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EP1989443B1 - Reciprocating-piston compressor having non-contact gap seal - Google Patents

Reciprocating-piston compressor having non-contact gap seal Download PDF

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Publication number
EP1989443B1
EP1989443B1 EP07722864A EP07722864A EP1989443B1 EP 1989443 B1 EP1989443 B1 EP 1989443B1 EP 07722864 A EP07722864 A EP 07722864A EP 07722864 A EP07722864 A EP 07722864A EP 1989443 B1 EP1989443 B1 EP 1989443B1
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EP
European Patent Office
Prior art keywords
cylinder
reciprocating
piston
piston rod
piston compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP07722864A
Other languages
German (de)
French (fr)
Other versions
EP1989443A1 (en
Inventor
Michel Rigal
Gilles Hebrard
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
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Publication date
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Publication of EP1989443A1 publication Critical patent/EP1989443A1/en
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Publication of EP1989443B1 publication Critical patent/EP1989443B1/en
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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
    • F04B25/00—Multi-stage pumps
    • F04B25/005—Multi-stage pumps 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
    • F04B25/00—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B3/00—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod

Definitions

  • the invention relates to a reciprocating compressor with at least two successively arranged along a cylinder axis working cylinders, in each of which a piston is guided axially movable, wherein the pistons have a common axially actuated piston rod which extends through a passage opening in a partition wall between the working cylinders , according to the preamble of claim 1.
  • a contact seal in the form of a sealing ring is usually provided between the passage opening and the piston rod in order to seal the working cylinders arranged in series behind one another.
  • the contact seals used so far provide friction, so that in view of the high number of compression strokes relatively large friction losses occur, which are reflected in high temperatures of up to 300 ° C in the gasket. For these reasons, a low-friction and heat-resistant material is necessary for the seals, which is correspondingly expensive.
  • a generic reciprocating compressor is for example from the EP 0 064 481 A which discloses the features defined in the preamble of claim 1, or DE 195 01 220 A1 known.
  • DE 44 09 751 A1 a pneumatic cylinder is described in which a roller bearing piston rod is sealed by non-contact seals against housing covers.
  • the seals are designed as gap seals around circumferential grooves.
  • a gap seal arranged on the outer circumference of the piston ensures a sealing of two working spaces against one another.
  • the present invention has for its object to further develop a reciprocating compressor of the type mentioned in such a way that it is cheaper to manufacture.
  • the invention is based on the idea of sealing the working cylinders in the region of the piston rod exclusively by means of a non-contact seal in the form of an axial gap seal formed between a radially outer peripheral surface of the piston rod and a radially inner peripheral surface of the throughbore.
  • the piston rod should extend through the through hole without Eisenorclnung a separate contact seal. Then the usual contact seals in the partitions between the working cylinders can be omitted, which bring the disadvantages mentioned above with it.
  • the invention uses the viscosity properties of the air, due to which compressed air with a rapid increase in pressure has a lower tendency to pass through a narrow gap than at a slower pressure increase.
  • the axially extending annular gap between the radially outer circumferential surface of the piston rod and the radially inner circumferential surface of the through hole forms a throttle, at which the gap flow loses pressure energy.
  • the gap consequently lowers a high pressure level to a substantially low level as a result of the throttling.
  • the leakage current flowing through the gap seal increases from one working cylinder to the other Working cylinder in the subsequent reversing movement of the piston rod to be compressed air volume in an advantageous manner.
  • At least the radially inner peripheral surface of the through-bore is provided with radial grooves arranged at an axial distance from one another.
  • the fluid flows from one chamber of the one higher pressure working cylinder into a lower pressure chamber of the other working cylinder through a plurality of constricted throttling points formed by the constrictions of the passage opening located between the grooves.
  • the kinetic energy of the fluid flow is almost completely converted to frictional heat, i. converted into energy loss.
  • the invention could also be embodied in a multi-stage reciprocating compressor, which performs a multi-stage compression of the intake air and in which each cylinder is associated with a compression stage.
  • the invention is used in a reciprocating compressor of an air brake system of a commercial vehicle for the reasons already mentioned above.
  • the in Fig.1 Reciprocating compressor 1 shown is of the type in which a plurality, preferably two cylinders 2, 4 are connected in series, wherein the cylinders 6, 8 axially guided in the cylinders 2, 4 are connected to a common piston rod 10, which is not shown for reasons of scale
  • Internal combustion engine of the commercial vehicle for generating compressed air for the compressed air brake system is driven in a reversible manner.
  • each of the cylinders 2, 4 in each case an independent compression operation of the input air, without first the compressed air generated by the one cylinder 2 is fed into the other cylinder 4 or vice versa.
  • the two cylinders 2, 4 each consist of a shell casing 12, 14, which are closed at the ends by bottom plates 18, 20, 22, 24 provided with passage openings 16.
  • the cylinders 2, 4 axially interposed is also a partition 26, in which at least one continuous, each with the associated passage opening 16 in the bottom plates 18, 20, 22, 24 of the cylinder 2, 4 aligned input channel 28 and an output channel 30 and a through hole 32 is formed for the piston rod 10.
  • the output channel 30 is via an output terminal extending transversely to it 34 with a compressed air supply, not shown, and the input channel 28 with a likewise extending transversely to him input terminal 36 with the environment in connection.
  • the passage openings 16 of the bottom plates 20, 22, which at the not the partition 26 facing the end of the shell casing 12; 14 are also aligned with input terminals 38, 42 and output terminals 40, 44, which are formed in these bottom plates 20, 22 axially mounted end pieces 46, 48.
  • a central passage opening 50 for the piston rod 10 is present in the bottom plate 20 and in the end piece 48 of the one cylinder 2, which is contacted by a bovine seal 54 held in a radially inner groove 52 of the end piece 48.
  • the pistons 6, 8 divide the cylinders 2, 4 respectively into a first cylinder chamber 56, 58 and into a second cylinder chamber 60, 62, the size of which depends on the respective position of the piston 6, 8.
  • the ring seal 54 then serves to seal the first cylinder chamber 56 of the one cylinder 2 from the environment.
  • the pistons 6, 8 also carry seals 64 at their radially outer circumferential surfaces, which seal the first cylinder chamber 56, 58 and the second cylinder chamber 60, 62 against each other.
  • the previously described seals 54, 64 are all contact seals, that is, the seal 54, 64 contacts the respective tread associated therewith.
  • an axial gap seal 66 is provided, which is preferably formed in the present case as a labyrinth gap seal.
  • a smooth-cylindrical or stepped gap seal is possible.
  • a narrow axial gap 66 is formed between a radially outer peripheral surface of the piston rod 10 and a radially inner peripheral surface of the through-opening 32 of the partition wall 26, which otherwise also between the two bottom plates 18, 24 and the piston rod 10 is present.
  • radial grooves 68 arranged at an axial distance from one another.
  • the volume of the two first cylinder chambers 56, 58 decreases with simultaneous enlargement of the two second cylinder chambers 60, 62, so that with increasing pressure P 1, the air in the first cylinder chambers 56, 58 compressed and discharged via the output ports 34, 44 to which a manifold, not shown, is completed to supply the compressed compressed air to the compressed air reservoir.
  • This flow movement is in Fig.1 characterized by the black, drawn in thick solid lines arrows 70.
  • the volume of the second cylinder chambers 60, 62 is increased, whereby the pressure P 2 there sinks and air is sucked in via the input ports 36, 38, as indicated by the black bordered arrows 72.
  • the reciprocating compressor 1 ' has a multi-stage construction, ie during one stroke the air compressed by the one cylinder 2' in the first cylinder chamber 56 'is conducted into the second cylinder chamber 62' of the other cylinder 4 ' the Reversierhubes the piston rod 10 'to be subjected to a further compression before the compressed air is supplied via the output port 40' the compressed air reservoir.
  • the first cylinder chamber 56 'of the one cylinder 2' has no output ports but is in fluid communication with the second cylinder chamber 62 'of the other cylinder 4' by means of a compressed air connection in the form of a compressed air channel 78. Furthermore, the second cylinder chamber 60 'of the one cylinder 2' with the first cylinder chamber 58 'of the other cylinder 4' through an overflow channel 80 'is connected.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Glass Compositions (AREA)
  • Developing Agents For Electrophotography (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Actuator (AREA)

