WO2025190845A1 - Compresseur à piston - Google Patents

Compresseur à piston

Info

Publication number
WO2025190845A1
WO2025190845A1 PCT/EP2025/056419 EP2025056419W WO2025190845A1 WO 2025190845 A1 WO2025190845 A1 WO 2025190845A1 EP 2025056419 W EP2025056419 W EP 2025056419W WO 2025190845 A1 WO2025190845 A1 WO 2025190845A1
Authority
WO
WIPO (PCT)
Prior art keywords
membrane
piston
chamber
channel
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
PCT/EP2025/056419
Other languages
German (de)
English (en)
Inventor
Frederic Strauss
Achim Koehler
Lars Konrad
Marco Lamm
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of WO2025190845A1 publication Critical patent/WO2025190845A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/0404—Details, component parts specially adapted for such pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0207—Lubrication with lubrication control systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F04B39/047—Sealing between piston and carter being provided by a bellow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F04B39/048—Sealing between piston and carter being provided by a diaphragm
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/06—Combinations of two or more pumps

Definitions

  • the present invention relates to a piston compressor according to the preamble of claim 1, a piston compressor system according to the preamble of claim 11 and a method for operating a piston compressor according to the preamble of claim 12.
  • Piston compressors are used for a wide variety of technical applications to compress gases.
  • a piston performs an oscillating motion.
  • the piston is mounted on a cylinder.
  • An inlet valve is used to introduce the gas into the compression chamber, and an outlet valve is used to discharge the gas from the compression chamber.
  • the compression chamber is defined at an end opposite the piston by a surface of a cylinder head.
  • the inlet valve and the outlet valve are generally integrated into the cylinder head.
  • the oscillating motion of the piston is achieved by means of a mechanism.
  • the mechanism is designed, for example, as a crank drive with a crankshaft and a connecting rod, or as a roller shoe with a roller and a drive shaft with at least one cam.
  • the mechanism is arranged in a lubrication chamber.
  • the lubrication chamber is supplied with a lubricant, such as lubricating oil, to lubricate the moving components of the mechanism.
  • a lubricant such as lubricating oil
  • the mechanism is driven, for example, by an electric motor.
  • the piston performs an oscillating movement between a top and bottom dead center, and the difference in the compression volume between the top and bottom dead centers of the piston defines the stroke volume.
  • the dead volume of the compression chamber is the volume of the compression chamber at the top dead center of the piston.
  • EP 0 541 482 B1 discloses a piston compressor for oil-free compression of gases, comprising at least one cylinder and a piston guided therein, which is provided with at least one slotted, so-called captured piston ring accommodated in an annular groove on the piston, which, with its circumferential surface facing away from the inner surface of the cylinder, defines a space of the annular groove acted upon by the pressure of the gas in the compression chamber of the cylinder and which, starting from this circumferential surface, has two radial, mutually parallel boundary surfaces, of which the surface facing the compression chamber extends over a part of the radial ring width, wherein the piston ring is guided in a sliding manner with its two parallel boundary surfaces on corresponding surfaces of the annular groove, wherein the remaining surface of the piston ring facing the compression chamber, starting from the circumferential surface facing the inner surface of the cylinder, is designed as a wedge surface, which extends at an angle of 5 to 15° to a line parallel to the boundary surface facing the compression chamber to to this boundary surface
  • DE 2020699 A1 discloses a plunger compressor with single- or multi-stage piston and/or cylinder designs, wherein at least one bellows is arranged as a diaphragm between each piston and the crankcase.
  • the bellows divides a cylinder chamber, the space beneath the piston, into a wet chamber, the diaphragm interior, and a dry chamber, the diaphragm exterior.
  • Piston compressor for compressing gases, comprising a cylinder, a piston which is mounted in the cylinder, a cylinder chamber and the cylinder chamber is divided by the piston into a first cylinder sub-chamber as a compression chamber for compressing the gas and into a second cylinder sub-chamber, an inlet valve for the compression chamber, an outlet valve for the compression chamber, a mechanism with which the piston is in mechanical operative connection for an oscillating movement of the piston, a lubricating chamber in which the mechanism is at least partially arranged and the mechanism can be lubricated with a lubricant in the lubricating chamber, a diaphragm and with the diaphragm the lubricating chamber is separated from the compression chamber in a fluid-tight manner and the diaphragm arranged in the second cylinder sub-chamber divides the second cylinder sub-chamber into a diaphragm interior and a diaphragm exterior, wherein the piston compressor comprises a pressure compensation device with a channel
  • a second cylinder space is a space between the piston and the mechanism and/or lubrication chamber, so that the second cylinder space is preferably partially delimited by the cylinder.
  • the second cylinder space is at least partially delimited by the cylinder.
  • the piston compressor comprises a connecting channel, and the membrane outer space is fluidly connected to the connecting channel with an inlet channel of the inlet valve, in particular a feed container for the gas to be compressed, in order to equalize the pressure of the fluid in the membrane outer space to the pressure in the inlet channel of the inlet valve.
  • the pressure in the membrane outer space and in the inlet channel of the inlet valve is essentially the same during operation, in particular with a deviation of less than 30%, 20%, or 10%.
  • Volume changes in the membrane outer space due to the movements of the piston can also be compensated for by introducing and/or discharging the gas to be compressed into and/or from the membrane outer space.
