EP1989443A1 - Reciprocating-piston compressor having non-contact gap seal - Google Patents

Reciprocating-piston compressor having non-contact gap seal

Info

Publication number
EP1989443A1
EP1989443A1 EP07722864A EP07722864A EP1989443A1 EP 1989443 A1 EP1989443 A1 EP 1989443A1 EP 07722864 A EP07722864 A EP 07722864A EP 07722864 A EP07722864 A EP 07722864A EP 1989443 A1 EP1989443 A1 EP 1989443A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
reciprocating compressor
piston rod
seal
peripheral surface
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.)
Granted
Application number
EP07722864A
Other languages
German (de)
French (fr)
Other versions
EP1989443B1 (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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH, Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Publication of EP1989443A1 publication Critical patent/EP1989443A1/en
Application granted granted Critical
Publication of EP1989443B1 publication Critical patent/EP1989443B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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.
  • the present invention is the object of further developing a reciprocating compressor of the type mentioned in such a way that it is cheaper to manufacture. This object is achieved by the features of claim 1.
  • 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 interposing a separate contact seal.
  • 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 high number of compression strokes per unit time and thus rapid increase in pressure in the working cylinders, which is usual for reciprocating air compressors in compressed-air brake systems of commercial vehicles, a low leakage is consequently to be expected.
  • the axially extending annular gap between the radially outer circumferential surface of the piston rod and the radially inner peripheral surface of the through bore 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.
  • a labyrinth gap seal In order to form a labyrinth gap seal, it is particularly preferred to provide at least the radially inner peripheral surface of the through bore with radial grooves arranged at an axial distance from one another.
  • the fluid flows from one chamber of the one higher pressure working cylinder to a lower pressure chamber of the other working cylinder through a plurality of constricted throttling points formed by the through holes between the grooves.
  • the kinetic energy of the fluid flow is almost completely converted to frictional heat, i. converted into energy loss.
  • the reciprocating compressor is reversing, wherein the leakage flow flowing through the gap seal from one working cylinder into the other working cylinder advantageously increases the volume of air to be compressed in the subsequent reversing movement of the piston rod.
  • 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.
  • FIG. 1 shows a cross-sectional view of a reciprocating compressor according to a preferred embodiment of the invention in a first position
  • FIG. 2 shows the reciprocating compressor of Figure 1 in a second position.
  • FIG. 3 is a cross-sectional view of a reciprocating compressor according to a further embodiment of the invention in a first position
  • FIG. 4 shows the reciprocating compressor of Figure 2 in a second position.
  • the reciprocating compressor 1 shown in Figure 1 is of the type in which a plurality, preferably two cylinders 2, 4 are connected in series, wherein in the cylinders 2, 4 axially guided pistons 6, 8 are connected to a common piston rod 10, which of an internal combustion engine, not shown for reasons of scale of the commercial vehicle for generating compressed air for the compressed air brake system is driven in a reversing manner.
  • a common piston rod 10 which of an internal combustion engine, not shown for reasons of scale of the commercial vehicle for generating compressed air for the compressed air brake system is driven in a reversing manner.
  • 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 connected via a transverse to it output connection 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 through-openings 16 of the bottom plates 20, 22, which are arranged at the not the partition 26 facing the end of the shell housing 12, 14, are also aligned with input terminals 38, 42 and output terminals 40, 44, which in this bottom plates 20, 22 axially attached End pieces 46, 48 are formed.
  • 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 tread associated therewith.
  • an axial gap seal 66 is provided, which in the present case is preferably designed 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 circumferential surface of the through-opening 32 of the partition wall 26, which also otherwise between the two bottom plates 18, 24 and the piston rod 10 is present.
  • 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.
  • arrows 70 the flow path of compressed air
  • black outlined arrows 72 the flow path sucked air
  • black outlined and hatched arrows 74 the flow path of a cylinder 2, 4 in the other cylinder 2, 4 flowing air
  • Arrows 76 drawn in narrow lines indicate the flow path of leakage flows.
  • the air sucked into the second cylinder chambers 60, 62 as well as the leakage air 76 that has flowed into the second cylinder chamber 60 of the one cylinder 2 through the gap 66 are compressed and via the outlet connections 34, 40 supplied to the compressed air supply.
  • 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.
  • each cylinder chamber 56, 58, 60, 62 first air is sucked in, compressed and ejected by increasing the volume, both piston surfaces of each piston 6, 8 acting in both directions acting surfaces.
  • the respectively resulting leakage stream 76 is not blown out into the environment, but rather contributes to increasing the volume of air to be compressed in the subsequent reversing movement of the piston rod 10.
  • the parts which are identical and function the same as in the preceding example are identified by the same reference numerals, but in each case with an additional apostrophe.
  • 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 80 'connected.
  • the piston 8 'of the other cylinder 4' compresses the compressed air which is already precompressed in the second cylinder chamber 62 'by the one cylinder 2' and pushes it out into the compressed air reservoir via the outlet connection 40 '.
  • the piston 6 'of the one cylinder 2' in turn pushes a small leakage flow 76 from the second cylinder chamber 60 'into the first cylinder chamber 58' of the other cylinder 4 'to assist the piston movement of the local piston 8' and to supply air for the next one To provide compaction process.

