EP1831562B1 - Piston-cylinder arrangement for a reciprocating compressor - Google Patents

Piston-cylinder arrangement for a reciprocating compressor Download PDF

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Publication number
EP1831562B1
EP1831562B1 EP05818221A EP05818221A EP1831562B1 EP 1831562 B1 EP1831562 B1 EP 1831562B1 EP 05818221 A EP05818221 A EP 05818221A EP 05818221 A EP05818221 A EP 05818221A EP 1831562 B1 EP1831562 B1 EP 1831562B1
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EP
European Patent Office
Prior art keywords
piston
cylinder arrangement
cylinder
arrangement according
bore
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EP05818221A
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German (de)
French (fr)
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EP1831562A1 (en
Inventor
Dieter Spurny
Dieter Weisse
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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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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0022—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons piston rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/144—Adaptation of piston-rods
    • F04B53/147—Mounting or detaching of piston rod

Definitions

  • the present invention relates to a piston-cylinder arrangement for a reciprocating compressor, in particular for a swash plate compressor, with a arranged in a cylinder axially movable piston made of light metal, the at least one in the piston movement direction through a through hole of the piston extending through fastening screw fastened frontally on a piston rod is.
  • the field of application of the present invention relates primarily to swash plate compressors, which represent a special form of reciprocating compressors for generating compressed air.
  • Swash plate compressors are used, for example, in commercial vehicles. In commercial vehicles, these are usually driven directly by the engine of the commercial vehicle and supply the compressed air supply of the compressed air vehicle electrical system. In commercial vehicles, the compressed air thus generated is used for example for operating a compressed air brake system.
  • a swash plate compressor for generating compressed air in commercial vehicles, which is constructed here largely dry running.
  • This has only a conventional oil-lubricated engine, which consists essentially of a arranged on a drive shaft swash plate with hemispheres in bearing cups, which form a bearing assembly for transmitting the rotational movement in an oscillating motion.
  • a conventional oil-lubricated engine which consists essentially of a arranged on a drive shaft swash plate with hemispheres in bearing cups, which form a bearing assembly for transmitting the rotational movement in an oscillating motion.
  • From the bearing arrangement extending piston rods to various pistons, which generate the compressed air by a reciprocating motion in associated cylinders.
  • a plurality of pistons are arranged adjacent to one another on a circumferential circle, in order to realize the highest possible delivery rate of the swash plate compressor.
  • the usually made of a light metal piston are equipped with suitable for oil-free dry running piston rings, so that the piston moves without contact in the cylinder bore.
  • the attachment of the existing light metal piston on the piston rod takes place here via a central fastening screw, which is coaxial with the piston rod and the longitudinal axis of the piston and comes into engagement with a corresponding threaded base bore on the piston facing the end face of the piston rod.
  • the piston is provided with a through hole.
  • an interposed washer is provided here.
  • a disadvantage of this prior art solution is that the head of the fastening screw protrudes beyond the piston surface, so that a corresponding recess for receiving the head of the fastening screw is required on the part of the cylinder. Furthermore, the hot, compressed compressed air flows around the head of the fastening screw around to finally flow out of the cylinder. This results in an extreme heating of the fastening screw, so that the connection point between the fastening screw and the piston rod is exposed by the prevailing temperature differences undesirable AC voltages.
  • the US 3,036,873 shows another solution for attaching a piston rod to the piston, wherein the head of the fastening screw does not protrude beyond the piston surface by this is housed in a corresponding countersinking of the piston.
  • a washer assembly in duplicate Execution, each consisting of a spring washer and a steel disc provided. This solution proves to be quite expensive to manufacture and assembly because of the many items.
  • the subject-matter of claim 1 is delimited from this document.
  • the invention includes the technical teaching that the through hole of the piston has a countersink, wherein a fastening bush is provided with an annular bottom portion and an adjacent hollow-cylindrical wall portion which projects into the depression of the through hole for receiving the head of the fastening screw, and via a adjoining the wall region of the fastening bushing and extending radially outwardly edge region abuts the adjacent piston surface.
  • the advantage of the solution according to the invention is, in particular, that it is hereby possible to completely countersink the head of the fastening screw. A supernatant is thus largely avoided.
  • a sinking of the mounting screw in the material of the piston would not be possible because the required material thicknesses of the existing light metal piston would not ensure reliable attachment.
  • the fastening screw does not heat up so much that the temperature differences associated therewith are no longer significant, and unwanted alternating voltages no longer occur. Rather, the connection point to the piston rod is thermally relieved by the cheaper compressed air supply.
  • the mounting bush receiving reduction in the piston in the depth is made larger than the axial length of the mounting sleeve, so that an axial tolerance compensation takes place by tightening the mounting screw. Manufacturing-related component tolerances on the piston can thus be compensated in a simple manner while securing the screw.
  • the fastening bushing can also be used for clamping at least one suction lamella on the piston by clamping the tongue-like suction lamella between the surface of the piston and the edge portion of the fastening bushing. Since the mounting bushing takes on a further function in this case, can be dispensed with separate attachment means for the Sauglamelle.
  • the suction lamella acts at this point as a check valve when sucking in the compressed air. The sucked in compressed air is in this respect conveyed through the piston into the pressure chamber and compressed here.
  • edge portion of the mounting bushing tapers in the thickness to create an opening angle for limiting the movement of the here clamped suction plate.
  • the edge portion has an outer radial, rounded rolling edge.
  • the rounded rolling edge serves to avoid fractures of the here clamped at least one suction lamella. Without this measure, the Danger that the suction plate is so bent due to the alternating stress occurring at the clamping point to the fastening bushing due to the opening and closing of the check valve that here a break occurs over time.
  • the radially outwardly extending edge section of the fastening bushing should be arranged at an angle of ⁇ 90 ° to the hollow-cylindrical, adjacent wall section.
  • the existing steel mounting bushing is made by deep drawing, stamping and punching.
  • this can be production technology produce in a very simple way.
  • the mounting bushing has a thickness of 0.3 to 1.5 millimeters, preferably 0.5 to 1 millimeter, when used within a swash plate type compressor of conventional sizes. This relatively small thickness is sufficient to produce the advantages of the invention.
  • the transition between the annular bottom portion to the adjacent cylindrical wall portion should be provided as well as the transition between the hollow cylindrical wall portion to the annular edge portion with a radius in the range of 0.5 to 1 millimeter. Radii in this range are sufficient to prevent cracking in the manufacture of the mounting bushing (deep drawing).
  • the piston-cylinder arrangement shown here consists of a cylinder 1, in which a piston 2 is arranged axially back and forth movable.
  • the piston 2 is made of aluminum here.
  • the piston 2 is provided with an outer radial piston ring assembly 3 which is in contact with the inner wall of the cylinder 2.
  • the piston 2 has a central through-bore 4, through which a fastening screw 5 extends. By means of the fastening screw 5 takes place a coaxial attachment of the piston 2 frontally on a piston rod 6.
  • the piston rod 6 transmits an axial movement of the engine of the - not shown here - swash plate compressor.
  • the serving for receiving the fastening screw 5 through hole 4 in the piston 2 is provided with a reduction.
  • the countersink serves to receive a fastening bushing 7, which acts between the piston 2 and the fastening screw 5.
  • the mounting bushing 7 is made of steel and thus supports the connection point between the fastening screw 5 and the piston 2 made of aluminum.
  • the fastening bushing 7 also serves to clamp at least one suction lamella 8 on the piston 2. This clamping attachment is achieved by clamping the suction lamella 8 between the piston surface 9 and the fastening bushing 7.
  • the suction blade 8 forms with a corresponding eccentric through hole 10 in Piston 2, a check valve, which serves to suck in air from the atmosphere through the piston. After compression of the air sucked in this way, it is discharged via an outlet valve 11 arranged on the front side of the cylinder.
  • the fastening bushing 7 consists of an annular bottom portion 12, to which an adjacent hollow cylinder-like wall portion 13 shoots.
  • the hollow cylinder-like wall section 13, in turn, is adjoined by an edge section 14 which extends radially outward.
  • the mounting bush 7 comes to the piston surface 9 of the piston 2 to the plant.
  • the tightening of the fastening screw 5 results in an axial spring action for tolerance compensation and securing the fastening screw 5.
  • the edge portion 14 of the fastening screw 5 continues to run in thickness in one Rejuvenation 15 off. To avoid fractures of the here clamped suction plate 8, the edge portion 14 also has an outside radial rounded rolling edge 16.
  • the mounting bush 7 of this embodiment is made of sheet steel having a thickness of 0.7 millimeters.
  • the transition between the annular bottom portion 12 to the adjacent cylindrical wall portion 13 as well as the transition between the hollow cylindrical wall portion 13 is provided to the annular edge portion 14 with a radius of 0.6 millimeters.
  • Fig. 3 To Fig. 3 is the mounting bushing 7 receiving reduction in the piston 2 in the depth is made larger than the axial length of the mounting sleeve 7 in the relaxed state. By tightening the fastening screw 5 is then carried out an axial tolerance compensation by the edge portion 14 springs.
  • the edge portion 14 of the mounting bushing 7 is tapered in thickness to create an opening angle 17 to limit the movement of the here clamped suction blade 8.
  • the fastening bushing 7 thus serves, in addition to an improvement of the screw connection, also as a clamp fastening of the at least one suction lamella 8 on the piston 2.

