EP1582706A2 - Internal combustion engine with cylinder lubricating system - Google Patents
Internal combustion engine with cylinder lubricating system Download PDFInfo
- Publication number
- EP1582706A2 EP1582706A2 EP05006988A EP05006988A EP1582706A2 EP 1582706 A2 EP1582706 A2 EP 1582706A2 EP 05006988 A EP05006988 A EP 05006988A EP 05006988 A EP05006988 A EP 05006988A EP 1582706 A2 EP1582706 A2 EP 1582706A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- lube oil
- lubricators
- cylinder
- oil
- electromagnetic valves
- 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
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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
- F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
-
- 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
- F01M1/06—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
- F01M1/00—Pressure lubrication
- F01M1/14—Timed lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/18—Other cylinders
- F02F1/20—Other cylinders characterised by constructional features providing for lubrication
-
- 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
- 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
- F01M2011/022—Arrangements of lubricant conduits for lubricating cylinders
Abstract
An internal combustion engine with a cylinder lubricating
system is proposed; with the system it becomes possible to
supply lube oil of required amount at required timing to each
of lubricators, and normal supply of lube oil is possible
even when malfunction occurs in some of the lubricators or
magnetic valves, and further the timing and amount of lube
oil supply can be adjusted even in engine operation in
accordance with varying factors such as properties of lube
oil, lube oil pressure, etc., resulting in a reduction of
lube oil consumption.
Lubricating oil pressure-fed by a lubricating oil pump is
accommodated in a common lube oil feeding section, the
lubricating oil accumulated in said common lube oil feeding
section is supplied to a plurality of lubricators (injectors)
through oil passages connecting said common lube oil feeding
section to said lubricators and injected to the inner surfaces
of cylinders of the engine by said lubricators, a plurality
of electromagnetic valves are provided for opening or closing
the oil passages and the timing and period of opening of each
of the valves are controlled independently so that lube oil
is injected from the lubricators to spaces between piston
rings once per one reciprocation of piston.
Description
The present invention relates to an internal combustion
engine with a cylinder lubricating system applied to a large
marine diesel engine, etc., lubricating oil pressure-fed by
a lubricating oil pump being accommodated in a common lube
oil feeding section, the lubricating oil in the common lube
oil feeding section being supplied to a plurality of
lubricators attached to engine cylinders to be supplied to
the inner surfaces of the cylinders by the system.
In large marine diesel engines, mechanical cylinder
lubricating system are widely used, in which, as disclosed
for example in patent literature 1 (Japanese Laid-Open Utility
Model Application No. 59-175619), a plurality of lubricators
are arranged along the circumferential direction of a cylinder,
and lubricating oil pressure-fed by an oil pump of plunger
type driven by the rotation of the crankshaft is supplied
to the inner surface of the cylinder by said lubricators.
In the lubricating system, a plurality of lubricators
(injectors) are arranged along the circumferential direction
of the cylinder, a rocker arm is oscillated by a cam formed
on a cam shaft driven by the crankshaft of the engine, the
plunger of a plunger type oil pump is provided so that an
end of which contacts an end of the rocker arm. The plunger
of the plunger type oil pump is reciprocated by the rocker
arm through the rotation of the cam, and lubricating oil is
supplied through an oil pipe connecting the oil pump to each
of the lubricators at timing in syntonization with the rotation
of the crankshaft to be supplied to the inner surface of the
cylinder by the lubricators. With the mechanical cylinder
lubricating system disclosed in said patent literature 1,
lubricating oil is supplied to the inner surface of the
cylinder from the lubricators at timing in syntonization with
engine rotation, so that the lube oil feed timing and the
characteristic of lube oil feed quantity are determined at
the stage of engine assembling, the timing and also quantity
of oil supplied are difficult to be adjusted, and it is
impossible to control the lubrication timing and the quantity
of lubricating oil supplied by each of a plurality of
lubricators.
As it is impossible with the prior art to control the amount
of lubricating oil to be supplied in accordance with varying
factors such as actual properties of the lubricating oil,
oil pressure, engine load, etc. Further, when some of the
plurality of lubricators malfunction, other functioning
lubricators can not help substitute for the function of the
troubled lubricators, so that wear in the inner surface of
cylinder or sticking tends to occur due to deteriorated
lubrication.
With the prior art, there are problems mentioned above,
and it is difficult to form an oil film extending over a wide
range particularly in the axial direction in the inner surface
of the cylinder. Therefore, it is difficult to achieve
lubrication performance capable to meet increasing output
of engine.
Further, with the prior art, as it is difficult to control
the timing of injecting lubricating oil to inner surface of
the cylinder, that is, to control the position of the piston
when lubricating oil is injected to the inner surface of the
cylinder, there may be a position for the piston not effective
for lubrication, resulting in a tendency that lubricating
oil consumption is increased and nevertheless wear or sticking
occurs in portions where lubrication oil is insufficiently
spread on the inner surface of the cylinder.
The present invention was made in light of the problems
in the prior art as mentioned above. An object of the invention
is to provide an internal combustion engine provided with
a cylinder lubricating system, in which it is possible to
supply necessary amount of lubricating oil to each of
lubricators or to each of positions to be supplied with
lubricating oil independently and at necessary timing in order
to make it possible to continue normal lube oil feeding even
when malfunction occurs in some of the lubricators, and further
it is possible to control the timing and amount of oil supply
in accordance with varying factors such as actual properties
and pressure of lubricating oil, engine load, etc. even during
engine operation, and lubricating oil consumption can be
reduced.
Another object of the invention is to attain lubrication
performance capable of meeting increased engine output
through evading wear and sticking due to lack of lubricating
oil on the inner surface of cylinder by allowing the formation
of oil film of uniform thickness spreading through wide range
of the inner surface of cylinder, particularly along the axial
direction of the cylinder, and to provide a cylinder
lubricating system with which lubricating oil consumption
can be reduced by eliminating non-effective lubrication.
To attain these objects, the present invention proposes
an internal combustion engine provided with a lubricating
system in which lubricating oil pressure-fed by a lubricating
oil pump is accommodated in a common lube oil feeding section,
the lubricating oil contained in said common lube oil feeding
section is supplied to a plurality of lubricators(injectors)
through oil passages connecting said common lube oil feeding
section to said lubricators and injected to the inner surfaces
of cylinders of the engine by said lubricators, wherein are
provided a plurality of electromagnetic valves for opening
or closing each of said oil passages independently, and a
controller for controlling the timing and period of opening
of each of said electromagnetic valves independently.
According to the invention, as the timing and period of
each of the electromagnetic valves connected to each of the
lubricators respectively are controlled independently, the
timing and amount of lube oil supply to the inner surface
of each cylinder can be adjusted independently in accordance
with the lubrication conditions in each cylinder at portions
to be supplied with lube oil.
By this, it becomes possible to supply required amount
of lube oil at required timing independently to portions to
be supplied with lube oil, and supply amount of lube oil can
be controlled to a minimum amount for maintaining each portion
to be supplied with lube oil in such a good lubrication
condition that the occurrence of wear or sticking can be
positively evaded. Therefore, lube oil consumption can be
reduced compared with prior art of cylinder lubricating system
in which the timing and amount of lube oil supply to a plurality
of lubricators are adjusted uniformly not independently.
In the invention, it is preferable that said controller
controls said electromagnetic valves so that when at least
one among two or more of said electromagnetic valves attached
per cylinder malfunctions, the opening period of other valve
or valves is lengthened.
By composing like this, the opening period, i. e. the supply
amount of lube oil of each of the electromagnetic valves can
be controlled independently, so that, when there occurs
malfunction in some of the electromagnetic valves, the
reduction in the amount of oil supply from lubricators
connected to said malfunctioning electromagnetic valves can
be complemented by lengthening the opening period of other
electromagnetic valves not malfunctioning. By this, lube oil
can be supplied to the inner surface of cylinder stably without
influenced by the occurrence of malfunction in some of the
electromagnetic valves.
In the invention, it is preferable that said controller
controls the opening period of said electromagnetic valves
so that the amount of oil supply which is determined as a
function of the opening period of the electromagnetic valves,
or lube oil injection ratio (injection amount of lube oil per
hour/engine load or engine output) calculated on the basis
of said amount of lube oil supply and engine load, is larger
than predetermined minimum amount of lube oil supply or minimum
lube oil injection ratio.