Landscapes

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

Hubkolbenverdichter mit berührungsloser Spaltdichtung Reciprocating compressor with non-contact gap seal
Beschreibungdescription
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 Hubkolbenverdichtern 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 Hubkolbenverdichtern in Druckluftbremsanlagen von Nutzfahrzeugen ist wegen des hohen Druckluftbedarfs eine hohe Verdichterleistung gefragt, so dass der Hubkolbenverdichter eine hohe Anzahl von Verdichtungshüben 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 the 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.
Der vorliegenden Erfindung liegt demgegenüber die Aufgabe zugrunde, einen Hubkolbenverdichter der eingangs erwähnten Art derart weiter zu entwickeln, dass er günstiger zu fertigen ist. Diese Aufgabe wird erfindungsgemäß durch die Merkmale von Anspruch 1 gelöst.The present invention is the object of further developing a reciprocating compressor of the type mentioned in such a way that it is cheaper to manufacture. This object is achieved by the features of claim 1.
Vorteile der ErfindungAdvantages 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 Zwischenordnung einer separaten Berührungsdichtung erstrecken. Dann entsteht zwar zwischen den Arbeitszylindern eine gewisse Leckage, jedoch stört diese bei der vorliegenden Bauart von Hubkolbenluftverdichtern mit wenigstens zwei hintereinander angeordneten Arbeitszylindern nicht, da jeder Arbeitszylinder ohnehin druckluftbeaufschlagt ist. 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 interposing a separate contact seal. Although then arises between the working cylinders a certain leakage, but this does not interfere with the present design of Hubkolbenluftverdichtern with at least two successively arranged working cylinders, since each cylinder is already pressurized air. 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 Hinter- grund der bei Hubkolbenluftverdichtern 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 high number of compression strokes per unit time and thus rapid increase in pressure in the working cylinders, which is usual for reciprocating air compressors in compressed-air brake systems of commercial vehicles, a low leakage is consequently to be expected.
Der sich axial erstreckende Ringspalt zwischen der radial äußeren Umfangsflä- che 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. Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der in den unabhängigen Ansprüchen angegebenen Erfindung möglich.The axially extending annular gap between the radially outer circumferential surface of the piston rod and the radially inner peripheral surface of the through bore 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. 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 wenigs- tens 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.In order to form a labyrinth gap seal, it is particularly preferred to provide at least the radially inner peripheral surface of the through bore 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 to a lower pressure chamber of the other working cylinder through a plurality of constricted throttling points formed by the through holes 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 bevorzugten Anwendung der Erfindung ist der Hubkolbenverdich- ter reversierend, wobei 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 vergrößert.According to a preferred application of the invention, the reciprocating compressor is reversing, wherein the leakage flow flowing through the gap seal from one working cylinder into the other working cylinder advantageously increases the volume of air to be compressed in the subsequent reversing movement of the piston rod.
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. ZeichnungMore specifically, it will be apparent from the following description of embodiments. 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,Embodiments of the invention are illustrated in the drawings and explained in more detail in the following description. 1 shows a cross-sectional view of a reciprocating compressor according to a preferred embodiment of the invention in a first position,
Fig.2 den Hubkolbenverdichter von Fig.1 in einer zweiten Stellung;2 shows the reciprocating compressor of Figure 1 in a second position.
Fig.3 eine Querschnittsdarstellung eines Hubkolbenverdichters gemäß ei- ner weiteren Ausführungsform der Erfindung in einer ersten Stellung;3 is a cross-sectional view of a reciprocating compressor according to a further embodiment of the invention in a first position;
