EP0859151A2 - Compressors, especially for compressed-air provision in a motor vehicle - Google Patents

Compressors, especially for compressed-air provision in a motor vehicle Download PDF

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Publication number
EP0859151A2
EP0859151A2 EP98101952A EP98101952A EP0859151A2 EP 0859151 A2 EP0859151 A2 EP 0859151A2 EP 98101952 A EP98101952 A EP 98101952A EP 98101952 A EP98101952 A EP 98101952A EP 0859151 A2 EP0859151 A2 EP 0859151A2
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EP
European Patent Office
Prior art keywords
compressor
oil
drive shaft
engine
cylinder head
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
EP98101952A
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German (de)
French (fr)
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EP0859151A3 (en
EP0859151B1 (en
Inventor
Hans Unger
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Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
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Individual
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Publication of EP0859151A2 publication Critical patent/EP0859151A2/en
Publication of EP0859151A3 publication Critical patent/EP0859151A3/en
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Publication of EP0859151B1 publication Critical patent/EP0859151B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B39/0016—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 with valve arranged in the piston
    • 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
    • F04B27/0895—Component parts, e.g. sealings; Manufacturing or assembly thereof driving means
    • 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
    • F04B27/10—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 having stationary cylinders
    • F04B27/1009—Distribution members
    • 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
    • F04B27/10—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 having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • 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
    • F04B27/10—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 having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • 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
    • 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
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F04B39/064—Cooling by a cooling jacket in the pump casing

Definitions

  • the invention relates to a compressor according to the preamble of the claim 1.
  • compressors are regulated by pressure regulating valves (governor).
  • pressure regulating valves here will the air flow delivered by the continuously running compressor in the idling phase throttled by a device on the suction valve of the compressor or by venting devices discharged into the atmosphere at the pressure control valves.
  • This idle phase energy consumed by the compressor is pure energy loss.
  • the share of this energy loss in the total energy consumption of the compressor is not inconsiderable, because in vehicles the switch-on time is ED, among them the time during which the compressor pumps compressed air into the system is rarely understood over 30% of the entire term. Stopping the compressor, e.g. B. via a shut-off clutch, is not practiced because the torque curve, especially the torque peaks, very large and expensive couplings required do.
  • the object of the invention is, in particular for to represent the compressed air generation in motor vehicles, which compressor is not subject to the aforementioned disadvantages and problems, and which at compact design, but can be manufactured at a comparable price, like compressors today's construction.
  • the compressor is characterized by a largely oil-free run, since by the stripping and sealing elements acting on the piston rods are very effective Sealing between engine and compressor part, d. H. compared to that the back of the piston located suction chamber is formed.
  • the axial piston compressor shown in Figures 1 and 2 in the form of a swash plate compressor has an oil-lubricated engine 1, which essentially from a swash plate 5 and hemispheres mounted on a drive shaft 3 7 in 9 pans.
  • the engine 1 of known mode of operation is used to make 3 straight-line movements when the drive shaft rotates to reach the piston rods 13 carrying the pistons 11.
  • Warehousing the piston rods 13 take place in bearing bores 15 on the oil-lubricated engine side.
  • the bearing bores 15 extend on a pitch circle at an angular distance to each other parallel to the longitudinal axis of the compressor by a middle Housing section 17, on which the piston facing oil-stripping sealing elements 19 are provided.
  • the ones on the back of the pistons Chambers 21 are through an annular space 22 ( Figure 1) to a common suction space connected, in which a suction port opens.
  • the pistons 11 are equipped with piston rings 23 suitable for oil-free dry running and move in the cylinder bores preferably without contact.
  • This suction valve provides the connection between the piston during the suction stroke Suction chamber and pressure chamber 24 forth, the valve in accordance with FIG left-hand movement of the individual piston opens such that air through the Suction port and the interconnected chambers 21 in the pressure chamber 24 arrives and with subsequent movement directed to the right according to FIG closing suction valve 25 via the pressure valve shown in the sectional view 29 and an annular pressure chamber 30 are pushed into the pressure connection 31 becomes.
  • the cylinder head 33 of the pressure valve 29 Cool the compressor in an optimal way, since more cooling surface is available.
  • the cooling oil and Lubricating oil circuit identical, the pressure oil via the inlet 35 from the Lubricant circuit of the vehicle engine is fed to the compressor.
  • the oil initially flows for cooling via the annular space 37 and the connection 39 through the cylinder head into the central oil chamber 41; this is through the front End of the drive shaft 3 of the compressor limited. Extends through the drive shaft centrally an oil hole 43, from which at different positions Branch off branch bores 45.
  • Branch bore is lubricated as shown, the right end of the drive shaft 3; Oil is drilled into the interior of the engine via further branch holes initiated. Inside the engine, the oil is used to lubricate all those with friction Divide and leave the compressor through an outlet 47, which communicates with the interior of the engine. In the area of lubrication A seal 48 is provided on the right-hand end of the drive shaft 3, which prevents oil from entering the suction chambers. Passes through the outlet 47 the oil back into the lubricant circuit of the vehicle engine.
  • cooling oil 41 is along the outer circumference of the housing or channels placed in the housing wall passed into the engine 1. In this case, the oil chamber 41 is opposite closed the facing end of the drive shaft 3.
  • the very favorable torque curve of the compressor described above makes use of a compact, inexpensive shutdown clutch possible. It is possible to use the shut-off clutch, here as an electromagnetic clutch 49 shown to accommodate space-saving in the interior of the compressor.
  • the Swash plate 5 is rotatably mounted on the drive shaft 3 and is at Excitation of the magnet from a magnetic disk fixedly attached to the drive shaft 3 51 driven.
  • the magnetic disk 51 takes frictional engagement one with the swash plate 5 e.g. Drive plate connected by screws 52 with.
  • the magnet is de-energized, the engagement between the drive plate is released and magnetic disc, so that the drive shaft 3 runs empty and the compressor pistons are switched off.
  • the control with a pneumatically switched clutch is of a similar design possible.
  • the drive shaft and the swash plate are separated, it is possible to produce the swash plate from an inexpensive and well lubricated material, such as. B. Al cast.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Abstract