By composing like this, the amount of lube oil supply is
increased by lengthening the opening period of concerned
electromagnetic valve when actual amount of lube oil supply
or lube oil injection ratio is smaller than the proper value
corresponding to engine operating conditions such as engine
rotation speed, engine load, etc., and the amount of lube
oil supply is decreased by shortening the opening period of
concerned electromagnetic valve when actual amount of lube
oil supply or lube oil injection ratio is larger than the
proper value corresponding to engine operating conditions,
so that the most proper amount of lube oil, with which the
inner surface of cylinder can be lubricated properly, can
be supplied all over the operation range of the engine.
In the invention, it is preferable that an engine rotation
speed detector for detecting the rotation speed of the engine
and a fuel input sensor for detecting the amount of fuel input
are provided, said controller calculates engine load on the
basis of the engine rotation speed and amount of fuel input
detected and controls the opening /closing of said
electromagnetic valves so that lube oil is injected from said
lubricators every cycle when the engine is operated at a high
load higher than a certain load, and once per a few number
of cycles when the engine is operated at a low load lower
than said certain load, whereby stable lubrication is
possible even when necessary amount of lube oil supply per
unit time is small, resulting in a reduced lube oil consumption
at low load operation(or low speed operation).
By composing like this, stable supply of lube oil is possible
on the basis of detected engine load (or engine rotation speed)
also when the engine is operating at low load(low rotation
speed) in which the amount of lube oil injected from a
lubricator is small.
Said controller calculates lube oil injection ratio
(injection amount of lube oil per hour/engine load or engine
output) on the basis of the amount of lube oil supply calculated
as a function of the opening of the electromagnetic valves
and engine load calculated from the detected engine rotation
speed and amount of fuel input, and controls the opening period
of said electromagnetic valves so that said calculated lube
oil injection ratio coincides with a lube oil injection ratio
determined beforehand.
By composing like this, each of the electromagnetic vales
is controlled so that the lube oil injection ratio (the amount
of lube oil supply per an hour/engine load or engine output)
calculated on the basis of the amount of lube oil supply and
detected engine load coincides the targeted lube oil injection
ratio, preferably a constant lube oil injection ratio all
over the operation range of the engine, so that the amount
of lube oil supply can be controlled accurately to supply
a minimum amount of lube oil with which the inner surface
of cylinder can be lubricated properly in accordance with
each operating condition of the engine, and as a result, lube
oil consumption can be maintained to a minimum all over the
engine operating range.
In the invention, it is preferable that a specific
gravimeter is provided to said common lube oil feeding section,
and said controller controls said electromagnetic valves so
that the opening period thereof coincides with a value
predetermined in correspondence with the value of specific
gravity of lube oil inputted beforehand in the controller
from said specific gravimeter or the value of actual specific
gravity detected by said specific gravimeter.
Further, said controller controls said electromagnetic
valves so that the opening timing and period thereof coincides
with values predetermined in correspondence with the value
of viscosity of lube oil inputted beforehand in the controller
from a viscosity meter attached to the common lube oil feeding
section or the value of actual viscosity detected by said
viscosity meter.
By composing like this, when lube oil of large specific
gravity is used, the opening period of electromagnetic valve
is shortened to evade increase of mass flow due to increased
specific gravity by reducing volume flow of lube oil, and
the opening period is lengthened to evade decrease of mass
flow due to decreased specific gravity by increasing volume
flow of lube oil.
Further, it is possible to prevent a decrease in the amount
of lube oil supply due to increased viscosity by advancing
the opening timing and lengthening the opening period of the
electromagnetic valves and lack of lube oil induced by an
increased viscosity can be evaded. Therefore, the amount of
lube oil supply can be maintained always to a targeted amount
without influenced by the viscosity of lube oil.
Therefore, by controlling the timing and period of opening
of electromagnetic valve in accordance with the properties
of lube oil such as specific gravity and viscosity, lube oil
supply can be controlled corresponding to the properties of
lube oil.
In the invention, it is preferable that a pressure detector
or a temperature detector is provided to said common lube
oil feeding section, and said controller controls said
electromagnetic valves so that the opening period thereof
coincides with periods predetermined in correspondence with
the pressure or temperature of lube oil in the common lube
oil feeding section detected by and inputted from said pressure
detector or temperature detector.
By composing like this, the opening period of
electromagnetic valve is shortened to decrease the amount
of lube oil supply as the supply pressure of lube oil in the
common lube oil feeding section which is common for each
cylinder increases and the opening period of electromagnetic
valve is lengthened to increase the amount of lube oil supply
as the pressure decreases, so that the amount of lube oil
supply can be maintained always to a targeted amount without
influenced by lube oil pressure.
In the invention, it is preferable that said controller
controls said electromagnetic valves so that the opening
period thereof coincides with periods predetermined in
correspondence with the lift thereof which is predetermined
or measured.
By composing like this, the opening period of electromagnetic
valve is shortened when the detected lift of electromagnetic
valve is larger than the predetermined value or
measured value of the lift, and the opening period of electromagnetic
valve is lengthened when the detected lift of electromagnetic
valve is smaller than the predetermined value or
measured value of the lift, so that the amount of lube oil
supply can be maintained always to a targeted amount without
influenced by the variations of the lift of electromagnetic
valve even if the lift varies due to manufacturing errors.
In the invention, it is preferable that said controller
controls said electromagnetic valves in correspondence with
the predetermined or measured value of the air gap of said
electromagnetic valve.
By composing like this, the opening period is controlled
on the basis of the predetermined or measured air gap between
the core and the armature, so that the amount of lube oil
supply can be maintained always to a targeted amount without
influenced by the variations of the air gap of electromagnetic
valve even if the air gap varies due to manufacturing errors.
In the invention, a variety of connections between the
electromagnetic valve and the lubricator can be possible as
follows:
A pressure regulating valve is provided to an end part
of the common lube oil feeding section, and the lube oil pump
discharges lube oil more than the amount injected to the
cylinders of the engine. By this, lube oil in the common lube
oil feeding section is allowed to circulate and the temperature
of the lube oil in the common lube oil feeding section is
maintained at uniform temperature.
In the invention, a return pipe is provided along the common
lube oil feeding section, and heat exchange is possible between
the lube oil in the common lube oil feeding section and that
in the return pipe.
By this, temperature difference between the entrance and
exit of the common lube oil feeding section is reduced by
heating the lube oil in the common lube oil feeding section
by the lube oil increased in temperature and passing through
the return pipe after regulated in pressure, and the
viscosity of the lube oil in the common lube oil feeding section
is evened along the length of the section.
In the invention, the opening area of each of the
electromagnetic valves is larger than the sum of the passage
area of the lubricators connected to the concerned
electromagnetic valve.
By this, even if opening areas varies among a plurality
of electromagnetic valves due to the variations of valve lifts,
required amount of lube oil supply through the lubricators
can be achieved without influenced by the variations of valve
lifts of the electromagnetic valves.
The present invention proposes a method of supplying lube
oil to cylinders in a system in which the lube oil pressure-fed
by a lube oil pump is supplied to lubricators attached to
a cylinder through electromagnetic valves for adjusting the
timing and amount of lube oil supply and oil passages to supply
the lube oil to the inner surface of a cylinder in which a
piston having a plurality of piston rings reciprocates,
wherein lube oil is injected from the lubricators to spaces
formed between the piston rings at least once per one
reciprocation of piston.
The above recited method of supplying lube oil to cylinders
is performed by a cylinder lubricating system in which the
lube oil pressure-fed by a lube oil pump is supplied to
lubricators attached to a cylinder through electromagnetic
valves for adjusting the timing and amount of lube oil supply
and oil passages to feed the lube oil to the inner surface
of a cylinder in which a piston having a plurality of piston
rings reciprocates, wherein are provided a crank angle sensor
for detecting engine crank angle, rotation speed detector
for detecting engine rotation speed, and a load detector for
detecting engine load, and a controller for controlling the
electromagnetic valves so that lube oil is injected from the
lubricators to spaces formed between piston rings at least
once per one reciprocation of piston on the basis of the values
detected by the crank angle sensor, rotation detector, and
load detector.
