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
  • F01M1/16—Controlling lubricant pressure or quantity
• • 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
  • F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
  • F01M2001/083—Lubricating systems characterised by the provision therein of lubricant jetting means for lubricating cylinders
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B3/00—Engines characterised by air compression and subsequent fuel addition
  • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

• the present invention relates to a lubrication system for dosing oil to one or more lubrication points in large piston engine cylinders, primarily in naval engines, and more specifically in the manner indicated in the introductory clause of claim 1.
• central lubrication devices each of which operates in connection with the lubrication points of one or more cylinders by pressing out oil portions through respective connecting pipes to the various oiling points at relevant moments of time.
• These moments or short time intervals are precisely defined in relation to the movement of the engine piston in the cylinder, the oil supply through a considered lubrication point ideally occurring exactly at the brief time lapse where a set of associated piston rings on the piston passes the concerned oiling point.
• the lubrication of the cylinder wall becomes ineffective, if the oil is supplied at moments where the cylinder wall is not being swept by the piston rings or special by oil scraping rings, respectively, exactly adjacent to the individual concerned lubrication point.
• the central lubrication devices are con ⁇ trolled in synchronism with the revolutions of the engine crankshaft and it is therefore relatively easy to adjust the device for supplying the various portions of lubricating oil to the various oiling points at reasonably relevant moments of time.
• a pressure oil accumulator may advantageously-be used which is placed in immediate proximity to the inlet of the individual dosing unit, such that it is possible by the relatively sudden opening of the valve to maintain the desired high supply pressure of the oil in an extra safe manner.
• a certain elasticity occurs in the longer supply pipe for the pressure oil, also because on average there must be correspondence between the oil supply from the oil pump and the inlet of oil at the oiling point.
• a primary aim is a lubrication with a determined oil quantity per round, even though it may be relevant to regulate this quantity, such as it is basically attempted by the use of the central lubricating devices, in which stroke adjustable piston pumps are provided for pressing out the oil to the individual oiling points or groups thereof.
• this principle may very well be applied without the said associated problems by a partial implementation of the known suggestion, viz. by the lubrication system being embodied as indicated in the characterizing clause of claim 1, i.e. in principle by effecting both the volumetric dosing and the time control by means of the locally placed dosing units.
• the dosing unit or units being designed for volumetrically determined intake and outlet of the oil portions, the latter will or may be correct regardless of the operating speed of the piston engine or the viscosity of the oil, and by the very fact of the dosing being controllable, an adaptation may easily be effectuated according to occurring parameter changes which may make such an adaptation desirable, e.g. a change of the oil viscosity.
• the dosing units may be embodied in a very simple manner, e.g.
• the pressurized oil may be used for filling the cylinder by its own pressure until the piston abuts the axial stop, and thereafter the pressurized oil may be used for emptying the measured-out oil volume to the oiling point, viz. in being connected to the cylinder space at the opposite side of the piston.
• the dosing will require no further operation energy, except for the valve control itself.
• the dosing units may be single-acting, with a working space which may be connected alternately to the inlet for pressurized oil, for filling of the working space, and to the oiling point for supplying oil thereto, and with a pressure champer, which is correspondingly alternately connectable to a return pipe and to the pressure oil inlet respectively, such that the piston may press out the oil in this champer during the filling of the working space and be pressed forwards by the pressurized oil for pressing out the measured-out oil volume.
• a differential piston one part of which operates in a pressure chamber of increased diameter relative the working chamber, the space between this piston and the narrower working piston simply being permanently connected to said return pipe.
