EP1527278B1 - Device for compressing gases - Google Patents

Device for compressing gases Download PDF

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Publication number
EP1527278B1
EP1527278B1 EP03737736A EP03737736A EP1527278B1 EP 1527278 B1 EP1527278 B1 EP 1527278B1 EP 03737736 A EP03737736 A EP 03737736A EP 03737736 A EP03737736 A EP 03737736A EP 1527278 B1 EP1527278 B1 EP 1527278B1
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EP
European Patent Office
Prior art keywords
seal
piston
cylinder
incisions
disc
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Expired - Lifetime
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EP03737736A
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German (de)
French (fr)
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EP1527278A1 (en
Inventor
Helmut Thurner
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Ventrex Automotive GmbH
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Ventrex Automotive GmbH
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Publication of EP1527278A1 publication Critical patent/EP1527278A1/en
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    • 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

Definitions

  • the present invention relates to a device according to the preamble of claim 1.
  • Such compressors which compress gases by means of a piston moved by an electromechanical or other type of drive in a cylinder, are known, see for example GB 1 396 230 ,
  • a driven via a crank or a connecting rod piston is set with a voltage applied to the inner wall of the cylinder seal in a reciprocating motion. This causes a compression of the gas on one side of the piston.
  • Such devices exist in a variety of designs and sizes and are used in a variety of fields for use. Also drive mechanisms of different types and performance are used.
  • the object of this invention is to propose a device of the type mentioned at the outset or a reciprocating compressor with a seal which has a friction and sealing behavior on the inner wall of the cylinder that is improved in comparison to previously known embodiments of conventional seals.
  • the solution of this problem is achieved by the features specified in claim 1.
  • the idea on which the invention is based is that a number of cuts, preferably 6 to 12, in particular 8 to 10, are formed in the seal mounted annularly around the piston.
  • This technically very simple and inexpensive to betechnikstelligende measure causes an improvement in the friction behavior and a better nestling of the seal on the cylinder inner wall. This results in an optimal sealing behavior between piston and cylinder and thus a highly efficient compression behavior.
  • the life of the seal is increased due to improved elastic properties without compromising the compression behavior.
  • the cuts, which are technically simple cause a significant improvement in the elasticity of the seal.
  • the regular distribution of the cuts along the annular seal cause balanced and quiet running properties of the piston.
  • a smooth movement and longevity of the piston and the seal in the cylinder are achieved by the structural features according to claim 2, 3 and / or 4.
  • An advantageous and effective embodiment of the sealing mechanism is described in the features of claims 5 to 7.
  • the storage and management of the seal is advantageously carried out according to claims 8, 9 and / or 10.
  • a small defined quantity of gas can flow from the compression space or working space located in front of the piston into the area behind the piston Intake space or depressurized space pass through and thus the pressure acting on the piston from the compression side is reduced.
  • a start-up relief can already start a relatively weak, for example, operated by a battery drive motor against a high back pressure, without that the allowable starting current is exceeded or various safety devices are triggered.
  • the leaks have a small cross-sectional area compared with the cylinder cross-section or the stroke volume of the piston, whereby the leakage losses are minimized after the start-up.
  • leaks allow design-related variations, depending mainly on the design and size of the piston or the entire compressor device. If the leaks are formed in the inner region of the support disk and of the guide disk, then they are arranged in alignment and permit the defined passage of gas through this feature.
  • the piston is mounted in the cylinder substantially tight.
  • a gas passage from the working space into the unpressurized space is essentially determined by the leakages.
  • a gas leakage from the working space into the non-pressurized space which occurs due to leaks, in particular in the gasket, fades into the background in comparison with the gas passage through the leaks.
  • an electromechanical drive 1 is fed in this case via a battery, not shown, which is connected via a cigarette lighter plug 9 and a cable 10 with a control console 12 and a further cable 13 to the drive or electric motor 1.
  • a rocker switch 11 located on the console 12, the power supply can be switched on and off.
  • the compression mechanism located in a drive chamber 3 or in the cylinder 2 is actuated by this drive 1 and the working fluid, in this case air, via a with a terminal 4 at the outlet 22 of the cylinder 2 attached pressure hose 5 via a pressure gauge 6 for pressure control and via an outlet 8 to the destination object, eg car tires, pressed.
  • the working fluid in this case air
  • a drive shaft of the drive 1 in the drive chamber 3 via a crank 23 with a push rod 14 is connected, which puts a piston 20 in the cylinder 2 in a reciprocating motion, that of the wall of the cylinder 2 and the piston 20th limited volume of the working space 26 before the piston 20 and the volume of the unpressurized space 24 behind the piston 20 is changed.
  • a check valve 27 the compressed air from the outlet 22 is prevented from flowing back into the working space 26.
  • the enlarged shown in Fig. 3, located in the cylinder 2 piston 20 comprises a fixed to the push rod 14 plate-shaped guide plate 16 on its head or working space side 26, a likewise fixed to the push rod 14 and optionally fixedly connected to the guide disc 16 in the interior dish-shaped support disk 15 on its rear side or its pressure-free space 24 facing side and an applied to the wall of the cylinder 2 annular seal 17.
  • the guide disk 16 is in the inner region, a preferably parallel to the wall of the cylinder 2 extending middle part 28 and a terminal peripheral flange 25 'articulated.
  • the support disk 15 is also divided into an inner region, a central part and a terminal peripheral flange 25.
  • the seal 17 is located between the height of the two peripheral flanges 25, 25 'of the support disk 15 and the guide disk 16 in the peripheral region of the piston 20. Between the seal 17, the support disk 15 and the guide disk 16 and their peripheral flanges 25, 25 'is a free space 27th
  • the inner surface of the cylinder 2 facing surface of the seal 17 is concave outward, in particular with a circular curvature, curved to compensate for the slightly oscillating movement of the present case only via the push rod 14 and not a crosshead guided piston 20 and to ensure a permanent tight contact between the wall of the cylinder 2 and the seal 17.