  • the gas to be compressed is essentially arranged in the membrane outer space, in particular at least 80%, 90% or 95% as a volume percent and/or mass percent, so that even in the event of leaks in the piston rings between the piston and the piston guide, no substances from the membrane outer space enter the compression chamber that could contaminate the gas to be compressed. If the membrane outer space is filled, for example, with ambient air, the gas to be compressed could be contaminated with the ambient air, for example, as hydrogen, which is harmful, and thus become unusable.
  • a first channel for introducing the compensating fluid into the membrane interior and a second channel for introducing and/or discharging the compensating fluid into and/or out of the membrane interior are formed for the membrane interior.
  • the piston compressor comprises a conveying device and with the conveying device, in particular a pump, the compensating fluid, preferably hydraulic oil, in particular lubricating oil, can be introduced into the membrane interior through the first channel.
  • the compensating fluid preferably hydraulic oil, in particular lubricating oil
  • the compensating fluid can be introduced into the membrane interior through the first channel with the conveying device during operation of the piston compressor, in particular continuously.
  • the piston compressor comprises a collecting tank and the second channel opens into the collecting tank.
  • the compensating fluid preferably hydraulic oil, in particular lubricating oil or lubricant, can be conducted through the second channel.
  • an excess of the compensating fluid introduced into the membrane interior can be discharged from the membrane interior through the second channel and introduced into the collecting container.
  • the piston compressor comprises an actuator and with the actuator the compensating fluid can be discharged and/or introduced into and/or from the collecting container depending on the pressure in the membrane outer space, in order to achieve a substantially identical pressure in the membrane inner space and in the membrane outer space during operation, in particular with a deviation of less than 30%, 20% or 10%.
  • the volume flow of the compensating fluid passed through the second channel with the actuator is thus controlled and/or regulated depending on the pressure in the membrane outer space and/or in the connecting channel and/or in the inlet channel of the inlet valve and/or in the feed container as the storage container for the gas to be compressed, in order to achieve a substantially identical pressure in the membrane inner space and in the membrane outer space, so that a substantially identical pressure exists in the membrane inner space and in the membrane outer space due to the fluid-conducting connection between the collecting container and the membrane interior.
  • the actuator is a valve, in particular a servo valve, which is fluidly connected via a control channel to the inlet channel of the inlet valve, in particular to the supply container of the gas to be compressed, in order to control the actuator with the pressure of the gas to be compressed in the inlet channel of the inlet valve.
  • the actuator is preferably controlled by changing the flow cross-sectional area for the compensating fluid and/or the lubricant, in particular by means of a movement of a control piston.
  • a piston compressor system according to the invention comprising at least two piston compressors, wherein the at least two piston compressors are each designed as a piston compressor as described in this patent application, and the membrane interiors of these at least two piston compressors are fluidly connected to one another via a compensation channel.
  • the volume changes of the compensating fluid, preferably hydraulic oil, in particular lubricating oil, in the at least two membrane interiors due to the stroke movements of the at least two pistons can thus be compensated by directing the compensating fluid from one membrane interior to another.
  • a method for operating a piston compressor for compressing gases comprising the steps of: a cylinder chamber is divided by a piston into a first cylinder sub-chamber as a compression chamber for compressing the gas and into a second cylinder sub-chamber, introducing a gas to be compressed into the compression chamber through an inlet valve, compressing the introduced gas in the compression chamber with a piston by the piston performing a reciprocating movement to reduce the volume of the compression chamber, discharging the gas compressed in the compression chamber from the compression chamber through an outlet valve, with a mechanism that is mechanically connected to the piston, an oscillating movement of the piston is carried out, with lubricant, in particular lubricating oil, in a lubricating chamber in which the mechanism is at least partially arranged, the mechanism is lubricated with the lubricant, the lubricating chamber is separated from the compression chamber in a fluid-tight manner by a membrane, and the second cylinder sub-chamber is divided by the membrane into a membrane interior and a membrane exterior
  • a compensating fluid is introduced into the membrane interior through a first channel for introducing a compensating fluid, in particular continuously and/or steadily, and an excess of the fluid introduced into the membrane interior through the first channel is discharged from the membrane interior through a second channel, in particular continuously and/or steadily, in particular during operation.
  • the volume flow of the fluid conducted through the second channel as a compensating fluid is controlled and/or regulated so that a substantially identical pressure, in particular with a deviation of less than 30%, 20%, or 10%, exists in the membrane interior and the membrane exterior.
  • the compensating fluid conducted through the second channel is introduced into the membrane interior and/or discharged from the membrane interior.
  • the membrane outer space is fluidly connected to an inlet channel of the inlet valve, in particular a feed container of the gas to be compressed, by a connecting channel, so that the pressure of the fluid in the membrane outer space substantially corresponds, in particular with a deviation of less than 30%, 20% or 10%, to the pressure in the inlet channel of the inlet valve by the gas to be compressed being introduced and/or discharged through the connecting channel into the membrane outer space.
  • the volume flow of the compensating fluid passed through the second channel is controlled and/or regulated by controlling and/or regulating the pressure of the compensating fluid in the second channel.
  • the pressure of the compensating fluid in the second channel is controlled and/or regulated so that the pressure in the membrane interior substantially corresponds to the pressure in the membrane exterior, in that the volume flow of the compensating fluid discharged from and/or introduced into the collecting container is controlled and/or regulated by an actuator, in particular a servo valve, as a function of the pressure in the inlet channel of the inlet valve and/or the pressure in the membrane exterior and/or the pressure of the gas to be compressed in the feed container.
  • an actuator in particular a servo valve
  • compensating fluid is passed through a compensating channel from at least one membrane interior into at least one other membrane interior.