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

Abstract

Disclosed is a piston-cylinder arrangement for a reciprocating compressor, especially a swashplate compressor, comprising a light metal piston (2) which is axially movable within a cylinder (1) and the face of which is fixed to a piston rod (6) via at least one fastening screw (5) that extends through a through-bore (4) of the piston (2) in the direction of travel of the piston. The inventive piston-cylinder arrangement is characterized in that the through-bore (4) of the piston (2) is provided with a recess while a fastening bush (7) encompassing an annular bottom section (12) and an adjacent hollow cylinder-type wall section (13) is provided. Said fastening bush (7) protrudes into the recess of the through-bore (4) in order to accommodate the head of the fastening screw (5) while resting against the adjacent piston area (9) via a radially outward extending peripheral section (14) which adjoins the wall section (13) of the fastening bush (7).

Description

Die vorliegende Erfindung betrifft eine Kolben-Zylinder-Anordnung für einen Kolbenverdichter, insbesondere für einen Taumelscheibenverdichter, mit einem in einem Zylinder angeordneten axial bewegbaren Kolben aus Leichtmetall, der über mindestens eine in Kolbenbewegungsrichtung durch eine Durchgangsbohrung des Kolbens hindurch verlaufende Befestigungsschraube stirnseitig an einer Kolbenstange befestigt ist.The present invention relates to a piston-cylinder arrangement for a reciprocating compressor, in particular for a swash plate compressor, with a arranged in a cylinder axially movable piston made of light metal, the at least one in the piston movement direction through a through hole of the piston extending through fastening screw fastened frontally on a piston rod is.