• the ordinary oil pressure may be used for providing a locally strongly increased oiling pressure at the dosing unit.
• the dosing units may also be double-acting, the cylinder chambers on the two sides of the piston being connectable alternately to the pressure oil inlet and the oiling point, respectively.
• the said return pipe may be altogether dispensable. Also by this arrangement there may be made use of a differential piston, in double, even though a return pipe must then be used.
• Fig. 1 is a schematic side view of a single cylinder of a naval diesel engine.
• Fig. 2 is a more detailed sectional view of an individual oil injection unit used in connection herewith, and
• Fig. 3 is a corresponding sectional view of a modified embodiment of the injection unit.
• the cylinder shown in Fig. 1 has a cylinder liner 2 in which is provided a number of oiling holes 4, each of which is connected through a short pipe 6 to an associated injection unit 8.
• These units 8 are supplied with pressure oil through supply pipes 10 from a high-pressure pump 12 suctioning from a tank 14, to which is conducted a supply pipe 16 from a non-illustrated supply of lubricating oil, and a return pipe 18 from the units 8.
• Electrical control cables are indicated in dotted lines 20 from a control unit 22 to the individual units 8.
• the cylinder is provided with a piston 24, which via a piston rod 26 and a connecting rod 28 is connected to a crank 30,32 in a crank housing.
• each unit has a piston cylinder 40 with an outlet pipe 42 connected to a switch-over valve 44, which, controlled by an actuator unit 46, may be switched to connection with the injector pipe 6 and the oil supply pipe 10, respectively.
• the short pipe 6 is provided with a check-valve 7, preventing backwards flow of oil from the oiling hole 4.
• a piston 48 is mounted in the cylinder 40, and at its rear end the cylinder 40 is connected to a pipe conduit 50 leading to a switch-over unit 52 which is co-operated with the switch-over valve 44 in such a manner that the conduit 50 will be connected to the oil pressure pipe 10 when the outlet pipe 42 is connected to the injector pipe 6, while the pipe conduit 50 will be connected to the return pipe 18, when the outlet pipe 42 is connected to the pressure pipe 10.
• a stopper rod 54 projecting in through the upper rear end of the cylinder 40, which rod determines the maximally retracted position of the piston 48.
• this rod is secured against being rotated, and at its outer end it is in thread engagement with a stationarily fixed nut 56, which may be caused to rotate by a step motor 58 controlled from the control unit 22 in Fig. l.
• a pressure transducer 60 may be placed in connection with the pipe 50, and optionally a corres ⁇ ponding transducer may.be placed at the outlet 42,6 from the cylinder 40. These transducers may be connected to the control unit 22 e.g. for control and supervision purposes.
• valve unit 44,52 In a preparatory phase the valve unit 44,52 is held in such a position in which the pipe 42 is connected to the pressure pipe 10 at the lower end of the cylinder 40, while at the upper end of the cylinder the pipe 50 is connected to the return pipe 18.
• pressurized oil will be injected into the lower end of the cylinder 40, such that the piston 48 is pressed upwards until it abuts the end of the stopper rod 54.
• an accurately determined volume of oil will be measured out in the cylinder 40 below the piston 48, given by the positioning of the stopper rod 54, i.e. by the signals received by the motor 58 from the control unit 22 through the cable 20.
• the control unit 22 receives a plurality of different, relevant informations from various sensors in the system, such that the oil volume injected into the cylinder 40 will be appropriate for the subsequent supply of this volume through the oiling hole 4.
• the control unit 22 will provide current to the activating unit 46 for switching the valve unit 44,52.
• this piston is thrust powerfully downwards so as to eject the oil portion in front of the piston with great force in front of the piston for delivery through the oiling hole 4 during a very brief time lapse, thus with an abrupt finishing of both the beginning and the ending phase of the opening period.
• the unit 46 may be activated for resetting the switch valve 44,52, such that once more a new oil portion may be filled into the upper space of the cylinder 40.
• the filling will once more take place until the piston 48 abuts the stopper rod 54, the position of which may be currently adjusted by the control of the step motor 58 from the control unit 22, based on detections from different relevant sensors.
• a detected reduced motor load may condition a reduced oil dosage, while at the same time, as a primary function, it may be desirable to increase the dosing, if a sudden change in the motor load has just occurred, also including a reduction hereof, as such changes may otherwise cause an increased cylinder wear.