  • the seal 17 has, on its side facing the working space 26, a head area 40 that is narrow in cross-section and a foot area 41 that is wider in cross-section on the side facing away from the working space 26.
  • a recess 43 is advantageously formed on the inner surface of the seal 17, in which a spring ring 18 is in particular fixed and preferably inserted snugly.
  • This spring ring 18 is accordingly between the central part 28 of the guide disc 16 and the head portion 40 of the seal 17.
  • the spring ring 18 is movable in a lifting movement of the piston 20 along or in front of this central part 28 of the guide disc 16 and up, with its upward movement or ., Its upward path from the peripheral flange 25 'of the guide disc 16 is limited.
  • the seal 17 is pressed by means of this spring ring 18 radially outward or on the lateral wall of the cylinder 2 and prevents there an undesirable gas passage.
  • a resilient clamping ring can be used instead of the spring ring 18 and a resilient clamping ring. In both cases, however, an air passage between the space 27 and the working space 26 at this point is possible.
  • the height H of the seal 17, measured in the direction of movement of the piston 20, is less than the distance A measured between the inner sides of the peripheral flanges 25, 25 'of the support disk 15 and the guide disk 16. Accordingly, the amplitude of movement of the seal 17 is at the difference D between the height H of the seal 17 and the distance A of the peripheral flanges 25, 25 'of the support disk 15 and the guide disk 16 is limited.
  • This embodiment causes in a suction movement, that is, upon movement of the piston 20 in the direction of the crank 23, a lifting of the seal 17 of the support disk 15 by the amount D, thus allowing a backflow of gas through the space 27 in the head-side working space 26th
  • the seal 17 is pressed tight against the peripheral flange 25 of the support disk 15, and gas passage is only possible through the defined leakages 19 described below.
  • the compressed air in the working chamber 26 is pressed by a check valve 27 from the outlet 22 and prevented by this check valve 27 at the same time flowing back into the working space 26.
  • the seal 17 consists of a largely heat-stable and / or substantially abrasion-resistant polymer, in particular with good running and sliding properties, preferably polytetrafluoroethylene (PTFE, Teflon) or polytetrafluoroethylene compounds, and optionally with carbon or carbon fibers and / or particles in one Proportion of 10 to 20% by weight, preferably from 15 to 25% by weight, of the PTFE or PTFE compound weight, are reinforced.
  • PTFE polytetrafluoroethylene
  • Teflon polytetrafluoroethylene
  • carbon or carbon fibers and / or particles in one Proportion of 10 to 20% by weight, preferably from 15 to 25% by weight, of the PTFE or PTFE compound weight, are reinforced.
  • the number of leaks 19, as well as their shape or cross-sectional shape depends on the performance of the drive mechanism, the amount of the initial back pressure, the size and design of the compressor device, the shape of the piston, etc.
  • the leaks 19 can through holes, milled recesses, Infiltrations or the like. Be formed, the shape of which is also determined by the production method. Accordingly, the leaks 19 may be formed in cross-section round, square or irregular shaped.
  • the total cross-sectional area of the at least one leakage 19 per cm 3 stroke volume of the piston 20 is between 0.005 and 0.1 mm 2 , preferably 0.01 and 0.06 mm 2 .
  • the formation of the leaks 19 can be done by design in the support plate 15 and / or the guide plate 16, both in the outer regions, ie the peripheral flanges 25, 25 ', in particular in the peripheral flange 25 of the support plate 15, as well as in the interior areas, to It should be noted that when training in the fixed and plan interconnected inner areas of the discs 15,16, the leaks 19 are advantageously arranged in alignment. Furthermore, there is the possibility of the formation of leaks in the entire region of the seal 17, in particular in the inside of the peripheral flange 25 of the support plate 15 facing the end face of the seal 17th
  • Fig. 4 shows a cross section through the seal 17. Good to see the working space 26 facing, narrow in cross-section head portion 40 with the at its Inner side of the spring ring 18 provided recess 43 and the slightly thicker foot portion 41.
  • cuts 45 are formed in the head portion 40. With regard to the characteristics of the cuts 45, it should be noted that the cuts 45 are made without material removal, ie are not milled, sawn, or the like. become.
  • the cuts 45 extend, starting from the upper end surface of the head portion 40 of the seal 17, at least until the beginning of the contact region 44 of the seal 17 with the inner wall of the cylinder 2, which in practice by the compression of the seal 17 against the wall of the cylinder 2 or by the tumbling movements of the piston 20 results.
  • the cuts 45 extend from the upper end surface of the head portion 40 of the gasket 17 to the in Fig. 5 geometrically determined, theoretical contact line 42 of the concave seal 17 with the inner wall of the cylinder 2.
  • the cuts 45 starting from the upper end face of the head portion 40 of the seal 17, at least extend to the lower end of the recess 43.
  • the maximum cuts 45 measured from the upper end surface of the head portion 40 of the seal 17, to the beginning of the foot portion 41 of the seal 17, ie to a maximum depth T.
  • Fig. 5 shows a plan view of the working space 26 on the annular seal 17.
  • the cuts 45 pass through the head portion 40 of the seal 17 completely.
  • the preferably 6 to 12, in particular 8 to 10, here 9 cuts 45 are distributed along the circumference of the annular seal 17 and at equal distances from each other and are inclined relative to the radius R of the seal 17 in the same direction, preferably at an angle a between 30 and 80 °, in particular between 40 and 70 °.
  • the surfaces of the cuts 45 are flat and are aligned perpendicular to the plane spanned by the seal 17.
  • the cuts 45 are advantageously identical to each other or have the same shape or dimensions.
  • Leakage is understood to mean a constantly open (gas) passage connection between the space in front of and behind the piston.

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

Abstract

The invention relates to a device for compressing gases, especially air, preferably for filling tyres of motor vehicles. Said device comprises a piston which is is mounted in a cylinder, can be displaced back and forth, and is driven by an especially electromechanical drive which is preferably connected to a battery. Said piston comprises an annular seal on the inner wall of the cylinder. According to the invention, the annular seal (17) has a number of cuts (45), preferably between 6 and 12, especially between 8 and 10, especially for improving the sealing and compression behaviour.

Description

Die vorliegende Erfindung betrifft eine Einrichtung gemäß dem Oberbegriff des Anspruchs 1.The present invention relates to a device according to the preamble of claim 1.

