EP3414456B1 - Machine à pistons alternatifs, notamment compresseur à pistons alternatifs à au moins deux étages, dispositif d'alimentation en air comprimé, système d'alimentation en air comprimé et véhicle, notamment voiture particulière équipée d'un dispositif d'alimentation en air comprimé - Google Patents

Machine à pistons alternatifs, notamment compresseur à pistons alternatifs à au moins deux étages, dispositif d'alimentation en air comprimé, système d'alimentation en air comprimé et véhicle, notamment voiture particulière équipée d'un dispositif d'alimentation en air comprimé Download PDF

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Publication number
EP3414456B1
EP3414456B1 EP17700772.1A EP17700772A EP3414456B1 EP 3414456 B1 EP3414456 B1 EP 3414456B1 EP 17700772 A EP17700772 A EP 17700772A EP 3414456 B1 EP3414456 B1 EP 3414456B1
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EP
European Patent Office
Prior art keywords
connecting rod
bearing pin
piston
elastomer
reciprocating
Prior art date
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Active
Application number
EP17700772.1A
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German (de)
English (en)
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EP3414456A1 (fr
Inventor
Klaus Bredbeck
Eugen Kloos
Uwe Stabenow
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ZF CV Systems Europe BV
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Wabco Europe BVBA
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Publication date
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Publication of EP3414456A1 publication Critical patent/EP3414456A1/fr
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Publication of EP3414456B1 publication Critical patent/EP3414456B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/005—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders with two cylinders
    • 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
    • F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
    • 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
    • F04B39/0005—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 adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B39/0005—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 adaptations of pistons
    • F04B39/0022—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 adaptations of pistons piston rods
    • 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
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0044—Pulsation and noise damping means with vibration damping supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/144—Adaptation of piston-rods
    • F04B53/145—Rod shock absorber

Definitions

  • the invention relates to a reciprocating piston machine, in particular a two- or multi-stage piston compressor, according to the preamble of claim 1. Furthermore, the invention relates to a compressed air supply system and a compressed air supply system and a vehicle, in particular a car, with a reciprocating piston machine, in particular with a piston compressor.
  • a compressed air supply system is used in vehicles of all kinds, in particular for supplying compressed air to an air suspension system of a car or a commercial vehicle.
  • Air suspension systems can also include level control devices with which the distance between the vehicle axle and the vehicle body can be adjusted.
  • An air suspension system of a pneumatic compressed air supply system mentioned at the beginning comprises a number of air bellows pneumatically connected to a common line (gallery), which can increase the vehicle body with increasing filling and lower with decreasing filling.
  • a common line such a system is used, for example, in an off-road vehicle and a sport utility vehicle (SUV) or a utility or passenger transport vehicle.
  • SUV sport utility vehicle
  • An air dryer with which the compressed air can be dried. This prevents the accumulation of moisture in the compressed air supply system, which can otherwise lead to valve-damaging ice crystal formation and other undesirable effects in the compressed air supply system and in the pneumatic system at comparatively low temperatures.
  • An air dryer has a desiccant, usually a bed of granules through which the compressed air can flow, so that the bed of granules - at a comparatively high pressure - can absorb moisture contained in the compressed air by adsorption. It has often proven useful to place the dry granules in a dryer cartridge which has a dryer bed for guiding a compressed air flow.
  • a compressed air supply system for use in a pneumatic compressed air supply system with a pneumatic system is operated with compressed air from a compressed air supply, for example at a pressure level of 5 bar to 20 bar.
  • the compressed air is made available to the compressed air supply by means of an air compressor (compressor), in the present case with a reciprocating piston machine, preferably with a two-stage or multi-stage piston compressor.
  • the compressed air supply supplied by the air compressor is pneumatically connected on the one hand to supply the pneumatic system with a compressed air connection and on the other hand pneumatically connected to a ventilation connection.
  • a vent valve arrangement Via a vent valve arrangement, the compressed air supply system and / or the pneumatic system can be vented to the venting connection by releasing air.
  • the reciprocating piston machine in the air compressor (compressor) of the compressed air supply is driven regularly by a drive motor, the drive power of which is passed on to one or more pistons of the preferably two- or multi-stage piston compressor via a crankshaft and one or more connecting rods; One piston each runs sealed in operation in one cylinder.
  • the reciprocating piston machine in the air compressor (compressor) of the compressed air supply can also be driven, for example, with a belt drive.
  • TWIN piston compressors have proven their worth; d. H. two-stage piston compressors, the two pistons of which are driven by two connecting rods assigned to each of them, e.g. are in turn aligned exactly along a cylinder axis, which is preferably aligned exactly parallel and center-symmetrically to cylinder running surfaces in the cylinder displacement for the piston.
  • such or another two-stage or multi-stage compressor can develop increasing operating noises during operation, which - as it turns out - can be caused primarily by structure-borne noise transmission by the connecting rod drive, among other things, in the drive motor of the compressor or its housing. It is desirable to have improved acoustics and a to nevertheless implement a connecting rod drive in a compressor in the form of the aforementioned reciprocating piston machine. In particular, this should also be sufficient for a particularly low noise level in the car sector.
  • DE 10 2004 020 104 discloses approximately a TWIN compressor with symmetrically mounted double pistons for a compressor, with an elongated piston carrier, which has a piston at each end, and with a connecting rod running approximately parallel to the piston carrier, which is rotatably mounted on a bolt of the piston carrier by means of a bearing and at a distance from it by means of a connecting rod bearing on an eccentric of a drive device.
  • the piston carrier contains an intermediate space, which is dimensioned for the freely movable reception of the connecting rod, and in which the connecting rod is freely movable.
  • the invention comes in, the task of which is to provide a reciprocating piston machine, in particular a two-stage or multi-stage piston compressor, preferably a TWIN compressor, and a compressed air supply system for operating a pneumatic system with a compressed air flow, by means of which improved acoustics and, nevertheless, a more reliable one Connecting rod drive can be realized in a piston compressor.
  • This should also be particularly suitable for noise level requirements in the car sector.
  • structure-borne noise emissions of a connecting rod drive in adjacent, radiating components, such as an electric motor, crank drive or similar components of an air compressor (compressor) are to be reduced.
  • the compressed air supply system should be comparatively compact.
  • the object of the invention is also to provide a corresponding compressed air supply system and a vehicle with the compressed air supply system, in particular for an air suspension system.
  • the DE4420861 A1 describes a crank drive device which has two oppositely arranged containers, movable or deformable elements provided in the containers, by means of which the capacities of the containers can be changed while maintaining their airtightness.
  • the elements are connected to each other by a single connector, and the connector is fixed to an eccentric shaft which is provided around a rotating shaft of a motor. Therefore, the rotation of the motor is naturally and smoothly converted into a linear reciprocation of the movable or deformable members by the single connector, and it becomes possible to make the distance between the containers shorter.
  • the WO2004029476A1 relates to a rotary shaft for rotation about an axis, which rotary shaft carries an eccentric, in cross section substantially circular, extending in the radial direction, with the radially outer surface of which an annular housing is connected, which provides a cavity, which is partially through radially inner and radially outer coaxial cylindrical surfaces are defined, the axis of which is offset from the axis of the shaft, the cavity receiving an annular inert mass and the radially inner and the radially outer surfaces of the cavity being opposite the radially inner and radially outer surfaces of the inert mass, whereby there are two pairs of opposing surfaces and one of these pairs forms bearing surfaces which cause relative rotation of the inertial mass and the housing about the axis of the coaxial cylindrical surfaces, and the other of these pairs is spaced apart from one another to define an annular space which receives a displaceable material, the inertial mass and the cavity having a dimension in the radial direction which has a maximum value at a first
  • the object with regard to the reciprocating piston machine is achieved with a reciprocating piston machine, in particular with the two-stage or multi-stage piston compressor, preferably TWIN compressor, of claim 1.
  • the elastomer element can extend along the bearing pin, so that it is located between the first connecting rod and the bearing pin, as well as the bearing pin and the second connecting rod. It can also be in a variation the first variant ("and"), a plurality of elastomer elements, for example two elastomer elements, may be provided, so that one of the elastomer elements is arranged between the first connecting rod and the bearing pin and another of the elastomer elements is arranged between the second connecting rod and the bearing pin is.