  • the sum of the volumes of the membrane interiors of the piston compressors is essentially constant, in particular with a deviation of less than 30%, 20% or 10%.
  • the volume flow of the compensating fluid introduced into and/or discharged from the collecting tank is expediently controlled and/or regulated by controlling and/or regulating the flow cross-sectional area for the compensating fluid in the actuator.
  • the actuator is fluidly connected to an inlet channel of the inlet valve, in particular a supply container of the gas to be compressed, by means of a control channel.
  • the membrane's outer space has no fluid-conducting connection to the ambient air.
  • the membrane's outer space is thus sealed from the environment.
  • the membrane interior is formed radially inside the membrane and the membrane exterior is formed outside the membrane.
  • the number of folds of the bellows is greater than 5, 10, 30, 50, 100 or 200.
  • the method described in this patent application is carried out with a piston compressor and/or piston compressor system described in this patent application.
  • the method described in this patent application can be carried out with the piston compressor and/or piston compressor system described in this patent application.
  • the mechanism, in particular the piston rod, is arranged at least partially in the membrane interior.
  • the membrane interior is fluidly connected to the lubrication chamber.
  • the membrane is designed as a bellows for practical purposes.
  • the diaphragm in particular the bellows, is indirectly or directly attached to the remaining piston compressor in a fluid-tight manner using at least one sealing means and/or fastening means, in particular at least one material connection and/or at least one clamping connection and/or at least one sealing ring and/or at least one fastening ring, in order to prevent the lubricant from penetrating from the lubrication chamber into the at least one compression chamber.
  • the remaining compressor is formed by a cylinder housing and/or a cylinder head and/or a housing for the mechanism and/or a flange plate and/or the piston.
  • the diaphragm in particular the bellows, is indirectly attached to the remaining piston compressor using at least one sealing ring.
  • the sealing ring is preferably made of metal and/or plastic.
  • a sealing ring made of metal and plastic is, for example, attached with one metal side to the remaining piston compressor, preferably the piston, made of metal, using a welded connection, and attached with another side of the plastic sealing ring to the plastic diaphragm using a welded connection.
  • the at least one sealing means and/or the at least one fastening means in particular the at least one sealing ring and/or the at least one fastening ring and/or the at least one material connection, is completely formed in the circumferential direction.
  • the membrane interior in particular with the membrane, is sealed fluid-tight with respect to the membrane exterior, so that no compensating fluid and optional lubricant can be conducted from the membrane interior into the membrane exterior.
  • the second cylinder subspace is divided by the membrane, in particular exclusively, in the radial direction with respect to the longitudinal axis of the cylinder into the membrane interior and the membrane exterior.
  • the membrane in particular the bellows, is arranged at least partially, in particular completely, between the piston and the mechanism in the direction of a longitudinal axis of the cylinder.
  • the membrane in particular the bellows, is substantially cylindrical in shape, in particular in the region within the at least one cylinder.
  • the piston is mechanically connected to the mechanism via a piston rod.
  • the membrane in particular the bellows, is fastened directly or indirectly in a materially bonded manner, in particular with at least one welded connection, as a sealing means and/or fastening means.
  • the piston stroke between the top and bottom dead center of the piston is less than 30%, 10%, 5%, or 3% of the extension of the diaphragm, in particular of the bellows, relevant for the stroke movement in the direction of the longitudinal axis of the cylinder.
  • the mechanical stress on the diaphragm at the extension relevant for the stroke movement is thus low during the piston stroke movement, so that the at least one diaphragm has a long service life.
  • the dead volume of the compression chamber is less than 10%, 5%, 3%, or 2% of the displacement volume of the compression chamber. This advantageously allows the piston compressor to achieve a high pressure of the gas to be compressed with a small piston stroke height.
  • the mechanism with a shaft having at least one cam and a roller.
  • the cylinder conveniently includes a cylinder head.
  • the roller comprises a cylindrical roller with a central bore, and a bearing pin is arranged in the central bore.
  • An annular gap is formed between the cylindrical roller and the bearing pin, and this annular gap is lubricated with the lubricant.
  • the axial ends of the bearing pin are mounted on the roller shoe, for example, with a plain bearing.
  • the material-to-material connection is designed as a welded connection and/or an adhesive connection.
  • the at least one welded joint is produced by laser welding.
  • a welded joint produced by laser welding can be easily distinguished from welded joints produced by other methods based on the structural properties of the welded joint, for example, the diameter of the weld seam and/or the geometry of the weld seam on the components being welded together.
  • the areal extent of the membrane is greater than 5 times, 10 times, 20 times, or 30 times the thickness of the membrane. The areal extent of the membrane is thus significantly greater than the thickness of the membrane.
  • the diaphragm is made of metal and/or plastic.
  • the plastic of the diaphragm is an elastomer.
  • the diaphragm is flexible to accommodate the piston's stroke movements.
  • the diaphragm is made of multiple layers, in particular layers of different materials such as metal and/or plastic.
  • One layer for example, a thin layer of a metal, e.g., aluminum foil, reduces the permeation of substances through the diaphragm.
  • the diaphragm has a very small permeation coefficient, particularly for lubricants.
  • Q P * F * t * Ap/d.
  • Q is the amount of gas or vapor that permeates through a layer of area F and thickness d in time t, when the pressure difference of the permeant in front of and behind the layer is Ap.
  • the gas permeability of the membrane for oxygen in cm 3 /m 2 *d*bar is preferably less than 30, 10, 1, or 0.1.
