EP0569790B1 - Lubrication circuit for engines with crank drive - Google Patents
Lubrication circuit for engines with crank drive Download PDFInfo
- Publication number
- EP0569790B1 EP0569790B1 EP19930106979 EP93106979A EP0569790B1 EP 0569790 B1 EP0569790 B1 EP 0569790B1 EP 19930106979 EP19930106979 EP 19930106979 EP 93106979 A EP93106979 A EP 93106979A EP 0569790 B1 EP0569790 B1 EP 0569790B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- crosshead
- lubrication
- channel
- crankcase
- central
- 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.)
- Expired - Lifetime
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
- F01M11/02—Arrangements of lubricant conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/16—Controlling lubricant pressure or quantity
Definitions
- the invention relates to a lubrication circuit of machines with a crank mechanism, in particular plunger and piston pumps for the high-pressure delivery of working media, of the type specified in the preamble of claim 1 (GB-A-2 006 390).
- a lubrication system is known from CS-A-212 094, in which the pressure lubricant is fed via a separate branch of the lubrication circuit to the outer circumference of the cross head provided with grooves for the piston rings on its edges.
- the crosshead has a longitudinal groove on its outer circumference, which is connected to the transverse opening for the crosshead pin.
- the disadvantages of the known lubrication circuit systems include the difficult machining of the lubrication openings in the crankshaft and the need for an additional distribution of the lubricant to the crossheads.
- Another problem is the cyclically interrupted supply of the lubricant into the joint of the cross-head journal bearing due to the arrangement of the lubrication paths between the rotating crankshaft and the bore in the connecting rod for the supply of the lubricant. Since the most stressed assembly of the cross-head journal bearing at the end of the lubrication paths is in the area of the greatest pressure losses, the risk of malfunctions in the crank mechanism increases.
- the object of the invention is to provide a lubrication system for machines with a crank mechanism, which eliminates the disadvantages mentioned above. This is achieved by designing the main lubrication channel in accordance with the characterizing part of claim 1.
- the central lubrication channel is provided with a flow regulator of the lubricant.
- the lubrication circuit according to the invention enables reliable pressure lubrication of the crossheads with the lubricant, which is then conveyed under pressure to the next lubrication points and spaces via simplified, shortened and generously dimensioned lubrication paths.
- the construction according to the invention enables the bearing gap of the cross-head journal to be constantly filled with lubricant without interruptions and pressure pulsations during the rotation of the crankshaft.
- the supply of the lubricant to all pressure lubrication points is carried out by a single central lubrication channel, the crankshaft being not interrupted by any lubrication holes, which considerably simplifies their manufacture and processing.
- a plurality of crosshead guides 101 are formed in a crankcase 1 provided with a trough 2, in which a plurality of crossheads 3 of the crank mechanism are slidably guided and a crankshaft 4 is rotatably mounted in main bearings 41 at the end parts thereof.
- Each crosshead 3, which is fixedly connected to a piston rod, has two lateral projections which delimit a central cutout for receiving a connecting rod head 52.
- a high bearing journal 31 is fixed in aligned transverse bores of the two approaches, on the central part of which the connecting rod head 52 is mounted via a slide bearing 32.
- Each connecting rod is rotatably supported in a bearing 51 on the crankshaft 4.
- a continuous central lubrication channel 6 is formed in the crankcase 1 perpendicular to the longitudinal axis of the crosshead guides 101, which passes through the intermediate walls of the crosshead guides 101 and to a lubricant source 7 arranged outside the crankcase 1, e.g. B. is connected via a pressure pump 7 and a filter 8.
- a regulator 9 for controlling the lubricating oil flow, e.g. B. with an overflow valve provided.
- supply line lubrication channels 61 to the main bearings 41 of the crankshaft 4 are formed in the crosshead guides 101, lubrication channels 62 to the connecting rod bearings 51 in the connecting rods 5 and lubrication channels 63 to the connecting rod bearings 32 in the crosshead pins 31.
- the inlets and outlets of the sections of the central lubrication channel 6 in the crosshead guides 101 are, for. B. expanded by semi-closed semicircular grooves 102, which are shown in Fig. 2.