  • the elastomer element can extend along the bearing pin, so that it is only between the first connecting rod and the bearing pin.
  • several elastomer elements for example two elastomer elements, can also be provided, so that one of the elastomer elements between the first connecting rod and the bearing pin and another of the elastomer elements also is arranged between the first connecting rod and the bearing pin.
  • the elastomer element can extend along the bearing pin, so that it is only between the second connecting rod and the bearing pin.
  • several elastomer elements for example two elastomer elements, can also be provided, so that one of the elastomer elements between the second connecting rod and the bearing pin and another of the elastomer elements also is arranged between the second connecting rod and the bearing pin.
  • the object relating to the compressed air supply system is achieved with a compressed air supply system of claim 23.
  • the invention also relates to a vehicle, in particular a car vehicle, of claim 24.
  • a compressed air supply system with a pneumatic system and with a compressed air supply system is used to operate the pneumatic system with a compressed air flow, in particular an air suspension system of a vehicle, preferably a car, the main pneumatic line supplying compressed air from an air compressor with a reciprocating piston machine, in particular a two-stage or multi-stage piston compressor, preferably TWIN -Compressor, according to one of claims 1 to 21 and pneumatically connects a compressed air connection to the pneumatic system.
  • a vehicle in particular a car, is provided with a pneumatic system, in particular an air spring system, and a compressed air supply system according to claim 22 for operating the pneumatic system with a compressed air flow.
  • a pneumatic system in particular an air spring system
  • a compressed air supply system according to claim 22 for operating the pneumatic system with a compressed air flow.
  • a cylinder axis is aligned essentially symmetrically to cylinder running surfaces for the pistons in the cylinder displacement of the at least one cylinder.
  • a cylinder axis with cylinder displacements aligned thereon is to be understood in particular to mean that the cylinder running surfaces on the cylinder displacements of a cylinder for the piston are exactly parallel and symmetrical to the cylinder axis.
  • the eccentric crankshaft journal - in particular also the drive shaft coupling - is preferably aligned parallel to a shaft axis aligned perpendicular to the cylinder axis; d. H. that the crankshaft journal and / or a connecting rod bearing surrounding it is perpendicular to the cylinder axis.
  • the invention is based on the consideration that, depending on the dynamics and pressure load required for an air compressor, a two- or multi-stage compressor, in particular a two-stage TWIN compressor or another reciprocating piston machine, is increasingly developing operating noises during operation, which - as it turns out - mainly through A structure-borne noise transmission can be caused by the connecting rod drive in the compressor drive motor.
  • the invention has now recognized that by at least one elastomer element for supporting at least one of the connecting rods opposite the bearing pin, i. H. of the first and / or second connecting rod compared to the bearing pin, improved acoustics can be realized in a compressor; also with a low noise level that is particularly acceptable for a car sector.
  • the concept of the present invention is also preferred for a commercial vehicle or passenger transport vehicle, especially if the compressed air supply system is designed for comparatively high pressure amplitudes.
  • previous solutions - shown in simplified form - provide ball bearings or plain bearings for mounting between the first connecting rod and the bearing pin, and between the second connecting rod and the bearing pin.
  • the invention has also recognized that a deflection of the first and second connecting rods with respect to one another or the longitudinal axes running along the connecting rods is slight, i. H. is below 20 °, in particular below 14 °.
  • the invention provides for connecting rod bearings, in particular rolling or sliding bearings, to be replaced by elastomer elements. Elastomer elements are backlash-free connecting elements with good damping properties. The noise development can hereby be significantly reduced. Storage with elastomer elements is possible due to the low deflection.
  • the invention enables an optimization of the acoustic behavior, in particular of a two-stage TWIN compressor, since the design criteria of the elastomer element can be freely parameterized.
  • the selection of the material, ie the hardness, and the geometry of the elastomer element, ie the diameter, the width, the wall thickness and / or similar parameters can be freely parameterized. This can lead, among other things, to a reduction in the development of noise, in particular the initial level, the level spread and the level increase over the operating period.
  • the free parameterization enables the elastomer element to always be adapted to the existing operating conditions.
  • the compressor acoustics is independent of the tolerance, since the storage on the Elastomer element has no bearing play dependency. Furthermore, the number of components can be reduced, since plain or roller bearings and their damping elements can be omitted. This also simplifies assembly, among other things. There is also no relative movement from adjacent surfaces, ie from sliding surfaces or rolling surfaces to a connecting rod inner surface or a bearing pin surface.
  • the elastomer element or a plurality of elastomer elements can also replace conventional slide or roller bearings, since these are compatible with the conventional connecting rod designs or the conventional connecting rod construction.
  • the invention also enables a play-free connection to be made between two connecting rods.
  • the power transmission between the compressor and crankshaft can also be improved due to the good damping properties of the elastomer element.
  • the elastomer element enables a relative movement between the two connecting rods of at least approximately 14 ° or +/- 7 °. Power transmission up to 1500 N and a maximum speed of approx. 0.20 m / s is also possible.
  • the reciprocating piston machine can be designed such that it is essentially maintenance-free and, for example, has a fatigue strength for approximately 1000 operating hours. For example, no initial and / or relubrication is necessary, as is the case for plain and / or roller bearings.
  • the reciprocating machine described here in the context of a compressed air supply system for use in a pneumatic compressed air supply system can in principle also be used in other areas of application, in particular where - as in the aforementioned compressed air supply systems - comparatively high and high pressure amplitudes are to be achieved.
  • the reciprocating piston machine can be used in a compressor for a car chassis control.
  • the reciprocating piston machine, in particular the piston compressor can be used in a multi-stage compressor with at least two compressor stages, which operate according to the trailing piston principle.
  • a connecting rod can be rigid without a spherical bearing or also articulated, in particular with a spherical bearing.
  • a piston can be held on the connecting rod, held or can be formed in one piece on the connecting rod.
  • the piston is preferably molded onto the connecting rod, firmly connected or held by means of a piston holder.
  • the first connecting rod can be moved directly by means of the eccentric crankshaft journal and the second connecting rod can be moved indirectly by means of the eccentric crankshaft journal, in particular directly by means of the first connecting rod.
  • the second connecting rod (as a drag connecting rod) can preferably be moved from the first connecting rod (as a drive connecting rod), the first connecting rod being moved directly by the crankshaft journal.
  • the at least one elastomer element is preferably a rubber element or is introduced as a rubber coating between the bearing pin and the connecting rod.
  • the rubber coating on the bolt surface and / or on the inner surface of the connecting rod introduced, for example vulcanized, injected or the like.
  • the elastomer element can be an applied layer, in particular an injected or vulcanized layer.
  • the applied layer is preferably applied to a bearing pin surface, an inner connecting rod surface of the first connecting rod and / or an inner connecting rod surface of the second connecting rod.
  • the elastomer element in particular in the form of an applied layer, serves to support rotary movements of the connecting rods around the bearing pin and to produce a spring effect.
  • the bearing connection between the bearing pin and the first or second connecting rod is realized by the elastomer element or the elastomer layer, so that a further bearing element, such as a ball bearing, roller bearing, plain bearing, plain bearing shell or the like, is dispensed with.
  • the elastomer element has a hardness that depends on the material.
  • a material, such as rubber, is preferably used for the elastomer element, which has good damping properties in order to enable noise reduction.
  • a rubber mixture can be used to adapt the properties of the rubber as a material for the elastomer element.
  • the properties of the elastomer element can be adjusted via the geometry of the elastomer element. For example, a shape, in particular the width, height, length, diameter and wall thickness, can be adapted in accordance with the respective operating conditions.
  • the elastomer element can be a separate part.
  • the elastomer element is preferably inserted between the bearing pin and the connecting rod or is clamped exclusively between the bearing pin and the connecting rod.
  • the elastomer element can extend along the longitudinal axis of the bearing pin, so that the elastomer element is arranged between the bearing pin and the first connecting rod and the second connecting rod.
  • a plurality of elastomer elements can also be arranged, each of which is arranged between the bearing pin and the first connecting rod or the bearing pin and the second connecting rod.