Das Einsatzgebiet der vorliegenden Erfindung bezieht sich vornehmlich auf Taumelscheibenverdichter, welche eine Spezialform von Kolbenverdichtern zur Erzeugung von Druckluft darstellen.The field of application of the present invention relates primarily to swash plate compressors, which represent a special form of reciprocating compressors for generating compressed air.

Taumelscheibenverdichter kommen beispielsweise bei Nutzfahrzeugen zur Anwendung. In Nutzfahrzeugen werden diese meist direkt über den Motor des Nutzfahrzeugs angetrieben und liefern die Druckluftzuspeisung des Druckluft-Bordnetzes. Bei Nutzfahrzeugen wird die so erzeugte Druckluft beispielsweise zum Betrieb einer Druckluft-Bremsanlage genutzt.Swash plate compressors are used, for example, in commercial vehicles. In commercial vehicles, these are usually driven directly by the engine of the commercial vehicle and supply the compressed air supply of the compressed air vehicle electrical system. In commercial vehicles, the compressed air thus generated is used for example for operating a compressed air brake system.

Aus der EP 0 859 151 A2 geht ein Taumelscheibenverdichter zur Drucklufterzeugung in Nutzfahrzeugen hervor, welcher hier weitestgehend trockenlaufend konstruiert ist. Dieser weist lediglich ein herkömmliches ölgeschmiertes Triebwerk auf, welches im Wesentlichen aus einer auf einer Antriebswelle angeordneten Taumelscheibe mit Halbkugeln in Lagerpfannen besteht, die eine Lageranordnung zur Übertragung der Drehbewegung in eine oszillierende Bewegung bilden. Von der Lageanordnung aus verlaufen Kolbenstangen zu diversen Kolben, welche durch eine Hin- und Herbewegung in zugeordneten Zylindern die Druckluft erzeugen. Hierbei sind mehrere Kolben auf einem Umfangskreis benachbart zueinander angeordnet, um eine möglichst hohe Förderleistung des Taumelscheibenverdichters zu realisieren.From the EP 0 859 151 A2 goes a swash plate compressor for generating compressed air in commercial vehicles, which is constructed here largely dry running. This has only a conventional oil-lubricated engine, which consists essentially of a arranged on a drive shaft swash plate with hemispheres in bearing cups, which form a bearing assembly for transmitting the rotational movement in an oscillating motion. From the bearing arrangement extending piston rods to various pistons, which generate the compressed air by a reciprocating motion in associated cylinders. In this case, a plurality of pistons are arranged adjacent to one another on a circumferential circle, in order to realize the highest possible delivery rate of the swash plate compressor.

Die gewöhnlich aus einem Leichtmetall bestehenden Kolben sind mit für den ölfreien Trockenlauf geeigneten Kolbenringen bestückt, so dass der Kolben sich berührungsfrei in der Zylinderbohrung bewegt. Die Befestigung des aus Leichtmetall bestehenden Kolbens an der Kolbenstange erfolgt hier über eine zentrale Befestigungsschraube, welche koaxial zur Kolbenstange sowie zur Längsachse des Kolbens verläuft und in eine korrespondierende Gewindegrundbohrung an der dem Kolben zugewandten Stirnseite der Kolbenstange zum Eingriff kommt. Zu diesem Zwecke ist der Kolben mit einer Durchgangsbohrung versehen. Um einen Materialabtrag von der druckkammerseitigen Kolbenfläche beim Festziehen der Befestigungsschraube zu vermeiden, ist hier eine dazwischen angeordnete Unterlegscheibe vorgesehen.The usually made of a light metal piston are equipped with suitable for oil-free dry running piston rings, so that the piston moves without contact in the cylinder bore. The attachment of the existing light metal piston on the piston rod takes place here via a central fastening screw, which is coaxial with the piston rod and the longitudinal axis of the piston and comes into engagement with a corresponding threaded base bore on the piston facing the end face of the piston rod. For this purpose, the piston is provided with a through hole. In order to avoid a removal of material from the pressure-chamber-side piston surface when tightening the fastening screw, an interposed washer is provided here.

Ein Nachteil dieser Lösung des Standes der Technik besteht darin, dass der Kopf der Befestigungsschraube über die Kolbenfläche hervorsteht, so dass seitens des Zylinders eine korrespondierende Ausnehmung zur Aufnahme des Kopfes der Befestigungsschraube erforderlich ist. Weiterhin strömt die heiße, verdichtete Druckluft um den Kopf der Befestigungsschraube herum, um schließlich aus dem Zylinder auszuströmen. Hierdurch kommt es zu einer extremen Aufheizung der Befestigungsschraube, so dass die Verbindungsstelle zwischen der Befestigungsschraube und der Kolbenstange durch die herrschenden Temperaturunterschiede unerwünschten Wechselspannungen ausgesetzt ist.A disadvantage of this prior art solution is that the head of the fastening screw protrudes beyond the piston surface, so that a corresponding recess for receiving the head of the fastening screw is required on the part of the cylinder. Furthermore, the hot, compressed compressed air flows around the head of the fastening screw around to finally flow out of the cylinder. This results in an extreme heating of the fastening screw, so that the connection point between the fastening screw and the piston rod is exposed by the prevailing temperature differences undesirable AC voltages.