  • the gas permeability of the membrane for hydrogen in cm 3 /m 2 *d*bar is preferably less than 50, 10, 1, or 0.2.
  • the cylinder has a longitudinal axis.
  • the longitudinal axis of the cylinder corresponds to the direction of movement of the piston mounted in the cylinder.
  • the mechanism comprises a shaft with at least one cam, and the at least one piston is indirectly supported by a roller shoe and a roller on the shaft with the at least one cam.
  • a shaft with at least one cam is expediently an eccentric shaft.
  • the mechanism is formed by a crankshaft and a connecting rod as a piston rod.
  • the piston compressor includes an electric motor to drive the piston compressor.
  • the electric motor drives the drive shaft with cams and/or the crankshaft.
  • the pressure that can be generated by the piston compressor is in the range of 100 bar to 1000 bar.
  • Fig. 1 shows a cross section of a piston compressor for compressing a gas in a first embodiment
  • Fig. 2 shows a section AA according to Fig. 1 of a roller with roller shoe and a drive shaft
  • Fig. 3 shows a cross section of the piston compressor for compressing a gas in a second embodiment
  • Fig. 4 shows a highly simplified cross-section of the piston compressor similar to the second embodiment according to Fig. 3 with a pressure compensation device and
  • Fig. 5 shows a piston compressor system with two piston compressors according to Fig. 4.
  • Fig. 1 shows a cross-section of a piston compressor 1 for compressing gases in a first exemplary embodiment.
  • the piston compressor 1 is used to compress gases, e.g., hydrogen or air, under high pressure.
  • gases e.g., hydrogen or air
  • the pressure that can be generated by the piston compressor 1 is, for example, in a range between 100 and 1000 bar.
  • the piston compressor 1 has a drive shaft 2 with two cams 3, which rotate about a rotational axis 26.
  • the drive shaft 2 is driven by an electric motor (not shown).
  • the rotational axis 26 lies in the plane of the drawing in Fig. 1 and is perpendicular to the plane of the drawing in Fig. 2.
  • a piston 5 is mounted in a cylinder 6 on a piston guide 7, which is formed by a cylinder housing 8.
  • Fully circumferential annular grooves 15 are formed on a radial outer side of the piston 5.
  • a piston ring 16 is arranged in each of the annular grooves 15.
  • a compression chamber 29 is delimited by the cylinder housing 8 with the cylinder head 17 and the piston 5.
  • the end 18 of the cylinder head 17 is the part of the surface of the cylinder head 17 that delimits the compression chamber 29 and does not function and/or is not designed as a cylinder 6.
  • An inlet channel 22 with an inlet valve 19 and an outlet channel 24 with an outlet valve 20 open into the compression chamber 29.
  • the gas flows through the inlet channel 22 with an inlet opening 21 into the compression chamber 29 and through the outlet channel 24 with a
  • the gas flows out of the compression chamber 29 under high pressure through the outlet opening 23.
  • the inlet valve 19, e.g. a check valve is designed such that only gas can flow into the compression chamber 29, and the outlet valve 20, e.g. a check valve, is designed such that only gas can flow out of the compression chamber 29.
  • the volume of the compression chamber 29 is changed due to an oscillating stroke movement of the piston 5.
  • the piston 5 is supported indirectly on the drive shaft 2 by a piston rod 14.
  • a roller shoe 9 with a roller 10 is attached to the end of the piston rod 14.
  • the roller 10 can perform a rotational movement, the rotation axis 25 of which lies in the plane of the drawing according to Fig. 1 and is perpendicular to the plane of the drawing in Fig. 2.
  • the drive shaft 2 with the at least one cam 3 has a shaft rolling surface 4 and the roller 10 has a roller rolling surface 11.
  • the roller running surface 11 of the roller 10 rolls on the shaft rolling surface 4 of the drive shaft 2 at a contact surface 12 with the two cams 3.
  • the roller shoe 9 is mounted as a plain bearing in a roller shoe bearing formed by the cylinder housing 8.
  • the roller shoe 9 and the piston 5 thus jointly perform an oscillating lifting movement.
  • the roller 10 is mounted in the roller shoe 9 with a plain bearing 13.
  • the roller shoe 9 with roller 10 and the drive shaft 2 with cam 3 thus function as a mechanism 40 for generating the oscillating movement of the piston 5.
  • the intake valve 19 and the exhaust valve 20 are installed or integrated in the cylinder head 17.
  • the cylinder head 17 is a component of the cylinder 6 or the cylinder housing 8.
  • the cylinder head 17 is fastened to the cylinder 6 and thus also to the cylinder housing 8 by means of fixing elements 38 as screws 39.
  • a part of the surface 18 of the cylinder head 17 forms a surface 18 or end 18, which delimits the compression chamber 29.
  • the intake valve 19 comprises a valve piston 30, an elastic element 35 as a spring 36 and a support element 37 for the spring 36. In a closed position of the valve piston 30, the valve piston 30 rests on a completely tangential
  • the valve sealing seat 32 runs fluid-tight in the direction of the circumference (Fig. 1).
  • the exhaust valve 20 similarly comprises a valve piston 31 for the exhaust valve 20, the elastic element 35 as the spring 36, and the support element 37 for the spring 36 (Fig. 1).
  • the spring 36 of the exhaust valve 20 rests on a valve sealing seat 33 in the closed position of the exhaust valve 20.
  • the valve sealing seat 32 for the inlet valve 19 and the valve sealing seat 33 for the exhaust valve 20 are formed as correspondingly shaped geometries on the cylinder head 17.
