure line (106).

5. The reciprocating compressor system according to one or more of the preceding claims, Its features are, The reciprocating compressor system (65) includes a lubrication system (104) having at least one lubricating oil line (77, 78), a lubricating oil container (81), and a lubricating oil delivery device (79, 80) for lubricating the at least one mechanical device (40) arranged in the lubrication chamber (44), and preferably, a heat exchanger (108) is installed or integrated in the lubrication system (104) for cooling the lubricating oil guided through the lubricating oil line (77, 78).

6. The reciprocating compressor system according to one or more of the preceding claims, Its features are, The reciprocating compressor system (65) includes a container (66) containing the gas to be compressed and / or a container (67) containing the compressed gas.

7. The reciprocating compressor system according to one or more of the preceding claims, Its features are, The reciprocating compressor system (65) includes at least one pressure sensor (72, 73, 74, 82, 112, 113), and more particularly multiple pressure sensors (72, 73, 74, 82, 112, 113) for sensing pressure.

8. The reciprocating compressor system according to claim 7, Its features are, The pressure of the gas in the suction line (68) and / or pressure line (69) and / or leakage return line (70) and / or connecting pressure line (106) and / or container (66) with the gas to be compressed and / or container (67) with the compressed gas can be sensed by means of the at least one pressure sensor (72, 73, 74, 82, 112, 113).

9. The reciprocating compressor system according to one or more of the preceding claims, Its features are, The reciprocating compressor system (65) includes at least one temperature sensor (114, 115, 116, 117, 118, 119), and more particularly multiple temperature sensors (114, 115, 116, 117, 118, 119) for sensing temperature.

10. The reciprocating compressor system according to claim 9, Its features are, The temperature of the gas in the suction line (68) and / or pressure line (69) and / or leakage return line (70) and / or connecting pressure line (106) and / or container (66) with the gas to be compressed and / or container (67) with the compressed gas can be sensed by means of the at least one temperature sensor (114, 115, 116, 117, 118, 119).

11. The reciprocating compressor system according to one or more of the preceding claims, Its features are, The reciprocating compressor system (65) includes a control and / or regulation unit (109) for controlling and / or regulating the reciprocating compressor system (65).

12. The reciprocating compressor system according to claim 11, Its features are, The pressure sensed by the at least one pressure sensor (72, 73, 74, 82, 112, 113) and / or the temperature sensed by the at least one temperature sensor (114, 115, 116, 117, 118, 119) can be transmitted to the control and / or regulation unit (109), and the reciprocating compressor system (65) can be controlled and / or regulated according to the sensed pressure and / or temperature, especially when the pressure and / or temperature exceeds or falls below at least one limit value for the pressure and / or the temperature, and a fault message can be issued and / or automatic shutdown can be performed.

13. The reciprocating compressor system according to one or more of the preceding claims, Its features are, The reciprocating compressor system (65) includes an electrolytic cell (110) for generating a gas to be compressed, particularly hydrogen, and the gas can be introduced from the electrolytic cell (110) into the container (66) containing the gas to be compressed at a generation pressure, particularly a generation pressure greater than 15 bar.

14. The reciprocating compressor system according to one or more of the preceding claims, Its features are, The delivery capacity of the reciprocating compressor (1) and / or the reciprocating compressor system (65) can be controlled and / or regulated by means of the control and / or regulation unit (109) so that the pressure of the gas to be compressed in the container (66) containing the gas to be compressed is greater than, and especially continuously greater than, a predetermined minimum pressure.

15. The reciprocating compressor system according to claim 13 or 14, Its features are, The delivery capacity of the reciprocating compressor (1) and / or the reciprocating compressor system (65) can be controlled and / or adjusted by means of the control and / or adjustment unit (109) according to the generating capacity of the electrolytic cell (110). In particular, the average delivery capacity of the reciprocating compressor (1) and / or the reciprocating compressor system (65) during the synchronization period substantially corresponds to the average generating capacity of the electrolytic cell (110) during the synchronization period.

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