Bei einem Axialkolbenkompressor, insbesondere Taumelscheibenkompressor für die Drucklufterzeugung in Kraftfahrzeugen, sind ein ölgeschmiertes Triebwerk (1) und ein ölfrei laufendes Luft-Verdichterteil vorgesehen. Die unter Führung einer Taumelscheibe (5) in Zylinderbohrungen laufenden Kolben (11) weisen an ihrer Rückseite jeweils den durch Kammern (21) gebildeten Saugraum und an ihrer Vorderseite den Druckraum (23) auf. Saugventile (25) sind an den Kolben angeordnet, während Druckventile (29) im durch Kühlöl oder Wasser gekühlten Zylinderkopf (33) vorgesehen sind. Die Abdichtung zwischen ölgeschmiertem Triebwerk (1) und ölfrei laufendem Verdichterteil erfolgt mittels am Außenumfang der Kolbenstangen (13) der Kolben wirkender Abdichtelemente (19). Bei Verwendung von Kühlöl zur Kühlung des Zylinderkopfs (33) dient dieses gleichzeitig als Schmieröl für das Triebwerk (1). <IMAGE>In an axial piston compressor, in particular a swash plate compressor for the generation of compressed air in motor vehicles, an oil-lubricated engine (1) and an oil-free air compressor part are provided. The pistons (11) running in cylinder bores under the guidance of a swash plate (5) each have on their rear side the suction chamber formed by chambers (21) and on their front side the pressure chamber (23). Suction valves (25) are arranged on the pistons, while pressure valves (29) are provided in the cylinder head (33) cooled by cooling oil or water. The seal between the oil-lubricated engine (1) and the oil-free compressor part is carried out by means of sealing elements (19) acting on the outer circumference of the piston rods (13) of the pistons. If cooling oil is used to cool the cylinder head (33), this also serves as lubricating oil for the engine (1). <IMAGE>

Description

Die Erfindung betrifft einen Kompressor nach dem Gattungsbegriff des Patentanspruchs 1.The invention relates to a compressor according to the preamble of the claim 1.

Für die Drucklufterzeugung in Kraftfahrzeugen werden heute weltweit Einzylinder- oder Zweizylinder-Kompressoren verwendet. Die Kompressoren sind an den Motoren der Fahrzeuge angebaut und werden über Zahnräder, vereinzelt auch über Keilriemen, vom Motor direkt angetrieben. Die Schmierung der Kompressoren erfolgt aus dem Ölkreislauf der Motoren. Hierbei gelangt zwangsläufig auch Öl über die Kompressorkolben in die Druckluft. Je nach Zustand der Kompressoren können dies erhebliche Ölmengen sein, die größtenteils an den Lüftungsöffnungen der Druckluftanlagen in die Umwelt, meist auf die Straße, ausgegeben werden und damit als Umweltbelastung anzusehen sind. Bei den heute üblichen hohen Betriebsdrücken und der damit verbundenen hohen thermischen Beanspruchung verkokt außerdem ein Teil dieses Öls im Kompressor; die Ölkohle lagert sich im Zylinderkopf des Kompressors und in den nachgeschalteten Geräten ab und beeinflußt dort sehr nachteilig deren Standzeit.For the generation of compressed air in motor vehicles, single-cylinder or Two-cylinder compressors are used. The compressors are on the motors of the vehicles and are attached via gears, occasionally also via V-belts, driven directly by the engine. The compressors are lubricated from the oil circuit of the engines. This inevitably also gets oil over the Compressor pistons in the compressed air. Depending on the condition of the compressors, this can be significant amounts of oil, mostly at the ventilation openings of the compressed air systems into the environment, mostly on the street, and thus as Environmental pollution. At today's high operating pressures and the associated high thermal stress also cokes part of this oil in the compressor; the oil carbon is stored in the cylinder head of the compressor and in the downstream devices and influences there very disadvantageously their service life.