According to the invention, as lube oil is supplied from
the lubricators to spaces formed between piston rings at least
once per one reciprocation of piston, the lube oil injected
from the lubricators and pooled in the spaces between piston
rings is spread by the reciprocation of the piston in the
axial direction on the inner surface of cylinder, and a uniform
oil film can be formed in a wide range particularly along
the axial direction on the inner surface of cylinder not only
near the portion where lube oil is injected from the
lubricators.
Therefore, lubrication on the inner surface of cylinder
is improved, the occurrence of wear and sticking of piston
rings can be evaded, and lubrication performance capable of
meeting high-powered engines can be achieved. Also an
reduction in lube oil consumption can be achieved by the
improvement of lubrication.
In the invention, it is preferable to compose as follows:
By composing like this, By the first method, the firstly
injected lube oil injected when the top piston ring is at
a position upper than the lubricators is carried upward by
the upward travel of the piston to upper portions of the
inner surface of the cylinder liner where lubrication
condition is severe, and the lube oil injected by the
succeeding second lube oil injection from the lubricators
and existing in the spaces between piston rings is carried
upward along the inner surfaces of the cylinder liner.
Therefore, lube oil can spread along the inner surface of
cylinder in the axial direction and particularly spreading
of lube oil toward upper portions of the inner surface is
improved.
(2) A first lube oil injection is done when the piston
is traveling downward and is at a positioned upper than the
lubricator(s) and then a second lube oil injection is done
to the spaces between the piston rings in the process of
downward traveling of the piston.
By composing like this, the firstly injected lube oil injected
when the top piston ring is at a position upper than the
lubricators is carried downward by the downward travel of
the piston to lower portions of the inner surface of the
cylinder liner, and the lube oil injected by the succeeding
second lube oil injection from the lubricators and existing
in the spaces between piston rings is carried downward along
the inner surfaces of the cylinder liner. Therefore, lube
oil can spread along the inner surface of the cylinder liner
in the axial direction and particularly spreading of lube
oil toward lower portions of the inner surface is improved.
(3) The lubricators are attached to the cylinder such that
the injection hole of each of the lubricator directs toward
directions circumferential to the inner surface of cylinder
so that lube oil is allowed to be injected from the lubricators
in directions circumferential to the inner surface of
cylinder.
By composing like this, lube oil can spread widely in the
circumferential direction.
(4) The lubricators are arranged in a plurality of rows
along the periphery of a cylinder, and lubricators belonging
to at least one row are attached to the cylinder such that
the injection hole of each of the lubricators directs toward
directions circumferential to the inner surface of cylinder
so that lube oil is allowed to be injected from the lubricators
in directions circumferential to the inner surface of
cylinder.
By composing like this, lube oil is injected from a plurality
of lubricators arranged in a plurality of row in the axial
direction of cylinder liner and lube oil injected from
lubricators belonging to at least a row is directed to the
circumferential direction of the inner surface of cylinder,
so that spreading of lube oil in the axial direction is improved
and lube oil spread widely also in the circumferential
direction on the inner surface of cylinder liner can be
improved.
A preferred embodiment of the present invention will now
be detailed with reference to the accompanying drawings. It
is intended, however, that unless particularly specified,
dimensions, materials, relative positions and so forth of
the constituent parts in the embodiments shall be interpreted
as illustrative only not as limitative of the scope of the
present invention.
FIG.1 is a overall connecting diagram of the first
embodiment of the electronic controlled lubricating system
of the present invention.
Referring to FIG.1, reference numeral 11 are cylinder
liners and two cylinders liners (cylinders) are shown in the
drawing. Reference numerals 12a, 12b, 12c, · · · , 12n (omitted)
are lubricators for feeding lube oil to the inner surface
of each cylinder 11. The plural lubricators 12a, 12b, 12c, · · · ,
12n are located along the periphery of each cylinder 11
preferably spaced equidistantly.
The timing and period of opening of each of these passages
16a, 16b, 16c, · · · , 16n is controlled by each of the
electromagnetic valves independently.
In FIG.7 is shown the structure of the electromagnetic
valve 17(17a, 17b, 17c, 17d, 17e, · · · , 17n) schematically.
In the drawing, reference numeral 172 is a valve case, 173
is a valve seat, 171 is a valve body, 174 is an armature fixed
on the valve body 171, 175 is a solenoid, 176 is a valve room.
In an electromagnetic valve like this, when the solenoid 175
is energized, the armature 174 is pulled up and the valve
body 171 is lifted up by a distance L, and the lube oil supplied
to the valve room 176 is sent out to an outlet passage 178.
In the drawing, Ga is the air gap between the undersurface
of the solenoid 175 and the upper surface of the armature
174 when said lift L is at its maximum.
In the cylinder lubricating system shown in FIG.1, when
the lube oil pressure-fed by the lube oil pump 14 and
accumulated in the common lube oil feeding section 15 and
each of the oil passages 16a, 16b, 16c, · · · , 16n is opened
by the actuation of each of the electromagnetic valves 17a,
17b, 17c, 17d, 17e, · · · , 17n each of which are controlled
independently by the controller 19, the lube oil accumulated
in the common lube oil feeding section 15 is supplied to each
of the lubricators 12a, 12b, 12c, · · · , 12n through each of
the lube oil passages 16a, 16b, 16c, · · · , 16n to be injected
to the inner surface of the cylinder liner 11.
Reference numeral 1 is an engine rotation speed detector
for detecting the rotation speed of the engine, 2 is a fuel
injection quantity sensor for detecting the quantity of fuel
injected into the cylinders, 3 is a crank angle sensor for
detecting crank angles of engine, i.e. rotation positions
of the crankshaft of engine. Reference numeral 4 is a load
detector by which engine load (output) is calculated from the
engine rotation speed detected by said engine rotation speed
detector 1 and the fuel injection quantity detected by said
fuel injection quantity sensor 2.
The engine rotation speed detected by the engine rotation
speed detector 1, the engine load detected(calculated) by
the load detector 4, the crank angle detected by the crank
angle sensor 3, the oil pressures of the lubricators 12a,
12b, 12c, · · · , 12n detected by the oil pressure sensors 21,
the specific gravity of lube oil measured by the specific
gravimeter 9 and viscosity of lube oil measured by the
viscosity meter 10, are inputted to a calculation part 191 (see
FIG.2) for calculating timing and period of opening of each
electromagnetic valve.
Further, measured lift L of each of the electromagnetic
valves 17a, 17b, 17c, 17d, 17e, · · · , 17n and measured air
gap Ga are also inputted to the calculation part 191 for
calculating timing and period of opening of electromagnetic
valve.
Next, the operation of the first embodiment will be
explained referring to FIG. 2 showing the control block diagram,
and FIG. 1.
The controller 19 performs calculations and controls on
the basis of each value detected and the target or permissible
values set in the setting part 192 as follows:
By composing like this, by lengthening the opening period
of the electromagnetic valve or valves other than the
malfunctioning valve of a concerned cylinder, reduction of
amount of lube oil supply through the lubricator connected
to the malfunctioning valve can be complemented by the other
valve or valves not malfunctioning, for each of the
electromagnetic valves can be controlled independently.
Therefore, even if some of the electromagnetic valves
connected to lubricators attached to one cylinder malfunction,
enough lube oil can be supplied to the inner surface of said
cylinder without influenced by the malfunction.
Further, the calculation part 191 for calculating the timing
and period of opening of electromagnetic valve compares the
actual amount of lube oil supply, which is calculated as a
function of the opening period of electromagnetic valve, or
lube oil injection ratio with the minimum amount of lube oil
or minimum lube oil injection ratio preset in the opening
timing and period setting part 192, and the opening period
of each of the electromagnetic valves 17a, 17b, 17c, · · · ,
17n is controlled so that lube oil of an amount larger than
the minimum amount is supplied or so that lube oil injection
ratio is larger than the minimum lube oil injection ratio.
That is, when actual lube oil amount supplied through some
of the lubricators or actual injection ratio thereof happens
to be smaller than the minimum amount or minimum injection
ratio, the opening period of each of electromagnetic valves
connected to those some of lubricators is lengthened to
increase the amount of lube oil supplied to those lubricators.