Abstract

Reciprocating compressor (1) comprises working cylinders (2, 4) sealed from each other in the region of a piston rod (10) by a seal in the form of an axial gap seal (66) formed between a radial outer peripheral surface of the piston rod and a radial inner peripheral surface of a through opening (32). An independent claim is also included for braking system of a vehicle actuated by compressed air an containing the above reciprocating compressor. Preferred Features: The radial inner peripheral surface of a through opening is provided with radial grooves (68) arranged at an axial distance from each other.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Hubkolbenverdichter mit wenigstens zwei hintereinander, entlang einer Zylinderachse angeordneten Arbeitszylindern, in welchen je ein Kolben axial beweglich geführt ist, wobei die Kolben eine gemeinsame axial betätigte Kolbenstange aufweisen, welche sich durch eine Durchgangsöffnung in einer Trennwand zwischen den Arbeitszylindern erstreckt, gemäß dem Oberbegriff von Anspruch 1.The invention relates to a reciprocating compressor with at least two successively arranged along a cylinder axis working cylinders, in each of which a piston is guided axially movable, wherein the pistons have a common axially actuated piston rod which extends through a passage opening in a partition wall between the working cylinders , according to the preamble of claim 1.

Bei den aus dem Stand der Technik bekannten Hubkolbenverdichtem ist üblicherweise zwischen der Durchgangsöffnung und der Kolbenstange eine Berührungsdichtung in Form eines Dichtrings vorgesehen, um die in Reihe hintereinander angeordneten Arbeitszylinder gegeneinander abzudichten. Vor allem beim Einsatz von Hubkolbenverdichtem in Druckluftbremsanlagen von Nutzfahrzeugen ist wegen des hohen Druckluftbedarfs eine hohe Verdichterleistung gefragt, so dass der Hubkolbenverdichter eine hohe Anzahl von Verdichtunghüben liefern muss. Die bisher verwendeten Berührungsdichtungen sorgen jedoch für Reibung, so dass angesichts der hohen Anzahl von Verdichtungshüben relativ große Reibungsverluste entstehen, welche sich auch in hohen Temperaturen von bis zu 300 °C im Bereich der Dichtung niederschlagen. Aus den genannten Gründen ist für die Dichtungen ein reibungsarmes und zugleich hitzebeständiges Material notwendig, welches entsprechend teuer ist.In reciprocating compressors known from the prior art, a contact seal in the form of a sealing ring is usually provided between the passage opening and the piston rod in order to seal the working cylinders arranged in series behind one another. Especially when using reciprocating compressors in air brake systems of commercial vehicles because of the high compressed air demand high compressor performance is in demand, so that the reciprocating compressor must deliver a high number of compression strokes. However, the contact seals used so far provide friction, so that in view of the high number of compression strokes relatively large friction losses occur, which are reflected in high temperatures of up to 300 ° C in the gasket. For these reasons, a low-friction and heat-resistant material is necessary for the seals, which is correspondingly expensive.