Geregelt sind diese Kompressoren durch Druckregelventile (Governor). Hierbei wird der vom ständig mitlaufenden Kompressor geförderte Luftstrom in der Leerlaufphase durch eine Einrichtung am Saugventil des Kompressors gedrosselt oder durch Entlüftungseinrichtungen an den Druckregelventilen in die Atmosphäre abgeleitet. Die in dieser Leerlaufphase vom Kompressor aufgenommene Energie ist reine Verlustenergie. Der Anteil dieser Verlustenergie am Gesamtenergieverbrauch des Kompressors ist nicht unbeträchtlich, denn in Fahrzeugen ist die Einschaltzeit ED, darunter versteht man die Zeit, in der der Kompressor Druckluft in die Anlage pumpt, selten über 30 % der gesamten Laufzeit anzusetzen. Ein Stillsetzen des Kompressors, z. B. über eine Abschaltkupplung, wird nicht praktiziert, weil der Drehmomentenverlauf, besonders die Drehmomentenspitzen, sehr große und kostspielige Kupplungen erforderlich machen. These compressors are regulated by pressure regulating valves (governor). Here will the air flow delivered by the continuously running compressor in the idling phase throttled by a device on the suction valve of the compressor or by venting devices discharged into the atmosphere at the pressure control valves. In the This idle phase energy consumed by the compressor is pure energy loss. The share of this energy loss in the total energy consumption of the compressor is not inconsiderable, because in vehicles the switch-on time is ED, among them the time during which the compressor pumps compressed air into the system is rarely understood over 30% of the entire term. Stopping the compressor, e.g. B. via a shut-off clutch, is not practiced because the torque curve, especially the torque peaks, very large and expensive couplings required do.

Ein weiterer Nachteil sind die negativen Drehmomentenanteile nach OT, als dem oberen Totpunkt des Kolbens im Kompressor. Diese führen bei Zahnradantrieb zu einem Flankenwechsel an den Zahnrädern und dadurch zu einer erheblichen Geräuschbelästigung. Bei Fahrzeugen, wo dies nicht gewünscht ist, wird durch kostspielige Maßnahmen an den Zahnrädern (z. B. Flankenspielminimierung, tangential vorgespannte Zahnräder), das genannte Problem mehr oder weniger befriedigend gelöst.Another disadvantage is the negative torque components after TDC than that top dead center of the piston in the compressor. These lead to gear drive a change of flanks on the gears and thereby considerable noise pollution. In vehicles where this is not desired, is by expensive Measures on the gear wheels (e.g. backlash minimization, tangential preloaded gears), the problem mentioned more or less satisfactory solved.

Davon ausgehend besteht die Aufgabe der Erfindung darin, einen insbesondere für die Drucklufterzeugung in Kraftfahrzeugen dienenden Kompressor darzustellen, welcher den vorgenannten Nachteilen und Problemen nicht unterliegt, und welcher bei kompakter Bauweise dennoch vergleichbar preisgünstig zu fertigen ist wie Kompressoren heutiger Bauweise.Proceeding from this, the object of the invention is, in particular for to represent the compressed air generation in motor vehicles, which compressor is not subject to the aforementioned disadvantages and problems, and which at compact design, but can be manufactured at a comparable price, like compressors today's construction.

Zur Lösung dieser Aufgabe dienen die Merkmale nach dem Kennzeichnungsteil des Patentanspruchs 1.To solve this problem, the features according to the labeling part of the Claim 1.

Der Kompressor kennzeichnet sich durch einen weitgehend ölfreien Lauf, da mittels der an den Kolbenstangen wirkenden Abstreif- und Dichtelementen eine sehr wirksame Abdichtung zwischen Triebwerk und Verdichterteil, d. h. gegenüber dem an der Rückseite der Kolben befindlichen Saugraum gebildet ist.The compressor is characterized by a largely oil-free run, since by the stripping and sealing elements acting on the piston rods are very effective Sealing between engine and compressor part, d. H. compared to that the back of the piston located suction chamber is formed.