Derartige Kompressoren, die mittels eines von einem elektromechanischen oder andersartigen Antrieb in einem Zylinder bewegten Kolbens Gase verdichten, sind bekannt, siehe dazu zum Beispiel GB 1 396 230 . Hierbei wird ein über eine Kurbel bzw. ein Pleuel angetriebener Kolben mit einer an der Innenwand des Zylinders anliegenden Dichtung in eine hin- und hergehende Bewegung versetzt. Dadurch wird eine Verdichtung des Gases auf einer Seite des Kolbens bewirkt. Derartige Einrichtungen existieren in vielfältigen Ausführungen und Größen und werden auf den verschiedensten Gebieten zum Einsatz gebracht. Auch Antriebsmechanismen unterschiedlicher Art und Leistung werden eingesetzt.Such compressors, which compress gases by means of a piston moved by an electromechanical or other type of drive in a cylinder, are known, see for example GB 1 396 230 , Here, a driven via a crank or a connecting rod piston is set with a voltage applied to the inner wall of the cylinder seal in a reciprocating motion. This causes a compression of the gas on one side of the piston. Such devices exist in a variety of designs and sizes and are used in a variety of fields for use. Also drive mechanisms of different types and performance are used.

Die Aufgabe dieser Erfindung ist es, eine Einrichtung der eingangs genannten Art bzw. einen Kolbenkompressor mit einer Dichtung vorzuschlagen, die ein im Vergleich zu bisher bekannten Ausführungsformen üblicher Dichtungen verbessertes Reibungs- und Dichtungsverhalten an der Innenwand des Zylinders aufweist.
Die Lösung dieser Aufgabe wird durch die im Anspruch 1 angegebenen Merkmale erreicht.
Die der Erfindung zugrundeliegende Idee besteht darin, dass in der ringförmig um den Kolben gelagerten Dichtung eine Anzahl von Schnitten, vorzugsweise 6 bis 12, insbesondere 8 bis 10, ausgebildet ist. Diese technisch sehr einfach und preiswert zu bewerkstelligende Maßnahme, bewirkt eine Verbesserung des Reibungsverhaltens und ein besseres Anschmiegen der Dichtung an der Zylinderinnenwand. Demzufolge ergibt sich ein optimales Dichtungsverhalten zwischen Kolben und Zylinder und dadurch ein höchst effizientes Kompressionsverhalten. Ferner wird die Lebensdauer der Dichtung aufgrund verbesserter elastischer Eigenschaften erhöht ohne das Kompressionsverhalten zu beeinträchtigen.
Die Schnitte, die technisch einfach ausgebildet sind, bewirken eine entscheidende Verbesserung der Elastizität der Dichtung. Die regelmäßige Verteilung der Schnitte entlang der ringförmigen Dichtung bewirken ausgeglichene und ruhige Laufeigenschaften des Kolbens.The object of this invention is to propose a device of the type mentioned at the outset or a reciprocating compressor with a seal which has a friction and sealing behavior on the inner wall of the cylinder that is improved in comparison to previously known embodiments of conventional seals.
The solution of this problem is achieved by the features specified in claim 1.
The idea on which the invention is based is that a number of cuts, preferably 6 to 12, in particular 8 to 10, are formed in the seal mounted annularly around the piston. This technically very simple and inexpensive to bewerkstelligende measure causes an improvement in the friction behavior and a better nestling of the seal on the cylinder inner wall. This results in an optimal sealing behavior between piston and cylinder and thus a highly efficient compression behavior. Furthermore, the life of the seal is increased due to improved elastic properties without compromising the compression behavior.
The cuts, which are technically simple, cause a significant improvement in the elasticity of the seal. The regular distribution of the cuts along the annular seal cause balanced and quiet running properties of the piston.

Eine ruhige Bewegung und Langlebigkeit des Kolbens und der Dichtung im Zylinder werden durch die konstruktiven Merkmale gemäß Anspruch 2, 3 und/oder 4 erreicht. Eine vorteilhafte und effektive Ausführung des Dichtungsmechanismus wird in den Merkmalen der Ansprüche 5 bis 7 beschrieben. Um bei der Kolbenrück- bzw. Ansaugbewegung einen Nachstrom von zu komprimierendem Gas in den kopfseitigen Arbeitsraum zu gewährleisten, erfolgt die Lagerung und Führung der Dichtung vorteilhafterweise gemäß den Ansprüchen 8, 9 und/oder 10.A smooth movement and longevity of the piston and the seal in the cylinder are achieved by the structural features according to claim 2, 3 and / or 4. An advantageous and effective embodiment of the sealing mechanism is described in the features of claims 5 to 7. In order to ensure a Nachstrom of gas to be compressed in the head-side working space in the Kolbenrück- or suction movement, the storage and management of the seal is advantageously carried out according to claims 8, 9 and / or 10.

Durch Leckagen kann bei der Kompressionsbewegung des Kolbens eine geringe definierte Menge Gas von dem vor dem Kolben liegenden Kompressionsraum bzw. Arbeitsraum in den hinter dem Kolben liegenden Ansaugraum bzw. drucklosen Raum durchtreten und somit wird der von der Kompressionsseite her auf den Kolben einwirkende Druck gemindert. Durch eine derartige Anlaufentlastung kann bereits ein relativ schwacher, beispielsweise ein von einer Batterie betriebener, Antriebsmotor gegen einen hohen Gegendruck anlaufen, ohne dass dabei der zulässige Anlaufstrom überschritten wird oder diverse Sicherheitsvorrichtungen ausgelöst werden. Die Leckagen haben eine im Vergleich zum Zylinderquerschnitt bzw. zum Hubvolumen des Kolbens geringe Querschnittsfläche, womit die Leckverluste nach erfolgtem Anlauf minimal gehalten werden. Die Positionierung, Form und Ausbildungsart der Leckagen gestatten konstruktionsbedingte Variationsmöglichkeiten, abhängig vor allem von der Bauart und Größe des Kolbens bzw. der gesamten Kompressoreinrichtung. Sind die Leckagen im Innenbereich der Stützscheibe und der Führungsscheibe ausgebildet, so sind sie fluchtend angeordnet und ermöglichen durch dieses Merkmal den definierten Gasdurchtritt.Due to leaks, during the compression movement of the piston, a small defined quantity of gas can flow from the compression space or working space located in front of the piston into the area behind the piston Intake space or depressurized space pass through and thus the pressure acting on the piston from the compression side is reduced. By such a start-up relief can already start a relatively weak, for example, operated by a battery drive motor against a high back pressure, without that the allowable starting current is exceeded or various safety devices are triggered. The leaks have a small cross-sectional area compared with the cylinder cross-section or the stroke volume of the piston, whereby the leakage losses are minimized after the start-up. The positioning, shape and type of training of leaks allow design-related variations, depending mainly on the design and size of the piston or the entire compressor device. If the leaks are formed in the inner region of the support disk and of the guide disk, then they are arranged in alignment and permit the defined passage of gas through this feature.