Ein gattungsgemäßer Hubkolbenverdichter ist beispielsweise aus der EP 0 064 481 A , welches die im Oberbegriff von Patentanspruch 1 definierten Merkmale offenbart, oder DE 195 01 220 A1 bekannt. In der DE 44 09 751 A1 wird ein Pneumatikzylinder beschrieben, bei dem eine wälzgelagerte Kolbenstange über berührungslose Dichtungen gegenüber Gehäusedeckeln abgedichtet ist. Die Dichtungen sind als Spaltdichtungen um umlaufenden Rillen ausgeführt. In gleicher Weise gewährleistet eine am Außenumfang des Kolbens angeordnete Spaltdichtung eine Abdichtung zweier Arbeitsräume gegeneinander.A generic reciprocating compressor is for example from the EP 0 064 481 A which discloses the features defined in the preamble of claim 1, or DE 195 01 220 A1 known. In the DE 44 09 751 A1 a pneumatic cylinder is described in which a roller bearing piston rod is sealed by non-contact seals against housing covers. The seals are designed as gap seals around circumferential grooves. In the same way, a gap seal arranged on the outer circumference of the piston ensures a sealing of two working spaces against one another.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, einen Hubkolbenverdichter der eingangs erwähnten Art derart weiter zu entwickeln, dass er günstiger zu fertigen ist.The present invention has for its object to further develop a reciprocating compressor of the type mentioned in such a way that it is cheaper to manufacture.

Diese Aufgabe wird erfindungsgemäß durch die Merkmale von Anspruch 1 gelöst.This object is achieved by the features of claim 1.

Offenbarung der ErfindungDisclosure of the invention

Die Erfindung beruht auf dem Gedanken, die Arbeitszylinder im Bereich der Kolbenstange ausschließlich durch eine berührungsfreie Dichtung in Form einer zwischen einer radial äußeren Umfangsfläche der Kolbenstange und einer radial inneren Umfangsfläche der Durchgangsbohrung ausgebildeten axialen Spaltdichtung gegeneinander abzudichten. Mit anderen Worten soll sich die Kolbenstange durch die Durchgangsöffnung ohne Zwischenorclnung einer separaten Berührungsdichtung erstrecken. Dann können die bisher üblichen Berührungsdichtungen in den Trennwänden zwischen den Arbeitszylindern entfallen, welche die eingangs erwähnten Nachteile mit sich bringen.The invention is based on the idea of sealing the working cylinders in the region of the piston rod exclusively by means of a non-contact seal in the form of an axial gap seal formed between a radially outer peripheral surface of the piston rod and a radially inner peripheral surface of the throughbore. In other words, the piston rod should extend through the through hole without Zwischenorclnung a separate contact seal. Then the usual contact seals in the partitions between the working cylinders can be omitted, which bring the disadvantages mentioned above with it.

Die Erfindung nutzt die Viskositätseigenschaften der Luft, aufgrund derer Druckluft unter schnellem Druckanstieg eine geringere Tendenz hat, einen engen Spalt zu passieren als bei langsamerem Druckanstieg. Vor dem Hintergrund der bei Hubkolbenluftverdichtem in Druckluftbremsanlagen von Nutzfahrzeugen üblichen hohen Anzahl von Verdichtungshüben je Zeit und damit schnellem Druckanstieg in den Arbeitszylindern ist folglich mit einer geringen Leckage zu rechnen.The invention uses the viscosity properties of the air, due to which compressed air with a rapid increase in pressure has a lower tendency to pass through a narrow gap than at a slower pressure increase. Against the background of the usual in Hubkolbenluftverdichtem in compressed air brake systems of commercial vehicles high number of compression strokes per time and thus rapid pressure increase in the working cylinders is therefore expected with a low leakage.

Der sich axial erstreckende Ringspalt zwischen der radial äußeren Umfangsfläche der Kolbenstange und der radial inneren Umfangsfläche der Durchgangsbohrung bildet eine Drossel, an welcher die Spaltströmung Druckenergie verliert. Der Spalt senkt abhängig von der Spaltweite folglich infolge der Drosselung ein hohes Druckniveau auf ein wesentlich niedriges Niveau ab.The axially extending annular gap between the radially outer circumferential surface of the piston rod and the radially inner circumferential surface of the through hole forms a throttle, at which the gap flow loses pressure energy. Depending on the gap width, the gap consequently lowers a high pressure level to a substantially low level as a result of the throttling.

Da der Hubkolbenverdichter reversierend ist, vergrößert der durch die Spaltdichtung strömende Leckagestrom von dem einen Arbeitszylinder in den anderen Arbeitszylinder das bei der anschließenden Reversierbewegung der Kolbenstange zu verdichtende Luftvolumen in vorteilhafter Weise.Since the reciprocating compressor is reversing, the leakage current flowing through the gap seal increases from one working cylinder to the other Working cylinder in the subsequent reversing movement of the piston rod to be compressed air volume in an advantageous manner.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der in den unabhängigen Ansprüchen angegebenen Erfindung möglich.The measures listed in the dependent claims advantageous refinements and improvements of the invention specified in the independent claims are possible.