Dadurch ist es möglich, die Saugventile auf den Kolben anzubringen, d. h. der Kompressor saugt durch die Kolben an. Dies hat wiederum den Vorteil, daß im Zylinderkopf mehr Raum für die Kühlung zur Verfügung steht, sodaß es in vielen Fällen möglich ist, den Kompressor mit Kühlöl aus dem Schmiermittelkreislauf des Fahrzeugs zu kühlen. Dies schließt aber nicht aus, daß bei höherer thermischer Beanspruchung Wasserkühlung für den Kompressor angewendet wird.This makes it possible to attach the suction valves to the piston, i.e. H. the compressor sucks in through the pistons. This in turn has the advantage that in the cylinder head more space is available for cooling, so in many cases is possible, the compressor with cooling oil from the lubricant circuit of the vehicle to cool. However, this does not exclude that with higher thermal stress Water cooling is applied to the compressor.

Vorteilhafte Ausgestaltungen und Weiterbildungen sind in den weiteren Patentansprüchen aufgeführt. Advantageous refinements and developments are in the further claims listed.

Die Erfindung ist nachfolgend anhand eines Ausführungsbeispiels unter Bezugnahme auf die beigefügte Zeichnung erläutert.

Figur 1
ist eine Längsschnittansicht des Kompressors gemäß der Erfindung, wobei einer der Kolben in versetzter Betriebsstellung gezeigt ist (Linie I-I in Fig. 2); und
Figur 2
ist eine Schnitt- und Draufsicht von Linie II - II in Figur 1.
The invention is explained below using an exemplary embodiment with reference to the accompanying drawings.
Figure 1
is a longitudinal sectional view of the compressor according to the invention, with one of the pistons shown in the offset operating position (line II in Fig. 2); and
Figure 2
is a sectional and plan view of line II - II in Figure 1.

Der in Figur 1 und 2 dargestellte Axialkolbenkompressor in Form eines Taumelscheibenkompressors weist ein ölgeschmiertes Triebwerk 1 auf, welches im wesentlichen aus einer auf einer Antriebswelle 3 gelagerten Taumelscheibe 5 und Halbkugeln 7 in Lagerpfannen 9 besteht. Das Triebwerk 1 von an sich bekannter Wirkungsweise wird verwendet, um bei Drehung der Antriebswelle 3 geradlinige Bewegungen der die Kolben 11 tragenden Kolbenstangen 13 zu erreichen. Die Lagerung der Kolbenstangen 13 erfolgt in Lagerbohrungen 15 auf der ölgeschmierten Triebwerksseite. Die Lagerbohrungen 15 erstrecken sich auf einem Teilkreis unter Winkelabstand zueinander parallel zur Längsachse des Kompressors durch einen mittleren Gehäuseabschnitt 17, an welchem den Kolben zugewandt ölabstreifende Abdichtelemente 19 vorgesehen sind. Die an der Rückseite der Kolben befindlichen Kammern 21 sind durch einen Ringraum 22 (Figur 1) zu einem gemeinsamen Saugraum verbunden, in welchen ein Sauganschluß mündet.The axial piston compressor shown in Figures 1 and 2 in the form of a swash plate compressor has an oil-lubricated engine 1, which essentially from a swash plate 5 and hemispheres mounted on a drive shaft 3 7 in 9 pans. The engine 1 of known mode of operation is used to make 3 straight-line movements when the drive shaft rotates to reach the piston rods 13 carrying the pistons 11. Warehousing the piston rods 13 take place in bearing bores 15 on the oil-lubricated engine side. The bearing bores 15 extend on a pitch circle at an angular distance to each other parallel to the longitudinal axis of the compressor by a middle Housing section 17, on which the piston facing oil-stripping sealing elements 19 are provided. The ones on the back of the pistons Chambers 21 are through an annular space 22 (Figure 1) to a common suction space connected, in which a suction port opens.

Die Kolben 11 sind mit für den ölfreien Trockenlauf geeigneten Kolbenringen 23 bestückt und bewegen sich in den Zylinderbohrungen vorzugsweise berührungsfrei.The pistons 11 are equipped with piston rings 23 suitable for oil-free dry running and move in the cylinder bores preferably without contact.