- pressure oil is passed from the source 7 via the filter 8 into the central lubrication channel 6 and from here via the corresponding vertical lubrication channels 61, 62, 63 to the individual lubrication points of the crank mechanism.
- the flow controller 9 is set so that a constant and uninterrupted supply of lubricant to both the exposed coupling points of the connecting rod 5 with the crosshead 3 as well as to the main bearing 41 of the crankshaft 4 and the connecting rod bearing 51 is ensured.
- the recorded execution is not the only possible solution according to the invention.
- the formation of a semi-closed semicircular groove 103 is unnecessary in each layer phase of the crosshead 3.
- the central lubrication channel 6 can also have an elongated cross section in order to ensure sufficient overlaps even with longer stroke lengths of the pistons.
- a plurality of axial bores can also be formed in the bearing journal 31, which communicate with the lubrication channels 62 and 63.
- the journals 31 can - as shown - be slightly shorter than the transverse bores in the cross heads 3 of the pistons, which results in end-side inlet and outlet chambers for the lubricating oil in and out of the cavities 311.
- the regulator 9 with its overflow valve can be replaced by another type of fitting or by an exchangeable or adjustable throttle.
- the lubrication circuit according to the invention can be used in all crank drives in which a constant and uninterrupted supply of the pressure lubricant to all lubrication points must be ensured.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
Description
Die Erfindung betrifft einen Schmierkreislauf von Maschinen mit Kurbeltrieb, insbesondere von Plunger- und Kolbenpumpen für die Hochdruckförderung von Arbeitsmedien, der im Oberbegriff des Patentanspruchs 1 angegebenen Gattung (GB-A-2 006 390).The invention relates to a lubrication circuit of machines with a crank mechanism, in particular plunger and piston pumps for the high-pressure delivery of working media, of the type specified in the preamble of claim 1 (GB-A-2 006 390).
Bei bekannten Schmierkreisläufen von Maschinen mit Kurbeltrieb erfolgt die Zuleitung und Verteilung des Druckschmiermittels in der Regel über Bohrungen in der Kurbelwelle. Von hier wird das Öl zum Haupt- und zum Pleuellager, und mit Hilfe einer weiteren Bohrung in den Pleuelstangen zu den Kreuzkopfzapfen geleitet. Zur Schmierung der eigentlichen Kreuzköpfe ist ein gesonderter Zweig des Schmierkreislaufes vorgesehen oder es wird ein Ölnebel erzeugt, was einen Sammelraum für das Öl oberhalb der Kreuzköpfe erforderlich macht.In known lubrication circuits of machines with a crank mechanism, the supply and distribution of the pressure lubricant is usually carried out through bores in the crankshaft. From here, the oil becomes the main and connecting rod bearings, and with the help of another hole in the connecting rods, the Phillips head directed. A separate branch of the lubrication circuit is provided for the lubrication of the actual crossheads or an oil mist is generated, which makes a collecting space for the oil above the crossheads necessary.
Aus der CS-A-212 094 ist ein Schmiersystem bekannt, bei dem das Druckschmiermittel über einen gesonderten Zweig des Schmierkreislaufes an den Außenumfang des an seinen Rändern mit Nuten für die Kolbenringe versehenen Kreuzkopfes herangeführt wird. Der Kreuzkopf hat an seinem Außenumfang eine Längsnut, die mit der Queröffnung für den Kreuzkopfzapfen verbunden ist.A lubrication system is known from CS-A-212 094, in which the pressure lubricant is fed via a separate branch of the lubrication circuit to the outer circumference of the cross head provided with grooves for the piston rings on its edges. The crosshead has a longitudinal groove on its outer circumference, which is connected to the transverse opening for the crosshead pin.