Aus der DE 299 06 232 U1 geht ein Kolbenverdichter hervor, dessen Kolbenstange in eine Gewindegrundbohrung des Kolbens eingeschraubt ist. Diese Lösung vermeidet, dass der Kopf der Befestigungsschraube über die Kolbenfläche hervorsteht. Allerdings ist die untere Kolbenfläche hierfür mit Verstärkungsrippen zu verstärken.From the DE 299 06 232 U1 goes out a reciprocating compressor whose piston rod is screwed into a threaded base bore of the piston. This solution avoids the head of the fastening screw protruding beyond the piston surface. However, the lower piston surface is to reinforce this with reinforcing ribs.

Die US 3,036,873 zeigt eine andere Lösung zur Befestigung einer Kolbenstange am Kolben, bei welcher der Kopf der Befestigungsschraube nicht über die Kolbenfläche hervorsteht, indem diese in einer korrespondierenden Senkung des Kolbens untergebracht ist. Zur Sicherung der Schraubverbindung ist eine Unterlegscheibenanordnung in zweifacher Ausführung, bestehend je aus einer Federscheibe und einer Stahlscheibe, vorgesehen. Diese Lösung erweist sich wegen der vielen Einzelteile recht aufwendig in der Herstellung und Montage. Der Gegenstand des Patentanspruchs 1 ist gegenüber diesem Dokument abgegrenzt.The US 3,036,873 shows another solution for attaching a piston rod to the piston, wherein the head of the fastening screw does not protrude beyond the piston surface by this is housed in a corresponding countersinking of the piston. To secure the screw is a washer assembly in duplicate Execution, each consisting of a spring washer and a steel disc provided. This solution proves to be quite expensive to manufacture and assembly because of the many items. The subject-matter of claim 1 is delimited from this document.

Es ist daher die Aufgabe der vorliegenden Erfindung eine Kolben-Zylinder-Anordnung der vorstehend beschriebenen Art dahingehend weiter zu verbessern, dass mittels mindestens einer Befestigungsschraube eine zuverlässige Schraubverbindung des Kolbens an der Kolbenstange mit einfachen technischen Maßnahmen realisierbar ist.It is therefore the object of the present invention to further improve a piston-cylinder arrangement of the type described above to the effect that by means of at least one fastening screw a reliable screw of the piston on the piston rod can be realized with simple technical measures.

Die Aufgabe wird ausgehend von einer Kolben-Zylinder-Anordnung gemäß dem Oberbegriff von Anspruch 1 in Verbindung mit dessen kennzeichnenden Merkmalen gelöst. Die nachfolgenden abhängigen Ansprüche geben vorteilhafte Weiterbildungen der Erfindung wieder.The object is achieved on the basis of a piston-cylinder arrangement according to the preamble of claim 1 in conjunction with its characterizing features. The following dependent claims give advantageous developments of the invention.

Die Erfindung schließt die technische Lehre ein, dass die Durchgangsbohrung des Kolbens eine Senkung aufweist, wobei eine Befestigungsbuchse mit einem kreisringförmigen Bodenabschnitt und einem benachbarten hohlzylinderartigen Wandabschnitt vorgesehen ist, die in die Senkung der Durchgangsbohrung zur Aufnahme des Kopfes der Befestigungsschraube hineinragt, und die über einen sich dem Wandbereich der Befestigungsbuchse anschließenden und nach radial außen hin erstreckenden Randbereich an der benachbarten Kolbenfläche zur Anlage kommt.The invention includes the technical teaching that the through hole of the piston has a countersink, wherein a fastening bush is provided with an annular bottom portion and an adjacent hollow-cylindrical wall portion which projects into the depression of the through hole for receiving the head of the fastening screw, and via a adjoining the wall region of the fastening bushing and extending radially outwardly edge region abuts the adjacent piston surface.

Der Vorteil der erfindungsgemäßen Lösung besteht insbesondere darin, dass es hiermit möglich wird, den Kopf der Befestigungsschraube vorzugsweise vollständig zu versenken. Ein Überstand wird somit weitestgehend vermieden. Ohne die erfindungsgemäß ausgebildete Befestigungsbuchse wäre ein Versenken der Befestigungsschraube im Material des Kolbens nicht möglich, da die erforderlichen Materialstärken des aus Leichtmetall bestehenden Kolbens eine zuverlässige Befestigung nicht sicherstellen würden. Erst durch die zusätzliche Befestigungsbuchse, welche vorzugsweise aus Stahl besteht, ist es möglich, den Kopf der Befestigungsschraube zu versenken und eine günstige Druckluftführung im Verdichtungsraum darzustellen. Die heiße, verdichtete Druckluft muss nicht mehr am Kopf der Befestigungsschraube vorbei ausströmen. Die Befestigungsschraube erwärmt sich also nicht mehr so stark, so dass die hiermit im Zusammenhang stehenden Temperaturunterschiede nicht mehr ins Gewicht fallen, und unerwünschte Wechselspannungen nicht mehr auftreten. Vielmehr wird die Verbindungsstelle zur Kolbenstange hin durch die günstigere Druckluftführung thermisch entlastet.The advantage of the solution according to the invention is, in particular, that it is hereby possible to completely countersink the head of the fastening screw. A supernatant is thus largely avoided. Without the inventively designed mounting bush a sinking of the mounting screw in the material of the piston would not be possible because the required material thicknesses of the existing light metal piston would not ensure reliable attachment. Only through the additional mounting bush, which is preferably made of steel, it is possible to sink the head of the mounting screw and a favorable compressed air guide in Represent compression space. The hot, compressed compressed air no longer has to flow past the head of the fastening screw. Thus, the fastening screw does not heat up so much that the temperature differences associated therewith are no longer significant, and unwanted alternating voltages no longer occur. Rather, the connection point to the piston rod is thermally relieved by the cheaper compressed air supply.