Der Kolben ist im Zylinder im wesentlichen dicht gelagert. Ein Gasdurchtritt vom Arbeitsraum in den drucklosen Raum wird im wesentlichen durch die Leckagen bestimmt. Ein durch Undichtheiten, insbesondere in der Dichtung, auftretender Gasdurchtritt vom Arbeitsraum in den drucklosen Raum tritt gegenüber dem Gasdurchtritt durch die Leckagen in den Hintergrund.The piston is mounted in the cylinder substantially tight. A gas passage from the working space into the unpressurized space is essentially determined by the leakages. A gas leakage from the working space into the non-pressurized space which occurs due to leaks, in particular in the gasket, fades into the background in comparison with the gas passage through the leaks.

Der folgenden Beschreibung, den Unteransprüchen und den Zeichnungen sind vorteilhafte Ausführungsformen der Einrichtung zu entnehmen.

  • Fig. 1 zeigt eine schematische Darstellung einer Kompressoranordnung inklusive Stromversorgung, Antrieb und Schlauchverbindungen.
  • Fig. 2 stellt den Kraftübertragungs- und den Kompressionsmechanismus im Überblick dar.
  • Fig. 3 zeigt eine schematische Schnittdarstellung des sich im Zylinder befindlichen Kolbens.
  • Fig. 4 zeigt einen Querschnitt durch eine Dichtung.
  • Fig. 5 zeigt eine Draufsicht auf eine ringförmige Dichtung mit Schnitten.
The following description, the subclaims and the drawings, advantageous embodiments of the device can be seen.
  • Fig. 1 shows a schematic representation of a compressor assembly including power supply, drive and hose connections.
  • Fig. 2 provides an overview of the power transmission and compression mechanisms.
  • Fig. 3 shows a schematic sectional view of the piston located in the cylinder.
  • Fig. 4 shows a cross section through a seal.
  • Fig. 5 shows a plan view of an annular seal with cuts.

Gemäß Fig. 1 wird ein in diesem Fall elektromechanischer Antrieb 1 über eine nicht dargestellte Batterie gespeist, die über einen Zigarettenanzünderstecker 9 und ein Kabel 10 mit einer Steuerungskonsole 12 und über ein weiteres Kabel 13 mit dem Antrieb bzw. Elektromotor 1 verbunden ist. Mit einem an der Konsole 12 befindlichen Wippschalter 11 lässt sich die Stromzufuhr ein- und ausschalten.According to Fig. 1 an electromechanical drive 1 is fed in this case via a battery, not shown, which is connected via a cigarette lighter plug 9 and a cable 10 with a control console 12 and a further cable 13 to the drive or electric motor 1. With a rocker switch 11 located on the console 12, the power supply can be switched on and off.

Der in einem Antriebsraum 3 bzw. im Zylinder 2 befindliche Kompressionsmechanismus wird über diesen Antrieb 1 betätigt und das Arbeitsmittel, in diesem Fall Luft, wird über einen mit einer Klemme 4 am Auslass 22 des Zylinders 2 befestigten Druckschlauch 5 über ein Manometer 6 zur Druckkontrolle und über einen Auslass 8 zum Destinationsobjekt, z.B. Autoreifen, gedrückt.The compression mechanism located in a drive chamber 3 or in the cylinder 2 is actuated by this drive 1 and the working fluid, in this case air, via a with a terminal 4 at the outlet 22 of the cylinder 2 attached pressure hose 5 via a pressure gauge 6 for pressure control and via an outlet 8 to the destination object, eg car tires, pressed.

Wie Fig. 2 überblicksmäßig darstellt, ist eine Antriebswelle des Antriebes 1 im Antriebsraum 3 über eine Kurbel 23 mit einer Schubstange 14 verbunden, die im Zylinder 2 einen Kolben 20 in eine hin- und hergehende Bewegung versetzt, der das von der Wand des Zylinders 2 und dem Kolben 20 begrenzte Volumen des Arbeitsraumes 26 vor dem Kolben 20 bzw. das Volumen des drucklosen Raumes 24 hinter dem Kolben 20 verändert. Durch ein Rückschlagventil 27 wird die aus dem Auslass 22 gedrückte Luft am Zurückströmen in den Arbeitsraum 26 gehindert.As Fig. 2 Surprisingly, a drive shaft of the drive 1 in the drive chamber 3 via a crank 23 with a push rod 14 is connected, which puts a piston 20 in the cylinder 2 in a reciprocating motion, that of the wall of the cylinder 2 and the piston 20th limited volume of the working space 26 before the piston 20 and the volume of the unpressurized space 24 behind the piston 20 is changed. By a check valve 27, the compressed air from the outlet 22 is prevented from flowing back into the working space 26.