Fig.4 den Hubkolbenverdichter von Fig.2 in einer zweiten Stellung.4 shows the reciprocating compressor of Figure 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 reciprocating compressor 1 shown in Figure 1 is of the type in which a plurality, preferably two cylinders 2, 4 are connected in series, wherein in the cylinders 2, 4 axially guided pistons 6, 8 are connected to a common piston rod 10, which of an internal combustion engine, not shown for reasons of scale of the commercial vehicle for generating compressed air for the compressed air brake system is driven in a reversing 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 Ausgangs- anschluss 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 connected via a transverse to it output connection 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 through-openings 16 of the bottom plates 20, 22, which are arranged at the not the partition 26 facing the end of the shell housing 12, 14, are also aligned with input terminals 38, 42 and output terminals 40, 44, which in this bottom plates 20, 22 axially attached End pieces 46, 48 are formed.
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 Ring- dichtung 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 beschriebe- nen 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 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 Be- rührungsdichtung, 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 Umfangsfläche der Durchgangsöffnung 32 der Trenn- wand 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. Im folgenden sollen in dicken Volllinien gezeichnete Pfeile 70 den Strömungsweg verdichteter Luft, schwarz umrandete Pfeile 72 den Strömungsweg angesaugter Luft, schwarz umrandete und mit einer Schraffur versehene Pfeile 74 den Strömungsweg von einem Zylinder 2, 4 in den anderen Zylinder 2, 4 strömender Luft und in schmalen Linien gezeichnete Pfeile 76 den Strömungsweg von Leckageströmen kennzeichnen. Vor diesem Hintergrund ist die Funktionsweise des Hubkolbenverdichters 1 wie folgt :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 in the present case is preferably designed 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 circumferential surface of the through-opening 32 of the partition wall 26, which also otherwise 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. The following are drawn in thick solid lines arrows 70 the flow path of compressed air, black outlined arrows 72 the flow path sucked air, black outlined and hatched arrows 74 the flow path of a cylinder 2, 4 in the other cylinder 2, 4 flowing air and Arrows 76 drawn in narrow lines indicate the flow path of leakage flows. Against this background, the operation of the reciprocating compressor 1 is as follows:
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 anstei- gendem Druck pi die in den ersten Zylinderkammern 56, 58 befindliche Luft komprimiert und über die Ausgangsanschlüsse 34, 44 ausgestoßen wird, an welche eine nicht gezeigte Sammelleitung angeschlossen ist, um die komprimierte Druckluft dem Druckluftvorrat zuzuführen. Diese Strömungsbewegung ist in Fig.1 durch die schwarzen, in dicken Volllinien gezeichneten Pfeile 70 ge- kennzeichnet.With a movement of the piston rod 10 according to FIG. 1 to the left, the volume of the two first cylinder chambers 56, 58 decreases while the two second cylinder chambers 60, 62 increase, so that when the pressure pi increases, the volume in the first cylinder chambers 56, 58 decreases Compressed air is compressed and discharged via the output ports 34, 44, to which a manifold, not shown, is connected to supply the compressed compressed air to the compressed air reservoir. This flow movement is indicated in FIG. 1 by the black arrows 70 drawn in thick solid lines.
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 = pi - P2 zwischen der ersten Zylinderkammer 58 des an- deren 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 Kolben- stange 10 komprimiert wird. 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 Ausgangsanschlϋsse 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 Zylinders 4 weitere Luft zuführt. 