Vorteilhafter Weise ist vorgesehen, dass die die Befestigungsbuchse aufnehmende Senkung im Kolben in der Tiefe größer ausgeführt ist als die axiale Länge der Befestigungsbuchse, so dass durch Anziehen der Befestigungsschraube ein axialer Toleranzausgleich erfolgt. Fertigungsbedingte Bauteiltoleranzen am Kolben können somit in einfacher Weise bei gleichzeitiger Sicherung der Schraubverbindung ausgeglichen werden.Advantageously, it is provided that the mounting bush receiving reduction in the piston in the depth is made larger than the axial length of the mounting sleeve, so that an axial tolerance compensation takes place by tightening the mounting screw. Manufacturing-related component tolerances on the piston can thus be compensated in a simple manner while securing the screw.

Gemäß einer die Erfindung verbessernden Maßnahme kann die Befestigungsbuchse daneben auch zur Klemmbefestigung mindestens einer Sauglamelle am Kolben durch Einspannen der zungenartigen Sauglamelle zwischen der Oberfläche des Kolbens und dem Randabschnitt der Befestigungsbuchse verwendet werden. Da die Befestigungsbuchse in diesem Fall eine weitere Funktion übernimmt, kann auf separate Befestigungsmittel für die Sauglamelle verzichtet werden. Die Sauglamelle wirkt an dieser Stelle als Rückschlagventil beim Ansaugen der Druckluft. Die angesaugte Druckluft wird insoweit durch den Kolben hindurch in den Druckraum gefördert und hier komprimiert.According to a measure improving the invention, the fastening bushing can also be used for clamping at least one suction lamella on the piston by clamping the tongue-like suction lamella between the surface of the piston and the edge portion of the fastening bushing. Since the mounting bushing takes on a further function in this case, can be dispensed with separate attachment means for the Sauglamelle. The suction lamella acts at this point as a check valve when sucking in the compressed air. The sucked in compressed air is in this respect conveyed through the piston into the pressure chamber and compressed here.

In diesem Zusammenhang ist gemäß einer weiteren die Erfindung verbessernden Maßnahme vorgesehen, dass der Randabschnitt der Befestigungsbuchse in der Dicke sich verjüngend ausläuft, um einen Öffnungswinkel zur Bewegungsbegrenzung der hier eingespannten Sauglamelle zu schaffen.In this context, it is provided according to a further measure improving the invention that the edge portion of the mounting bushing tapers in the thickness to create an opening angle for limiting the movement of the here clamped suction plate.

Weiterhin ist es von Vorteil, wenn der Randabschnitt eine außenradiale, abgerundete Abrollkante aufweist. Die abgerundete Abrollkante dient einer Vermeidung von Brüchen der hier eingespannten mindestens einen Sauglamelle. Ohne diese Maßnahme bestünde die Gefahr, dass die Sauglamelle aufgrund der durch das Öffnen und Schließen des Rückschlagventils auftretenden Wechselbeanspruchung an der Einspannstelle zur Befestigungsbuchse hin derart geknickt wird, dass hier im laufe der Zeit eine Bruchstelle entsteht.Furthermore, it is advantageous if the edge portion has an outer radial, rounded rolling edge. The rounded rolling edge serves to avoid fractures of the here clamped at least one suction lamella. Without this measure, the Danger that the suction plate is so bent due to the alternating stress occurring at the clamping point to the fastening bushing due to the opening and closing of the check valve that here a break occurs over time.

Gemäß einer weiteren, die Erfindung verbessernden Maßnahme sollte der sich nach radial außen hin erstreckende Randabschnitt der Befestigungsbuchse unter einem Winkel von < 90° zu dem hohlzylindrischen, benachbarten Wandabschnitt angeordnet sein. Hierdurch wird eine axiale Federwirkung der Befestigungsbuchse beim Anziehen der Befestigungsschraube gewährleistet, was die Schraubverbindung zusätzlich sichert und den axialen Toleranzausgleich ermöglicht, da der federnde Randbereich als eine Art Federscheibe wirkt. Sollte die Befestigungsbuchse gleichzeitig auch der Klemmbefestigung von Sauglamellen dienen, so ist durch den federnden Randabschnitt der Öffnungswinkel sichergestellt.According to a further measure improving the invention, the radially outwardly extending edge section of the fastening bushing should be arranged at an angle of <90 ° to the hollow-cylindrical, adjacent wall section. As a result, an axial spring action of the mounting sleeve when tightening the fastening screw is ensured, which additionally secures the screw and allows the axial tolerance compensation, since the resilient edge region acts as a kind of spring washer. If the mounting bushing also serve for the clamping attachment of suction blades, the opening angle is ensured by the resilient edge portion.