Zu den Nachteilen der bekannten Schmierkreislaufsysteme gehören die schwierige Bearbeitung der Schmieröffnungen in der Kurbelwelle und die Notwendigkeit einer zusätzlichen Verteilung des Schmiermittels zu den Kreuzköpfen. Problematisch ist ferner die zyklisch unterbrochene Zuführung des Schmiermittels in die Fuge der Kreuzkopfzapfenlagerung infolge der Anordnung der Schmierwege zwischen der rotierenden Kurbelwelle und der Bohrung in der Pleuelstange für die Zuführung des Schmiermittels. Da die meistbeanspruchte Baugruppe der Kreuzkopfzapfenlagerung am Ende der Schmierwege im Bereich der größten Druckverluste liegt, erhöht sich die Gefahr von Funktionsstörungen des Kurbeltriebes.The disadvantages of the known lubrication circuit systems include the difficult machining of the lubrication openings in the crankshaft and the need for an additional distribution of the lubricant to the crossheads. Another problem is the cyclically interrupted supply of the lubricant into the joint of the cross-head journal bearing due to the arrangement of the lubrication paths between the rotating crankshaft and the bore in the connecting rod for the supply of the lubricant. Since the most stressed assembly of the cross-head journal bearing at the end of the lubrication paths is in the area of the greatest pressure losses, the risk of malfunctions in the crank mechanism increases.
Aufgabe der Erfindung ist es, ein Schmiersystem für Maschinen mit einem Kurbeltrieb zu schaffen, das die oben genannten Nachteile beseitigt. Das wird durch die Gestaltung des Hauptschmierkanals gemäß dem kennzeichen des Anspruchs 1 erreicht.The object of the invention is to provide a lubrication system for machines with a crank mechanism, which eliminates the disadvantages mentioned above. This is achieved by designing the main lubrication channel in accordance with the characterizing part of claim 1.
Vorteilhaft sind in den Kreuzkopfführungen an den Übergängen des zentralen Schmierkanals in die Hohlräume der Kreuzkopfzapfen halbgeschlossene halbrunde Nuten und am Austritt aus dem Kurbelgehäuse der zentrale Schmierkanal mit einem Durchflußregler des Schmiermittels vorgesehen.In the crosshead guides at the transitions of the central lubrication channel into the cavities of the crosshead journals, semi-closed semicircular grooves and at the outlet are advantageous the crankcase, the central lubrication channel is provided with a flow regulator of the lubricant.
Der Schmierkreislauf gemäß der Erfindung ermöglicht eine zuverlässige Druckschmierung der Kreuzköpfe mit dem Schmiermittel, das anschließend unter Druck zu den nächsten Schmierstellen und -räumen über vereinfachte, verkürzte und reichlich dimensionierte Schmierwege gefördert wird. Die erfindungsgemäße Konstruktion ermöglicht die ständige Füllung des Lagerspaltes des Kreuzkopfzapfens mit Schmiermittel ohne Unterbrechungen und Druckpulsationen während der Drehung der Kurbelwelle. Die Zuführung des Schmiermittels an alle Druckschmierstellen wird von einem einzigen zentralen Schmierkanal vorgenommen, wobei die Kurbelwelle durch keinerlei Schmierbohrungen unterbrochen ist, was deren Herstellung und Bearbeitung wesentlich vereinfacht.The lubrication circuit according to the invention enables reliable pressure lubrication of the crossheads with the lubricant, which is then conveyed under pressure to the next lubrication points and spaces via simplified, shortened and generously dimensioned lubrication paths. The construction according to the invention enables the bearing gap of the cross-head journal to be constantly filled with lubricant without interruptions and pressure pulsations during the rotation of the crankshaft. The supply of the lubricant to all pressure lubrication points is carried out by a single central lubrication channel, the crankshaft being not interrupted by any lubrication holes, which considerably simplifies their manufacture and processing.
Weitere Vorzüge und Besonderheiten der Erfindung ergeben sich aus der folgenden Beschreibung von bevorzugten Ausführungsbeispielen anhand der Zeichnung. Es zeigen:
- Fig. 1
- einen Schnitt durch das Kurbelgehäuse mit einem Kurbeltrieb in der Ebene des zentralen Schmierkanals;
- Fig. 2
- einen Teilausschnitt einer halbrunden Nut am Durchgang des Schmierkanals durch die Kreuzkopfführung; und
- Fig. 3
- das Verhältnis und die Anordnung des zentralen Schmierkanals und des Hohlraumes des Kreuzkopfzapfens in Bezug auf den Kreuzkopfhub.