Jede der an der Rückseite der Kolben befindlichen Kammern 21 - als Saugraum wirkend - ist in vorstehend genannter Weise durch je einen Kolben 11 vom Druckraum 24 des Kompressors getrennt, wobei jeder der Kolben 11 ein Saugventil 25 trägt. Dieses Saugventil stellt während des Saughubes des Kolbens die Verbindung zwischen Saugraum und Druckraum 24 her, wobei sich das Ventil bei gemäß Figur 1 links gerichteter Bewegung des einzelnen Kolbens öffnet, derart, daß Luft durch den Sauganschluß und die miteinander verbundenen Kammern 21 in den Druckraum 24 gelangt und bei nachfolgender, gemäß Figur 1 nach rechts gerichteter Bewegung bei sich schließendem Saugventil 25 über das in der Schnittansicht dargestellte Druckventil 29 und eine ringförmige Druckkammer 30 in den Druckanschluß 31 ausgeschoben wird.Each of the chambers 21 located at the rear of the pistons - acting as a suction space - Is in the aforementioned manner by a piston 11 from the pressure chamber 24 of the compressor separately, each of the pistons 11 carrying a suction valve 25. This suction valve provides the connection between the piston during the suction stroke Suction chamber and pressure chamber 24 forth, the valve in accordance with FIG left-hand movement of the individual piston opens such that air through the Suction port and the interconnected chambers 21 in the pressure chamber 24 arrives and with subsequent movement directed to the right according to FIG closing suction valve 25 via the pressure valve shown in the sectional view 29 and an annular pressure chamber 30 are pushed into the pressure connection 31 becomes.

Durch die vorstehend erläuterte Zweiteilung des Arbeitsvolumens in Saugraum und Druckraum ist es möglich, den die Druckventile 29 tragenden Zylinderkopf 33 des Kompressors in optimaler Weise zu kühlen, da mehr Kühlfläche zur Verfügung steht. Bei dem in Figur 1 und 2 dargestellten Ausführungsbeispiel sind der Kühlöl- und Schmierölkreislauf identisch, wobei das Drucköl über den Einlaß 35 aus dem Schmiermittelkreislauf des Fahrzeugmotors dem Kompressor zugeführt wird. Hierbei strömt das Öl zunächst zur Kühlung über den Ringraum 37 und die Verbindung 39 durch den Zylinderkopf in die zentrale Ölkammer 41; diese ist durch das stirnseitige Ende der Antriebswelle 3 des Kompressors begrenzt. Durch die Antriebswelle erstreckt sich zentral eine Ölbohrung 43, von welcher an verschiedenen Positionen Zweigbohrungen 45 abzweigen. Mit Hilfe der bezüglich der Ölkammer 41 ersten Zweigbohrung wird gemäß Darstellung das rechte Ende der Antriebwelle 3 geschmiert; über weitere Zweigbohrungen wird Öl in den Innenbereich des Triebwerks eingeleitet. Im Inneren des Triebwerks dient das Öl zum Schmieren sämtlicher reibungsbehafteter Teile und verläßt den Kompressor durch einen Auslaß 47, welcher mit dem Inneren des Triebwerks in Verbindung steht. Im Bereich der Schmierung des rechtseitigen Endes der Antriebswelle 3 ist eine Dichtung 48 vorgesehen, welche das Eindringen von Öl in die Saugräume verhindert. Über den Auslaß 47 gelangt das Öl wieder in den Schmiermittelkreislauf des Fahrzeugmotors.Due to the division of the working volume into the suction space and Pressure chamber, it is possible for the cylinder head 33 of the pressure valve 29 Cool the compressor in an optimal way, since more cooling surface is available. In the embodiment shown in Figures 1 and 2, the cooling oil and Lubricating oil circuit identical, the pressure oil via the inlet 35 from the Lubricant circuit of the vehicle engine is fed to the compressor. Here the oil initially flows for cooling via the annular space 37 and the connection 39 through the cylinder head into the central oil chamber 41; this is through the front End of the drive shaft 3 of the compressor limited. Extends through the drive shaft centrally an oil hole 43, from which at different positions Branch off branch bores 45. With the help of the first with respect to the oil chamber 41 Branch bore is lubricated as shown, the right end of the drive shaft 3; Oil is drilled into the interior of the engine via further branch holes initiated. Inside the engine, the oil is used to lubricate all those with friction Divide and leave the compressor through an outlet 47, which communicates with the interior of the engine. In the area of lubrication A seal 48 is provided on the right-hand end of the drive shaft 3, which prevents oil from entering the suction chambers. Passes through the outlet 47 the oil back into the lubricant circuit of the vehicle engine.

Der Transport des Kühlöls ist nicht auf die Verbindung aus Ölbohrung 43 und Zweigbohrungen 45 beschränkt, d. h. da einer weiteren Variante wird das Kühlöl 41 entlang dem Außenumfang des Gehäuses bzw. in der Gehäusewandung plazierten Kanälen in das Triebwerk 1 geleitet. In diesem Falle ist die Ölkammer 41 gegenüber dem zugewandten Ende der Antriebswelle 3 verschlossen.The transport of the cooling oil is not on the connection of the oil hole 43 and branch holes 45 restricted, d. H. as a further variant, the cooling oil 41 is along the outer circumference of the housing or channels placed in the housing wall passed into the engine 1. In this case, the oil chamber 41 is opposite closed the facing end of the drive shaft 3.