  • two elastomer elements can also be arranged between the bearing pin and the first connecting rod and / or two elastomer elements between the bearing pin and the second connecting rod.
  • only one elastomer element can also be arranged between the first connecting rod and the bearing pin and / or only one elastomer element between the second connecting rod and the bearing pin.
  • the elastomer element preferably serves to enable the connecting rods to rotate around the bearing pin and to produce a damping effect.
  • the bearing connection between the bearing pin and the first or second connecting rod is through the Elastomer element realized, so that a further bearing element, such as a ball bearing, roller bearing, slide bearing or the like is dispensed with.
  • the elastomer element alone thus serves to absorb or compensate for the rotary movement and can produce a damping effect.
  • the elastomer element is ring-shaped, bush-shaped or sleeve-shaped.
  • the shape of the elastomer element can also be adapted to the shapes of the components adjacent to the elastomer element and / or supported by the elastomer element.
  • the elastomer element can also be hollow cylindrical.
  • the wall thickness of the elastomer element is preferably constant. In one development, the wall thickness changes along a longitudinal axis of the elastomer element, in particular the wall thickness increases or decreases.
  • the wall thickness and the change in the wall thickness are preferably adapted to the operating conditions and in particular to the components in contact with the elastomer element, such as, for example, the connecting rod and the bearing pin.
  • the elastomer element is plate-shaped, in particular a knob or ring segment.
  • the elastomer element can have one, two or more ring segments, for example elastomer ring segments, in particular rubber ring segments.
  • the ring segments are preferably arranged opposite one another and in particular around the bearing pin.
  • the parameters of the ring segments can also be adapted according to the operating conditions, in particular their geometry and the material used can be selected according to the operating conditions.
  • the use of ring segments enables a reduction in the restoring torque.
  • the reduction from an elastomer element surrounding the circumference to elastomer ring segments leads to a reduction in material consumption and to smaller elements. As a result, load transmission is only necessary in two ring segments.
  • Platelet-shaped elastomer elements i.e. Elastomer plates can be arranged around the bearing pin, for example 180 elastomer plates can be arranged around the bearing pin, so that each elastomer plate covers 2 ° of the bearing pin surface.
  • the elastomer element is connected to a metal carrier or in contact.
  • the metal carrier can be, for example, a metal bushing, a metal sleeve, a metal ring or several metal plates.
  • the elastomer element can, for example, be clamped into the metal carrier, glued on, vulcanized or injected.
  • the metal carrier preferably encloses the elastomer element.
  • the elastomer element can also be clamped, glued, vulcanized or sprayed on, for example around the metal carrier. In this case, the elastomer element preferably encloses the metal carrier.
  • An elastomer element can also be arranged between two metal carriers, for example in a sandwich-like manner.
  • a metal carrier can also be arranged between two elastomer elements, for example in a sandwich-like manner.
  • the elastomer elements can be sprayed onto the metal carrier and injected into it, or they can also be separate parts, for example elastomer rings, which can be inserted into it or placed around it.
  • the elastomer element has at least two elastomer rings.
  • the elastomer rings are preferably arranged in parallel and at a distance from one another around the bearing pin.
  • the elastomer rings can both be arranged between the first connecting rod and the bearing pin or the second connecting rod and the bearing pin.
  • one of the elastomer rings can also be arranged between the first connecting rod and the bearing pin and the second connecting rod and the bearing pin.
  • three elastomer rings can also be arranged. In this case, for example, two elastomer rings can be arranged between the second connecting rod and the bearing pin and an elastomer ring between the first connecting rod and the bearing pin.
  • Elastomer platelets or segmented elastomer rings can also be arranged between the connecting rods and the bearing pin.
  • the elastomer element has at least one elastomer plate which is only arranged on one side, in particular on a bearing pin top.
  • the elastomer element can have at least two elastomer platelets located opposite one another and arranged on the upper side of the bearing pin and a lower side of the bearing pin. The two elastomer plates arranged opposite one another serve to support the bearing bolts and at least one of the connecting rods.
  • the at least one elastomer element is arranged between an inner and an outer metal carrier.
  • the inner metal carrier is preferably connected to the bearing pin and the outer metal carrier is connected to at least one of the connecting rods.
  • the term connected here means, inter alia, clamped, clamped, clamped, pressed, molded, injected, vulcanized, applied, inserted, attached and introduced.
  • the connection can, for example, be such that an elastomer element is clamped between the inner and the outer metal carrier, for example in the form of an elastomer ring.
  • the elastomer element is particularly preferably firmly and directly connected to the inner and outer metal carrier, for example by introducing the elastomer element as a coating or layer onto an outer surface of the inner metal carrier and an inner surface of the outer metal carrier, e.g. B. is injected, vulcanized or introduced by one or more other methods.
  • the inner metal carrier with the bearing pin and the outer metal carrier with at least one of the connecting rods can be firmly and directly connected, for example by clamping the metal carrier under tension.
  • a plurality of metal supports can also be arranged one inside the other or, for example, a metal support between two elastomer elements. An arrangement of several alternating layers of metal supports and elastomer elements is also possible.
  • the elastomer elements can have different material properties in order to adapt the connecting rod bearing to the operating conditions.
  • the at least one elastomer element is arranged between an inner metal carrier and at least one of the connecting rods.
  • the inner metal carrier is preferably connected to the bearing pin and the elastomer element to at least one of the connecting rods.
  • the connection can, for example, be such that the elastomer element is clamped, for example in the form of an elastomer ring, between the inner metal carrier and at least one of the connecting rods.
  • the elastomer element is particularly preferably firmly and directly connected to the inner metal carrier and to at least one of the connecting rods, for example by introducing the elastomer element as a coating or layer onto an outer surface of the inner metal carrier and a connecting rod surface of at least one of the connecting rods, e.g. . B. is injected, vulcanized or introduced by one or more other methods.
  • the at least one elastomer element is arranged between the bearing pin and an outer metal carrier.
  • the elastomer element is preferably connected to the bearing pin and the outer metal carrier to at least one of the connecting rods.
  • the connection can, for example, be such that the elastomer element is clamped, for example in the form of an elastomer ring, between the bearing pin and the outer metal carrier is.
  • the elastomer element is particularly preferably firmly and directly connected to the bearing pin and the outer metal carrier, for example by introducing the elastomer element as a coating or layer onto a bearing pin surface of the bearing pin and an inner surface of the outer metal carrier, e.g. B. is injected, vulcanized or introduced by one or more other methods.
  • the elastomer element is designed as a rubber element and is injected between two steel sleeves. This component is preferably pressed into a connecting rod and / or pressed onto the bearing pin.
  • a further development provides for the elastomer element to be designed as a rubber element and to be sprayed onto a steel bushing. This component is preferably pressed into a connecting rod and / or glued.
  • the elastomer element can be designed as a rubber element and sprayed onto a steel bushing and / or injected into a connecting rod.
  • the elastomer element can also be mounted as a rubber element as a solid rubber part, for example pressed in and / or glued.
  • the elastomer element can be designed as a rubber element which is arranged at least in two parts on the circumference of the connecting rod.
  • the at least one elastomer element has at least two ring segments which are separate from one another. Of the at least two separate ring segments, at least one first ring segment is arranged on a bearing pin upper side between bearing pin and connecting rod and at least one second ring segment is arranged on a lower side of the bearing pin between bearing pin and connecting rod.
  • the separated ring segments of the elastomer element can, for example, enclose at most a quarter of the circumference on the top of the bearing pin and at most a quarter of the circumference on the bottom of the bearing pin, so that at least half of the circumference of the bearing pin is free of the elastomer element.
  • a maximum deflection angle of the deflection of the connecting rods between respective longitudinal axes of the connecting rods is at most 14 °, for example at most 10 ° and preferably approximately 7 °.
  • the first connecting rod is mounted directly on the crankshaft journal by means of a connecting rod bearing the first piston is held on the first connecting rod by means of a piston holder.
  • the second piston can be molded onto the second connecting rod.
  • a connecting rod with an integrally formed piston and a drive connecting rod with a piston held thereon are preferably implemented.
  • a piston integrally formed on the connecting rod or a piston held on the connecting rod can be realized as required.
  • an integrally formed piston has proven particularly useful.
  • a drive connecting rod with a piston held thereon has proven particularly useful.