By composing like this, when the actual amount of lube
oil supply or lube oil injection ratio calculated as a function
of the opening period of electromagnetic valve is smaller
than the minimum value determined corresponding to engine
operation conditions, the opening period of the concerned
electromagnetic valve is lengthened to increase the amount
of lube oil to be supplied to the cylinder, and when said
actual amount is larger than said minimum value determined
corresponding to engine operation conditions, the opening
period of the concerned electromagnetic valve is shortened
to decrease the amount of lube oil to be supplied to the cylinder,
so that an amount of lube oil capable of properly lubricating
the inner surface of the cylinder 11 can be supplied always
in accordance with engine operating conditions.
Further, in the timing and period of opening setting part
192 are set lube oil feeding modes of feeding lube oil from
the lubricator 12a, 12b, 12c, · · · , 12n once per a few number
of cycles of engine rotation when the engine is operated under
low load lower than a certain reference load and feeding lube
oil from the lubricator 12a, 12b, 12c, · · · , 12n for every
cycle when the engine is operated under high load higher than
a certain reference load.
The timing and period of opening calculating part 191
selects a lube oil feeding mode corresponding to the engine
rotation speed and engine load inputted from the engine
rotation speed detector 1 and load detector 4 respectively
from the modes set in the timing and period of opening setting
part 192, lube oil is supplied from the lubricators 12a, 12b,
12c, · · · , 12n once per a few number of cycles of engine rotation
when the engine is operated under low load lower than a certain
reference load, and lube oil is supplied from the lubricators
12a, 12b, 12c, · · · , 12n for every cycle when the engine is
operated under high load higher than a certain reference load.
By composing like this, lube oil is supplied in accordance
with the detected engine load (or engine rotation speed) such
that lube oil is supplied for every cycle when operating at
a high load(or high rotation speed) with which lubricating
condition on the inner surface of cylinder is severe and lube
oil is supplied once for a few number of cycles when operating
at a low load (or low rotation speed) with which the lubricating
condition is not so severe, so that lubricating oil consumption
is decreased particularly in low load operation.
Further, in the timing and period of opening setting part
192 is set relations between reference(target) values of
engine load(or rotation speed) and lube oil injection
ratio(injection amount of lube oil per hour/engine load or
engine output) of the amount of the fuel supplied from the
lubricators 12a, 12b, 12c, · · · , 12n.
The timing and period of opening calculating part 191
calculates lube oil injection ratio on the basis of the actual
amount of oil supplied to cylinder and the detected engine
load, compares the calculated lube oil injection ratio with
the reference(target) value of lube oil injection ratio
corresponding to the engine load set in the timing and period
of opening setting part 192, and the opening periods of each
of the electromagnetic valves 17a, 17b, 17c, · · · , 17n are
controlled according to the result of comparison so that the
opening period thereof coincides with said reference (target)
value.
P14
By composing like this, as the opening period of each of
the electromagnetic valves 17a, 17b, 17c, · · · , 17niscontrolled
so that the lube oil injection ratio calculated on the basis
of actual amount of lube oil supply and detected engine load
coincide with reference value of lube oil injection ratio
targeted, preferably a constant value, in all over the engine
operation conditions, lube oil is accurately controlled to
be supplied to the inner surface of the cylinder liner 11
by an amount with which proper lubrication is carried out
and lube oil consumption can be reduced to a minimum in all
over the operation conditions of the engine.
Further, in the timing and period of opening setting part
192 is set a relation between the lube oil feeding pressure
to the cylinder liner 11 and the opening period of the
electromagnetic valve, i.e. the amount of lube oil supply.
The timing and period of opening calculating part 191 takes
out from the timing and period of opening setting part 192
the opening period of each of the electromagnetic valves 17a,
17b, 17c, · · · , 17n corresponding to the detected lube oil
feeding pressure in the common lube oil feeding section 15
sent from the pressure sensor 21.
By composing like this, it is possible to decrease the
amount of lube oil supply as the oil pressure increases by
shortening the opening period of the electromagnetic valves
17a, 17b, 17c, · · · , 17n, and to increase the amount of lube
oil supply as the oil pressure decreases by lengthening the
opening period of the electromagnetic valves 17a, 17b, 17c, · · · ,
17n, so that the amount of lube oil supply can be maintained
always to a targeted amount without influenced by lube oil
pressure.
In the timing and period of opening setting part 192 is
set a relation between the specific gravity of lube oil and
the opening period of the electromagnetic valve, i.e. the
amount of lube oil supply such that the opening period is
shortened as the specific gravity of lube oil increases and
the opening period is lengthened as the specific gravity of
lube oil decreases.
The timing and period of opening calculating part 191 takes
out from the timing and period of opening setting part 192
the opening period of each of the electromagnetic valves 17a,
17b, 17c, · · · , 17n corresponding to the detected specific
gravity of lube oil inputted from the specific gravimeter.
By composing like this, it is possible to decrease the
amount of lube oil supply, i.e. volume flow rate of lube oil
as the specific gravity of oil increases by shortening the
opening period of the electromagnetic valves 17a, 17b, 17c, · · · ,
17n, and to increase the amount of lube oil supply as the
specific gravity of lube oil decreases by lengthening the
opening period of the electromagnetic valves 17a, 17b, 17c, · · · ,
17n, so that the amount of lube oil supply can be maintained
always to a targeted amount without influenced by the specific
gravity of lube oil.
Further, in the timing and period of opening setting part
192 is set a relation between the viscosity of lube oil and
the timing and period of opening of the electromagnetic valve,
i.e. the amount of lube oil supply such that the timing is
advanced and the period is lengthened as the viscosity of
lube oil increases and the timing is retarded and the period
is shortened as the viscosity of lube oil decreases.
The timing and period of opening calculating part 191
takes out from the timing and period of opening setting part
192 the timing and period of each of the electromagnetic
valves 17a, 17b, 17c, · · · , 17n corresponding to the detected
viscosity of lube oil inputted from the viscosity meter.
By composing like this, it is possible to prevent a decrease
in lubricating ability due to viscosity rise by advancing
the opening timing resulting in an increase in the amount
of lube oil supply, and by lengthening the opening period
of the electromagnetic valves 17a, 17b, 17c, · · · , 17n which
results in lengthening the period of lube oil being supplied
to the inner surface of cylinder liner 11. Therefore, the
amount of lube oil supply can be maintained always to a targeted
amount.
In the timing and period of opening setting part 192 is
set a relation between the lift L of the electromagnetic valve
as shown in FIG.7 and the opening period thereof so that the
opening period is shortened as the lift L increases in order
that the amount of lube oil supply is always constant.
The timing and period of opening calculating part 191 takes
out from the timing and period of opening setting part 192
the opening period of each of the electromagnetic valves 17a,
17b, 17c, · · · , 17n corresponding to the measured value of
lift L.
By composing like this, it is possible to shorten the opening
period of the electromagnetic valves 17a, 17b, 17c, · · · ,
17n when measured value of lift L is larger than the set value
of the lift L, and to lengthen the opening period when measured
value of lift L is smaller than the set value of the lift
L, so that, even if there are variations in valve lifts of
electromagnetic valves due to manufacturing errors, the
amount of lube oil supply can be maintained always to a targeted
amount without influenced by said errors.
In the timing and period of opening setting part 192 is
set a relation between the air gap Ga of the electromagnetic
valve as shown in FIG.7 and the opening period thereof so
that the opening period is shortened as the air gap Ga increases
in order that the amount of lube oil supply is always constant.
The timing and period of opening calculating part 191 takes
out from the timing and period of opening setting part 192
the opening period of each of the electromagnetic valves 17a,
17b, 17c, · · · , 17n corresponding to the measured value of
air gap Ga.
By composing like this, it is possible to shorten the opening
period of the electromagnetic valves 17a, 17b, 17c, · · · ,
17n when measured value of air gap Ga is larger than the set
value of the air gap Ga, and to lengthen the opening period
when measured value of lift L is smaller than the set value
of the air gap Ga, so that, even if there are variations in
sir gaps of electromagnetic valves due to manufacturing errors,
the amount of lube oil supply can be maintained always to
a targeted amount without influenced by said errors.