Der in Fig. 3 vergrößert dargestellte, im Zylinder 2 befindliche Kolben 20 umfasst eine an der Schubstange 14 fixierte tellerförmige Führungsscheibe 16 auf seiner Kopf- bzw. Arbeitsraumseite 26, eine ebenfalls an der Schubstange 14 fixierte und gegebenenfalls mit der Führungsscheibe 16 im Innenbereich fest verbundene tellerförmige Stützscheibe 15 auf seiner Rückseite bzw. seiner dem drucklosen Raum 24 zugekehrten Seite und eine an die Wand des Zylinders 2 anliegende ringförmige Dichtung 17. Die Führungsscheibe 16 ist in den Innenbereich, einen vorzugsweise parallel zur Wand des Zylinders 2 verlaufenden Mittelteil 28 und einen endständigen peripheren Flansch 25' gegliedert. Die Stützscheibe 15 gliedert sich ebenfalls in einen Innenbereich, einen Mittelteil und einen endständigen peripheren Flansch 25. Die Dichtung 17 befindet sich höhenmäßig zwischen den beiden peripheren Flanschen 25, 25' der Stützscheibe 15 und der Führungsscheibe 16 im Umfangsbereich des Kolbens 20. Zwischen der Dichtung 17, der Stützscheibe 15 und der Führungsscheibe 16 bzw. deren peripheren Flanschen 25, 25' befindet sich ein Freiraum 27.The enlarged shown in Fig. 3, located in the cylinder 2 piston 20 comprises a fixed to the push rod 14 plate-shaped guide plate 16 on its head or working space side 26, a likewise fixed to the push rod 14 and optionally fixedly connected to the guide disc 16 in the interior dish-shaped support disk 15 on its rear side or its pressure-free space 24 facing side and an applied to the wall of the cylinder 2 annular seal 17. The guide disk 16 is in the inner region, a preferably parallel to the wall of the cylinder 2 extending middle part 28 and a terminal peripheral flange 25 'articulated. The support disk 15 is also divided into an inner region, a central part and a terminal peripheral flange 25. The seal 17 is located between the height of the two peripheral flanges 25, 25 'of the support disk 15 and the guide disk 16 in the peripheral region of the piston 20. Between the seal 17, the support disk 15 and the guide disk 16 and their peripheral flanges 25, 25 'is a free space 27th

Die der Innenwand des Zylinders 2 zugekehrte Fläche der Dichtung 17 ist konkav nach außen, insbesondere mit kreisförmiger Krümmung, gewölbt, um die leicht pendelnde Bewegung des im vorliegenden Fall nur über die Schubstange 14 und nicht über einen Kreuzkopf geführten Kolbens 20 auszugleichen bzw. zuzulassen und dabei einen ständigen dichten Kontakt zwischen der Wand des Zylinders 2 und der Dichtung 17 zu gewährleisten.The inner surface of the cylinder 2 facing surface of the seal 17 is concave outward, in particular with a circular curvature, curved to compensate for the slightly oscillating movement of the present case only via the push rod 14 and not a crosshead guided piston 20 and to ensure a permanent tight contact between the wall of the cylinder 2 and the seal 17.

Die Dichtung 17 weist an ihrer dem Arbeitsraum 26 zugewandten Seite einen im Querschnitt schmalen Kopfbereich 40 und an der dem Arbeitsraum 26 abgewandten Seite einen im Querschnitt breiteren Fußbereich 41 auf. In der Höhe des Kopfbereiches 40 ist an der Innenfläche der Dichtung 17 vorteilhafterweise eine Ausnehmung 43 ausgebildet, in die ein Federring 18 insbesondere fest und vorzugsweise mit Passsitz eingesetzt ist. Dieser Federring 18 liegt demgemäß zwischen dem Mittelteil 28 der Führungsscheibe 16 und dem Kopfbereich 40 der Dichtung 17. Der Federring 18 ist bei einer Hubbewegung des Kolbens 20 entlang bzw. vor diesem Mittelteil 28 der Führungsscheibe 16 auf- und ab bewegbar, wobei seine Aufwärtsbewegung bzw. sein Aufwärtsweg vom peripheren Flansch 25' der Führungsscheibe 16 begrenzt ist. Die Dichtung 17 wird mittels dieses Federringes 18 radial nach außen bzw. an die seitliche Wand des Zylinders 2 gedrückt und verhindert dort einen unerwünschten Gasdurchtritt. Anstelle des Federringes 18 kann auch ein federnder Spannring eingesetzt werden. In beiden Fällen ist jedoch ein Luftdurchtritt zwischen dem Freiraum 27 und dem Arbeitsraum 26 an dieser Stelle möglich.The seal 17 has, on its side facing the working space 26, a head area 40 that is narrow in cross-section and a foot area 41 that is wider in cross-section on the side facing away from the working space 26. In the height of the head portion 40, a recess 43 is advantageously formed on the inner surface of the seal 17, in which a spring ring 18 is in particular fixed and preferably inserted snugly. This spring ring 18 is accordingly between the central part 28 of the guide disc 16 and the head portion 40 of the seal 17. The spring ring 18 is movable in a lifting movement of the piston 20 along or in front of this central part 28 of the guide disc 16 and up, with its upward movement or ., Its upward path from the peripheral flange 25 'of the guide disc 16 is limited. The seal 17 is pressed by means of this spring ring 18 radially outward or on the lateral wall of the cylinder 2 and prevents there an undesirable gas passage. Instead of the spring ring 18 and a resilient clamping ring can be used. In both cases, however, an air passage between the space 27 and the working space 26 at this point is possible.

Die Höhe H der Dichtung 17, gemessen in Bewegungsrichtung des Kolbens 20, ist geringer als der zwischen den Innenseiten der peripheren Flanschen 25, 25' der Stützscheibe 15 und der Führungsscheibe 16 gemessene Abstand A. Dementsprechend ist die Bewegungsamplitude der Dichtung 17 auf die Differenz D zwischen der Höhe H der Dichtung 17 und dem Abstand A der peripheren Flansche 25, 25' der Stützscheibe 15 und der Führungsscheibe 16 beschränkt. Diese Ausführung bewirkt bei einer Ansaugbewegung, das heißt bei einer Bewegung des Kolbens 20 in Richtung der Kurbel 23, ein Abheben der Dichtung 17 von der Stützscheibe 15 um den Betrag D und ermöglicht damit ein Nachströmen von Gas über den Freiraum 27 in den kopfseitigen Arbeitsraum 26. Beim Kompressionshub wird die Dichtung 17 dicht an den peripheren Flansch 25 der Stützscheibe 15 gedrückt und ein Gasdurchtritt ist nur mehr durch die im folgenden beschriebenen definierten Leckagen 19 möglich. Die im Arbeitsraum 26 komprimierte Luft wird durch ein Rückschlagventil 27 aus dem Auslass 22 gedrückt und durch dieses Rückschlagventil 27 gleichzeitig am Zurückströmen in den Arbeitsraum 26 gehindert.The height H of the seal 17, measured in the direction of movement of the piston 20, is less than the distance A measured between the inner sides of the peripheral flanges 25, 25 'of the support disk 15 and the guide disk 16. Accordingly, the amplitude of movement of the seal 17 is at the difference D between the height H of the seal 17 and the distance A of the peripheral flanges 25, 25 'of the support disk 15 and the guide disk 16 is limited. This embodiment causes in a suction movement, that is, upon movement of the piston 20 in the direction of the crank 23, a lifting of the seal 17 of the support disk 15 by the amount D, thus allowing a backflow of gas through the space 27 in the head-side working space 26th In the compression stroke, the seal 17 is pressed tight against the peripheral flange 25 of the support disk 15, and gas passage is only possible through the defined leakages 19 described below. The compressed air in the working chamber 26 is pressed by a check valve 27 from the outlet 22 and prevented by this check valve 27 at the same time flowing back into the working space 26.