  • the connecting rod bearing can be implemented as a ring ball bearing, which is preferably formed in the form of a ring ball bearing on the crankshaft journal, that is to say directly on the crankshaft journal.
  • the connecting rod bearing can also be a ring ball bearing and / or a spherical bearing.
  • a reciprocating piston machine has proven particularly useful as a piston compressor with a two-stage compressor with a first and second compressor stage for the provision of compressed air for a compressed air supply system.
  • the two-stage compressor can be designed as a TWIN compressor.
  • the piston compressor can also be designed as a two-cylinder or multi-cylinder compressor.
  • first connecting rod of the second, in particular high-pressure, compressor stage is formed, the first connecting rod being mounted directly on the crankshaft journal by means of a connecting rod bearing.
  • the second connecting rod of the first, in particular low-pressure, compressor stage is formed.
  • One aspect of the invention relates to the use of the reciprocating piston machine, in particular the piston compressor in a compressor or air compressor for a car chassis control.
  • FIG. 1 shows in detail D an air compressor with a reciprocating piston machine in the form of a two-stage piston compressor 400 with a first compressor stage 401 and a second compressor stage 402, which is driven by a motor 500 as the drive motor M.
  • Such a piston compressor 400 is preferably used for pneumatic compressed air supply systems 1000 like one in FIG. 1 is shown.
  • FIG. 1 shows a pneumatic circuit diagram of a pneumatic compressed air supply system 1000 with a compressed air supply system 1001 with an air dryer arrangement 100 and a pneumatic system 1002 in the form of an air spring system.
  • the compressed air supply system 1001 is used to operate the pneumatic system 1002.
  • the compressed air supply system 1001 has a aforementioned compressed air supply 1 and a compressed air connection 2 to the pneumatic system 1002.
  • the compressed air supply 1 is formed with an air supply 0, an air filter 0.1 arranged upstream of the air supply 0 and an air compressor arranged downstream of the air supply 0 via the air supply line 270 and driven by the motor 500.
  • the air compressor is formed here as an example of a reciprocating piston machine in the form of a double air compressor, namely a two-stage piston compressor 400 with a first compressor stage 401 and a second compressor stage 402 and a connection of the compressed air supply 1 (not shown).
  • connection of the compressed air supply 1 in the main pneumatic line 200 is followed by the connection of the drying container 101 of the air dryer arrangement 100 to the first part 201 of the main pneumatic line.
  • the air dryer of the air dryer arrangement 100 is also pneumatically connected by means of the second part 202 of the main pneumatic line for guiding a compressed air flow DL to the pneumatic system 1002.
  • a branch line 230 branches off from the main pneumatic line 200 on the compressed air supply line 1 and connects to a ventilation line 240 for ventilation to a ventilation filter 3.1 connected downstream of the ventilation connection 3; the ventilation is connected to the ventilation line 240 by means of a further branch connection 241 and a connection section 242, and also to a further ventilation line 260 via the branch connection 261.
  • the main pneumatic line 200 thus pneumatically connects the compressed air supply 1 and the compressed air connection 2, the air dryer arrangement 100 being arranged in the main pneumatic line 200 and furthermore an unlockable check valve 311 and a first throttle 331 being arranged in the direction of the compressed air connection 2.
  • the pneumatically unlockable check valve 311 is part of the directional control valve arrangement 310 which, in addition to the unlockable check valve 311, has a controllable vent valve 312 in series connection with a second throttle 332 in the vent line 230.
  • the pneumatically unlockable check valve 311 is also arranged in a series connection with the first throttle 331 in the main pneumatic line 200, the main pneumatic line 200 being the only pneumatic line of the first pneumatic connection which continues to the pneumatic system 1002 with a further pneumatic line 600.
  • the series arrangement of the first throttle 331 and the pneumatically unlockable check valve 311 is thus arranged between the air dryer arrangement 100 and the compressed air connection 2 to the pneumatic system 1002 in the main pneumatic line 200.
  • the compressed air supply system 1001 has a second pneumatic connection which is pneumatically connected to the main pneumatic line 200 and the ventilation connection 3 and further filter 3.1 and / or silencer; namely the aforementioned ventilation line 230.
  • the nominal diameter of the second throttle 332 is above the nominal diameter of the first throttle 331.
  • vent valve 312 arranged in the second pneumatic connection is formed as a 2/2 valve in the vent line 230, which is separate from the pneumatically unlockable check valve 311.
  • the controllable vent valve 312 is thus, as an indirectly switched relay valve, part of a valve arrangement 300 with a control valve 320 in the form of a 3/2-way solenoid valve.
  • the control valve 320 can be electrically controlled to the coil 322 of the control valve 320 with an electrical control signal, which can be transmitted via an electrical control line 321, in the form of a voltage and / or current signal. With this electrical actuation, the control valve 320 can be operated from the in FIG. 1 shown in the currentless manner, the position interrupting the pneumatic control line 250 is transferred to a pneumatically open position in which the pressure derived from the main pneumatic line 200 is transmitted via the pneumatic control line 250 for the pneumatic control of the controllable vent valve 312 as a relay valve.
  • controllable vent valve 312 is additionally provided with a pressure limiter 313.
  • the pressure limiter 313 engages via a pneumatic control line upstream of the vent valve 312 - specifically between the second throttle 332 and the vent valve 312 - a pressure which, when a threshold pressure is exceeded, lifts the piston 314 of the vent valve 312 against the force of an adjustable spring 315 from the valve seat - that is to say brings the controllable vent valve 312 into the open position even without actuation via the control valve 320. In this way, it is avoided that an unintentionally excessive pressure arises in the pneumatic system 1000.
  • the control valve 320 separates the control line 250 and is pneumatically connected to the ventilation line 240 via a further ventilation line 260 for ventilation via the ventilation connection 3.
  • a line section 251 of the control line 250 which is located between the vent valve 312 and the control valve 320, is in FIG FIG. 1 shown closed position of the control valve 320 connected to the further vent line 260 between the control valve 320 and the vent port 3.
  • the further ventilation line 260 connects to the ventilation line 230 and the further ventilation line 240 in the further branch connection 261. They are thus brought together in a section of a ventilation line 240 which lies between the further branch connection 261 and the ventilation connection 3.
  • the vent valve 312 can thus be opened by pressurizing the piston 314 via the control valve 320.
  • the piston 314 is in the present case designed as a double piston, so that it is provided with particular advantage that the transfer of the control valve 320 into the — in the above-opened state not only leads to the opening of the vent valve 312, but also to the unlockable check valve 311.
  • the control valve 320 of the solenoid valve arrangement 300 serves to control the vent valve 312 and the check valve 311, which is provided separately from the check valve 311.
  • This further operating position which can be assumed by the compressed air supply system 1001, can be used during operation to vent the pneumatic system 1002 and at the same time to regenerate the air dryer arrangement 100.
  • the operating position of the compressed air supply system 1001 shown serves, when the check valve 311 flows through in the forward direction, primarily for filling the pneumatic system 1002 via the main pneumatic line 200 and the further pneumatic line 600.
  • the pneumatic system 1002 of the FIG. 1 in the form of an air suspension system in this case has a number of four so-called bellows 1011, 1012, 1013, 1014, which are each assigned to a wheel of a car vehicle, not shown, and form an air suspension of the vehicle.
  • the air suspension system has a memory 1015 for storing quickly available compressed air for the bellows 1011, 1012, 1013, 1014.
  • Those bellows 1011 to 1014 are each arranged upstream of a spring branch line 601, 602, 603, 604 from a gallery 610 a solenoid valve 1111, 1112, 1113, 1114, which in each case acts as a level control valve for opening or closing a bellows 1011 to 1014 Air spring is used.
  • the solenoid valves 1111 to 1114 in the spring branch lines 601 to 604 are designed as 2/2-way valves in a valve block 1110.
  • a memory 1015 is preceded by a solenoid valve 1115 in the form of a further 2/2-way valve as a storage valve in a storage branch line 605.
  • the solenoid valves 1011 to 1015 are connected by means of the spring and storage branch lines 601 to 604 and 605 to a common collecting line, namely the aforementioned gallery 610 and then to the further pneumatic line 600.