- Fig. 1
- a section through the crankcase with a crank mechanism in the plane of the central lubrication channel;
- Fig. 2
- a partial section of a semicircular groove at the passage of the lubrication channel through the crosshead guide; and
- Fig. 3
- the ratio and arrangement of the central lubrication channel and the cavity of the crosshead pin in relation to the crosshead stroke.
Wie aus Fig. 1 ersichtlich, sind in einem mit einer Wanne 2 versehenen Kurbelgehäuse 1 mehrere Kreuzkopfführungen 101 ausgebildet, in denen mehrere Kreuzköpfe 3 des Kurbeltriebes gleitend geführt und an deren Endteilen eine Kurbelwelle 4 in Hauptlagern 41 drehbar gelagert sind. Jeder mit einer Kolbenstange fest verbundene Kreuzkopf 3 weist zwei seitliche Ansätze auf, die einen mittleren Ausschnitt zur Aufnahme eines Pleuelstangenkopfes 52 begrenzen. In fluchtenden Querbohrungen der beiden Ansätze ist jeweils ein hoher Lagerzapfen 31 fixiert, auf dessen mittlerem Teil der Pleuelstangenkopf 52 über ein Gleitlager 32 gelagert ist. Jede Pleuelstange ist in einem Lager 51 auf der Kurbelwelle 4 drehbar gelagert. In einem mittleren Abschnitt des Hubweges des Kreuzkopfzapfens 31 ist im Kurbelgehäuse 1 senkrecht zur Längsachse der Kreuzkopfführungen 101 ein durchgehender zentraler Schmierkanal 6 gebildet, der die Zwischenwände der Kreuzkopfführungen 101 durchsetzt und an eine außerhalb des Kurbelgehäuses 1 angeordnete Schmiermittelquelle 7, z. B. über eine Druckpumpe 7 und einen Filter 8, angeschlossen ist. In der zu einem Sammelbehälter führenden Auslaßseite ist ein Regler 9 zum Steuern des Schmieröldurchflusses, z. B. mit einem Überströmventil, vorgesehen.As can be seen from FIG. 1, a plurality of
Der Querschnitt des zentralen Schmierkanals 6 ist im Verhältnis zum jeweiligen Hohlraum 311 im Kreuzkopfzapfen 31 so ausgebildet, daß sich in jeder Hublage des Kreuzkopfes 3 die Durchflußflächen überschneiden, wobei für den Durchmesser D des zentralen Schmierkanales 6 im Vergleich zum Durchmesser d des jeweiligen Hohlraumes 311 der Kreuzkopfzapfen 31 und der Länge L des Hubes des Kreuzkopfes 3 das Verhältnis
Senkrecht zur Achse des zentralen Schmierkanals 6 sind in den Kreuzkopfführungen 101 Zuleitungs-Schmierkanäle 61 zu den Hauptlagern 41 der Kurbelwelle 4, in den Pleuelstangen 5 Schmierkanäle 62 zu den Pleuellagern 51 und in den Kreuzkopfzapfen 31 Schmierkanäle 63 zu den Pleuelstangenlagern 32 ausgebildet. Die Ein- und Ausmündungen der Abschnitte des zentralen Schmierkanals 6 in den Kreuzkopfführungen 101 sind z. B. durch halbgeschlossene halbrunde Nuten 102 erweitert, die in Fig. 2 dargestellt sind.Perpendicular to the axis of the
Im Betrieb wird Drucköl von der Quelle 7 über das Filter 8 in den zentralen Schmierkanal 6 und von hier aus über die entsprechenden senkrechten Schmierkanäle 61, 62, 63 zu den einzelnen Schmierstellen des Kurbeltriebes geleitet. Der Durchflußregler 9 ist so eingestellt, daß eine ständige und ununterbrochene Schmiermittelzufuhr sowohl an sämtliche exponierten Kopplungsstellen der Pleuelstange 5 mit dem Kreuzkopf 3 als auch an die Hauptlager 41 der Kurbelwelle 4 und an die Pleuelstangenlager 51 gewährleistet ist.In operation, pressure oil is passed from the source 7 via the filter 8 into the