Besonders bevorzugt ist zur Ausbildung einer Labyrinthspaltdichtung wenigstens die radial innere Umfangsfläche der Durchgangsbohrung mit in Axialabstand zueinander angeordneten radialen Nuten versehen. In einer solchen Labyrinthspaltdichtung strömt das Fluid- aus einer Kammer des einen Arbeitszylinders höheren Drucks in eine Kammer niedrigeren Drucks des anderen Arbeitszylinders durch mehrere eingeschnürte Drosselstellen, welche durch die zwischen den Nuten angeordneten Einschnürungen der Durchgangsöffnung gebildet werden. In den erweiterten Räumen nach den Drosselstellen, d.h. in den Nuten wird die kinetische Energie der Fluidströmung fast vollständig in Reibungswärme, d.h. in Verlustenergie umgesetzt.Particularly preferably, to form a labyrinth gap seal, at least the radially inner peripheral surface of the through-bore is provided with radial grooves arranged at an axial distance from one another. In such a labyrinth gap seal, the fluid flows from one chamber of the one higher pressure working cylinder into a lower pressure chamber of the other working cylinder through a plurality of constricted throttling points formed by the constrictions of the passage opening located between the grooves. In the extended spaces after the throttle points, i. in the grooves, the kinetic energy of the fluid flow is almost completely converted to frictional heat, i. converted into energy loss.

Gemäß einer Weiterbildung könnte die Erfindung auch bei einem mehrstufigen Hubkolbenverdichter ausgeführt sein, welcher eine mehrstufige Verdichtung der angesaugten Luft durchführt und bei welchem jeder Arbeitszylinder einer Verdichtungsstufe zugeordnet ist.According to a development, the invention could also be embodied in a multi-stage reciprocating compressor, which performs a multi-stage compression of the intake air and in which each cylinder is associated with a compression stage.

Besonders bevorzugt wird die Erfindung bei einem Hubkolbenverdichter einer Druckluftbremsanlage eines Nutzfahrzeugs aus den oben bereits genannten Gründen eingesetzt.Particularly preferably, the invention is used in a reciprocating compressor of an air brake system of a commercial vehicle for the reasons already mentioned above.

Genaueres geht aus der folgenden Beschreibung von Ausführungsbeispielen hervor.More specifically, it will be apparent from the following description of embodiments.

Zeichnung.Drawing.

Nachstehend sind Ausführungsbeispiele der Erfindung in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. In der Zeichnung zeigt

Fig.1
eine Querschnittsdarstellung eines Hubkolbenverdichters gemäß einer bevorzugten Ausführungsform der Erfindung in einer ersten Stellung,
Fig.2
den Hubkolbenverdichter von Fig.1 in einer zweiten Stellung;
Fig.3
eine Querschnittsdarstellung eines Hubkolbenverdichters gemäß einer weiteren Ausführungsform der Erfindung in einer ersten Stellung;
Fig.4
den Hubkolbenverdichter von Fig.2 in einer zweiten Stellung:
Embodiments of the invention are illustrated in the drawings and explained in more detail in the following description. In the drawing shows
Fig.1
1 is a cross-sectional view of a reciprocating compressor according to a preferred embodiment of the invention in a first position,
Fig.2
the reciprocating compressor of Fig.1 in a second position;
Figure 3
a cross-sectional view of a reciprocating compressor according to another embodiment of the invention in a first position;
Figure 4
the reciprocating compressor of Fig.2 in a second position:

Beschreibung der AusführungsbeispieleDescription of the embodiments

Der in Fig.1 gezeigte Hubkolbenverdichter 1 ist von dem Typ, bei welchem mehrere, bevorzugt zwei Zylinder 2, 4 hintereinandergeschaltet sind, wobei die in den Zylindern 2, 4 axial geführten Kolben 6, 8 mit einer gemeinsamen Kolbenstange 10 verbunden sind, welche von einer aus Maßstabsgründen nicht gezeigten Brennkraftmaschine des Nutzfahrzeugs zur Erzeugung von Druckluft für die Druckluftbremsanlage in reversierender Weise angetrieben wird. Hierbei erfolgt in jedem der Zylinder 2, 4 jeweils ein unabhängiger Verdichtungsvorgang der Eingangsluft, ohne dass zunächst die von dem einen Zylinder 2 erzeugte Druckluft in den anderen Zylinder 4 eingespeist wird oder umgekehrt.The in Fig.1 Reciprocating compressor 1 shown is of the type in which a plurality, preferably two cylinders 2, 4 are connected in series, wherein the cylinders 6, 8 axially guided in the cylinders 2, 4 are connected to a common piston rod 10, which is not shown for reasons of scale Internal combustion engine of the commercial vehicle for generating compressed air for the compressed air brake system is driven in a reversible manner. In this case, in each of the cylinders 2, 4 in each case an independent compression operation of the input air, without first the compressed air generated by the one cylinder 2 is fed into the other cylinder 4 or vice versa.

Die beiden Zylinder 2, 4 bestehen aus jeweils einem Mantelgehäuse 12, 14, welche endseitig durch mit Durchgangsöffnungen 16 versehene Bodenplatten 18, 20, 22, 24 verschlossen sind. Den Zylindern 2, 4 axial zwischengeordnet ist außerdem eine Trennwand 26, in welcher wenigstens ein durchgehender, jeweils mit der zugeordneten Durchgangsöffnung 16 in den Bodenplatten 18, 20, 22, 24 der Zylinder 2, 4 fluchtender Eingangskanal 28 und ein Ausgangskanal 30 sowie eine Durchgangsöffnung 32 für die Kolbenstange 10 ausgebildet ist. Der Ausgangskanal 30 steht über einen quer zu ihm verlaufenden Ausgangsanschluss 34 mit einem nicht gezeigten Druckluftvorrat und der Eingangskanal 28 mit einem ebenfalls quer zu ihm verlaufenden Eingangsanschluss 36 mit der Umgebung in Verbindung.The two cylinders 2, 4 each consist of a shell casing 12, 14, which are closed at the ends by bottom plates 18, 20, 22, 24 provided with passage openings 16. The cylinders 2, 4 axially interposed is also a partition 26, in which at least one continuous, each with the associated passage opening 16 in the bottom plates 18, 20, 22, 24 of the cylinder 2, 4 aligned input channel 28 and an output channel 30 and a through hole 32 is formed for the piston rod 10. The output channel 30 is via an output terminal extending transversely to it 34 with a compressed air supply, not shown, and the input channel 28 with a likewise extending transversely to him input terminal 36 with the environment in connection.