  • the gallery 610 is thus pneumatically connected to the compressed air connection 2 of the compressed air supply system 1001 via the pneumatic line 600.
  • the solenoid valves 1111 to 1115 are arranged in a valve block 1010 with the five valves.
  • the solenoid valves are in FIG.
  • the solenoid valves 1111 to 1115 are formed as de-energized closed solenoid valves.
  • Other modified embodiments, not shown here, can implement a different arrangement of the solenoid valves - fewer solenoid valves can also be used within the valve block 1010.
  • the solenoid valves 1111 to 1114 upstream of the bellows 1011 to 1014 and / or the solenoid valve 1115 upstream of the accumulator 1015 are brought into an open position.
  • bellows 1011 to 1015 can be cross-connected (e.g. in the off-road mode of a vehicle), bellows 1011 to 1015 can be filled from memory 1015 or pressure measured in pneumatic system 1002 via gallery 610, without the compressed air supply system 1001 being pressurized.
  • the air dryer arrangement 100 is protected against unnecessary exposure to compressed air due to the check valve 311 blocked by the compressed air connection 2 to the compressed air supply 1 and the closed control valve 320.
  • pressurizing the air dryer arrangement 100 with compressed air is not advantageous in every operating position of the pneumatic system 1002. Rather, it is advantageous for an effective and rapid regeneration of the air dryer system 100 if this is carried out exclusively in the event of a venting of the pneumatic system 1002 from the compressed air connection 2 to the compressed air supply 1 with the check valve 311 unlocked.
  • the control valve 320 is brought into an open switching position, so that both the vent valve 312 opens and the check valve 311 is unlocked.
  • the pneumatic system 1002 can be vented via the first throttle 331, the unlocked check valve 311 with regeneration of the air dryer arrangement 100, and then via the second throttle 332 and the opened vent valve 312 for venting via the vent connection 3.
  • a control piston 314 pneumatically controllable by the control valve 320 is provided as a double relay piston with a relay venting body 314.1 of the venting valve and a relay unlocking body 314.2 for the unlockable double check valve of the present Unlocking the check valve 311 and simultaneously actuating the vent valve 312 via the two coupled actuating elements - namely via the relay unlocking body 314.2 and the relay vent body 314.1 - which can be designed as a one-piece double relay body or in a modification as a separate body.
  • the aforementioned actuation elements of the double relay piston can be formed as one-piece areas of a double relay piston.
  • FIG. 2nd now explains the details of the concept of the invention using the example of a reciprocating piston machine specifically in the form of the two-stage piston compressor 400 of the FIG. 1 .
  • FIG. 2nd shows this a reciprocating piston machine in the form of a double compressor according to the detail D of FIG. 1 , namely a TWIN compressor designed as a two-stage piston compressor 400 with a first compressor stage 401 and a second compressor stage 402 as well as with a motor 500, which is coupled as a drive motor M with a drive shaft 501 to a crankshaft 430 of the piston compressor 400.
  • a TWIN compressor designed as a two-stage piston compressor 400 with a first compressor stage 401 and a second compressor stage 402 as well as with a motor 500, which is coupled as a drive motor M with a drive shaft 501 to a crankshaft 430 of the piston compressor 400.
  • the crankshaft 430 has a drive shaft coupling 431, which serves as a receptacle for the drive shaft 501 of the drive motor M.
  • the crankshaft 430 is rotatably mounted on the outside of the drive shaft coupling 431 in a bearing 502, which in the present case is designed as a ring ball bearing.
  • the bearing 502 in turn is held on the motor housing 503 by a corresponding holding mechanism.
  • the crankshaft 430 which can be driven during operation by means of the drive motor M is designed via the drive shaft coupling 431 for coupling the drive shaft 501 of the drive motor 500 for driving the crankshaft 430.
  • the crankshaft 430 also has an eccentric crankshaft journal 432, which is formed eccentrically to the axis A on the crankshaft 430 and extends along an eccentric axis, which is referred to here as the shaft axis E.
  • the eccentric crankshaft journal 432 is designed to drive a first connecting rod P1 directly and a second connecting rod P2 indirectly.
  • the eccentric crankshaft journal 432 is designed by means of a first connecting rod bearing L1 for direct mounting and for direct driving of the first connecting rod P1.
  • the second connecting rod P2 is in turn movably mounted on the first connecting rod P1 functioning as the drive connecting rod P1, ie as a drag connecting rod, via a bearing pin L2B partially enclosed by an elastomer element L2 in the form of three elastomer rings L2E1, L2E2, L2E3.
  • the first connecting rod bearing L1 is designed as a ring ball bearing.
  • the elastomer element L2 in the form of the elastomer rings L2E1, L2E2, L2E3 completely encloses the bearing pin L2B in this exemplary embodiment.
  • the elastomer element L2 can, for example, in the form of elastomer ring segments L2Ea and L2Eb (cf. FIG. 6 ) only partially surround the bearing pin L2B, for example on the top and bottom of the bearing pin L2B.
  • the elastomer element extends L2 in the form of elastomer ring segments L2Ea and L2Eb over approximately the upper quarter of the circumference and the lower quarter of the circumference of the bearing pin L2B, so that the lateral quarters of the bearing pin L2B are not in contact with the elastomer element L2.
  • the elastomer element L2 enables the connecting rods P1 and P2 to be supported without play.
  • the elastomer element L2 also has great damping properties, so that the elastomer element L2 enables noise reduction.
  • the first piston K1 is inserted as a separate part into the head end of the first connecting rod P1 by means of a piston holder K11 and held there.
  • the second piston K2 is integrally and integrally formed on the head end K22 of the second connecting rod P2 - that is, along a cylinder axis Z distally opposite the first piston K1.
  • the second connecting rod P2 is a one-piece, approximately ring-like component - as in FIG. 2nd visible - suspended on the elastomer element L2 so that it can rotate.
  • an eccentric rotary movement of the crankshaft journal 432 can be achieved while the compressor 400 is operating while the crankshaft 430 is rotating, so that the first and second pistons K1, K2 are moved back and forth to compress compressed air in the corresponding second and first compressor stage 402, 401 are each moved.
  • the second piston K2 of the first compressor stage 401 moves in a cylinder displacement 411 of the first cylinder 410 in the first (low pressure) compressor stage 401.
  • the first piston K1 moves in a cylinder displacement 421 of a second cylinder 420 of the second (high pressure) Compressor stage 402.
  • the first and second cylinders 410, 420 are part of a housing 440 of the entire air compressor with piston compressor 400, drive motor M and crankshaft 430.
  • the housing 440 of the air compressor is connected to the housing of a compressed air supply system 1001 by further components 441, as shown in FIG. 1 is shown.
  • FIG. 2nd shows the TWIN compressor 400, in this case in an operating position, according to which the second piston K2 of the (low-pressure) compressor stage 401 is in a stroke position HS, that is to say the compression of the air in the displacement 411 is imminent.
  • the first piston K1 of the second compressor stage 402 is in a compression position VS, ie compressed air is compressed from the second high pressure stage 402 and can be discharged to the compressed air supply system 1001.
  • the movement of the first and second pistons K1, K2 during operation of the piston compressor 400 basically takes place along the cylinder axis Z. This lies in the center symmetry of the cylinder surfaces Z1 and Z2 of the first and second cylinder displacement 411, 421 for the second and first pistons K2, K1 of the first and second cylinders 410, 420.
  • the connecting rod length of the first connecting rod P1 is given 52.00 mm as an example of the magnitude of the high-pressure stage 420 of the piston compressor 400.
  • the connecting rod of the first connecting rod P1 can, for example, also have a connecting rod length between 50 and 70 mm, in particular a connecting rod length of 66 mm.
  • the second connecting rod can have, for example, a connecting rod length between 40 and 60 mm, in particular a connecting rod length of 53 mm.
  • the distance between a piston head of the piston 2 and the eccentric crankshaft journal can be, for example, between 15 and 25 mm, in particular 21 mm.
  • the aforementioned dimensions can enable a connecting rod deflection angle of up to 20 °, for example 14 ° and in particular 7 °.
  • the bearing pin L2B has a diameter of 8 mm and can have diameters between 5 mm and 12 mm.