Vorzugsweise ist die aus Stahl bestehende Befestigungsbuchse durch Tiefziehen, Prägen und Stanzen hergestellt. Somit lässt diese sich fertigungstechnisch in denkbar einfacher Weise produzieren.Preferably, the existing steel mounting bushing is made by deep drawing, stamping and punching. Thus, this can be production technology produce in a very simple way.

Es ist ausreichend, wenn die Befestigungsbuchse bei Anwendung innerhalb eines Taumelscheibenverdichters üblicher Größen eine Dicke von 0,3 bis 1,5 Millimeter, vorzugsweise 0,5 bis 1 Millimeter aufweist. Diese relativ geringe Dicke ist ausreichend, um die erfindungsgemäßen Vorteile hervorzurufen. Insbesondere in diesem Dickebereich sollte der Übergang zwischen dem kreisringförmigen Bodenabschnitt zu dem benachbarten zylindrischen Wandabschnitt genauso wie der Übergang zwischen dem hohlzylindrischen Wandabschnitt zu dem kreisringförmigen Randabschnitt mit einem Radius im Bereich von 0,5 bis 1 Millimeter versehen sein. Radien in diesem Bereich sind hinreichend, um eine Rissbildung bei der Herstellung der Befestigungsbuchse (Tiefziehen) zu vermeiden.It is sufficient if the mounting bushing has a thickness of 0.3 to 1.5 millimeters, preferably 0.5 to 1 millimeter, when used within a swash plate type compressor of conventional sizes. This relatively small thickness is sufficient to produce the advantages of the invention. In particular, in this thickness range, the transition between the annular bottom portion to the adjacent cylindrical wall portion should be provided as well as the transition between the hollow cylindrical wall portion to the annular edge portion with a radius in the range of 0.5 to 1 millimeter. Radii in this range are sufficient to prevent cracking in the manufacture of the mounting bushing (deep drawing).

Weiter die Erfindung verbessernden Maßnahmen werden nachstehend gemeinsam mit der Beschreibung eines bevorzugten Ausführungsbeispiels der Erfindung anhand der Figuren näher dargestellt. Es zeigt:

Fig.1
eine Kolben-Zylinder-Einheit eines Taumelscheibenverdichters,
Fig.2
eine Befestigungsbuchse zur Befestigung des Kolbens an der Kolbenstange der Kolben-Zylinder-Einheit nach Fig. 1 im nicht-eingebauten Zustand, und
Fig.3
die Befestigungsbuchse nach Fig. 1 im eingebauten Zustand.
Further measures improving the invention will be described in more detail below together with the description of a preferred embodiment of the invention with reference to FIGS. It shows:
Fig.1
a piston-cylinder unit of a swash plate compressor,
Fig.2
a fastening bush for attaching the piston to the piston rod of the piston-cylinder unit after Fig. 1 in the non-installed state, and
Figure 3
the mounting socket after Fig. 1 in the installed state.

Gemäß Fig.1 besteht die hier dargestellte Kolben-Zylinder-Anordnung aus einem Zylinder 1, in welchem ein Kolben 2 axial hin- und her bewegbar angeordnet ist. Der Kolben 2 besteht hier aus Aluminium. Der Kolben 2 ist mit einer außenradialen Kolbenringanordnung 3 versehen, welche mit der Innenwandung des Zylinders 2 in Kontakt steht. Der Kolben 2 weist eine zentrale Durchgangsbohrung 4 auf, durch welche sich eine Befestigungsschraube 5 erstreckt. Mittels der Befestigungsschraube 5 erfolgt eine koaxiale Befestigung des Kolbens 2 stirnseitig an einer Kolbenstange 6. Die Kolbenstange 6 überträgt eine axiale Bewegung seitens des Triebwerks des - hier nicht weiter dargestellten - Taumelscheibenverdichters.According to Fig.1 the piston-cylinder arrangement shown here consists of a cylinder 1, in which a piston 2 is arranged axially back and forth movable. The piston 2 is made of aluminum here. The piston 2 is provided with an outer radial piston ring assembly 3 which is in contact with the inner wall of the cylinder 2. The piston 2 has a central through-bore 4, through which a fastening screw 5 extends. By means of the fastening screw 5 takes place a coaxial attachment of the piston 2 frontally on a piston rod 6. The piston rod 6 transmits an axial movement of the engine of the - not shown here - swash plate compressor.

Die zur Aufnahme der Befestigungsschraube 5 dienende Durchgangsbohrung 4 im Kolben 2 ist mit einer Senkung versehen. Die Senkung dient der Aufnahme einer Befestigungsbuchse 7, welche zwischen dem Kolben 2 und der Befestigungsschraube 5 wirkt. Die Befestigungsbuchse 7 besteht aus Stahl und unterstützt insoweit die Verbindungsstelle zwischen der Befestigungsschraube 5 und dem aus Aluminium bestehenden Kolben 2.The serving for receiving the fastening screw 5 through hole 4 in the piston 2 is provided with a reduction. The countersink serves to receive a fastening bushing 7, which acts between the piston 2 and the fastening screw 5. The mounting bushing 7 is made of steel and thus supports the connection point between the fastening screw 5 and the piston 2 made of aluminum.