Die aufgezeichnete Ausführung ist nicht die einzige mögliche Lösung gemäß der Erfindung. So kann sich bei günstig gewähltem Verhältnis der Größen d, D, L und somit bei Sicherung einer genügenden Überdeckung des zentralen Schmierkanales 6 und des Hohlraumes 311 der Kreuzkopfzapfen 31 in jeder Lagenphase des Kreuzkopfes 3 die Bildung einer halbverschlossenen halbrunden Nut 103 erübrigen. Ferner kann der zentrale Schmierkanal 6 auch einen länglichen Querschnitt aufweisen, um ausreichende Überlappungen auch bei größeren Hublängen der Kolben sicherzustellen. Ferner können in den Lagerzapfen 31 statt des axial durchgehenden Hohlraumes 311 auch mehrere Axialbohrungen ausgebildet sein, die mit den Schmierkanälen 62 und 63 kommunizieren. Zweckmäßig können die Lagerzapfen 31 auch - wie dargestellt - geringfügig kürzer als die Querbohrungen in den Kreuzköpfen 3 der Kolben sein, wodurch sich endseitige Ein- und Auslaufkammern für das Schmieröl in bzw. aus den Hohlräumen 311 ergeben. Schließlich kann der Regler 9 mit seinem Überströmventil durch einen anderen Armaturentyp oder durch eine austauschbare bzw. einstellbare Drossel ersetzt werden.The recorded execution is not the only possible solution according to the invention. Thus, with a favorably chosen ratio of the sizes d, D, L and thus ensuring a sufficient overlap of the
Der Schmierkreislauf gemäß der Erfindung kann bei sämtlichen Kurbeltrieben verwendet werden, bei denen eine ständige und ununterbrochene Zuführung des Druckschmierstoffes an alle Schmierstellen gesichert sein muß.The lubrication circuit according to the invention can be used in all crank drives in which a constant and uninterrupted supply of the pressure lubricant to all lubrication points must be ensured.
Claims (3)
- A lubrication circuit of the machines with a crank mechanism especially of the plunger and piston pumps where in a crankcase (1) and least one crosshead (3) provided with a crosshead pin (3) is placed in a moveable position in a crosshead guide (101) and connected by means of a rod (5) to a crankshaft (4) which is placed in the crankcase (1) by main bearings (41) and where the lubrication circuit is represented by one central lubricating through-channel (6) placed in the crankcase (1) in the crosshead pin middle stroke (31) normal to the crosshead guide longitudial axis (101) where the rod lubricating channels (62) for the rod bearings (51) and the crosshead pin (31) lubricating channels (63) for the pin bearings (32) are branching off and where in the crosshead (3) pin (31) at least one axial through-hollow (311) is formed which is during the crosshead (3) stroke connected all the time with the central lubricating channel (6) and due to it the lubricant flow channel is formed characterized by the fact that the through-channels (61) for the main bearings (41) of the crankshaft (4) branchig off the lubricating channel (6) in the crankcase (1) and that the central lubricating chanel (6) is formed in such a way that the following relations are given for its diameter (D) compared to the hollow (311) diameter (d) of the crosshead pins (31) and the stroke lenght (L) of the crosshead (3)
- The lubrication circuit according to the claim 1 is characterized by the fact that in the transition points in the central lubricating channel (6) in the hollow (311) of the crosshead pins (31) in the crosshead guide (101) hemi-closed half-ring grooves (102) are placed.