  • the maximum speed for this embodiment is up to 2700 revolutions per minute, which results in a maximum sliding speed of approximately 0.14 m / s, in particular 0.137 m / s.
  • the maximum speed is preferably between 1500 and 3500 revolutions per minute.
  • the cylinder axis Z is oriented such that it runs along a radius around the shaft axis E (eccentric axis E).
  • the shaft axis E runs exactly perpendicular to the cylinder axis Z.
  • the eccentric crankshaft journal 432 of the crankshaft 430 is also arranged exactly perpendicular to the cylinder axis Z in the piston compressor 400.
  • a sufficiently reliable and sealing running of the second and first pistons K2, K1 in the first (low-pressure) compressor stage or (high-pressure) compressor stage 401, 402 is thus also guaranteed along the cylinder axis Z due to the running direction of the pistons K2, K1 .
  • a reciprocating piston machine in the form of a TWIN compressor 400 with first and second compressor stages 401, 402 in which the first connecting rod P1 of the second, namely (high-pressure) compressor stage 402 is formed, the first connecting rod P1 using the Connecting rod bearing L1 is mounted directly on the crankshaft journal 432 - that is, as a connecting rod - and the second connecting rod P2 of the first, here (low-pressure) compressor stage 401 is formed, the second connecting rod P2 being indirectly connected to the crankshaft journal 432 by means of the elastomer element L2 is mounted directly on the first connecting rod P1, i.e. as a connecting rod on the drive connecting rod.
  • FIG. 3a shows a reciprocating piston machine in the form of a two-stage piston compressor 400 with a first connecting rod P1 for a first piston K1 of a second (high pressure) stage 401 and a second connecting rod P2 for a second piston K2 of a first (low pressure) stage 402 in a front view .
  • FIG. 4 is a sectional view along section AA of the reciprocating engine in the form of the two-stage piston compressor 400 of FIG. 3a shown.
  • the elastomer element L2 in this exemplary embodiment is designed as an elastomer ring L2E extending along the entire longitudinal axis of the bearing bolt L2B; this is the only one - according to the first variant ("and") of the invention - arranged on the bearing pin L2B.
  • the elastomer element L2B in the form of an elastomer ring L2E is thus arranged between the bearing pin L2B and both the connecting rod P1 and the connecting rod P2 and supports them elastically against one another. Otherwise, the reciprocating piston machine in the form of the two-stage piston compressor 400 does not differ from that in FIG Fig. 2 shown embodiment.
  • FIG. 4th shows a section of a reciprocating piston machine in the form of a two-stage piston compressor 400 with a first connecting rod P1 for a piston K1 of a second (high pressure) stage and a second connecting rod P2 with elastomer elements in the form of elastomer rings L2E1, L2E2, L2E3; these are - according to the modification of the first variant ("and") of the invention - arranged on the bearing pin L2B.
  • piston K1 is held by piston holder K11, but can also be formed on connecting rod P1 in an alternative exemplary embodiment.
  • the elastomer rings L2E1 and L2E3 are arranged between the bearing bolts L2B and connecting rods P2 and support them elastically against each other.
  • the elastomer ring L2E2 is arranged between the bearing pin L2B and connecting rod P1 and resiliently supports them against each other.
  • the elastomer rings L2E1, L2E3 and L2E2 have different heights in this exemplary embodiment.
  • the elastomer ring L2E2 is higher than the elastomer rings L2E1 and L2E3, so that it completely covers the larger inside surface of the connecting rod P1.
  • the connecting rod inside surfaces of the connecting rod P2 are smaller than the connecting rod inside surface of the connecting rod P1.
  • only the connecting rod P1 is supported by the elastomer ring L2E2 while the elastomer rings L2E1 and L2E3 are not present.
  • FIG. 5 shows a first embodiment of an elastomer element L2 in the form of an elastomer ring L2E.
  • the elastomer ring L2E in this embodiment is made of rubber or a rubber mixture. Alternatively, another elastic material with good damping properties can be used.
  • the height, width, length, wall thickness and the diameter of the elastomer ring L2E can be freely selected.
  • the aforementioned parameters are preferably adapted to the operating conditions and the respective reciprocating piston machine.
  • FIG. 6 shows a second embodiment of an elastomer element L2 in the form of two elastomer ring segments L2Ea and L2Eb; these could be like the elastomer rings on the bearing pin L2B of the bearing bolts designated L2E1, L2E2, L2E3 FIG. 4th to be ordered; according to a further modification of the first variant ("and") [or also second variant ("or") of the invention only on a single connecting rod] - be arranged as at least two elastomer ring segments L2Ea and L2Eb.
  • the two elastomer ring segments L2Ea and L2Eb are separated from one another and are arranged opposite one another in this exemplary embodiment.
  • an arrangement which is displaced relative to one another is also possible, but should be such that a bearing pin arranged between the elastomer ring segments L2Ea and L2Eb is possible.
  • more than two elastomer ring segments can also be arranged, for example three elastomer ring segments.
  • the center points of the elastomer ring segments can, for example, each be offset from one another on the circumference so that they are at least partially opposite one another.
  • six elastomer ring segments are arranged on a circumference, each with an angular distance from their center points of 60 °.
  • elastomer ring segment enclosing 270 °.
  • the elastomer ring segments can enclose a circumference of 0 ° to 360 °.
  • FIG. 7 shows an elastomer element L2 in the form of an elastomer ring L2E, which encloses a metal carrier MT in the form of a metal sleeve MTi.
  • the metal sleeve MTi is arranged inside the elastomer ring L2E.
  • the metal sleeve MTi is pressed in here.
  • the metal sleeve MTi can also be glued in.
  • an elastomer layer or an elastomer coating can be sprayed or vulcanized onto the metal sleeve MTi.
  • the arrangement of an elastomer element L2 together with a metal carrier MT increases the rigidity of the elastomer element L2 or the bearing component composed of the elastomer element L2 and the metal carrier MT.
  • FIG. 8a shows an elastomer element L2 in the form of an elastomer ring L2E which is sandwiched between two metal carriers MT in the form of metal sleeves MTi and MTa.
  • FIG. 8b shows a schematic representation of the in FIG. 8a shown storage component composed of elastomer element L2 and metal sleeves MTi and MTa.
  • an elastomer layer can also be injected between the metal sleeves MTi and MTa.
  • the arrangement between two metal sleeves further increases the rigidity of the assembled bearing component.
  • FIG. 9 shows a third embodiment of an elastomer element L2 in the form of an elastomer layer L2ES or elastomer coating sprayed onto part of the bearing pin surface L2BO.
  • the elastomer layer L2ES can also be vulcanized.
  • the elastomer layer L2ES can also be injected between the connecting rod inner surface of the connecting rod P1 and the bearing pin surface L2BO, so that it connects the connecting rod P1 and the bearing pin L2B firmly and directly.
  • the elastomer layer L2ES is in this FIG. 9 - So preferably according to the second variant ("or") of the invention only on a single connecting rod, namely the first connecting rod P1-- arranged as at least one annular layer.
  • FIG. 10th shows a first connecting rod P1 with an elastomer element L2 arranged in it in the form of an elastomer ring L2E2, which encloses a metal carrier MT in the form of a metal sleeve MTi.
  • the connecting rod P1 can be supported against a bearing pin L2B (not shown) by the bearing component composed of the elastomer ring L2E2 and the metal sleeve MTi.
  • the storage component is in this FIG. 10th - So preferably according to the second variant ("or") of the invention only on a single connecting rod, namely the first connecting rod P1-- arranged.
  • FIG. 9 and FIG. 10th could nevertheless, according to the first variant, also the elastomer layer L2ES or the elastomer element L2 on the second connecting rod P2 (not shown in FIG FIG. 9 , FIG. 10th ) be arranged.