Daneben dient die Befestigungsbuchse 7 auch einer Klemmbefestigung mindestens einer Sauglamelle 8 am Kolben 2. Diese Klemmbefestigung wird durch Einspannen der Sauglamelle 8 zwischen der Kolbenfläche 9 und der Befestigungsbuchse 7 erzielt. Die Sauglamelle 8 bildet mit einer korrespondierenden außermittigen Durchgangsbohrung 10 im Kolben 2 ein Rückschlagventil, welches einem Ansaugen von Luft aus der Atmosphäre durch den Kolben hindurch dient. Nach Komprimierung der so angesaugten Luft wird diese über ein stirnseitig am Zylinder angeordnetes Auslassventil 11 abgegeben.In addition, the fastening bushing 7 also serves to clamp at least one suction lamella 8 on the piston 2. This clamping attachment is achieved by clamping the suction lamella 8 between the piston surface 9 and the fastening bushing 7. The suction blade 8 forms with a corresponding eccentric through hole 10 in Piston 2, a check valve, which serves to suck in air from the atmosphere through the piston. After compression of the air sucked in this way, it is discharged via an outlet valve 11 arranged on the front side of the cylinder.

Gemäß Fig.2 besteht die Befestigungsbuchse 7 aus einem kreisringförmigen Bodenabschnitt 12, dem sich ein benachbarter hohlzylinderartiger Wandabschnitt 13 anschießt. Dem hohlzylinderartigen Wandabschnitt 13 wiederum schließt sich ein sich nach radial außen hin streckender Randabschnitt 14 an. Über den Randabschnitt 14 kommt die Befestigungsbuchse 7 an der Kolbenfläche 9 des Kolbens 2 zur Anlage. Der Randabschnitt 14 verläuft unter einem Winkel von < 90° zu dem hohlzylindrischen Wandabschnitt 13. Beim Festziehen der Befestigungsschraube 5 ergibt sich hieraus eine axiale Federwirkung zum Toleranzausgleich und zur Sicherung der Befestigungsschraube 5. Der Randabschnitt 14 der Befestigungsschraube 5 läuft weiterhin in der Dicke in eine Verjüngung 15 aus. Zur Vermeidung von Brüchen der hier eingespannten Sauglamelle 8 weist der Randabschnitt 14 außerdem eine außenradiale abgerundete Abrollkante 16 auf.According to Fig.2 the fastening bushing 7 consists of an annular bottom portion 12, to which an adjacent hollow cylinder-like wall portion 13 shoots. The hollow cylinder-like wall section 13, in turn, is adjoined by an edge section 14 which extends radially outward. About the edge portion 14, the mounting bush 7 comes to the piston surface 9 of the piston 2 to the plant. The tightening of the fastening screw 5 results in an axial spring action for tolerance compensation and securing the fastening screw 5. The edge portion 14 of the fastening screw 5 continues to run in thickness in one Rejuvenation 15 off. To avoid fractures of the here clamped suction plate 8, the edge portion 14 also has an outside radial rounded rolling edge 16.

Die Befestigungsbuchse 7 dieses Ausführungsbeispiels besteht aus Stahlblech mit einer Dicke von 0,7 Millimetern. Hiermit korrespondierend ist der Übergang zwischen dem kreisringförmigen Bodenabschnitt 12 zu dem benachbarten zylindrischen Wandabschnitt 13 genauso wie der Übergang zwischen dem hohlzylindrischen Wandabschnitt 13 zu dem kreisringförmigen Randabschnitt 14 mit einem Radius von 0,6 Millimetern versehen.The mounting bush 7 of this embodiment is made of sheet steel having a thickness of 0.7 millimeters. Correspondingly, the transition between the annular bottom portion 12 to the adjacent cylindrical wall portion 13 as well as the transition between the hollow cylindrical wall portion 13 is provided to the annular edge portion 14 with a radius of 0.6 millimeters.

Nach Fig. 3 ist die die Befestigungsbuchse 7 aufnehmende Senkung im Kolben 2 in der Tiefe größer ausgeführt ist als die axiale Länge der Befestigungsbuchse 7 im entspannten Zustand. Durch Anziehen der Befestigungsschraube 5 erfolgt dann ein axialer Toleranzausgleich, indem der Randbereich 14 einfedert. Der Randabschnitt 14 der Befestigungsbuchse 7 läuft in der Dicke sich verjüngend aus, um einen Öffnungswinkel 17 zur Bewegungsbegrenzung der hier eingespannten Sauglamelle 8 zu schaffen. Die Befestigungsbuchse 7 dient somit neben einer Verbesserung der Schraubverbindung hier auch als Klemmbefestigung der mindestens einen Sauglamelle 8 am Kolben 2.To Fig. 3 is the mounting bushing 7 receiving reduction in the piston 2 in the depth is made larger than the axial length of the mounting sleeve 7 in the relaxed state. By tightening the fastening screw 5 is then carried out an axial tolerance compensation by the edge portion 14 springs. The edge portion 14 of the mounting bushing 7 is tapered in thickness to create an opening angle 17 to limit the movement of the here clamped suction blade 8. The fastening bushing 7 thus serves, in addition to an improvement of the screw connection, also as a clamp fastening of the at least one suction lamella 8 on the piston 2.