Die Dichtung 17 besteht aus einem weitgehend hitzestabilen und/oder weitgehend abriebfesten Polymer, insbesondere mit guten Lauf- und Gleiteigenschaften, vorzugsweise Polytetrafluorethylen (PTFE, Teflon) oder Polytetrafluorethylen-Compounds, und kann gegebenenfalls mit Kohle- oder Kohlenstofffasern und/oder -partikeln in einem Anteil von 10 bis zu 20 Gew-%, vorzugsweise von 15 bis 25 Gew-%, des PTFE- bzw. PTFE-Compound-Gewichts, verstärkt werden.The seal 17 consists of a largely heat-stable and / or substantially abrasion-resistant polymer, in particular with good running and sliding properties, preferably polytetrafluoroethylene (PTFE, Teflon) or polytetrafluoroethylene compounds, and optionally with carbon or carbon fibers and / or particles in one Proportion of 10 to 20% by weight, preferably from 15 to 25% by weight, of the PTFE or PTFE compound weight, are reinforced.

Die Anzahl der Leckagen 19, ebenso wie ihre Form bzw. Querschnittsform richtet sich nach der Leistung der Antriebsmechanismus, der Höhe des Anfangsgegendrucks, der Größe und Bauart der Kompressoreinrichtung, der Form des Kolbens usw. Die Leckagen 19 können durch Bohrungen, Einfräsungen, Ausnehmungen, Einsickungen oder dgl. ausgebildet werden, wobei deren Formgebung auch durch die Herstellungsmethode bestimmt wird. Dementsprechend können die Leckagen 19 im Querschnitt rund, eckig oder auch unregelmäßig geformt ausbildet sein. Die gesamte Querschnittsfläche der zumindest einen Leckage 19 beträgt pro cm3 Hubvolumen des Kolbens 20 zwischen 0,005 und 0,1 mm2, vorzugsweise 0,01 und 0,06 mm2.The number of leaks 19, as well as their shape or cross-sectional shape depends on the performance of the drive mechanism, the amount of the initial back pressure, the size and design of the compressor device, the shape of the piston, etc. The leaks 19 can through holes, milled recesses, Infiltrations or the like. Be formed, the shape of which is also determined by the production method. Accordingly, the leaks 19 may be formed in cross-section round, square or irregular shaped. The total cross-sectional area of the at least one leakage 19 per cm 3 stroke volume of the piston 20 is between 0.005 and 0.1 mm 2 , preferably 0.01 and 0.06 mm 2 .

Die Ausbildung der Leckagen 19 kann konstruktionsbedingt in der Stützscheibe 15 und/oder der Führungsscheibe 16 erfolgen, sowohl in den Außenbereichen, also den peripheren Flanschen 25, 25', insbesondere im peripheren Flansch 25 der Stützscheibe 15, als auch in den Innenbereichen, wobei zu beachten ist, dass bei Ausbildung in den fest und plan miteinander verbundenen Innenbereichen der Scheiben 15,16, die Leckagen 19 vorteilhafterweise fluchtend angeordnet sind. Des Weiteren besteht die Möglichkeit der Ausbildung von Leckagen im gesamten Bereich der Dichtung 17, insbesondere in der der Innenseite des peripheren Flansches 25 der Stützscheibe 15 zugekehrten Endfläche der Dichtung 17.The formation of the leaks 19 can be done by design in the support plate 15 and / or the guide plate 16, both in the outer regions, ie the peripheral flanges 25, 25 ', in particular in the peripheral flange 25 of the support plate 15, as well as in the interior areas, to It should be noted that when training in the fixed and plan interconnected inner areas of the discs 15,16, the leaks 19 are advantageously arranged in alignment. Furthermore, there is the possibility of the formation of leaks in the entire region of the seal 17, in particular in the inside of the peripheral flange 25 of the support plate 15 facing the end face of the seal 17th