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Claims (24)

  1. Machine à pistons alternatifs (400), en particulier compresseur à pistons à deux ou plusieurs étages (400), présentant :
    - au moins un cylindre (410, 420) ainsi qu'au moins un premier piston (K1) associé au cylindre (420) et un deuxième piston (K2) associé au cylindre ou à un cylindre (410), les pistons (K1, K2), pendant le fonctionnement, étant déviés dans une chambre de course de cylindre respective (411, 421) de l'au moins un cylindre (410, 420),
    - un vilebrequin (430) pouvant être entraîné pendant le fonctionnement avec un maneton de vilebrequin excentrique (432) et un accouplement d'arbre d'entraînement (431), qui est réalisé pour accoupler un arbre d'entraînement (500) d'un moteur d'entraînement (M, 500) pour l'entraînement du vilebrequin (432),
    - une première bielle (P1) réalisée pour dévier le premier piston (K1),
    - une deuxième bielle (P2) réalisée pour dévier le deuxième piston (K2), et
    - un tourillon de palier (L2B), autour duquel la première (P1) et la deuxième (P2) bielle peuvent être tournées l'une par rapport à l'autre,
    la première bielle (P1) pouvant être déplacée au moyen du maneton de vilebrequin excentrique (432) et la deuxième bielle (P2) étant supportée de manière déplaçable au moyen du tourillon de palier (L2B) sur la première bielle (P1) et
    - entre le tourillon de palier (L2B) d'une part et la première bielle (P1) d'autre part étant disposé au moins un, en particulier un premier, élément élastomère (L2 ; L2E ; L2E2 ; L2Ea, L2Eb ; L2ES) supportant élastiquement l'un contre l'autre le tourillon de palier (L2B) d'une part et la première bielle (P1) d'autre part, et/ou
    - entre le tourillon de palier (L2B) d'une part et la deuxième bielle (P2) d'autre part, étant disposé l'au moins un ou au moins un, en particulier un deuxième, élément élastomère (L2 ; L2E ; L2E1 ; L2E3 ; L2Ea, L2Eb), supportant élastiquement l'un contre l'autre le tourillon de palier (L2B) d'une part et la deuxième bielle (P2) d'autre part.
  2. Machine à pistons alternatifs (400) selon la revendication 1, caractérisée en ce que le maneton de vilebrequin excentrique (432) et/ou l'accouplement d'arbre d'entraînement (431) sont orientés parallèlement à un axe d'arbre (E) s'étendant perpendiculairement à un axe de cylindre (Z).
  3. Machine à pistons alternatifs (400) selon la revendication 1 ou 2, caractérisée en ce
    - qu'au moins l'une des bielles (P1) est supportée directement ou indirectement sur le maneton de vilebrequin (432) au moyen d'au moins un palier de bielle (L1), et/ou
    - que le piston (K1, K2) est façonné, connecté fixement ou retenu au moyen d'une fixation de piston (K11) du piston (K1) au niveau de la ou d'au moins une bielle (P1, P2).
  4. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 3, caractérisée en ce que la première bielle (P1) peut être déplacée directement au moyen du maneton de vilebrequin excentrique (432) et la deuxième bielle (P2) peut être déplacée indirectement au moyen du maneton de vilebrequin excentrique (432), en particulier au moyen de la première bielle (P1), de préférence au moins la deuxième bielle (P2) pouvant être déplacée en tant que bielle menée par la première bielle (P1) en tant que bielle d'entraînement.
  5. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 4, caractérisée en ce que l'au moins un élément élastomère (L2 ; L2E ; L2E1 ; L2E2 ; L2E3 ; L2Ea, L2Eb ; L2ES) est un élément en caoutchouc ou est introduit en tant que revêtement en caoutchouc entre le tourillon de palier (L2B) et la bielle (P1, P2), en particulier sur la surface du tourillon de palier (L2BO) et/ou sur une surface intérieure de la bielle.
  6. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 5, caractérisée en ce que l'élément élastomère (L2 ; L2E ; L2E1, L2E2, L2E3 ; L2Ea, L2Eb) est une pièce séparée, en particulier est inséré ou serré entre le tourillon de palier (L2B) et la bielle (P1, P2), en particulier est inséré ou serré exclusivement entre le tourillon de palier (L2B) et la bielle (P1), et/ou l'élément élastomère (L2 ; L2E ; L2E1, L2E2, L2E3 ; L2Ea, L2Eb) sert à supporter des mouvements de rotation de la bielle (P1, P2) autour du tourillon de palier (L2B) et à générer un effet d'amortissement.
  7. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 5, caractérisée en ce que l'élément élastomère (L2 ; L2ES) est une couche appliquée, en particulier une couche pulvérisée ou vulcanisée, de préférence est une couche appliquée sur une surface du tourillon de palier (L2BO), une surface intérieure de bielle de la première bielle (P1) et/ou une surface intérieure de bielle de la deuxième bielle (P2), et/ou l'élément élastomère (L2 ; L2ES) sert à supporter des mouvements de rotation des bielles (P1, P2) autour du tourillon de palier (L2BO) et à générer un amortissement.
  8. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 7, caractérisée en ce que l'élément élastomère (L2 ; L2E ; L2E1 ; L2E2 ; L2E3 ; L2ES) est annulaire, en forme de douille ou en forme de manchon.
  9. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 7, caractérisée en ce que l'élément élastomère (L2) est en forme de plaque, en particulier est une noppe ou est en forme de segment annulaire (L2, L2Ea, L2Eb).
  10. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 9, caractérisée en ce que l'élément élastomère (L2) est connecté à, ou est en contact avec, un support métallique (MT, MTi, MTa), en particulier une douille métallique, un manchon métallique (MTi, MTa), une bague métallique ou plusieurs plaquettes métalliques.
  11. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 10, caractérisée en ce que l'élément élastomère (L2 ; L2E1, L2E2, L2E3) présente au moins deux bagues élastomères (L2 ; L2E1, L2E2, L2E3) qui sont disposées parallèlement et à distance l'une de l'autre autour du tourillon de palier (L2B).
  12. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 12, caractérisée en ce que l'élément élastomère (L2) présente au moins une plaquette en élastomère disposée seulement d'un côté, en particulier au niveau d'un côté supérieur du tourillon de palier, ou présente au moins deux plaquettes en élastomère opposées l'une à l'autre, disposées au niveau du côté supérieur du tourillon de palier et d'un côté inférieur du tourillon de palier.
  13. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 10, caractérisée en ce que l'au moins un élément élastomère (L2 ; L2E) est disposé entre un support métallique intérieur (MTi) et extérieur (MTa), et le support métallique intérieur (MTi) est connecté au tourillon de palier (L2B) et le support métallique extérieur (MTb) est connecté, en particulier est connecté fixement et directement, à au moins l'une des bielles (P1, P2).
  14. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 13, caractérisée en ce que l'au moins un élément élastomère (L2 ; L2E ; L2E2) est disposé entre un support métallique intérieur (MTi) et au moins l'une des bielles (P1, P2), et le support métallique intérieur (MTi) est connecté au tourillon de palier (L2B) et l'élément élastomère (L2 ; L2E ; L2E2) est connecté, notamment fixement et directement, à au moins l'une des bielles (P1, P2) .
  15. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 14, caractérisée en ce que l'au moins un élément élastomère (L2 ; L2E) est disposé entre le tourillon de palier (L2B) et un support métallique extérieur (MTa) et l'élément élastomère (L2 ; L2E) est connecté, en particulier fixement et directement, au tourillon de palier (L2B), et le support métallique extérieur (MTa) est connecté à au moins l'une des bielles (P1, P2).
  16. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 15, caractérisée en ce que l'au moins un élément élastomère (L2 ; L2Ea, L2Eb) présente au moins deux segments annulaires (L2Ea, L2Eb) séparés l'un de l'autre.
  17. Machine à pistons alternatifs (400) selon la revendication 16, dans laquelle, parmi les au moins deux segments annulaires séparés (L2Ea, L3Eb), au moins un premier segment annulaire (L2Ea) est disposé sur un côté supérieur du tourillon de palier entre le tourillon de palier (L2B) et la bielle (P1, P2), et au moins un deuxième segment annulaire (L2Eb) est disposé sur un côté inférieur du tourillon de palier entre le tourillon de palier (L2B) et la bielle (P1, P2).
  18. Machine à pistons alternatifs (400) selon la revendication 16 ou 17, caractérisée en ce que les segments annulaires séparés les uns des autres de l'élément élastomère (L2) entoure au plus un quart de la périphérie sur le côté supérieur du tourillon de palier et au plus un quart de la périphérie sur le côté inférieur du tourillon de palier, de telle sorte qu'au moins la moitié de la périphérie de la surface de tourillon de palier (L2BO) du tourillon de palier (L2B) soit exempte d'élément élastomère (L2).