Im Falle der Verwendung von Wasser aus dem Kühlkreislauf des Fahrzeugmotors für die Kühlung des Kompressors ist der vorgenannte Schmiermittel- und Kühlmittelkreislauf getrennt und die in Figur 1 dargestellte Verbindung 39 entfällt. Durch den Einlaß 35 wird nur Kühlwasser eingeleitet. In dem anhand von Figur 1 und 2 dargestellten Ausführungsbeispiel sind der Kühlwasserauslaß und der an anderer Stelle des Kompressors befindliche Schmiermitteleinlaß nicht gezeigt.In the case of using water from the cooling circuit of the vehicle engine for the cooling of the compressor is the aforementioned lubricant and coolant circuit separated and the connection 39 shown in Figure 1 is omitted. By the Inlet 35 is only introduced cooling water. In the illustrated with reference to Figures 1 and 2 Embodiment are the cooling water outlet and that elsewhere of the compressor lubricant inlet is not shown.

Der sehr günstige Drehmomentverlauf des vorstehend beschriebenen Kompressors macht die Verwendung von einer kompakten, kostengünstigen Abschaltkupplung möglich. Es ist möglich, die Abschaltkupplung, hier als elektromagnetische Kupplung 49 dargestellt, platzsparend im Innenraum des Kompressors unterzubringen. Die Taumelscheibe 5 ist hierbei drehbar auf der Antriebswelle 3 gelagert und wird bei Anregung des Magneten von einer drehfest auf der Antriebswelle 3 befestigten Magnetscheibe 51 angetrieben. Die Magnetscheibe 51 nimmt hierbei unter Reibschluß eine mit der Taumelscheibe 5 z.B. durch Schrauben verbundene Mitnehmerscheibe 52 mit. Bei Entregung des Magneten löst sich der Eingriff zwischen Mitnehmerscheibe und Magnetscheibe, so daß die Antriebswelle 3 leer durchläuft und die Kompressorkolben abgeschaltet sind.The very favorable torque curve of the compressor described above makes use of a compact, inexpensive shutdown clutch possible. It is possible to use the shut-off clutch, here as an electromagnetic clutch 49 shown to accommodate space-saving in the interior of the compressor. The Swash plate 5 is rotatably mounted on the drive shaft 3 and is at Excitation of the magnet from a magnetic disk fixedly attached to the drive shaft 3 51 driven. The magnetic disk 51 takes frictional engagement one with the swash plate 5 e.g. Drive plate connected by screws 52 with. When the magnet is de-energized, the engagement between the drive plate is released and magnetic disc, so that the drive shaft 3 runs empty and the compressor pistons are switched off.

In ähnlicher Bauweise ist die Regelung mit einer pneumatisch geschalteten Kupplung möglich.The control with a pneumatically switched clutch is of a similar design possible.

Mit der vorstehend erläuterten Art der Abschaltregelung ist es möglich, im Durchtrieb durch den Kompressor andere Geräte, wie z. B. eine Lenkhilfepumpe anzutreiben, auch wenn der Kompressor ausgekuppelt ist. Die mögliche Regelung des Kompressors mit einer Abschaltkupplung hat neben der optimalen Energieeinsparung den Vorteil, die Standzeit der ölfrei laufenden Kolbenringe 23 als auch die Standzeit der Abdichtelemente 19 auf den Kolbenstangen 13 so zu erhöhen, daß unter der Berücksichtigung der eingangs erwähnten Einschaltzeit ED von maximal 30 % mit diesen Bauteilen eine insgesamt ausreichende Standzeit erreicht wird.With the type of shutdown control explained above, it is possible in the through drive through the compressor other devices, such as. B. to drive a power steering pump, even when the compressor is disengaged. The possible regulation of the compressor with a shut-off clutch has besides the optimal energy saving Advantage, the service life of the oil-free piston rings 23 and the service life of the Sealing elements 19 on the piston rods 13 so that taking into account the switch-on time ED mentioned above of a maximum of 30% with these Components a sufficient overall service life is achieved.

Weil im erfindungsgemäßen Kompressor die Antriebswelle und die Taumelscheibe getrennt sind, ist es möglich, die Taumelscheibe aus einem kostengünstig herstellbaren und gut gleitfähigen Werkstoff, wie z. B. Al-Guß herzustellen. Because in the compressor according to the invention the drive shaft and the swash plate are separated, it is possible to produce the swash plate from an inexpensive and well lubricated material, such as. B. Al cast.