- The lubrication circuit according to the claims 1 or 2 is characterized by the fact that the central lubrication channel (6) at the crankcase (1) outlet is provided with a lubricant flow controller (9).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CS921427A CZ142792A3 (en) | 1992-05-13 | 1992-05-13 | lubrication circuit of machines with crank mechanism |
CZ142792 | 1992-05-13 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0569790A1 EP0569790A1 (en) | 1993-11-18 |
EP0569790B1 true EP0569790B1 (en) | 1996-09-18 |
Family
ID=5348624
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19930106979 Expired - Lifetime EP0569790B1 (en) | 1992-05-13 | 1993-04-29 | Lubrication circuit for engines with crank drive |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0569790B1 (en) |
CZ (1) | CZ142792A3 (en) |
DE (1) | DE59303814D1 (en) |
SK (1) | SK278221B6 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017117516A1 (en) * | 2017-08-02 | 2019-02-07 | Man Truck & Bus Ag | Device for lubricating an internal combustion engine |
US10871227B1 (en) * | 2020-01-31 | 2020-12-22 | Black Horse, Llc | Power end of a pump |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB503007A (en) * | 1937-10-18 | 1939-03-29 | Sulzer Ag | Improvements in or relating to reciprocating engines having a crosshead between a piston rod and a connecting rod |
DE2747694B2 (en) * | 1977-10-25 | 1979-11-08 | Balcke-Duerr Ag, 4030 Ratingen | Lubrication of the crank mechanism of reciprocating piston engines and machines, in particular piston pumps |
DE3333844A1 (en) * | 1983-09-20 | 1985-03-28 | Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart | CYLINDER HEAD FOR A PREFERRED MULTI-CYLINDER INTERNAL COMBUSTION ENGINE |
JPS60155710U (en) * | 1984-03-27 | 1985-10-17 | 本田技研工業株式会社 | Lubrication system in internal combustion engines |
-
1992
- 1992-05-13 CZ CS921427A patent/CZ142792A3/en unknown
- 1992-05-13 SK SK142792A patent/SK278221B6/en unknown
-
1993
- 1993-04-29 DE DE59303814T patent/DE59303814D1/en not_active Expired - Fee Related
- 1993-04-29 EP EP19930106979 patent/EP0569790B1/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
EP0569790A1 (en) | 1993-11-18 |
CZ278114B6 (en) | 1993-08-11 |
DE59303814D1 (en) | 1996-10-24 |
SK278221B6 (en) | 1996-04-03 |
CZ142792A3 (en) | 1993-08-11 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE2649785A1 (en) | PUMP WITH SEVERAL RETURNING PISTONS | |
DE19826460C2 (en) | bearing arrangement | |
DE2747843A1 (en) | PISTON PUMP, IN PARTICULAR HIGH PRESSURE PISTON PUMP IN A HORIZONTAL CONSTRUCTION | |
DE19641052C2 (en) | Device for cooling lubricating oil of a V-engine | |
DE10246200B4 (en) | Oil supply device for a double piston compressor | |
EP0569790B1 (en) | Lubrication circuit for engines with crank drive | |
DE102006006121B4 (en) | Internal combustion engine with arranged in at least two parallel cylinder banks cylinders | |
EP1676989A1 (en) | Internal combustion engine with a piston cooling device | |
DE2631376B1 (en) | Cross-head journal bearings for piston engines, especially for diesel internal combustion engines | |
DE102006045899B4 (en) | Crank drive for crank drive pump and use in a fuel pump | |
EP1664513B1 (en) | Device for guiding media in a cylinder block and crankcase | |
DE69117978T2 (en) | OIL MIST AS A LUBRICANT | |
EP3857068A1 (en) | Labyrinth piston compressor | |
EP0907009A2 (en) | Coolant and lubricant passage for internal combustion engines | |
DE102017201741B4 (en) | Piston connecting rod device for direct piston lubrication and cooling | |
AT402321B (en) | CYLINDER HEAD FOR INTERNAL COMBUSTION ENGINES | |
DE69108635T2 (en) | V engine. | |
DE19942102B4 (en) | Lubricating structure for an internal combustion engine | |
DE1526395A1 (en) | Rotary piston internal combustion engine, in particular rotary piston internal combustion engine | |
DE2936068A1 (en) | PISTON PIN | |
WO2020064782A1 (en) | Piston compressor and method for operating same | |
DE2854234A1 (en) | CROSS-HEAD PIN BEARINGS FOR PISTON MACHINES, IN PARTICULAR FOR DIESEL ENGINEERING MACHINES | |
DE1528407A1 (en) | Hydraulic displacement device | |
DE4107315C2 (en) | ||
DE2523999A1 (en) | SWASHPLATE COMPRESSOR |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT DE GB IT |
|
17P | Request for examination filed |
Effective date: 19940502 |
|
17Q | First examination report despatched |
Effective date: 19950206 |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): DE |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE |
|
REF | Corresponds to: |
Ref document number: 59303814 Country of ref document: DE Date of ref document: 19961024 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 19970626 Year of fee payment: 5 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed | ||
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 19990202 |