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 ausge- blasen, sondern trägt dazu bei, das bei der anschließenden Reversierbewegung der Kolbenstange 10 zu verdichtende Luftvolumen zu vergrößern.At the same time, the volume of the second cylinder chambers 60, 62 is increased, whereby the pressure P2 there sinks and air is sucked in via the input ports 36, 38, as indicated by the black bordered arrows 72. Because of the pressure gradient dp = pi-P2 between the first cylinder chamber 58 of the other cylinder 4 and the second cylinder chamber 60 of the one cylinder 2, a small leakage stream symbolized by a narrow arrow 76 results through the gap 66, which, however, does not interfere 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. In this reversing movement of the piston rod 10 shown in FIG. 2, the air sucked into the second cylinder chambers 60, 62 as well as the leakage air 76 that has flowed into the second cylinder chamber 60 of the one cylinder 2 through the gap 66 are compressed and via the outlet connections 34, 40 supplied to the compressed air supply. 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. As a result of the reversing movements of the piston rod 10, in each cylinder chamber 56, 58, 60, 62 first air is sucked in, compressed and ejected by increasing the volume, both piston surfaces of each piston 6, 8 acting in both directions acting surfaces. However, the respectively resulting leakage stream 76 is not blown out into the environment, but rather contributes to increasing the volume of air to be compressed in the subsequent reversing movement of the piston rod 10.
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 zu- sätzlichen 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 FIGS. 3 and 4, the parts which are identical and function the same as in the preceding 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 80 '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 verklei- nernde 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 Kolbenbewegung. Gleichzeitig saugt der eine Zylinder 2' über den Eingangsanschluss 36' Luft aus der Umgebung in seine zweite Zylinderkammer 60' ein.When the piston rod 10 'in FIG. 3 is moved to the left, the air in the first cylinder chamber 56' of the one cylinder 2 'is pressurized by the decreasing volume and via the compressed air duct 78' into the second cylinder chamber 62 'of the cylinder other cylinder 4 'initiated there and 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. Due to 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 a leakage flow 76 '. in the second cylinder chamber 60 'of the one cylinder 2' and there supports the piston movement. 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 dieIn the context of the reversing movement of the piston rod 10 'according to FIG. 4 to the right, the air sucked into the second cylinder chamber 60' of the one cylinder 2 'is compressed and the largest part via the overflow channel 80' into the first cylinder chamber 58 'of the other cylinder 4'. pushed to the there
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 bereitzustellen. BezugszeichenlisteTo assist piston movement to the right. At the same time, the piston 8 'of the other cylinder 4' compresses the compressed air which is already precompressed in the second cylinder chamber 62 '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 'into the first cylinder chamber 58' of the other cylinder 4 'to assist the piston movement of the local piston 8' and to supply air for the next one To provide compaction process. LIST OF REFERENCE NUMBERS
1 Hubkolbenverdichter1 reciprocating compressor
2 Zylinder 4 Zylinder2 cylinders 4 cylinders
6 Kolben6 pistons
8 Kolben8 pistons
10 Kolbenstange10 piston rod
12 Mantelgehäuse 14 Mantelgehäuse12 shell housing 14 shell housing
16 Durchgangsöffnungen16 passages
18 Bodenplatte18 base plate
20 Bodenplatte20 base plate
22 Bodenplatte 24 Bodenplatte22 base plate 24 base plate
26 Trennwand26 partition
28 Eingangskanal28 input channel
30 Ausgangskanal30 output channel
32 Durchgangsöffnung 34 Ausgangsanschluss32 passage opening 34 output connection
36 Eingangsanschluss36 input connection
38 Eingangsanschluss38 input connection
40 Ausgangsanschluss40 output connection
42 Eingangsanschluss 44 Ausgangsanschluss42 input connection 44 output connection
46 Endstück46 tail
48 Endstück48 tail
50 Durchgangsöffnung 52 Nut50 passage opening 52 groove
54 Dichtung54 seal
56 erste Zylinderkammer56 first cylinder chamber
58 erste Zylinderkammer58 first cylinder chamber
60 zweite Zylinderkammer 62 zweite Zylinderkammer60 second cylinder chamber 62 second cylinder chamber
64 Dichtungen64 seals
66 Spaltdichtung66 gap seal
68 Nuten68 grooves
70 Pfeil 72 Pfeil70 arrow 72 arrow
74 Pfeil74 arrow
76 Pfeil76 arrow
78 Druckluftkanal 0 Überströmkanal 78 Compressed air channel 0 Overflow channel