BezugszeichenlisteReference list

11
= Triebwerk= Engine
33rd
= Antriebswelle= Drive shaft
55
= Taumelscheibe= Swashplate
77
= Halbkugel= Hemisphere
99
= Lagerpfanne= Storage pan
1111
= Kolben= Piston
1313
= Kolbenstange= Piston rod
1515
= Lagerbohrung= Bearing bore
1717th
= Gehäuseabschnitt= Housing section
1919th
= Abdichtelement= Sealing element
2121
= Kammer= Chamber
2222
= Ringraum= Annulus
2323
= Kolbenring= Piston ring
2424th
= Druckraum= Pressure chamber
2525th
= Saugventil= Suction valve
2929
= Druckventil= Pressure valve
3030th
= Druckkammer= Pressure chamber
3131
= Druckanschluß= Pressure connection
3333
= Zylinderkopf= Cylinder head
3535
= Einlaß= Inlet
3737
= Ringraum= Annulus
3939
= Verbindung= Connection
4141
= Ölkammer= Oil chamber
4343
= Ölbohrung= Oil drilling
4545
= Zweigbohrung= Branch hole
4747
= Auslaß= Outlet
4848
= Dichtung= Seal
4949
= elektromagnetische Kupplung= electromagnetic clutch
5151
= Magnetscheibe= Magnetic disc
5252
= Mitnehmerscheibe= Drive plate

Claims (7)

Kompressor, insbesondere für die Drucklufterzeugung in Kraftfahrzeugen, mit einem durch eine Antriebswelle angetriebenen, mit einer Taumelscheibe versehenen und durch Öl geschmierten Triebwerk, welches mittels Kolbenstangen mit in Zylinderbohrungen laufenden Kolben in Verbindung steht, gekennzeichnet durch folgende Merkmale: a) das ölgeschmierte Triebwerk (1) des Kompressors ist mittels gegenüber jeder der Kolbenstangen (13) wirkender Abdichtelemente (19) gegenüber an der Rückseite der Kolben (11) bestehenden, ölfreien Kammern (21) abgedichtet; b) die Kammern (21) sind durch einen Ringraum (22) miteinander verbunden und stehen mit einem gemeinsamen Sauganschluß in Verbindung; und c) jeder Kolben (11) trägt ein Saugventil (25), derart, daß die Druckräume (24) des Kompressors zwischen Kolbenvorderseite und Zylinderkopf (33) gebildet sind. Compressor, in particular for the generation of compressed air in motor vehicles, with an engine driven by a drive shaft, provided with a swash plate and lubricated by oil, which is connected by means of piston rods to pistons running in cylinder bores, characterized by the following features: a) the oil-lubricated engine (1) of the compressor is sealed by means of sealing elements (19) acting against each of the piston rods (13) against oil-free chambers (21) existing on the rear of the pistons (11); b) the chambers (21) are connected to one another by an annular space (22) and are connected to a common suction connection; and c) each piston (11) carries a suction valve (25) such that the pressure chambers (24) of the compressor are formed between the front of the piston and the cylinder head (33). Kompressor nach Anspruch 1, gekennzeichnet durch folgende Merkmale: a) der Zylinderkopf (33) trägt die Druckventile (29) des Kompressors; und b) der Zylinderkopf (33) weist wenigstens einen Kühlmittelraum (Ringraum 37) zur Kühlung der Druckseite des Kompressors mittels Kühlöl oder Wasser auf. Compressor according to claim 1, characterized by the following features: a) the cylinder head (33) carries the pressure valves (29) of the compressor; and b) the cylinder head (33) has at least one coolant space (annular space 37) for cooling the pressure side of the compressor by means of cooling oil or water. Kompressor nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß bei Verwendung von Kühlöl das Triebwerk (1) des Kompressors durch das Kühlöl des Zylinderkopfs (33) geschmiert ist. Compressor according to claim 1 or 2, characterized in that when cooling oil is used, the engine (1) of the compressor is lubricated by the cooling oil of the cylinder head (33). Kompressor nach Anspruch 3, gekennzeichnet durch folgende Merkmale: a) der Ringraum (37) im Inneren des Zylinderkopfs (33) steht mit einem Einlaß (35) für das Kühl- und Schmieröl in Verbindung; b) der Zylinderkopf (33) begrenzt im Inneren des Kompressors eine zentral in Richtung des Triebwerks (1) sich erstreckende, über eine Verbindung (39) mit dem Ringraum (37) in Verbindung stehende Ölkammer (41); und c) die Ölkammer (41) ist triebwerksseitig durch die Antriebswelle (3) begrenzt und steht über mit in der Antriebswelle verlaufenden, zum Triebwerk führenden Bohrungen (Ölbohrung 43; Zweigbohrungen 45) in Verbindung. Compressor according to claim 3, characterized by the following features: a) the annular space (37) inside the cylinder head (33) communicates with an inlet (35) for the cooling and lubricating oil; b) the cylinder head (33) delimits in the interior of the compressor an oil chamber (41) which extends centrally in the direction of the engine (1) and is connected to the annular space (37) via a connection (39); and c) the oil chamber (41) is delimited on the engine side by the drive shaft (3) and is connected to bores (oil bore 43; branch bores 45) running in the drive shaft and leading to the engine. Kompressor nach einem der vorangehenden Ansprüche, gekennzeichnet durch eine im Inneren des Kompressors die Antriebswelle (3) umgebende, elektromagnetisch oder pneumatisch betätigbare Kupplung (49) zur Koppelung der Antriebswelle (3) mit der Taumelscheibe (5).Compressor according to one of the preceding claims, characterized by an electromagnetically or pneumatically operable clutch (49) surrounding the drive shaft (3) in the interior of the compressor for coupling the drive shaft (3) to the swash plate (5). Kompressor nach Anspruch 5, dadurch gekennzeichnet, daß die Taumelscheibe (5) drehbar auf der Antriebswelle (3) gelagert und mittels der Kupplung (49) drehfest mit der Antriebswelle (3) koppelbar ist, so daß die Taumelscheibe (5) und die Antriebswelle (3) aus unterschiedlichen Werkstoffen hergestellt werden können.A compressor according to claim 5, characterized in that the swash plate (5) is rotatably mounted on the drive shaft (3) and can be coupled in a rotationally fixed manner to the drive shaft (3) by means of the coupling (49), so that the swash plate (5) and the drive shaft ( 3) can be made from different materials. Kompressor nach Anspruch 6, dadurch gekennzeichnet, daß die Antriebswelle (3) aus Stahl besteht, und daß die Taumelscheibe (5) aus einem kostengünstig herstellbaren, gut gleitlagerfähigen Werkstoff, z. B. Aluminium-Guß, ausgeführt ist.Compressor according to claim 6, characterized in that the drive shaft (3) consists of steel, and that the swash plate (5) made of an inexpensive to produce, well slide-bearing material, eg. B. cast aluminum.
EP98101952A 1997-02-17 1998-02-05 Compressors, especially for compressed-air provision in a motor vehicle Expired - Lifetime EP0859151B1 (en)