Die Durchgangsöffnungen 16 der Bodenplatten 20, 22, welche an dem nicht der Trennwand 26 zugewandten Ende der Mantelgehäuse 12; 14 angeordnet sind, fluchten ebenfalls mit Eingangsanschlüssen 38, 42 bzw. Ausgangsanschlüssen 40, 44, welche in auf diese Bodenplatten 20, 22 axial aufgesetzten Endstücken 46, 48 ausgebildet sind.The passage openings 16 of the bottom plates 20, 22, which at the not the partition 26 facing the end of the shell casing 12; 14 are also aligned with input terminals 38, 42 and output terminals 40, 44, which are formed in these bottom plates 20, 22 axially mounted end pieces 46, 48.

Weiterhin ist in der Bodenplatte 20 und in dem Endstück 48 des einen Zylinders 2 eine zentrale Durchgangsöffnung 50 für die Kolbenstange 10 vorhanden, welche durch eine in einer radial inneren Nut 52 des Endstücks 48 gehaltenen Rinddichtung 54 kontaktiert wird. Die Kolben 6, 8 teilen die Zylinder 2, 4 jeweils in eine erste Zylinderkammer 56, 58 und in eine zweite Zylinderkammer 60, 62, deren Größe- von der jeweiligen Stellung des Kolbens 6, 8 abhängt. Die Ringdichtung 54 dient dann dazu, die erste Zylinderkammer 56 des einen Zylinders 2 gegenüber der Umgebung abzudichten.Furthermore, a central passage opening 50 for the piston rod 10 is present in the bottom plate 20 and in the end piece 48 of the one cylinder 2, which is contacted by a bovine seal 54 held in a radially inner groove 52 of the end piece 48. The pistons 6, 8 divide the cylinders 2, 4 respectively into a first cylinder chamber 56, 58 and into a second cylinder chamber 60, 62, the size of which depends on the respective position of the piston 6, 8. The ring seal 54 then serves to seal the first cylinder chamber 56 of the one cylinder 2 from the environment.

Weiterhin tragen auch die Kolben 6, 8 an ihren radial äußeren Umfangsflächen Dichtungen 64, welche jeweils die erste Zylinderkammer 56, 58 und die zweite Zylinderkammer 60, 62 gegeneinander abdichten. Bei den bisher beschriebenen Dichtungen 54, 64 handelt es sich durchweg um Berührungsdichtungen, d.h., dass die Dichtung 54, 64 die ihr jeweils zugeordnete Lauffläche kontaktiert.Furthermore, the pistons 6, 8 also carry seals 64 at their radially outer circumferential surfaces, which seal the first cylinder chamber 56, 58 and the second cylinder chamber 60, 62 against each other. The previously described seals 54, 64 are all contact seals, that is, the seal 54, 64 contacts the respective tread associated therewith.

Um die zweite Zylinderkammer 60 des einen Zylinders 2 gegenüber der ersten Zylinderkammer 58 des anderen Zylinder 4 abzudichten, ist jedoch keine Berührungsdichtung, sondern eine axiale Spaltdichtung 66 vorgesehen, welche im vorliegenden Fall vorzugsweise als Labyrinthspaltdichtung ausgebildet ist. Alternativ ist auch eine glattzylindrische oder gestufte Spaltdichtung möglich. Hierzu ist zwischen einer radial äußeren Umfangsfläche der Kolbenstange 10 und einer radial inneren Umfängsfläche der Durchgangsöffnung 32 der Trennwand 26 ein schmaler axialer Spalt 66 ausgebildet, welcher im übrigen auch zwischen den beiden Bodenplatten 18, 24 und der Kolbenstange 10 vorhanden ist. Zur Ausbildung einer Labyrinthspaltdichtung 66 ist zudem wenigstens die radial innere Umfangsfläche der Durchgangsöffnung 32 der Trennwand 26 mit in Axialabstand zueinander angeordneten radialen Nuten 68 versehen.In order to seal the second cylinder chamber 60 of the one cylinder 2 with respect to the first cylinder chamber 58 of the other cylinder 4, however, no contact seal, but an axial gap seal 66 is provided, which is preferably formed in the present case as a labyrinth gap seal. Alternatively, a smooth-cylindrical or stepped gap seal is possible. For this purpose, a narrow axial gap 66 is formed between a radially outer peripheral surface of the piston rod 10 and a radially inner peripheral surface of the through-opening 32 of the partition wall 26, which otherwise also between the two bottom plates 18, 24 and the piston rod 10 is present. To form a labyrinth gap seal 66, at least the radially inner circumferential surface of the through-opening 32 of the partition wall 26 is also provided with radial grooves 68 arranged at an axial distance from one another.