  • the inlet valve 19 and the exhaust valve 20 with the valve pistons 30, 31 are pneumatically actuated.
  • the inlet valve 19 is opened and the outlet valve 20 is closed during the increase in the volume of the compression chamber 29 and vice versa during the stroke movement of the piston 5 during the reduction in the volume of the compression chamber 29.
  • the piston 5 is mounted on the cylinder 6 and performs an oscillating translational movement in the direction of a longitudinal axis 41 of the cylinder 6.
  • the drive shaft 2 with the cam 3 and the roller 10 with the roller shoe 9 form the mechanism 40 for the oscillating movement of the piston 5.
  • the mechanism 40 is arranged in a lubrication chamber 44, and the lubrication chamber 44 is delimited by a partially shown housing 45 for the mechanism 40 and for the lubrication chamber 44.
  • the mechanism 40 is lubricated with a lubricant, for example, lubricating oil or fuel.
  • the lubricant is necessary due to the design of the bearings of the moving components as a plain bearing.
  • the piston compressor 1 compresses, for example, hydrogen for a fuel cell or air or oxygen for breathing in the compression chamber 29.
  • the gas to be compressed must therefore not be contaminated with the lubricant from the lubrication chamber 44, even in very small quantities.
  • the mounting of the radial outer side of the piston 5 with the piston rings 16 on the cylinder 6 as a gap seal does not allow a complete hermetic separation of the lubrication chamber 44 from the compression chamber 29 with the gas to be compressed.
  • the lubrication chamber 44 is hermetically separated and sealed from the compression chamber 29 by a membrane 34 as a bellows 34.
  • the cylinder 6 as the cylinder housing 8 with cylinder
  • the head 17 and the housing 45 for the lubrication chamber 44 delimit a cylinder chamber 49.
  • the cylinder chamber 49 is divided by the piston 5 into a first cylinder sub-chamber 50 as the compression chamber 29 and a second cylinder sub-chamber 51.
  • the diaphragm 34 divides the second cylinder sub-chamber 51 in a fluid-tight manner in the radial direction 70 into a diaphragm interior 52 and a diaphragm exterior 53.
  • a radial direction 70 is perpendicular to the longitudinal axis 41 of the cylinder 6.
  • An axial direction 69 is parallel to the longitudinal axis 41 of the cylinder 6.
  • a circumferential direction 71 or tangential direction 72 is aligned in the circumferential direction or tangential to the piston 5 or the piston rod 14.
  • the bellows 34 as the diaphragm 34 is made of metal and/or plastic. The plastic is in particular an elastomer. The areal extent of the diaphragm 34 is substantially greater than the thickness of the diaphragm 34.
  • An annular flange plate 43 is arranged between the cylinder housing 8 and a housing 45 for the mechanism 40 in the direction of a longitudinal axis 41 of the cylinder 6.
  • a lower end region of the bellows 34, as the diaphragm 34, is fastened between the cylinder housing 8 and the flange plate 43 in a force-fitting manner as a clamped connection using a compressive force.
  • the flange plate 43 is screwed to the housing 45 for the mechanism 40 using fixing elements 38 as screws 39. Due to this pre-tensioning of the lower end region of the diaphragm 34 between the cylinder housing 8 and the housing 45 for the mechanism 40, a force-fitting sealing means 42 is formed. Due to the structural geometry of the piston compressor 1, without the sealing means 42, a lubricant would flow along the diaphragm 34 between the diaphragm 34 and the flange plate 43 and be discharged into the environment.
  • the fastening means 47 is designed as a material-to-material connection, in particular a welded connection and/or an adhesive connection.
  • the fastening means 47 is formed in a tangential direction completely circumferentially between the upper end region of the diaphragm 34 and the piston 5.
  • the diaphragm 34 is additionally formed between the upper end of the piston rod 14 and the piston 5.
  • the diaphragm 34 also comprises a disk- or plate-shaped region with an extension 48 essentially in the direction of the longitudinal axis 41, and this region is also partially arranged between the piston rod 14 and the piston 5.
  • This disk- or plate-shaped region of the diaphragm 34 adapts to the geometry of the underside of the piston 5 due to its deformability and bendability and therefore has curves and/or corners in this area.
  • the relevant extension 48 of the bellows 34 in the direction of the longitudinal axis 41 i.e. the area of the diaphragm 34 which absorbs the stroke movements of the piston 5 between the top and bottom dead center, is significantly greater than the stroke height of the piston 5 than the difference between the top and bottom dead center of the piston 5.
  • the extension 48 is, for example, 10 cm and the stroke height of the piston 5 is 0.9 cm. In Fig. 1, the extension 48 and the stroke height of the piston 5 are not drawn to scale for graphic reasons.
  • the mechanical stress for the deformation of the diaphragm 34 is therefore low because a small deformation occurs per unit length of the extension 48.
  • the diaphragm 34 can thus be designed not only as a bellows 34 in this relevant area with the extension 48, but also as a simple diaphragm without folding. Due to this minimal deformation of the diaphragm 34 in this relevant area with the extension 48, the diaphragm 34 has a service life that corresponds at least to the service life of the piston compressor 1.
  • Fig. 3 shows a second embodiment of the piston compressor 1.
  • the diaphragm 34 in the second embodiment according to Fig. 3 is formed in one piece in a similar manner to the first embodiment, but without the disk-shaped or plate-shaped region of the diaphragm 34 between the essentially cylinder jacket-shaped region of the bellows 34 with an extension 48 essentially in the direction of the longitudinal axis 41 of the cylinder 6.