In the timing and period of opening setting part 192 is
set a relation between the sulfur concentration in fuel and
the opening period of the electromagnetic valve so that the
opening period is determined to allow a minimum amount of
lube oil necessary to neutralize the sulfur to flow.
The timing and period of opening calculating part 191 takes
out from the timing and period of opening setting part 192
the opening period of each of the electromagnetic valves 17a,
17b, 17c, · · · , 17n corresponding to the sulfur concentration
in fuel.
By composing like this, it is possible to suppress
increasing of sulfur which deteriorate lubrication on the
inner surface of cylinder by controlling the opening period
of the electromagnetic valves 17a, 17b, 17c, · · · , 17n and
maintaining a minimum flow of lube oil necessary to neutralize
the sulfur in fuel.
In FIG. 3 to FIG. 5 showing the second to fourth embodiments,
a variety of connections between the electromagnetic valves
17 and the lubricators 12 are shown.
In the second embodiment shown in FIG.3, a plurality of
the lubricators 12 are attached to one cylinder as shown by
12a, 12b, 12c, 12d, 12e, · · · , 12n , and oil passages connecting
to the lubricators 12 are composed to consist of main passages
161, 162, 163, and 164 and branch oil passages 16a, 16b, 16c,
16d, 16e, · · · , 16n (corresponding to the oil passages in the
first embodiment) branching from the main passages 161, 162,
163, and 164 to be connected to each of the lubricators 12a,
12b, 12c, 12d, 12e, · · · , 12n. An electromagnetic valve 17
is provided to each of main oil passages, that is, a valve
17A and a valve 17B are provided to the main oil passages
161, and 162 respectively and another valve 17A and valve
17B are provided to the main oil passages 163 and 164
respectively. Thus, by controlling a plurality of lubricator
12 by one electromagnetic valve 17, the number of
electromagnetic valves 17 is reduced.
By the way, detectors and sensors shown in FIG. 1 are omitted
in FIG.3.
In the third embodiment shown in FIG.4, the branch oil
passages 16a, 16b, 16c, 16d, 16e, · · · , 16n connected to the
lubricators 12a, 12b, 12c, 12d, 12e, · · · , 12n arranged along
the periphery of one cylinder liner 11 are connected
alternately to the main oil passages 161, 162, 163, and 164.
The electromagnetic valves 17A and 17B provided to the main
oil passages 161 and 162 control respectively the lube oil
flow to the alternately disposed lubricators, that is, for
example, the valves 17A controls the lubricators 12a, 12c,
and 12d, and valves 17B controls the lubricators 12b, 12d,
and 12n. By this, controlling of lube oil supply is evened
along the circumferential direction of the cylinder.
The composition other than the points mentioned above is
the same as that of the first embodiment shown in FIG.1 or
the second embodiment shown in FIG.3 and the same component
is indicated by the same reference numeral.
By the way, detectors and sensors shown in FIG. 1 are omitted
in FIG.3.
In the fourth embodiment shown in FIG.5, a plurality of
the lubricators 12 are attached to one cylinder as shown by
12a, 12b, 12c, 12d, 12e, · · · , 1 2 n , and oil passages
connecting to the lubricators 12 are composed to consist of
main passages 161, 162, 163, and 164 and branch oil passages
16a, 16b, 16c, 16d, 16e, · · · , 16n (corresponding to the oil
passages in the first embodiment) branching from the main
passages 161, 162, 163, and 164 to be connected to each of
the lubricators 12a, 12b, 12c, 12d, 12e, · · · , 12n, as is
in the case of the second embodiment. In this fourth embodiment,
a plurality of controllers 19A and 19B instead of a single
controller 19 in the second embodiment, and the
electromagnetic valves 17A and 17B are controlled
independently by the controller 19A, and 19B respectively.
The composition other than the points mentioned above is
the same as that of the first embodiment shown in FIG. 1 or
the second embodiment shown in FIG.3 and the same component
is indicated by the same reference numeral.
By the way, detectors and sensors shown in FIG. 1 are omitted
in FIG.5.
In the fifth embodiment shown in FIG.6, a return pipe 23
and a pressure regulation valve 22 are provided to allow the
lube oil in the common lube oil feeding section 15 to return
to the lube oil pump 14 so that lube oil temperature in the
common lube oil feeding section 15 is even along the widely
extending section 15 by heating the lube oil in the common
lube oil feeding section 15 by the lube oil in the return
pipe 23.
The composition other than the points mentioned above is
the same as that of the first embodiment shown in FIG.1 or
the second embodiment shown in FIG.3 and the same component
is indicated by the same reference numeral.
By the way, detectors and sensors shown in FIG. 1 are omitted
in FIG.6.
In each of the embodiments, the opening area of each of
the electromagnetic valves 17(17a, 17b, 17c, · · · , 17n) is
larger than the sum of the passage area of the lubricators
connected to the concerned electromagnetic valve (for example,
In FIG.4, the opening area of the valve 17A is larger than
the sum of the passage area of the lubricator 12a, 12b, and
12c) .
By this, even if opening areas varies among a plurality
of electromagnetic valves due to the variations of valve lifts,
required amount of lube oil supply through the lubricators
can be obtained without influenced by the variations of valve
lifts of the electromagnetic valves.
FIG.8 is an overall schematic representation of the sixth
embodiment of the cylinder lubricating system of a diesel
engine according to the present invention, and FIG. 9. is an
enlarged detail of a part indicated by Z in FIG.8.
In FIG.8 and FIG.9, reference numeral 11 is a cylinder
liner (cylinder) , 51 is a piston which reciprocates along the
inner surface 11a of the cylinder liner 11, 52 are a few number
of piston rings received in ring groove of the piston 52 (in
the drawing, four rings are provided). Reference numeral 53
are spaces between the piston rings 52 formed between the
inner surface of the cylinder liner 11 and the outer surface
of the piston 51. Reference numeral 56 is a cylinder cover,
55 is an exhaust valve, and 58 is a combustion chamber. The
composition mentioned above is the same as that of prior art.
Reference numeral 1 is an engine rotation speed detector
for detecting the rotation speed of the engine, 4 is a load
detector for detecting engine load (fuel injection quantity,
etc.), 3 is crank angle sensor for detecting crank angles
of engine, i.e. rotation positions of the crankshaft of engine .
Each of the electromagnetic valves 70 is controlled
independently by the controller 19 to adjust the timing and
period of opening thereof.
When the diesel engine provided with the fifth embodiment
is in operation, the lube oil pressure-fed by the lube oil
pump 14 is accumulated in the common lube oil feeding section
15. When each of the oil passages 156 is opened by each of
the electromagnetic valves 70 controlled independently by
the controller 19, the lube oil accumulated in the common
lube oil feeding section 15 is supplied to the lubricators
12 through the oil passages 156 and injected to the inner
surface of the cylinder liner 11 from each of the lubricators
12.
The controller 19 controls the timing and period of opening
of each of the electromagnetic valves 70 on the basis of the
detected values of crank angle, engine rotation speed, and
engine load by the first or second method described in the
following.
The controlling by the first method is done as follows:
By the first method, the firstly injected lube oil injected
when the top piston ring is at a position upper than the
lubricators 12 (at a position upper than the upper lubricators
in the case the lubricators are arranged in two rows as this
example) is carried upward by the upward travel of the piston
51 to upper portions of the inner surface of the cylinder
liner 11 where lubrication condition is severe, and the lube
oil injected by the succeeding second lube oil injection from
the lubricators 12 and existing in the spaces 53 between piston
rings is carried upward along the inner surfaces of the
cylinder liner 11. Therefore, lube oil can spread along the
inner surface 11a of the cylinder liner in the axial direction
and particularly spreading of lube oil toward upper portions
of the inner surface 11a is improved.
The controlling by the first method is done as follows:
When the piston 51 travels downward, a first lube oil
injection is done from the lubricators 12 arranged in two
rows when the bottom piston ring(lowermost piston ring of
the four piston rings in the drawing) is at a position upper
than the lubricators 12(at a position upper than the lower
lubricators in the case the lubricators are arranged in two
rows as this example), then a second lube oil injection is
done in the process of downward travel of the piston 51. As
there are three spaces 53 between piston rings in the example,
it is intended to inject lube oil at least to the lowermost
space between piston rings, and lube oil is injected to other
spaces between piston rings by either of the lubricators
arranged in two rows.