Im folgenden sollen in dicken Volllinien, gezeichnete Pfeile 70 den Strömungsweg verdichteter Luft, schwarz umrandete Pfeile 72 den Strömungsweg angesaugter Luft, schwarze umrandete und mit einer Schraffur versehene Pfeile 74 den Strömungsweg von einem Zylinder 2, 4 in den anderen Zylinder 2, 4 strösender Luft und in schmalen Linien gezeichnete-Pfeile 76 den Strömungsweg von Leckageströmen kennzeichnen: Vor diesem Hintergrund ist die Funktionsweise des Hubkolbenverdichters 1 wie folgt : Bei einer Bewegung der Kolbenstange 10 gemäß Fig. 1 nach links verkleinert sich das Volumen der beiden ersten Zylinderkammern 56, 58 bei gleichzeitiger Vergrößerung der beiden zweiten Zylinderkammern 60, 62, so dass bei ansteigendem Druck P1 die in den ersten Zylinderkammern 56, 58 befindliche Luft komprimiert und über die Ausgangsanschlüsse 34, 44 ausgestoßen wird, an welche eine nicht gezeigte Sammelleitung abgeschlossen ist, um die komprimierte Druckluft dem Druckluftvorrat zuzuführen. Diese Strömungsbewegung ist in Fig.1 durch die schwarzen, in dicken Volllinien gezeichneten Pfeile 70 gekennzeichnet.The following are in thick solid lines, drawn arrows 70, the flow path of compressed air, black outlined arrows 72, the flow path sucked air, black edged and provided with a hatched arrows 74, the flow path of a cylinder 2, 4 in the other cylinder 2, 4 flowing air and arrows shown in narrow lines 76 mark the flow path of leakage flows. Against this background, the operation of the reciprocating compressor 1 is as follows: When the piston rod 10 moves according to FIG Fig. 1 to the left, the volume of the two first cylinder chambers 56, 58 decreases with simultaneous enlargement of the two second cylinder chambers 60, 62, so that with increasing pressure P 1, the air in the first cylinder chambers 56, 58 compressed and discharged via the output ports 34, 44 to which a manifold, not shown, is completed to supply the compressed compressed air to the compressed air reservoir. This flow movement is in Fig.1 characterized by the black, drawn in thick solid lines arrows 70.

Gleichzeitig wird das Volumen der zweiten Zylinderkammern 60, 62 vergrößert, wodurch der Druck P2 dort sinkt und über die Eingangsanschlüsse 36, 38 Luft angesaugt wird, wie die schwarz umrandeten Pfeile 72 kennzeichnen. Aufgrund des Druckgefälles dp = p1 - p2 zwischen der ersten Zylinderkammer 58 des anderen Zylinders 4 und der zweiten Zylinderkammer 60 des einen Zylinders 2 ergibt sich eine kleiner, durch einen schmalen Pfeil 76 symbolisierter Leckagestrom durch den Spalt 66 hindurch, welcher allerdings nicht störend ist, da er dazu beiträgt, die zweite Zylinderkammer 60 des einen Zylinders 2 mit Luft zu füllen, welche im Laufe der anschließenden Reversierbewegung der Kolbenstange 10 komprimiert wird.At the same time, the volume of the second cylinder chambers 60, 62 is increased, whereby the pressure P 2 there sinks and air is sucked in via the input ports 36, 38, as indicated by the black bordered arrows 72. Due to the pressure gradient dp = p 1 - p 2 between the first cylinder chamber 58 of the other cylinder 4 and the second cylinder chamber 60 of the cylinder 2 results in a small, symbolized by a narrow arrow 76 leakage current through the gap 66 therethrough, which, however, not disturbing is because it helps to fill the second cylinder chamber 60 of the one cylinder 2 with air, which is compressed in the course of the subsequent reversing movement of the piston rod 10.

Bei dieser in Fig.2 gezeigten Reversierbewegung der Kolbenstange 10 wird die zuvor in die zweiten Zylinderkammern 60, 62 eingesaugte Luft wie auch die durch den Spalt 66 in die zweite Zylinderkammer 60 des einen Zylinders 2 eingeströmte Leckageluft 76 verdichtet und über die Ausgangsanschlüsse 34, 40 dem Druckluftvorrat zugeführt. Gleichzeitig wird über die Eingangsanschlüsse 36, 42 neue Luft in die ersten Zylinderkammern 56, 58 eingesaugt. Hierdurch entsteht wiederum ein nun entgegen gerichteter Leckagestrom 76 durch den Spalt, welcher der ersten Zylinderkammer 58 des anderen Zylinder 4 weitere Luft zuführt.At this in Fig.2 shown reversing movement of the piston rod 10, the previously sucked into the second cylinder chambers 60, 62 air is compressed as well as the flowed through the gap 66 into the second cylinder chamber 60 of a cylinder 2 leakage air 76 and fed via the output ports 34, 40 to the compressed air reservoir. At the same time, new air is sucked into the first cylinder chambers 56, 58 via the input connections 36, 42. This in turn creates a now opposing leakage flow 76 through the gap, which feeds the first cylinder chamber 58 of the other cylinder 4 more air.

Durch die Reversierbewegungen der Kolbenstange 10 wird daher in jede Zylinderkammer 56, 58, 60, 62 zunächst Luft durch Volumenvergrößerung _eingesaugt, verdichtet und ausgestoßen, wobei beide Kolbenflächen eines jeden Kolbens 6, 8 in beiden Richtungen wirkende Wirkflächen darstellen. Der jeweils dabei entstehende-Leckagestrom 76 wird jedoch nicht in die Umgebung ausgeblasen, sondern trägt, dazu bei, das bei der anschließenden Reversierbewegung der Kolbenstange 10 zu verdichtende Luftvolumen zu, vergrößern.As a result of the reversing movements of the piston rod 10, in each cylinder chamber 56, 58, 60, 62, air is first drawn in, compressed and ejected by increasing the volume, with both piston surfaces of each piston 6, 8 acting in both directions. However, the respectively resulting leakage current 76 is not blown into the environment, but contributes to the increase in the subsequent reversing movement of the piston rod 10 to be compressed air volume to enlarge.