• the increased dosing should be maintained through a certain period of time after the occurred change, e.g. 15-30 minutes, which may easily be adjusted by means of a timer and optional sensors connected thereto for detection of conditions which may influence the optimal length of the period through which the increased lubrication is maintained.
• the pressure oil in the inlet 10 is stille used for pressing forward the piston 48 for dosing oil from the measuring chamber in front of the piston, but here the unit is designed as a double-acting unit.
• the shown change-over valve 62 sends pressure oil from the pipe 10 into the right hand end of the cylinder 40 through a pipe 64, while the left hand end of the cylinder is connected to a parallel change-over valve 66, position I, through a pipe 68.
• This valve is permanently connected to the concerned lubrication point or points through a short pipe 70.
• the pipes 64 and 68 are connected to the I-positions of the respective change-over valves 62 and 66, but moreover, they are connected through pipe extensions 74 and 76 to the II-positions of the respective opposite change-over valves.
• the cylinder 40 is entirely oil-filled at both sides of the piston 48.
• the piston 48 With the pair 62,66 of change-over valves in the shown position II, the piston 48 will be in the illustrated end position to the right.
• the valve 62,66 is changed into position I. Pressure oil from the pipe 10 will then flow to the right end of the cylinder through the valve 62 and the pipe 64.
• the piston 48 is thereby displaced to the left and presses out oil through the pipe 68 to the lubricating pipe 70. This pressing out abruptly stops, when the piston 48 abuts the left end of the cylinder.
• valve 62,66 is again shifted to position II. Pressure oil from the pipe 10 will then flow to the left end of the cylinder through the valve 66 and the pipe 68.
• the piston 48 is thereby displaced to the right and forces out the oil portion which was at the right side of the piston through the pipe 64, the valve 62 and the pipe 74 to the lubrication pipe 70. This forcing abruptly stops, when the piston 48 abuts the stopper rod 54.
• connection conduits 6 between the dosing units and the motor cylinder may be kept quite short, such that from a flow-technical point of view they may appear entirely rigid and thus without any noticeable accumulator effect, as would be undesired here.
• each dosing unit may be arranged so as to operate in connection with several lubrication points simultaneously, inasfar as normally several lubrication points are placed in the same cross section of the engine cylinder. Furthermore, an individual dosing unit will be able to operate in connection with several lubrication points at different moments, viz. through a suitable shifter equipment.
• the dosing units do not necessarily have to be placed immediately next to the oiling points. Already the possibility of positioning right next to the cylinder area will entail a noticeable reduction of the length of the lubrication pipes relative to current practice, and optionally the units may then be placed in local groups.
• the pressure oil per se which is used for producing the injection force, but the invention is not limited hereto.
• a compressed-air system may be used, e.g. in connection with a differential piston arrangement for amplifyring the pressure exerted on the dosing piston.
• a strong electromagnet may be used for projecting the dosing piston against a suitable spring effect. In such cases the inlet oil does not have to be conveyed at any particularly high pressure.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Lubrication Of Internal Combustion Engines (AREA)

Applications Claiming Priority (3)

Publications (2)

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ID=8099701

Family Applications (1)

Country Status (8)

Cited By (1)

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• 1991
  • 1991-05-24 DK DK98391A patent/DK98391D0/da not_active Application Discontinuation
• 1992
  • 1992-05-22 PL PL92301420A patent/PL171160B1/pl unknown
  • 1992-05-22 EP EP92910956A patent/EP0678152B1/fr not_active Expired - Lifetime
  • 1992-05-22 JP JP50977892A patent/JP3485319B2/ja not_active Expired - Lifetime
  • 1992-05-22 DE DE69221642T patent/DE69221642T2/de not_active Expired - Lifetime
  • 1992-05-22 WO PCT/DK1992/000165 patent/WO1992020909A1/fr not_active Ceased
  • 1992-05-22 KR KR1019930703570A patent/KR100251573B1/ko not_active Expired - Lifetime
  • 1992-05-22 DK DK92910956T patent/DK0678152T3/da active
  • 1992-05-22 ES ES92910956T patent/ES2106869T3/es not_active Expired - Lifetime

Non-Patent Citations (1)

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