By the second method, the firstly injected lube oil injected
when the top piston ring is at a position upper than the
lubricators 12 (at a position upper than the lower lubricators
in the case the lubricators are arranged in two rows as this
example) is carried downward by the downward travel of the
piston 51 to lower portions of the inner surface of the cylinder
liner 11 , and the lube oil injected by the succeeding second
lube oil injection from the lubricators 12 and existing in
the spaces 53 between piston rings is carried downward along
the inner surfaces of the cylinder liner 11. Therefore, lube
oil can spread along the inner surface 11a of the cylinder
liner in the axial direction and particularly spreading of
lube oil toward lower portions of the inner surface 11a is
improved.
The lubricators 12 arranged along the periphery of the
cylinder liner 11(arranged in two rows in this example) may
be attached to the cylinder such that the injection hole of
each of the lubricators is directed to directions
circumferential to the inner surface 11a of cylinder liner
so that lube oil spreads widely in the circumferential
direction of the inner surface 11a of cylinder.
When the lubricators 12 are arranged in a plurality of
rows(two rows in this example) along the periphery of the
cylinder liner 11, the injection hole of lubricators belonging
at least to a row may be attached to the cylinder liner 11
such that the injection hole of each of the lubricators is
directed to directions circumferential to the inner surface
11a of cylinder liner is directed. In this case also lube
oil can be spread widely in the circumferential direction
of the inner surface 11a of cylinder.
By this, lube oil is injected from a plurality of lubricators
arranged in a plurality of row in the axial direction of
cylinder liner 11 and lube oil injected from lubricators
belonging to at leas a row is directed to the circumferential
direction of the inner surface of cylinder, so that the
spreading of lube oil in the axial direction is improved and
lube oil spreads widely also in the circumferential direction
on the inner surface 11a of cylinder liner.
According to the sixth embodiment, lube oil is injected
from the lubricators 12 to the spaces 53 between piston rings
at least once per one reciprocation of the piston 51, and
the lube oil pooled in the spaces 53 between piston rings
is transferred in the axial direction of the inner surface
11a of cylinder liner, so that an oil film of even thickness
is formed on a wide range of the inner surface 11a of cylinder,
particularly over a wide range along the axial direction
thereof not only near portions where lube oil is injected
from the lubricators.
By this, lubrication of the inner surface 11a of cylinder
liner is improved, and the occurrence of wear or sticking
of piston rings 52 can be evaded. Also, lubrication oil
consumption is decreased due to the improved lubrication 12.
As has been described in the foregoing, according to the
cylinder lubricating system of the present invention, it
becomes possible to supply lube oil of required amount at
required timing to each lubricator, that is, to each portion
of the inner surface of cylinder independently, and normal
supply of lube oil is possible even when malfunction occurs
in some of the lubricators including magnetic valves to open
/ close the oil passages to supply lube oil to the lubricators.
Further, the timing and amount of lube oil supply can be
adjusted even in engine operation in accordance with varying
factors such as properties of lube oil, lube oil pressure,
etc. In addition, lube oil consumption can be reduced.
Further, according to the present invention, it becomes
possible to supply lube oil of required amount at required
timing to each lubricator, that is, to each portion of the
inner surface of cylinder independently, and supply amount
of lube oil or lube oil injection ratio can be controlled
so that a minimum amount of lube oil required to maintain
good lubricating condition in the inner surface of cylinder
to positively evade the occurrence of wear or sticking of
piston or piston rings is supplied on the inner surface of
cylinder. Therefore, lube oil consumption can be reduced
compared with prior art of cylinder lubricating system in
which the timing and amount of lube oil supply to a plurality
of lubricators are adjusted uniformly not independently.
The timing and supply amount or injection ratio of lube
oil can be adjusted easily even in engine operation.
Further, according to the invention, as lube oil is supplied
from lubricators to spaces between piston rings at least once
per one reciprocation of piston, the lube oil supplied and
pooled in the spaces between piston rings is carried in the
axial direction on the inner surface of cylinder and an oil
film of even thickness is formed on a wide range of the inner
surface 11a of cylinder, particularly over a wide range along
the axial direction thereof not only near portions where lube
oil is injected from the lubricators.
By this, lubrication of the inner surface of cylinder liner
is improved, and the occurrence of wear or sticking of piston
rings can be evaded. Also, lubrication oil consumption is
decreased due to the improved lubrication.
Claims (23)
- An internal combustion engine provided with a lubricating system in which lubricating oil pressure-fed by a lubricating oil pump is accommodated in a common lube oil feeding section, the lubricating oil contained in said common lube oil feeding section is supplied to a plurality of lubricators(injectors) through oil passages connecting said common lube oil feeding section to said lubricators and injected to the inner surfaces of cylinders of the engine by said lubricators, wherein are provided a plurality of electromagnetic valves for opening or closing each of said oil passages independently, and a controller for controlling the timing and period of opening of each of said electromagnetic valves independently.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein said controller controls said electromagnetic valves so that when at least one among two or more of said electromagnetic valves which are attached per cylinder malfunctions, the opening period of other valve or valves is lengthened.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein said controller controls the opening period of said electromagnetic valves so that the amount of oil supply which is determined as a function of the opening period of the electromagnetic valves, or lube oil injection ratio(injection amount of lube oil per hour/engine load or engine output) calculated on the basis of said amount of lube oil supply and engine load, is larger than predetermined minimum amount of lube oil supply or minimum lube oil injection ratio.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein an engine rotation speed detector for detecting the rotation speed of the engine and a fuel input sensor for detecting the amount of fuel input are provided, said controller calculates engine load on the basis of the engine rotation speed and amount of fuel input detected and controls the opening /closing of said electromagnetic valves so that lube oil is injected from said lubricators every cycle when the engine is operated at a high load higher than a certain load, and once per a few number of cycles when the engine is operated at a low load lower than said certain load, whereby stable lubrication is possible even when necessary amount of lube oil supply per unit time is small.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein said controller calculates lube oil injection ratio (injection amount of lube oil per hour/engine load or engine output) on the basis of the amount of lube oil supply calculated as a function of the opening of the electromagnetic valves and engine load calculated from the detected engine rotation speed and amount of fuel input, and controls the opening period of said electromagnetic valves so that said calculated lube oil injection ratio coincides with a lube oil injection ratio determined beforehand.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein a specific gravimeter is provided to said common lube oil feeding section, and said controller controls said electromagnetic valves so that the opening period thereof coincides with a value predetermined in correspondence with the value of specific gravity of lube oil inputted beforehand in the controller from said specific gravimeter or the value of actual specific gravity detected by said specific gravimeter.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein said controller controls said electromagnetic valves so that the opening timing and period thereof coincides with values predetermined in correspondence with the value of viscosity of lube oil inputted beforehand in the controller from a viscosity meter attached to the common lube oil feeding section or the value of actual viscosity detected by said specific gravimeter.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein a pressure detector or a temperature detector is provided to said common lube oil feeding section, and said controller controls said electromagnetic valves so that the opening period thereof coincides with periods predetermined in correspondence with the pressure or temperature of lube oil in the common lube oil feeding section detected by and inputted from said pressure detector or temperature detector.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein said controller controls said electromagnetic valves so that the opening period thereof coincides with periods predetermined in correspondence with the lift thereof which is predetermined or measured.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein said controller controls said electromagnetic valves in correspondence with the predetermined or measured value of the air gap of said electromagnetic valve.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein a plurality of lubricators are provided per cylinder, each of said oil passages is connected to each of said lubricators, and each of said electromagnetic valves is provided to each of said oil passages.
- The internal combustion engine provided with a lubricating system according to claim 11, wherein a plurality of lubricators are provided per cylinder, lube oil passages consist of a main passage and branch passages branching from said main passage and connecting to each of said lubricators respectively, said electromagnetic valve is provided to the main oil passage, and a single electromagnetic valve presides lube oil supply to a plurality of lubricators.