Bei dem zweiten Ausführungsbeispiel der Erfindung nach den Fig.3 und 4 sind die gegenüber dem vorhergehenden Beispiel gleichbleibenden und gleichwirkenden Teile durch die gleichen Bezugszeichen, jeweils jedoch mit einem zusätzlichen Apostroph gekennzeichnet. Im Unterschied zu diesem ist der Hubkolbenverdichter 1' mehrstufig aufgebaut, d.h., dass während eines Hubes die von dem einen Zylinder 2' in der ersten Zylinderkammer 56' verdichtete Luft in die zweite Zylinderkammer 62' des anderen Zylinders 4' geleitet wird, um dort während des Reversierhubes der Kolbenstange 10' einer weiteren Verdichtung unterzogen zu werden, bevor die Druckluft über den Ausgangsanschluss 40' dem Druckluftvorrat zugeführt wird. Deshalb hat die erste Zylinderkammer 56' des einen Zylinders 2' keine Ausgangsanschlüsse sondern steht mittels einer Druckluftverbindung in Form eines Druckluftkanals 78 mit der zweiten Zylinderkammer 62' des anderen Zylinders 4' in Strömungsverbindung. Weiterhin ist die zweite Zylinderkammer 60' des einen Zylinders 2' mit der ersten Zylinderkammer 58' des anderen Zylinders 4' durch einen Überströmkanal 80' verbunden.In the second embodiment of the invention according to the Figure 3 and 4 If the parts which are the same and have the same effect in comparison with the previous example are identified by the same reference numerals, but in each case with an additional apostrophe. In contrast to this, the reciprocating compressor 1 'has a multi-stage construction, ie during one stroke the air compressed by the one cylinder 2' in the first cylinder chamber 56 'is conducted into the second cylinder chamber 62' of the other cylinder 4 ' the Reversierhubes the piston rod 10 'to be subjected to a further compression before the compressed air is supplied via the output port 40' the compressed air reservoir. Therefore, the first cylinder chamber 56 'of the one cylinder 2' has no output ports but is in fluid communication with the second cylinder chamber 62 'of the other cylinder 4' by means of a compressed air connection in the form of a compressed air channel 78. Furthermore, the second cylinder chamber 60 'of the one cylinder 2' with the first cylinder chamber 58 'of the other cylinder 4' through an overflow channel 80 'is connected.

Bei einer Bewegung der Kolbenstange 10' in Fig.3. nach links wird die Luft in der ersten Zylinderkammer 56' des einen-Zylinders 2' durch das sich verkleinernde Volumen unter Druck gesetzt und über den Druckluftkanal 78' in die zweite Zylinderkammer 62' des anderen Zylinders 4' eingeleitet und unterstützt dort die Kolbenbewegung des diesem Zylinder 4' zugeordneten Kolbens 8', welcher die in dessen erster Zylinderkammer 58' vorhandene Luft verdichtet und über den Ausgangsanschluss-34 dem Druckluftvorrat zuführt. Durch das Druckgefälle zwischen dem höheren Druck p1' in der ersten Zylinderkammer 58' des anderen Zylinders 4' und dem demgegenüber niedrigeren Druck p2' in der zweiten Zylinderkammer 60' des einen Zylinders 2' strömt ein geringer Teil der Druckluft als Leckagestrom 76' in die zweite Zylinderkammer 60' des einen Zylinders 2' und unterstützt dort die Kotbenbewegung. Gleichzeitig saugt der eine Zylinder 2' über den Eingangsanschluss 36' Luft aus der Umgebung in seine zweite Zylinderkammer 60' ein.Upon movement of the piston rod 10 'in Figure 3 , to the left, the air in the first cylinder chamber 56 'of the one-cylinder 2' is pressurized by the decreasing volume and introduced via the compressed air passage 78 'in the second cylinder chamber 62' of the other cylinder 4 'and there supports the piston movement of this Cylinder 4 'associated piston 8', which compresses the existing in the first cylinder chamber 58 'existing air and via the output port 34 to the compressed air supply. As a result of the pressure gradient between the higher pressure p 1 'in the first cylinder chamber 58' of the other cylinder 4 'and the lower pressure p 2 ' in the second cylinder chamber 60 'of the one cylinder 2', a small portion of the compressed air flows as leakage flow 76 '. in the second cylinder chamber 60 'of the one cylinder 2' and there supports the Kotbenbewegung. At the same time, one cylinder 2 'sucks air from the environment into its second cylinder chamber 60' via the inlet connection 36 '.