Fig. 4 zeigt einen Querschnitt durch die Dichtung 17. Gut zu erkennen sind der dem Arbeitsraum 26 zugekehrte, im Querschnitt schmale Kopfbereich 40 mit der an seiner Innenseite für den Federring 18 vorgesehenen Ausnehmung 43 und der etwas dickere Fußbereich 41. Im Kopfbereich 40 sind Schnitte 45 ausgebildet. Zu Charakteristik der Schnitte 45 ist zu bemerken, dass die Schnitte 45 ohne Materialabtragung ausgebildet werden, also nicht gefräst, gesägt o.ä. werden. Die Schnitte 45 reichen, ausgehend von der oberen Endfläche des Kopfbereichs 40 der Dichtung 17, mindestens bis zum Beginn des Berührungsbereichs 44 der Dichtung 17 mit der Innenwand des Zylinders 2, der sich in der Praxis durch die Kompression der Dichtung 17 an die Wand des Zylinders 2 bzw. durch die taumelnden Bewegungen des Kolbens 20 ergibt. Vorzugsweise reichen die Schnitte 45 jedoch, ausgehend von der oberen Endfläche des Kopfbereichs 40 der Dichtung 17, bis zur in Fig. 5 geometrischen ermittelten, theoretischen Berührungslinie 42 der konkaven Dichtung 17 mit der Innenwand des Zylinders 2. Eine Alternative ist auch, dass die Schnitte 45, ausgehend von der oberen Endfläche des Kopfbereichs 40 der Dichtung 17, mindestens bis zum unteren Ende der Ausnehmung 43 reichen. Maximal reichen die Schnitte 45, gemessen von der oberen Endfläche des Kopfbereichs 40 der Dichtung 17, bis zum Beginn des Fußbereichs 41 der Dichtung 17, also bis in eine maximale Tiefe T. Fig. 4 shows a cross section through the seal 17. Good to see the working space 26 facing, narrow in cross-section head portion 40 with the at its Inner side of the spring ring 18 provided recess 43 and the slightly thicker foot portion 41. In the head portion 40 cuts 45 are formed. With regard to the characteristics of the cuts 45, it should be noted that the cuts 45 are made without material removal, ie are not milled, sawn, or the like. become. The cuts 45 extend, starting from the upper end surface of the head portion 40 of the seal 17, at least until the beginning of the contact region 44 of the seal 17 with the inner wall of the cylinder 2, which in practice by the compression of the seal 17 against the wall of the cylinder 2 or by the tumbling movements of the piston 20 results. Preferably, however, the cuts 45 extend from the upper end surface of the head portion 40 of the gasket 17 to the in Fig. 5 geometrically determined, theoretical contact line 42 of the concave seal 17 with the inner wall of the cylinder 2. An alternative is also that the cuts 45, starting from the upper end face of the head portion 40 of the seal 17, at least extend to the lower end of the recess 43. The maximum cuts 45, measured from the upper end surface of the head portion 40 of the seal 17, to the beginning of the foot portion 41 of the seal 17, ie to a maximum depth T.

Fig. 5 zeigt eine Draufsicht vom Arbeitsraum 26 auf die ringförmige Dichtung 17. Die Schnitte 45 durchsetzen den Kopfbereich 40 der Dichtung 17 vollständig. Die vorzugsweise 6 bis 12, insbesondere 8 bis 10, hier 9 Schnitte 45 sind längs des Umfangs der ringförmigen Dichtung 17 und in gleichen Abständen zueinander verteilt und sind relativ zum Radius R der Dichtung 17 in die gleiche Richtung geneigt, vorzugsweise mit einem Winkel a zwischen 30 und 80°, insbesondere zwischen 40 und 70°. Die Flächen der Schnitte 45 sind eben und sind senkrecht zu der von der Dichtung 17 aufgespannten Ebene ausgerichtet. Die Schnitte 45 sind vorteilhafterweise untereinander gleich ausgebildet bzw. besitzen gleiche Form bzw. Abmessungen. Fig. 5 shows a plan view of the working space 26 on the annular seal 17. The cuts 45 pass through the head portion 40 of the seal 17 completely. The preferably 6 to 12, in particular 8 to 10, here 9 cuts 45 are distributed along the circumference of the annular seal 17 and at equal distances from each other and are inclined relative to the radius R of the seal 17 in the same direction, preferably at an angle a between 30 and 80 °, in particular between 40 and 70 °. The surfaces of the cuts 45 are flat and are aligned perpendicular to the plane spanned by the seal 17. The cuts 45 are advantageously identical to each other or have the same shape or dimensions.

Unter Leckage wird eine ständig offene (Gas)Durchlassverbindung zwischen dem vor und dem hinter dem Kolben liegenden Raum verstanden.Leakage is understood to mean a constantly open (gas) passage connection between the space in front of and behind the piston.

Claims (10)