- The internal combustion engine provided with a lubricating system according to claim 12, wherein the branched passages branching from each of the main passages are connected to lubricators located alternately along the periphery of cylinder, whereby even if one of the electromagnetic valves malfunctions lube oil can be supplied to the lubricators provided all around the periphery of cylinder excepting the lubricators connected to the malfunctioned electromagnetic valves.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein a plurality of lubricators are provided per cylinder and a plurality of controllers are provided to control one or a plurality of said electromagnetic valves.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein a pressure regulating valve is provided to an end part of the common lube oil feeding section, and the temperature of the lube oil in the common lube oil feeding section is maintained at uniform temperature by pressure- feeding lube oil of more than the lube oil supplied to engine lubrication by use of the lubricating oil pump and allowing lube oil to circulate through the common lube oil feeding section.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein a return pipe is provided along the common lube oil feeding section, and heat exchange is possible between the lube oil in the common lube oil feeding section and that in the return pipe.
- The internal combustion engine provided with a lubricating system according to claim 1, wherein the opening area of each of the electromagnetic valves is larger than the sum of the passage area of the lubricators connected to the concerned electromagnetic valve.
- A method of supplying lube oil to cylinders in a system in which the lube oil pressure-fed by a lube oil pump is supplied to lubricators attached to a cylinder through electromagnetic valves for adjusting the timing and amount of lube oil supply and oil passages to feed the lube oil to the inner surface of a cylinder in which a piston having a plurality of piston rings reciprocates, wherein lube oil is injected from the lubricators to spaces formed between the piston rings at least once per one reciprocation of piston.
- The method of supplying lube oil to cylinders according to claim 18, wherein a first lube oil injection is done when the piston is traveling upward and is at a positioned lower than the lubricator (s) and then a second lube oil injection is done to the spaces between the piston rings in the process of upward traveling of the piston.
- The method of supplying lube oil to cylinders according to claim 18, wherein a first lube oil injection is done when the piston is traveling downward and is at a positioned upper than the lubricator (s) and then a second lube oil injection is done to the spaces between the piston rings in the process of downward traveling of the piston.
- The method of supplying lube oil to cylinders according to claim 18, wherein the lubricators are attached to the cylinder such that the injection hole of each of the lubricator directs toward directions circumferential to the inner surface of cylinder so that lube oil is allowed to be injected from the lubricators in directions circumferential to the inner surface of cylinder.
- The method of supplying lube oil to cylinders according to claim 18, wherein the lubricators are arranged in a plurality of rows along the periphery of a cylinder, and lubricators belonging to at least one row are attached to the cylinder such that the injection hole of each of the lubricator directs toward directions circumferential to the inner surface of cylinder so that lube oil is allowed to be injected from the lubricators in directions circumferential to the inner surface of cylinder.
- A cylinder lubricating system in which the lube oil pressure -fed by a lube oil pump is supplied to lubricators attached to a cylinder through electromagnetic valves for adjusting the timing and amount of lube oil supply and oil passages to feed the lube oil to the inner surface of a cylinder in which a piston having a plurality of piston rings reciprocates, wherein are provided a crank angle sensor for detecting engine crank angle, rotation speed detector for detecting engine rotation speed, a load detector for detecting engine load, and a controller for controlling the electromagnetic valves so that lube oil is injected from the lubricators to spaces formed between piston rings at least once per one reciprocation of piston on the basis of the values detected by the crank angle sensor, rotation speed detector, and load detector.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004108158A JP3897770B2 (en) | 2004-03-31 | 2004-03-31 | Internal combustion engine with cylinder lubrication device |
| JP2004108158 | 2004-03-31 | ||
| JP2005054678 | 2005-02-28 | ||
| JP2005054678A JP4402609B2 (en) | 2005-02-28 | 2005-02-28 | Cylinder lubrication device |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| EP1582706A2 true EP1582706A2 (en) | 2005-10-05 |
| EP1582706A3 EP1582706A3 (en) | 2005-11-09 |
| EP1582706B1 EP1582706B1 (en) | 2008-07-16 |
Family
ID=34889462
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP05006988A Not-in-force EP1582706B1 (en) | 2004-03-31 | 2005-03-31 | Internal combustion engine with cylinder lubricating system |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP1582706B1 (en) |
| KR (2) | KR100750542B1 (en) |
| CN (2) | CN1676888B (en) |
| DE (1) | DE602005008126D1 (en) |
| DK (1) | DK1582706T3 (en) |
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| EP2177720A1 (en) * | 2008-10-16 | 2010-04-21 | Wärtsilä Schweiz AG | Large diesel engine |
| EP2395208A1 (en) | 2010-06-11 | 2011-12-14 | Wärtsilä Schweiz AG | Large motor with a cylinder lubrication device and method for lubricating a cylinder of a large motor |
| RU2457339C2 (en) * | 2007-05-18 | 2012-07-27 | Ханс Йенсен Лубрикаторс А/С | Lubricator and method of dispensing cylinder oil |
| JP2012163098A (en) * | 2011-02-04 | 2012-08-30 | Waertsilae Schweiz Ag | Cylinder lubrication device |
| WO2012126473A3 (en) * | 2011-03-18 | 2012-11-08 | Hans Jensen Lubricators A/S | Dosing of cylinder lubricating oil into large cylinders |
| EP2677129A1 (en) * | 2009-06-23 | 2013-12-25 | Hans Jensen Lubricators A/S | Lubrication of cylinders of large diesel engines, such as marine engines |
| KR20140071488A (en) * | 2011-10-12 | 2014-06-11 | 가부시키가이샤 아이에이치아이 | Two-cycle engine and method for lubricating two-cycle engine |
| WO2015144182A1 (en) * | 2014-03-25 | 2015-10-01 | Hans Jensen Lubricators A/S | Method and system for dosing lubrication oil into cylinders |
| EP3130771A1 (en) * | 2015-08-13 | 2017-02-15 | Winterthur Gas & Diesel AG | Lubricator for a cylinder liner, lubrication method, and cylinder liner |
| DK201670585A1 (en) * | 2016-08-05 | 2018-01-15 | Hans Jensen Lubricators As | Safety system for lubrication of the cylinder of a large slow-running internal combustion engine and a large slow-running two-stroke internal combustion engine |
| CN111156093A (en) * | 2019-12-31 | 2020-05-15 | 潍柴动力股份有限公司 | Control method and device for diesel-alcohol dual-fuel engine |
| WO2021213603A1 (en) * | 2020-04-22 | 2021-10-28 | Hans Jensen Lubricators A/S | Method for lubricating large slow-running marine diesel engines |
| CN115443371B (en) * | 2020-04-22 | 2024-05-17 | 汉斯延森注油器公司 | Method for lubricating large low-speed marine diesel engine |
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| CN102322309A (en) * | 2011-09-27 | 2012-01-18 | 上海北星实业有限公司 | Method and device for lubricating crank shaft on engine |
| US9004039B2 (en) * | 2012-10-23 | 2015-04-14 | GM Global Technology Operations LLC | Cylinder lubrication system |