Im Rahmen der Reversierbewegung der Kolbenstange 10' gemäß Fig.4 nach rechts wird die in die zweite Zylinderkammer 60' des einen Zylinders 2' eingesaugte Luft verdichtet und der größte Teil über den Überstromkanal 80' in die erste Zylinderkammer 58' des anderen Zylinders 4' geschoben, um dort die Kolbenbewegung nach rechts zu unterstützen. Gleichzeitig verdichtet der Kolben 8' des anderen Zylinders 4' die in dessen zweiter Zylinderkammer 62' anstehende, durch den einen Zylinder 2'bereits vorverdichtete Druckluft und schiebt sie über den Ausgangsanschluss 40' in den Druckluftvorrat aus. Dabei schiebt der Kolben 6' des einen Zylinders '2' wiederum einen kleinen Leckagestrom 76 von der zweiten Zylinderkammer 60' in die erste Zylinderkammer 58' des anderen Zylinders 4', um die Kolbenbewegung des dortigen Kolbens 8' zu unterstützen und um Luft für den nächsten Verdichtungsvorgang kiereitzustellen.As part of the reversing movement of the piston rod 10 'according to Figure 4 to the right, the air sucked into the second cylinder chamber 60 'of the one cylinder 2' is compressed and the largest part is pushed via the overflow channel 80 'into the first cylinder chamber 58' of the other cylinder 4 'to assist the piston movement to the right. At the same time, the piston 8 'of the other cylinder 4' compresses the compressed air in its second cylinder chamber 62 ', which is already precompressed by the one cylinder 2', and pushes it out into the compressed air reservoir via the outlet connection 40 '. In this case, the piston 6 'of the one cylinder' 2 'in turn pushes a small leakage flow 76 from the second cylinder chamber 60' in the first cylinder chamber 58 'of the other cylinder 4' to support the piston movement of the local piston 8 'and air for the place the next compaction process.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Hubkolbenverdichterreciprocating
22
Zylindercylinder
44
Zylindercylinder
66
Kolbenpiston
88th
Kolbenpiston
1010
Kolbenstangepiston rod
1212
Mantelgehäusecover housing
1414
Mantelgehäuse.Cover housing.
1616
DurchgangsöffnungenThrough openings
1818
Bodenplattebaseplate
2020
Bodenplattebaseplate
2222
Bodenplattebaseplate
2424
Bodenplattebaseplate
2626
Trennwandpartition wall
2828
Eingangskanalsinput channel
3030
Ausgangskanaloutput channel
3232
DurchgangsöffnungThrough opening
3434
Ausgangsanschlussoutput port
3636
Eingangsanschlussinput port
3838
Eingangsanschlussinput port
4040
Ausgangsanschlussoutput port
4242
Eingangsanschlussinput port
4444
Ausgangsanschlussoutput port
4646
Endstücktail
4848
Endstücktail
5050
Durchgangsöffnung-Durchgangsöffnung-
5252
Nutgroove
5454
Dichtungpoetry
5656
erste Zylinderkammerfirst cylinder chamber
5858
erste Zylinderkammerfirst cylinder chamber
6060
zweite Zylinderkammersecond cylinder chamber
6262
zweite Zylinderkammersecond cylinder chamber
6464
Dichtungenseals
6666
Spaltdichtunggap seals
6868
Nutengroove
7070
Pfeilarrow
7272
Pfeilarrow
7474
Pfeilarrow
7676
Pfeilarrow
7878
bruckluftkanalBruck air duct
8080
Überströmkanaloverflow

Claims (4)

  1. A reversing reciprocating-piston compressor (1; 1') for compressing air having at least two working cylinders (2, 4; 2', 4') which are arranged in series and along a cylinder axis and in which in each case one piston (6, 8; 6', 8') is guided in an axially movable manner, with the pistons (6, 8; 6', 8') having a common axially actuated piston rod (10; 10') which extends through a passage opening (32, 32') in a partition (26, 26') between the working cylinders (2, 4; 2', 4'), characterized in that the working cylinders (2, 4; 2', 4') are sealed off with respect to one another in the region of the piston rod (10, 10') exclusively by means of a non-contact seal in the form of an axial gap seal (66, 66') which is formed between a radially outer circumferential surface of the piston rod (10, 10') and a radially inner circumferential surface of the passage opening (32, 32') which is formed in such a manner that a leakage flow (76; 76') which flows through the gap seal (66; 66') from the one working cylinder (2, 4; 2', 4') into the other working cylinder (2, 4; 2', 4') increases an air volume which is to be compressed during the subsequent reversing movement of the piston rod (10, 10').
  2. The reciprocating-piston compressor as claimed in claim 1, characterized in that, to form a labyrinth gap seal, at least the radially inner circumferential surface of the passage opening (32, 32') is provided with radial grooves (68; 68') which are arranged with an axial spacing to one another.
  3. The reciprocating-piston compressor as claimed in claim 1 or 2, characterized in that said reciprocating-piston compressor is designed as a multi-stage reciprocating-piston compressor (1') for a multi-stage compression, in which multi-stage reciprocating-piston compressor (1') each working cylinder (2', 4') is assigned to a compression stage.
  4. A compressed-air-actuated brake system of a vehicle, comprising a reciprocating-piston compressor (1; 1') as claimed in at least one of the preceding claims.
EP07722864A 2006-02-20 2007-02-20 Reciprocating-piston compressor having non-contact gap seal Not-in-force EP1989443B1 (en)

Applications Claiming Priority (2)

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DE102006007743.1A DE102006007743B4 (en) 2006-02-20 2006-02-20 Reciprocating compressor with non-contact gap seal
PCT/EP2007/001444 WO2007096127A1 (en) 2006-02-20 2007-02-20 Reciprocating-piston compressor having non-contact gap seal

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EP1989443A1 EP1989443A1 (en) 2008-11-12
EP1989443B1 true EP1989443B1 (en) 2009-08-12

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EP (1) EP1989443B1 (en)
JP (1) JP5119168B2 (en)
CN (1) CN101421514B (en)
AT (1) ATE439520T1 (en)
BR (1) BRPI0707982A2 (en)
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WO (1) WO2007096127A1 (en)

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BRPI0707982A2 (en) 2011-05-17
DE102006007743A1 (en) 2007-08-23
DE102006007743B4 (en) 2016-03-17
DE502007001299D1 (en) 2009-09-24
US8147215B2 (en) 2012-04-03
US20090220364A1 (en) 2009-09-03
ATE439520T1 (en) 2009-08-15
JP5119168B2 (en) 2013-01-16
EP1989443A1 (en) 2008-11-12
WO2007096127A1 (en) 2007-08-30
JP2009527683A (en) 2009-07-30
CN101421514A (en) 2009-04-29
CN101421514B (en) 2011-04-20

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