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DE19706066 1997-02-17
DE19706066A DE19706066A1 (en) 1997-02-17 1997-02-17 Compressor providing compressed air in vehicle

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WO2006066828A1 (en) * 2004-12-20 2006-06-29 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Piston-cylinder arrangement for a reciprocating compressor
WO2006066827A1 (en) * 2004-12-20 2006-06-29 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Dry running swashplate compressor comprising a coated swashplate
DE102004061235A1 (en) * 2004-12-20 2006-07-06 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Dry-running swash plate compressor with a roller bearing swashplate
DE102004061224B4 (en) * 2004-12-20 2010-09-09 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Piston-cylinder arrangement, in particular for a swash plate compressor
CN101922431A (en) * 2009-06-15 2010-12-22 法雷奥热系统（日本）公司 Piston compressor
CN106489025A (en) * 2014-07-08 2017-03-08 Gea博客有限公司 Compressor

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Publication number Priority date Publication date Assignee Title
WO2006066830A1 (en) * 2004-12-20 2006-06-29 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Dry-running compressor, particularly a swash-plate compressor, with a piston-rod mounting
WO2006066828A1 (en) * 2004-12-20 2006-06-29 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Piston-cylinder arrangement for a reciprocating compressor
WO2006066827A1 (en) * 2004-12-20 2006-06-29 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Dry running swashplate compressor comprising a coated swashplate
DE102004061237A1 (en) * 2004-12-20 2006-07-06 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Dry running swash plate compressor with a coated swash plate
DE102004061235A1 (en) * 2004-12-20 2006-07-06 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Dry-running swash plate compressor with a roller bearing swashplate
DE102004061233B3 (en) * 2004-12-20 2006-07-13 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Dry running compressor, in particular swash plate compressor, with a piston rod storage
DE102004061236B3 (en) * 2004-12-20 2006-08-31 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Piston-cylinder arrangement for a reciprocating compressor
DE102004061224B4 (en) * 2004-12-20 2010-09-09 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Piston-cylinder arrangement, in particular for a swash plate compressor
CN101922431A (en) * 2009-06-15 2010-12-22 法雷奥热系统（日本）公司 Piston compressor
CN106489025A (en) * 2014-07-08 2017-03-08 Gea博客有限公司 Compressor
CN106489025B (en) * 2014-07-08 2020-07-21 Gea博客有限公司 Compressor with a compressor housing having a plurality of compressor blades

Also Published As

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EP0859151A3 (en) 1999-08-04
EP0859151B1 (en) 2003-04-23
US6247901B1 (en) 2001-06-19
DE19706066A1 (en) 1997-11-20
DE59808007D1 (en) 2003-05-28

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