Claims

Patentansprüche claims
1. Hubkolbenverdichter (1 ; 1 ') mit wenigstens zwei hintereinander, ent- lang einer Zylinderachse angeordneten Arbeitszylindern (2, 4; 2', 4'), in welchen je ein Kolben (6, 8; 6', 8') axial beweglich geführt ist, wobei die Kolben (6, 8; 6', 8') eine gemeinsame axial betätigte Kolbenstange (10; 10') aufweisen, welche sich durch eine Durchgangsöffnung (32, 32') in einer Trennwand (26, 26') zwischen den Arbeitszy- lindern (2, 4; 2', 4') erstreckt, dadurch gekennzeichnet, dass die1. Reciprocating compressor (1, 1 ') having at least two working cylinders (2, 4, 2', 4 ') arranged behind a cylinder axis, in each of which a piston (6, 8, 6', 8 ') axially is movably guided, wherein the pistons (6, 8, 6 ', 8') have 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
Arbeitszylinder (2, 4; 2', 4') im Bereich der Kolbenstange (10, 10') ausschließlich durch eine berührungslose Dichtung in Form einer zwischen einer radial äußeren Umfangsfläche der Kolbenstange (10, 10') und einer radial inneren Umfangsfläche der Durchgangsöffnung (32, 32') ausgebildeten axialen Spaltdichtung (66, 66') gegeneinander abgedichtet sind.Working cylinder (2, 4, 2 ', 4') in the region of the piston rod (10, 10 ') exclusively by a non-contact seal in the form of a between a radially outer peripheral surface of the piston rod (10, 10') and a radially inner peripheral surface of the through hole (32, 32 ') formed axial gap seal (66, 66') are sealed against each other.
2. Hubkolbenverdichter nach Anspruch 1 , dadurch gekennzeichnet, dass zur Ausbildung einer Labyrinthspaltdichtung wenigstens die ra- dial innere Umfangsfläche der Durchgangsöffnung (32, 32') mit in2. reciprocating compressor according to claim 1, characterized in that for forming a labyrinth gap seal at least the radial inner peripheral surface of the passage opening (32, 32 ') with in
Axialabstand zueinander angeordneten radialen Nuten (68; 68') versehen ist.Axially spaced radial grooves (68, 68 ') is provided.
3. Hubkolbenverdichter nach Anspruch 1 oder 2, dadurch gekenn- zeichnet, dass er ein reversierender Hubkolbenverdichter (1 , 1 ') ist und der durch die Spaltdichtung (66; 66') strömende Leckagestrom (76; 76') von dem einen Arbeitszylinder (2, 4; 2', 4') in den anderen Arbeitszylinder (2, 4,; 2', 4') das bei der anschließenden Reversier- bewegung der Kolbenstange (10; 10') zu verdichtende Luftvolumen vergrößert. 3. Reciprocating compressor according to claim 1 or 2, characterized in that it is a reversing reciprocating compressor (1, 1 ') and the through the gap seal (66, 66') flowing leakage current (76, 76 ') of the one working cylinder ( 2, 4, 2 ', 4') in the other working cylinder (2, 4, 2 ', 4') increases the volume of air to be compressed in the subsequent reversing movement of the piston rod (10, 10 ').
4. Hubkolbenverdichter nach Anspruch 3, dadurch gekennzeichnet, dass er als mehrstufiger Hubkolbenverdichter (V) für eine mehrstufige Verdichtung ausgeführt ist, bei welchem jeder Arbeitszylinder (2', 4') einer Verdichtungsstufe zugeordnet ist.4. Reciprocating compressor according to claim 3, characterized in that it is designed as a multi-stage reciprocating compressor (V) for a multi-stage compression, in which each working cylinder (2 ', 4') is associated with a compression stage.
5. Druckluftbetätigte Bremsanlage eines Fahrzeugs, beinhaltend einen Hubkolbenverdichter (1 ; 1 ') nach wenigstens einem der vorhergehenden Ansprüche. 5. A pneumatically operated brake system of a vehicle, comprising a reciprocating compressor (1, 1 ') according to 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)

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ATE439520T1 (en) 2009-08-15
BRPI0707982A2 (en) 2011-05-17
CN101421514A (en) 2009-04-29
DE102006007743A1 (en) 2007-08-23
CN101421514B (en) 2011-04-20
WO2007096127A1 (en) 2007-08-30
US20090220364A1 (en) 2009-09-03
DE502007001299D1 (en) 2009-09-24
DE102006007743B4 (en) 2016-03-17
EP1989443B1 (en) 2009-08-12
JP2009527683A (en) 2009-07-30
JP5119168B2 (en) 2013-01-16
US8147215B2 (en) 2012-04-03

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