Die Erfindung beschränkt sich nicht auf das vorstehend angegebene bevorzugte Ausführungsbeispiel. Es sind vielmehr auch Abhandlungen hiervon denkbar, welche vom Schutzbereich der nachfolgenden Ansprüche umfasst sind. So ist es beispielsweise auch möglich, die Befestigungsbuchse aus einem mehr oder weniger starken Stahlblech mit an die Blechdecke angepassten Radien herzustellen. Dieses ist lediglich eine Dimensionierungsfrage, welche von den geometrischen Abmessungen der Kolben-Zylinder-Anordnung abhängt.The invention is not limited to the preferred embodiment given above. On the contrary, it is also possible to devise therefrom articles which are covered by the scope of protection of the following claims. For example, it is also possible to produce the fastening bushing from a more or less strong steel sheet with radii adapted to the metal ceiling. This is merely a dimensioning issue, which depends on the geometric dimensions of the piston-cylinder assembly.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Zylindercylinder
22
Kolbenpiston
33
KolbenringanordnungPiston ring assembly
44
DurchgangsbohrungThrough Hole
55
Befestigungsschraubefixing screw
66
Kolbenstangepiston rod
77
Befestigungsbuchsemounting bushing
88th
Sauglamellesuction plate
99
Kolbenflächepiston area
1010
DurchgangsbohrungThrough Hole
1111
Auslassventiloutlet valve
1212
Bodenabschnittbottom section
1313
Wandabschnittwall section
1414
Randabschnittedge section
1515
Verjüngungrejuvenation
1616
Abrollkanteroll-off edge
1717
Öffnungswinkelopening angle

Claims (8)

  1. Piston-cylinder arrangement for a reciprocating compressor, in particular a swash-plate compressor, with a light-metal piston (2) that can move axially in a cylinder (1), which is attached to the end of a piston rod (6) by means of at least one fixing screw (5) that extends in the piston movement direction through a bore (4) passing through the piston, the bore (4) of the piston (2) being countersunk,
    characterised in that a fixing insert (7) with a circular bottom section (12) and an adjoining, hollow-cylindrical wall section (13) is provided, which is inserted into the countersink depression of the bore (4) to hold the head of the fixing screw (5), and which comes in contact against the adjacent piston surface (9) along a rim section (14) that is connected to the wall section (13) of the fixing insert (7) and extends radially outwards.
  2. Piston-cylinder arrangement according to Claim 1,
    characterised in that the countersink depression in the piston (2) that accommodates the fixing insert (7) is deeper that the axial length of the fixing insert (7), so that axial tolerances are compensated by tightening the fixing screw (5).
  3. Piston-cylinder arrangement according to Claim 1,
    characterised in that the fixing insert (7) also serves to hold at least one suction lamina (8) onto the piston (2) by clamping it between the piston surface (9) and the rim section (14).
  4. Piston-cylinder arrangement according to Claim1 or 2,
    characterised in that the rim section (14) that extends radially outwards is arranged at an angle smaller than 90° to the hollow-cylindrical wall section (13), so that the said tolerance compensation takes place by virtue of the axial elasticity of the rim section (14).
  5. Piston-cylinder arrangement according to Claim 3,
    characterised in that the rim section (14) of the fixing insert (7) has a taper (15) towards the edge, in order to provide an opening angle (17) to limit the movement of the suction lamina (8) clamped here.
  6. Piston-cylinder arrangement according to Claim 1,
    characterised in that the rim section (14) has a radially outer, rounded edge (16) to avoid breaking the at least one suction lamina (8) clamped here.
  7. Piston-cylinder arrangement according to Claim 1,
    characterised in that the fixing insert (7) consists of steel sheet and is produced by the production steps of deep-drawing, pressing and stamping.
  8. Swash-plate compressor with at least one piston-cylinder unit according to any of the preceding claims.
EP05818221A 2004-12-20 2005-12-16 Piston-cylinder arrangement for a reciprocating compressor Not-in-force EP1831562B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004061236A DE102004061236B3 (en) 2004-12-20 2004-12-20 Piston-cylinder arrangement for a reciprocating compressor
PCT/EP2005/013602 WO2006066828A1 (en) 2004-12-20 2005-12-16 Piston-cylinder arrangement for a reciprocating compressor

Publications (2)

Publication Number Publication Date
EP1831562A1 EP1831562A1 (en) 2007-09-12
EP1831562B1 true EP1831562B1 (en) 2008-06-18

Family

ID=35825981

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05818221A Not-in-force EP1831562B1 (en) 2004-12-20 2005-12-16 Piston-cylinder arrangement for a reciprocating compressor

Country Status (4)

Country Link
EP (1) EP1831562B1 (en)
AT (1) ATE398731T1 (en)
DE (2) DE102004061236B3 (en)
WO (1) WO2006066828A1 (en)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3036873A (en) * 1961-09-13 1962-05-29 Kimwood Machine Co Piston and piston rod connection
US3961868A (en) * 1974-02-21 1976-06-08 Thomas Industries, Inc. Air compressor
US5644969A (en) * 1996-06-28 1997-07-08 Thomas Industries Inc. Wobble piston and cylinder arrangement
DE19706066A1 (en) * 1997-02-17 1997-11-20 Hans Dipl Ing Unger Compressor providing compressed air in vehicle
ITTO980311A1 (en) * 1998-04-10 1999-10-10 Abac Aria Compressa COMPRESSOR.

Also Published As

Publication number Publication date
DE102004061236B3 (en) 2006-08-31
ATE398731T1 (en) 2008-07-15
EP1831562A1 (en) 2007-09-12
WO2006066828A1 (en) 2006-06-29
DE502005004481D1 (en) 2008-07-31

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