  19. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 18, caractérisée en ce qu'un angle de déviation maximal de déviation des bielles (P1, P2) entre des axes longitudinaux respectifs des bielles (P1, P2) vaut au plus 14°, par exemple au plus 10°, de préférence environ 7°.
  20. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 19, caractérisée en ce que
    - la première bielle (P1) est supportée directement sur le maneton de vilebrequin (432) au moyen d'un palier de bielle (L1), et le premier piston (k1) est retenu sur la première bielle (P1) au moyen d'une fixation de piston (K11), et
    - le deuxième piston (K2) est façonné sur la deuxième bielle (P2).
  21. Machine à pistons alternatifs (400) selon l'une quelconque des revendications 1 à 20, caractérisée en ce que
    le compresseur de piston (400) est formé en tant que compresseur à deux ou plusieurs étages (400), avec au moins un premier et un deuxième étage de compresseur (401, 402), ou sous forme de compresseur à deux cylindres ou plusieurs cylindres, la première bielle (P1) du deuxième étage de compresseur (402), notamment l'étage haute pression du compresseur, étant formée, la première bielle (P1) étant supportée directement sur le maneton de vilebrequin (432) au moyen d'un palier de bielle (L1), et/ou la deuxième bielle (P2) du premier étage de compresseur (401), en particulier de l'étage basse pression du compresseur, étant formée.
  22. Installation d'alimentation en air comprimé (1001) pour faire fonctionner une installation pneumatique (1002), en particulier une installation de ressort pneumatique d'un véhicule, de préférence d'un véhicule de tourisme, comprenant un écoulement d'air comprimé (DL), présentant :
    - un agencement de sécheur d'air (100) dans une conduite pneumatique principale (200) qui relie pneumatiquement une alimentation en air comprimé (1) d'un compresseur d'air (400) et un raccord d'air comprimé (2) à l'installation pneumatique (1002), et
    - un agencement de soupape (300) raccordé pneumatiquement à la conduite pneumatique principale (200) pour commander l'écoulement d'air comprimé (DL) et un sécheur d'air (101) dans la conduite pneumatique principale (200),
    - un compresseur d'air (400) avec une machine à pistons alternatifs (400), en particulier un compresseur à pistons à deux ou plusieurs étages (400) selon l'une quelconque des revendications 1 à 21, étant raccordé à l'alimentation en air comprimé (1).
  23. Système d'alimentation en air comprimé (1000) comprenant une installation pneumatique (1002) et une installation d'alimentation en air comprimé (1001) selon la revendication 22, pour faire fonctionner l'installation pneumatique (1002) avec un écoulement d'air comprimé (DL), en particulier une installation de ressort pneumatique d'un véhicule, de préférence d'un véhicule de tourisme, la conduite pneumatique principale (1002) reliant pneumatiquement une alimentation en air comprimé (1) d'un compresseur d'air (400) avec une machine à pistons alternatifs (400), en particulier un compresseur à pistons à deux ou plusieurs étages (400) selon l'une quelconque des revendications 1 à 21, et un raccord d'air comprimé (2) à l'installation pneumatique (1002).
  24. Véhicule, en particulier véhicule de tourisme, comprenant une installation pneumatique (1002), en particulier une installation de ressort pneumatique, et une installation d'alimentation en air comprimé (1001) selon la revendication 22, pour faire fonctionner l'installation pneumatique (1002) avec un écoulement d'air comprimé (DL).
EP17700772.1A 2016-02-11 2017-01-19 Machine à pistons alternatifs, notamment compresseur à pistons alternatifs à au moins deux étages, dispositif d'alimentation en air comprimé, système d'alimentation en air comprimé et véhicle, notamment voiture particulière équipée d'un dispositif d'alimentation en air comprimé Active EP3414456B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016001596.9A DE102016001596A1 (de) 2016-02-11 2016-02-11 Hubkolbenmaschine, insbesondere zwei- oder mehrstufiger Kolbenkompressor, Druckluftversorgungsanlage, Druckluftversorgungssystem und Fahrzeug, insbesondere PKW mit einer Druckluftversorgungsanlage
PCT/EP2017/000062 WO2017137143A1 (fr) 2016-02-11 2017-01-19 Machine à pistons alternatifs, notamment compresseur à pistons alternatifs à au moins deux étages, dispositif d'alimentation en air comprimé, système d'alimentation en air comprimé et véhicle, notamment voiture particulière équipée d'un dispositif d'alimentation en air comprimé

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EP3414456A1 EP3414456A1 (fr) 2018-12-19
EP3414456B1 true EP3414456B1 (fr) 2020-03-11

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US (1) US10641257B2 (fr)
EP (1) EP3414456B1 (fr)
CN (1) CN108496001B (fr)
DE (1) DE102016001596A1 (fr)
WO (1) WO2017137143A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102068329B1 (ko) * 2018-08-31 2020-01-20 주식회사 삼홍사 멀티 스텝 높낮이 조절 장치
DE102018128557A1 (de) 2018-11-14 2020-05-14 Wabco Gmbh Hubkolbenmaschine, Druckluftversorgungsanlage, Fahrzeug und Verfahren zur Herstellung einer Hubkolbenmaschine
CN111469619A (zh) * 2020-04-26 2020-07-31 安美科(安徽)汽车电驱有限公司 一种汽车空气悬架用空气供给设备
US12019460B2 (en) 2021-06-24 2024-06-25 Apple Inc. Shared compressor
CN217652875U (zh) * 2021-10-25 2022-10-25 思科普有限责任公司 封装式制冷剂压缩机
US11913441B2 (en) * 2021-12-29 2024-02-27 Transportation Ip Holdings, Llc Air compressor system having a hollow piston forming an interior space and a check valve in a piston crown allowing air to exit the interior space
US20240309860A1 (en) * 2023-03-19 2024-09-19 Weidong Lu Integrated air supply unit

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3122311A1 (de) * 1980-06-13 1982-03-18 IAO Industrie Riunite S.p.A., 10092 Beinasco, Torino Vorrichtung zur elastischen befestigung eines vibrierenden teils an einem stuetzbauteil
DE3340733A1 (de) * 1983-11-10 1985-05-23 Bayrisches Druckguss-Werk Thurner GmbH & Co KG, 8015 Markt Schwaben Kolbenverdichter
US4729291A (en) * 1986-07-18 1988-03-08 Ingersoll-Rand Company Gas compressor
JPH074487A (ja) 1993-06-17 1995-01-10 Ouken Seiko Kk クランク駆動機構
GB0222480D0 (en) * 2002-09-27 2002-11-06 Ricardo Consulting Eng Torsionally damped rotary shafts
DE102004020104A1 (de) * 2004-04-24 2005-11-17 Arnold Müller GmbH & Co KG Doppelkolben für einen Verdichter
DE102006043047A1 (de) * 2006-09-14 2008-03-27 Zf Friedrichshafen Ag Lagerung eines kupplungsseitigen Pumpenantriebsrades bei einer Off-Axis Pumpenanordnung in einem Automatgetriebe
CN100432375C (zh) * 2007-03-03 2008-11-12 谈诚 一种以最佳尺寸比例设计的摆动活塞机械
CN102664512B (zh) * 2012-05-09 2014-01-29 林贵生 一种无源永磁耦合传动、制动或负载装置
DE102013003513A1 (de) * 2013-03-04 2014-09-04 Wabco Gmbh Verdichteranordnung zum Betreiben einer Druckluftversorgungsanlage, Druckluftversorgungsanlage und Druckluftversorgungssystem sowie Fahrzeug mit einer solchen Druckluftversorgungsanlage

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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Publication number Publication date
WO2017137143A1 (fr) 2017-08-17
CN108496001B (zh) 2020-04-21
DE102016001596A1 (de) 2017-08-17
WO2017137143A8 (fr) 2018-04-19
US20190032647A1 (en) 2019-01-31
US10641257B2 (en) 2020-05-05
EP3414456A1 (fr) 2018-12-19
CN108496001A (zh) 2018-09-04

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