  • the bellows 34 is fastened in a fluid-tight manner at an upper end indirectly with a sealing ring 46 at the lower end of the piston 5 in a region with the annular grooves 15.
  • the diaphragm 34 is connected in a fluid-tight manner at an upper end with the sealing means 42 as the fastening means 47 to a lower end of the sealing ring 46.
  • the sealing means 42 and the fastening means 47 between the sealing ring 46 and the membrane 34 are formed by a material connection, in particular a welded connection and/or an adhesive connection.
  • the welded connection is produced, for example, by laser welding.
  • an upper end of the sealing ring 46 is fixed to the lower end of the piston 5.
  • the sealing means 42 and the fastening means 47 between the The sealing ring 46 and the piston 5 are formed by a material-to-material connection, in particular a welded connection and/or an adhesive connection.
  • the sealing ring 46 as the fastening ring 46 and the sealing means 42 as well as the fastening means 47 are formed to extend completely around the circumferential direction 71.
  • the material-to-material connection between the seal 46 and the fastening ring 46 thus also seals the diaphragm interior 52 with lubricating oil from the diaphragm exterior 53 in a fluid-tight manner.
  • the piston rod 14 is mounted on a bearing bush with a plain bearing, and due to a gap between the bearing bush and the piston rod 14, lubricating oil flows from the lubricating chamber 44 into the diaphragm interior 52.
  • the bearing bush is fastened to the housing 45.
  • Figs. 1 to 3 Two exemplary embodiments of the piston compressor 1 are shown in Figs. 1 to 3. These exemplary embodiments according to Figs. 1 to 3, which are described above, serve to fundamentally explain the functioning of the piston compressor 1 with the bellows 34 as the diaphragm 34.
  • the exemplary embodiments of the piston compressor 1 shown in Figs. 1 to 3 additionally have a pressure compensation device 54, but the pressure compensation device 54 and, for example, also the channels 55, 56 are not shown in Figs. 1 to 3.
  • the pressure compensation device 54 is shown in a greatly simplified exemplary embodiment of the piston compressor 1 in Figs. 4 and 5.
  • the cylinder 6 delimits a cylinder chamber 49.
  • the cylinder chamber 49 also includes a space between the piston 5 and the mechanism 40 and/or the lubrication chamber 44.
  • the cylinder chamber 49 is divided by the piston 5 into a first cylinder sub-chamber 50 and a first cylinder sub-chamber 51.
  • the first cylinder sub-chamber 50 forms the compression chamber 29.
  • a space outside the piston guide 7, for example a space between the piston 5 and the mechanism 40 and/or the lubrication chamber 44, is also considered to be the cylinder chamber 49 and thus also the first cylinder sub-chamber 50 and the second cylinder sub-chamber 51.
  • the diaphragm 34 divides the second cylinder sub-chamber 51 into a diaphragm interior 52 and a diaphragm exterior 53.
  • the piston rod 14 is arranged within the diaphragm interior 53.
  • the piston rod 14 is part of the mechanism 40 and the lubrication chamber 44 with the mechanism 40 is not completely sealed fluid-tight from the piston rod 14, so that a fluid-conducting connection between the lubrication chamber 44 and the diaphragm interior 52.
  • the diaphragm interior 52 is also supplied with lubricant, in particular lubricating oil.
  • the diaphragm exterior 53 is fluidly connected by a connecting channel 57 from the inlet channel 22 to the inlet channel 14 and thus also fluidly connected to an inlet container 58 containing the gas to be compressed. Due to this fluid-conducting connection to the connecting channel 57, the pressure in the diaphragm exterior 53, as a function of time during operation, essentially corresponds to the pressure in the inlet channel 22 and/or the inlet container 58. In particular, pressure fluctuations occurring in the inlet channel 22 during the opening or closing of the inlet valve 19 and due to the connection of the connecting channel 57 to the inlet channel 22 are transmitted to the diaphragm exterior 53 with a slight time delay.
  • the pressure in the compression chamber 29 essentially corresponds to the pressure in the membrane outer space 53.
  • the pressure in the compression chamber 29 is slightly greater than in the membrane outer space 53.
  • Leakage gas flowing from the compression chamber 29 along the piston rings 16 and the piston guide 7 into the diaphragm outer space 53 can thus escape through the connecting channel 57.
  • the volume of the diaphragm outer space 53 changes during the stroke movement of the piston 5, and also during the stroke movements with the change in the volume of the diaphragm outer space 53, the pressure of the compensating fluid, as the gas to be compressed, in the diaphragm outer space 53 essentially corresponds to the pressure in the inlet channel 22, because the connecting channel 57 is sufficiently dimensioned for the introduction and discharge of the compensating fluid into and from the diaphragm outer space 53.
  • the channels 55, 56 are each connected to a bore in the cylinder housing 8 and a line.
  • the first channel 55 serves to continuously introduce a compensating fluid into the diaphragm interior 52.
  • a conveying device 59 as a pump 60 for example a diaphragm pump, continuously conveys lubricant as lubricating oil as compensating fluid from a collecting container 66 through the first channel 55 into the diaphragm interior 52.
  • the second channel 56 serves to introduce and/or discharge the compensating fluid as the lubricating oil as hydraulic oil into the diaphragm interior 52 and/or from the diaphragm interior 52.