  1. A device for compressing gases, especially air, preferably for inflating the tires of vehicles, having a piston (20) which is driven by a drive which especially is electromechanic and preferably connected to a battery, which is supported in a cylinder (2) and may be moved upwards and downwards, and which comprises an annular seal (17) adjacent to the interior wall of said cylinder (2), said annular seal (17) having a top portion (40) facing the working space (26) in front of the piston (20) and a bottom portion (41) facing the unpressurised space (24) behind the piston (20), said annular seal (17) having a number of incisions (45), preferably 6 to 12, especially 8 to 10, which are formed without taking off any material and especially serve to improve the sealing and compression behaviour, characterised in
    - that said incisions (45) extend through the entire top portion (40) of said seal (17) from the outer circumference to the inner area of the seal (17) and
    - that the incisions (45) maximally extend from the top end surface of the top portion (40) of the seal (17) to the beginning of a bottom area (41) of the seal (17), i.e. to a depth (T).
  2. The device according to claim 1, characterised in that said piston (20) comprises: a guiding disc (16) which is attached to its connecting rod (14), is preferably plate-shaped and has a middle section (28) which is preferably parallel to the cylinder's (2) wall, and a peripheral flange (25') which is disposed at its top side or at the side facing a working space (26); a supporting disc (15) which is attached to the connecting rod (14) and is preferably plate-shaped, said supporting disc (15) having a middle section and a peripheral flange (25) at its back side or at the side facing the unpressurised space (24), said annular seal (17) being optionally disposed in the circumferential area of the piston (20) between the two peripheral flanges (25, 25') of the supporting disc (15) and the guiding disc (16), respectively.
  3. The device according to claim 1 and claim 2, characterised in that the seal (17) is made of a largely heat-resistant and/or a largely abrasion-resistant polymer, especially having good running and sliding characteristics, preferably of polytetrafluoroethylene (PTFE, Teflon) or polytetrafluoroethylene composites which are optionally reinforced with carbon fibres and/or particles which are contained in an amount of 10 to 20 % by weight, preferably of 15 to 25 % by weight, of the weight of the PTFE or the PTFE compound.
  4. The device according to any one of the claims 1 to 3, characterised in that the outer surface of the seal (17) which is facing the wall of the cylinder (2) is curved outwards in a concave shape, especially having a circular curve, and/or
    - that the seal (17) has a top portion (40) which is narrow in section at the side facing the working space (26) and a bottom portion (41) which is wider in section than the top portion (40) at the side which is turned away from said working space (26), a recess (43) being optionally formed in the inner surface of the top portion (40), and/or
    - that a circular, air permeable spring ring (18), preferably a coil spring compression ring, is disposed adjacent to the inner surface of the seal (17) between said seal (17) and the middle section (28) of the guiding disc (16), preferably in the recess (43) in the top area (40) of the seal (17), into which it is particularly preferably snugly fit, said spring ring (18) pressing the seal (17) against the inner wall of the cylinder (2).
  5. The device according to any one of the claims 1 to 4, characterised in that the height (H) of the seal (17) is smaller than the distance (A) measured between the inner surfaces of the peripheral flanges (25, 25') of the supporting disc (15) and the guiding disc (16), respectively.
  6. The device according to any one of the claims 2 to 5, characterised in that the spring ring (18) is moved upwards and downwards along the middle section (28) of the guiding disc (16) depending on the piston's (20) stroke movement and in that the upward movement or the upward travel of the spring ring (18) is limited by the peripheral flange (25') of the guiding disc (16), and/or
    - in that an end face of the seal (17) which is turned away from the working space is supported by the peripheral flange (25') of the supporting disc (15) during the compression stroke of the piston (20) and in that an end face of the spring ring (18) and/or the seal (17) which faces the working space is/are supported by the peripheral flange (25') of the guiding disc (16) during the intake stroke of the piston (20), and/or
    - in that the supporting disc (15) and the guiding disc (16) are connected to the connecting rod (14) and optionally are connected to each other at their inner sides.
  7. The device according to any one of the claims 1 to 6, characterised in that at least one defined leak (19) is provided in the piston (20) for letting gas pass from the working space (26) in front of the piston (20) into the unpressurised space (24) behind the piston (20) during the compression stroke, the entire sectional area of the at least one leakage (19) optionally amounting to 0.005 to 0.1 mm2, preferably to 0.01 to 0.06 mm2, per cm3 of the piston displacement, and/or
    - that the leak(s) (19) is/are formed as milled-out portions, recesses, grooves, bores, or the like in the supporting disc (15) and/or the guiding disc (16) and in the peripheral flange (25) of the supporting disc (15) and/or in the seal (17), especially in the end face of the seal (17) facing the peripheral flange (25) of the supporting disc (15), and/or
    - that the leaks (19) in the supporting disc (15) and the leaks in the guiding disc (16) are aligned.
  8. The device according to any one of the claims 1 to 7, characterised in that the incisions (45), starting at the top end face of the top area (40) of the seal (17), extend at least up to a depth to the beginning of the contact area (44) of the seal (17) and the inner wall of the cylinder (2), preferably to the theoretical, geometric contact line (42) of the seal (17) and the inner wall of the cylinder (2), and/or
    - in that the incisions (45), starting at the top end face of the top area (40) of the seal (17), extend at least to the bottom end of the recess (43).
  9. The device according to any one of the claims 1 to 8, characterised in that the surfaces of the incisions (45) are flat and extend vertically to the plane of the seal (17).
  10. The device according to any one of the claims 1 to 9, characterised in that the incisions (45) are distributed at regular intervals along the circumference of the annular seal (17), the distances between them being equal, and/or
    - in that all incisions (45) are inclined in the same direction in relation to the radius (R) of the seal (17), preferably at an angle (a) between 30 and 80°, particularly preferably at an angle (a) between 40 and 70°, and/or
    - in that the incisions (45) all have the same form and/or the same dimensions.
EP03737736A 2002-07-24 2003-07-23 Device for compressing gases Expired - Lifetime EP1527278B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT0112702A AT414270B (en) 2002-07-24 2002-07-24 DEVICE FOR COMPACING GASES
AT11272002 2002-07-24
PCT/AT2003/000210 WO2004011805A1 (en) 2002-07-24 2003-07-23 Device for compressing gases

Publications (2)

Publication Number Publication Date
EP1527278A1 EP1527278A1 (en) 2005-05-04
EP1527278B1 true EP1527278B1 (en) 2011-10-26

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Application Number Title Priority Date Filing Date
EP03737736A Expired - Lifetime EP1527278B1 (en) 2002-07-24 2003-07-23 Device for compressing gases

Country Status (4)

Country Link
EP (1) EP1527278B1 (en)
AT (2) AT414270B (en)
AU (1) AU2003245104A1 (en)
WO (1) WO2004011805A1 (en)

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Publication number Priority date Publication date Assignee Title
CN103573611A (en) * 2012-07-20 2014-02-12 株式会社日立产机系统 Reciprocating compressor

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US2274304A (en) * 1939-09-05 1942-02-24 Clarence J Perry Piston
FR1116445A (en) * 1954-08-10 1956-05-08 Tecalemit Seal for scraper piston used for emptying drums
AU412693B1 (en) * 1967-06-27 1971-04-27 Manilyn Air Compressors Pty. Limited Improvements in or relating to air compressors
DE2235987A1 (en) * 1972-07-21 1974-01-31 Linde Ag PISTONS FOR PISTON MACHINE, IN PARTICULAR FOR DRY RUNNING
US3897072A (en) * 1973-02-12 1975-07-29 Crane Packing Co Slit ring with connecting membrane
JPS62255666A (en) * 1986-04-28 1987-11-07 N D C Kk Piston member for strut
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DE4429097A1 (en) * 1994-08-17 1996-02-22 Thurner Bayer Druckguss Piston compressor for gaseous media
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DK28697A (en) * 1997-03-14 1998-09-15 Man B & W Diesel As Piston for an internal combustion engine, in particular a two-stroke diesel engine
DE29717654U1 (en) * 1997-10-02 1998-11-12 Alusuisse Bayrisches Druckguß-Werk GmbH & Co. KG, 85570 Markt Schwaben Piston for a piston compressor
DE29814962U1 (en) * 1998-08-20 1999-11-04 Alusuisse Bayrisches Druckguß-Werk GmbH & Co. KG, 85570 Markt Schwaben Piston for a piston compressor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103573611A (en) * 2012-07-20 2014-02-12 株式会社日立产机系统 Reciprocating compressor
CN103573611B (en) * 2012-07-20 2015-11-25 株式会社日立产机系统 Reciprocal compressor

Also Published As

Publication number Publication date
EP1527278A1 (en) 2005-05-04
AU2003245104A1 (en) 2004-02-16
AT414270B (en) 2006-10-15
ATA11272002A (en) 2006-01-15
WO2004011805A1 (en) 2004-02-05
ATE530769T1 (en) 2011-11-15

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