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| JP6973187B2 (en) * | 2018-03-06 | 2021-11-24 | トヨタ自動車株式会社 | Fuel injection timing control device for internal combustion engine |
| CN108343830A (en) * | 2018-03-31 | 2018-07-31 | 上汽通用五菱汽车股份有限公司 | Engine cylinder hole lubricating arrangement |
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| EP0049603A2 (en) * | 1980-10-04 | 1982-04-14 | The British Petroleum Company p.l.c. | Lubrication system |
| EP0509189A1 (en) * | 1991-04-18 | 1992-10-21 | Mitsubishi Jukogyo Kabushiki Kaisha | Multicylinder engine |
| DE19743955A1 (en) * | 1996-10-11 | 1998-04-16 | Man B & W Diesel Gmbh | Cylinder lubricator in IC engine |
| US6547038B1 (en) * | 1998-11-05 | 2003-04-15 | Hans Jensen Lubricators A/S | Lubrication system for large diesel engines |
| US20040026174A1 (en) * | 2000-10-24 | 2004-02-12 | Sven Lauritsen | Dosing system |
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| DK171974B1 (en) * | 1988-11-01 | 1997-09-01 | Mitsubishi Heavy Ind Ltd | Lubricator for a cylinder in an internal combustion engine |
| JPH02135612U (en) * | 1989-04-14 | 1990-11-13 | ||
| DK173533B1 (en) | 1999-01-18 | 2001-02-05 | Man B & W Diesel As | Method of lubricating a cylinder in an internal combustion engine as well as cylinder lubrication system and connecting element |
| DE19959300A1 (en) | 1999-12-09 | 2001-06-21 | Man B & W Diesel As Kopenhagen | Engine has lubricant ejection devices of constant capacity and frequency of ejection processes is varied to vary quantity of lubricant delivered to cylinder surface |
| DE19959309A1 (en) | 1999-12-09 | 2001-06-21 | Man B & W Diesel As Kopenhagen | Engine has switching valves next to lubricant outlets with which supply lines can be blocked or opened at times determined by controller from lubricant demand derived from measurements |
| JP3806398B2 (en) * | 2002-11-28 | 2006-08-09 | 三菱重工業株式会社 | Cylinder lubrication device |
| JP3897770B2 (en) | 2004-03-31 | 2007-03-28 | 三菱重工業株式会社 | Internal combustion engine with cylinder lubrication device |
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2005
- 2005-03-31 DE DE602005008126T patent/DE602005008126D1/en active Active
- 2005-03-31 CN CN2005100716192A patent/CN1676888B/en not_active Expired - Fee Related
- 2005-03-31 DK DK05006988T patent/DK1582706T3/en active
- 2005-03-31 KR KR1020050027386A patent/KR100750542B1/en active IP Right Grant
- 2005-03-31 EP EP05006988A patent/EP1582706B1/en not_active Not-in-force
- 2005-03-31 CN CNB2007101063953A patent/CN100549369C/en not_active Expired - Fee Related
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2007
- 2007-03-23 KR KR1020070028621A patent/KR20070041697A/en active Search and Examination
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0049603A2 (en) * | 1980-10-04 | 1982-04-14 | The British Petroleum Company p.l.c. | Lubrication system |
| EP0509189A1 (en) * | 1991-04-18 | 1992-10-21 | Mitsubishi Jukogyo Kabushiki Kaisha | Multicylinder engine |
| DE19743955A1 (en) * | 1996-10-11 | 1998-04-16 | Man B & W Diesel Gmbh | Cylinder lubricator in IC engine |
| US6547038B1 (en) * | 1998-11-05 | 2003-04-15 | Hans Jensen Lubricators A/S | Lubrication system for large diesel engines |
| US20040026174A1 (en) * | 2000-10-24 | 2004-02-12 | Sven Lauritsen | Dosing system |
Cited By (27)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2457339C2 (en) * | 2007-05-18 | 2012-07-27 | Ханс Йенсен Лубрикаторс А/С | Lubricator and method of dispensing cylinder oil |
| EP2177720A1 (en) * | 2008-10-16 | 2010-04-21 | Wärtsilä Schweiz AG | Large diesel engine |
| US8813714B2 (en) | 2009-06-23 | 2014-08-26 | Hans Jensen Lubricators A/S | Lubrication of cylinders of large diesel engines, such as marine engines |
| EP2677129A1 (en) * | 2009-06-23 | 2013-12-25 | Hans Jensen Lubricators A/S | Lubrication of cylinders of large diesel engines, such as marine engines |
| EP2395208A1 (en) | 2010-06-11 | 2011-12-14 | Wärtsilä Schweiz AG | Large motor with a cylinder lubrication device and method for lubricating a cylinder of a large motor |
| JP2012163098A (en) * | 2011-02-04 | 2012-08-30 | Waertsilae Schweiz Ag | Cylinder lubrication device |
| EP3434872A1 (en) * | 2011-03-18 | 2019-01-30 | Hans Jensen Lubricators A/S | Dosing of cylinder lubricating oil into large cylinders |
| CN103939174A (en) * | 2011-03-18 | 2014-07-23 | 汉斯延森注油器公司 | System and method for dosing cylinder lubrication oil into large diesel engine cylinders |
| CN103939174B (en) * | 2011-03-18 | 2017-04-12 | 汉斯延森注油器公司 | System and method for dosing cylinder lubrication oil into large diesel engine cylinders |
| RU2638142C2 (en) * | 2011-03-18 | 2017-12-11 | Ханс Йенсен Лубрикейторс А/С | System and method of lubricating oil metering for cylinders to cylinders of large diesel engines |
| WO2012126473A3 (en) * | 2011-03-18 | 2012-11-08 | Hans Jensen Lubricators A/S | Dosing of cylinder lubricating oil into large cylinders |
| EP2722500A3 (en) * | 2011-03-18 | 2017-02-15 | Hans Jensen Lubricators A/S | System and method for dosing cylinder lubrication oil into large diesel engine cylinders |
| KR20140071488A (en) * | 2011-10-12 | 2014-06-11 | 가부시키가이샤 아이에이치아이 | Two-cycle engine and method for lubricating two-cycle engine |
| KR101865407B1 (en) * | 2011-10-12 | 2018-06-07 | 가부시키가이샤 아이에이치아이 | Two-cycle engine and method for lubricating two-cycle engine |
| EP2961951B1 (en) | 2014-03-25 | 2016-11-30 | Hans Jensen Lubricators A/S | Method and system for dosing lubrication oil into cylinders |
| KR20160134846A (en) * | 2014-03-25 | 2016-11-23 | 한스 옌젠 루브리케이터스 에이/에스 | Method and system for dosing lubricating oil into cylinders |
| EP2961951A4 (en) * | 2014-03-25 | 2016-02-24 | Hans Jensen Lubricators As | Method and system for dosing lubrication oil into cylinders |
| WO2015144182A1 (en) * | 2014-03-25 | 2015-10-01 | Hans Jensen Lubricators A/S | Method and system for dosing lubrication oil into cylinders |
| EP2961951B2 (en) † | 2014-03-25 | 2019-10-23 | Hans Jensen Lubricators A/S | Method and system for dosing lubrication oil into cylinders |
| KR102216353B1 (en) | 2014-03-25 | 2021-02-17 | 한스 옌젠 루브리케이터스 에이/에스 | Method and system for dosing lubricating oil into cylinders |
| EP3130771A1 (en) * | 2015-08-13 | 2017-02-15 | Winterthur Gas & Diesel AG | Lubricator for a cylinder liner, lubrication method, and cylinder liner |
| DK201670585A1 (en) * | 2016-08-05 | 2018-01-15 | Hans Jensen Lubricators As | Safety system for lubrication of the cylinder of a large slow-running internal combustion engine and a large slow-running two-stroke internal combustion engine |
| DK179182B1 (en) * | 2016-08-05 | 2018-01-15 | Hans Jensen Lubricators As | Safety system for lubrication of the cylinder of a large slow-running internal combustion engine and a large slow-running two-stroke internal combustion engine |
| CN111156093A (en) * | 2019-12-31 | 2020-05-15 | 潍柴动力股份有限公司 | Control method and device for diesel-alcohol dual-fuel engine |
| WO2021213603A1 (en) * | 2020-04-22 | 2021-10-28 | Hans Jensen Lubricators A/S | Method for lubricating large slow-running marine diesel engines |
| CN115443371A (en) * | 2020-04-22 | 2022-12-06 | 汉斯延森注油器公司 | Method for lubricating large low-speed marine diesel engine |
| CN115443371B (en) * | 2020-04-22 | 2024-05-17 | 汉斯延森注油器公司 | Method for lubricating large low-speed marine diesel engine |
Also Published As
| Publication number | Publication date |
|---|---|
| DK1582706T3 (en) | 2008-09-29 |
| EP1582706B1 (en) | 2008-07-16 |
| DE602005008126D1 (en) | 2008-08-28 |
| CN1676888A (en) | 2005-10-05 |
| CN101054913A (en) | 2007-10-17 |
| KR20060045405A (en) | 2006-05-17 |
| EP1582706A3 (en) | 2005-11-09 |
| CN1676888B (en) | 2010-09-01 |
| KR100750542B1 (en) | 2007-08-20 |
| KR20070041697A (en) | 2007-04-19 |
| CN100549369C (en) | 2009-10-14 |
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