  • the compensating fluid is discharged through the second channel 56 or is introduced into the diaphragm interior 52 through the second channel 56. Due to the continuous introduction of the compensating fluid through the first channel 55, the compensating fluid introduced through the first channel 55 is essentially discharged as excess from the diaphragm interior 52 through the second channel 56, except for leaks and escape of the compensating fluid as the lubricating oil along the piston rod 14 into the lubrication chamber. Due to the change in the volume of the diaphragm interior 52 during the reciprocating movement of the piston 5, compensating fluid can optionally also flow into the diaphragm interior 52 through the second channel 56. However, the piston compressor 1 is designed with a small stroke volume and a large volume of the diaphragm interior 52 due to the large expansion 48 of the bellows 34, so that preferably no introduction through the second channel 56 into the diaphragm interior 52 occurs.
  • the compensating fluid passed through the second channel 56 is introduced into a collecting tank 66 or optionally discharged.
  • the collecting tank 66 has a vent valve 67 and is at ambient pressure of 1 bar.
  • the collecting tank 66 thus functions as a buffer reservoir to equalize the volume in the diaphragm interior 52. Due to the fluid-conducting connection of the diaphragm interior 52 with the lubrication chamber 44, an exchange of the lubricating oil in the diaphragm interior 52 with the lubricating oil in the lubrication chamber 44 also takes place.
  • the volume of the collecting tank 66 is sufficiently dimensioned; for example, the volume of the collecting tank 66 is greater than 2 times, 3 times, 5 times, or 10 times the maximum volume of the diaphragm interior 52 at the top dead center of the piston 5.
  • the liquid Liquid lubricating oil drains off at the bottom of the collecting container 66, and above the liquid lubricating oil is air from the environment, which has been introduced or discharged via the vent valve 67.
  • An actuator 63 in the form of a valve 64, in particular a proportional valve or servo valve, is installed in the second channel 56.
  • a control channel 65 connects the actuator 63 in a fluid-conducting manner to the feed container 58 of the gas to be compressed and thus also in a fluid-conducting manner to the inlet channel 22 of the inlet valve 19 and, due to the connecting channel 57, also in a fluid-conducting manner to the outer space 53 of the diaphragm.
  • the lubricating oil introduced into the collecting container 66 through the second channel 56 is then fed back into the inner space 52 of the diaphragm through the first channel 55 using the conveying device 59, for example a lubricant pump 60.
  • the lubricant delivered by the conveyor device 59 as lubricating oil is also introduced into the lubrication chamber 44.
  • the second channel 56 is fluidically connected to a pressure equalization tank (not shown) via an additional channel with an actuator (structurally analogous to the actuator 63 as a control valve 64).
  • the essentially incompressible hydraulic oil is separated from a compressible gas space by a membrane, so that a pressure can be built up in the second channel 56 with the aid of the pressure equalization tank and the actuator in the additional channel is controlled and/or regulated such that the pressure in the membrane interior 52 essentially corresponds to the pressure in the membrane exterior 53.
  • the actuator 63 has a control piston (not shown) and depending on the position of the control piston, lubricant is introduced into the collecting container 66.
  • the position of the control piston changes the available flow cross-sectional area.
  • the movement of the control piston (not shown) of the actuator 63 is controlled in that the control piston is mechanically connected to a control diaphragm (not shown).
  • the gas to be compressed exerts a compressive force on the control diaphragm through the control channel 65 due to the action of one side of the control diaphragm with the gas to be compressed from the control channel 65.
  • the gas to be compressed from the control channel 65 thus exerts a compressive force on the control piston in a first direction.
  • an elastic element for example a spring, exerts a compressive force on the control piston in a second direction which is opposite to the first direction.
  • the control diaphragm and the elastic element thus form an actuator for moving the control piston as a function of the pressure in the control channel 65.
  • the actuator for moving the control piston can also be embodied by a linear motor, and the linear motor is controlled by the pressure of the gas to be compressed, which pressure is detected by a pressure sensor (not shown), for example at the inlet channel 22 and/or at the connecting channel 57 and/or in the diaphragm outer space 53 and/or at the inlet container 58.
  • the linear motor is controlled and/or regulated by a control and/or regulation unit (not shown) as a function of the pressure detected by the pressure sensor.
  • the excess of the compensating fluid introduced into the membrane interior 52 as the lubricant is introduced into the collecting container 66 depending on the pressure in the membrane interior 52 and the variable volume of the membrane interior 52 and is optionally discharged from the collecting container 66.
  • the control element 63 with the actuator is designed such that the amount of lubricant is passed through the second channel 56 as the compensating fluid such that the pressure in the membrane interior 52 essentially corresponds to the pressure in the membrane exterior 53 as a function of time.
  • a variable volume flow and/or mass flow is thus introduced through the second channel 56 into the collecting container 66 and optionally discharged as a function of time and thus also as a function of the pressure in the control channel 65, ie also as a function of the pressure in the inlet channel 22 and in the membrane outer space 53, so that the pressure in the membrane inner space 52 is substantially identical to the pressure in the membrane outer space 53.
  • Fig. 5 shows a piston compressor system 68 with two piston compressors 1.
  • the two piston compressors 1 each have a membrane interior 52.
  • the two membrane interiors 52 are fluidly connected to one another by a compensation channel 61.
  • the compensation channel 61 is fluidly connected to the second channel 56, analogous to the exemplary embodiment in Fig. 4.
  • the spatial arrangement of the two piston compressors 1 with respect to the drive shaft 2 with two cams 3 as well as the geometry of the drive shaft 2 with the two cams 3 are designed such that the oscillating movement of the two pistons 5 in the two piston compressors 1 is directed in opposite directions.
  • the second piston compressor 1 performs a pressure stroke and vice versa, so that during the oscillating movements of the two piston compressors 1, the sum of the volumes of the membrane interiors 52 of the two piston compressors 1 is essentially constant, in particular with a deviation of less than 30%, 20%, or 10%.
  • the collecting container 66 can therefore be dimensioned smaller in the piston compressor system 45 than in the exemplary embodiment in Fig. 4, because the collecting container 66 essentially does not function as a buffer storage. The change in the volume of the membrane interiors 52 of the two piston compressors 1 during the stroke movements of the two pistons 5 is thus compensated for by directing the compensating fluid as the lubricant from one membrane interior 52 to another membrane interior 52.
  • the pressure compensation device 54 controls and/or regulates the introduction and discharge of the compensating fluid into the membrane interior 52 such that the pressure of the compensating fluid in the membrane interior 52 as the lubricant essentially corresponds to the pressure of the gas to be compressed in the membrane exterior 53.
  • the mechanical stresses on the membrane 34 as the bellows 34 are thus low, so that the bellows 34 can advantageously be dimensioned with a small wall thickness, and lower stresses, in particular residual stresses, occur within the membrane 34.
  • the membrane 34 has a long service life and low manufacturing costs.

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

Abstract

L'invention concerne un compresseur à piston (1) pour comprimer des gaz, le compresseur à piston comprenant : un piston (5) ; une chambre de cylindre (49), la chambre de cylindre (49) étant divisée par le piston (5) en une première sous-chambre de cylindre (50), qui agit comme une chambre de compression (29) pour comprimer le gaz, et une seconde sous-chambre de cylindre (51) ; un mécanisme (40) auquel le piston (5) est relié mécaniquement pour le mouvement oscillant du piston (5) ; une chambre de lubrification (44) dans laquelle le mécanisme (40) est au moins partiellement placé, le mécanisme (40) pouvant être lubrifié avec un lubrifiant dans la chambre de lubrification (44) ; une membrane (34) au moyen de laquelle la chambre de lubrification (44) est isolée fluidiquement de la chambre de compression (29), la membrane (34) placée dans la seconde sous-chambre de cylindre (51) divisant la seconde sous-chambre de cylindre (51) en un intérieur de membrane (52) et un extérieur de membrane (53), le compresseur à piston (1) comprenant un dispositif de compensation de pression (54) ayant un canal (55, 56, 57) pour introduire et/ou évacuer un fluide de compensation dans l'intérieur de membrane (52) et/ou hors de celui-ci en fonction de la pression dans l'extérieur de membrane (53) et/ou inversement et/ou dans l'extérieur de membrane (53) et/ou hors de celui-ci en fonction de la pression dans l'intérieur de membrane (52) afin d'obtenir une pression sensiblement identique dans l'intérieur de membrane (52) et l'extérieur de membrane (53).
PCT/EP2025/056419 2024-03-11 2025-03-10 Compresseur à piston Pending WO2025190845A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102024202267.5A DE102024202267A1 (de) 2024-03-11 2024-03-11 Kolbenkompressor
DE102024202267.5 2024-03-11

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WO2025190845A1 true WO2025190845A1 (fr) 2025-09-18

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2025/056419 Pending WO2025190845A1 (fr) 2024-03-11 2025-03-10 Compresseur à piston

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DE (1) DE102024202267A1 (fr)
WO (1) WO2025190845A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2020699A1 (de) 1970-04-28 1971-11-11 Frankfurter Maschb Ag Vorm Pok Tauchkolbenkompressor
US3620652A (en) * 1968-12-13 1971-11-16 Philips Corp Compressor with rolling diaphragm seal
US5046929A (en) * 1988-04-27 1991-09-10 Digital Equipment Corporation Seal compressor
EP0541482B1 (fr) 1991-11-06 1995-03-29 Maschinenfabrik Sulzer-Burckhardt AG Compresseur à piston pour comprimer un gaz sans lubrification

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3140742A1 (de) * 1981-10-14 1983-04-28 Mannesmann Rexroth GmbH, 8770 Lohr "pumpe, insbesondere zum foerdern einer giftigen fluesigkeit"
DE3901071A1 (de) * 1989-01-16 1990-08-02 Uraca Pumpen Kolbenpumpe
US4976591A (en) * 1990-03-02 1990-12-11 Intevep, S.A. Self lubricating, two stage variable compressor
DE10035625A1 (de) * 2000-07-21 2002-02-28 Siemens Ag Pumpe mit einem Faltenbalg als Abdichtung
DE102016004420A1 (de) * 2016-04-12 2017-10-12 Linde Aktiengesellschaft Verdichter mit Doppelmembran und Leckagering
DE102017202521B4 (de) * 2017-02-16 2022-02-24 Stasskol Gmbh Kompressor mit Bewegungskompensationseinrichtung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3620652A (en) * 1968-12-13 1971-11-16 Philips Corp Compressor with rolling diaphragm seal
DE2020699A1 (de) 1970-04-28 1971-11-11 Frankfurter Maschb Ag Vorm Pok Tauchkolbenkompressor
US5046929A (en) * 1988-04-27 1991-09-10 Digital Equipment Corporation Seal compressor
EP0541482B1 (fr) 1991-11-06 1995-03-29 Maschinenfabrik Sulzer-Burckhardt AG Compresseur à piston pour comprimer un gaz sans lubrification

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