Internal combustion engine

An internal combustion engine comprises a cylinder, a piston reciprocating in the cylinder, piston rings arranged on the periphery of the piston, and at least a pair of oil ports symmetrically provided in a wall member of the cylinder. The oil ports communicate with the space between the wall member and the piston and are positioned to open onto the portion below the lowermost piston ring during the reciprocation of the piston. A system supplies a portion of the lubricating oil for the internal combustion engine under pressure to this space through the oil ports, and conduits communicate the oil ports with the supply system.

BACKGROUND OF THE INVENTION 
The present invention relates to the improvement of an internal combustion 
engine which is powered by converting the reciprocating motion of a piston 
to rotating motion. 
In such type of an internal combustion engine with the reciprocating piston 
there is generally provided a predetermined piston clearance between the 
piston and the inner wall of the cylinder. Because thermal expansion of 
the piston, which is especially made of aluminum alloy, is greater than 
the cylinder, it is necessary to provide a large piston clearance. 
Therefore, the piston swings about the piston pin within the piston 
clearance when the moving direction of the piston is reversed at the 
stroke ends. This means that the periphery of the piston strikes the inner 
wall of the cylinder to make a slapping noise. 
SUMMARY OF THE INVENTION 
An object of the present invention is to provide an improved reciprocating 
engine in which piston slapping may be prevented to abate the noise, and 
in which, wear of the piston and cylinder may be decreased, and which has 
the effect of cooling the piston. 
According to the invention improved internal combustion engine comprises a 
cylinder, a piston reciprocating in the cylinder, piston rings arranged on 
the periphery of the piston, and at least a pair of oil ports 
symmetrically provided in a wall member of the cylinder. The oil ports 
communicate with the space between the wall member and the piston and are 
positioned to open into the portion below the lowermost piston ring during 
the reciprocation of the piston when the piston is at the bottom dead 
center and positioned to open onto a lower end portion of the piston skirt 
when the piston is at the top dead center. A system supplies a portion of 
the lubricating oil for the internal combustion engine under pressure to 
this space through the oil ports, and conduits communicate the oil ports 
with the supply system. 
In such an engine, the lubricating oil tends to enter the combustion 
chamber passing over the oil ring, because excessive oil is supplied under 
pressure. Therefore, it is a further object of the present invention to 
provide an improved internal combustion engine which may prevent the 
lubricating oil from entering into the combustion chamber and in which the 
returning of the excess oil is certainly effected to reduce the 
consumption of lubricating oil. To this end, an oil return hole passing 
through the piston is additionally provided between the oil ring and gas 
ring, whereby the lubricating oil which enters between the oil ring and 
the gas ring, without remaining therein, is sent back to the crank case. 
Further features and advantages of the present invention will be apparent 
from the ensuing description of preferred embodiments given merely by way 
of example with reference to the accompanying drawings.

DESCRIPTION OF THE PREFERRED EMBODIMENT 
FIGS. 1 and 2 show an embodiment in which the present invention is applied 
to a diesel engine. In the drawings, there are cooperatively provided a 
cylinder block 1, a cylinder head 2, a cylinder 3, and a piston 4 slidably 
engaged in the cylinder 3. Formed in the upper portion of the cylinder 3 
is a combustion chamber 7 provided with an intake or exhaust valve 5 and a 
fuel injection nozzle 6. Piston rings 8 comprising gas rings 8a and an oil 
ring 8b are engaged in annular grooves provided in the periphery of the 
piston 4, so that the piston 4 slidably reciprocates in the cylinder 3 
keeping airtight engagement with the cylinder. 
In accordance with the present invention, a pair of diametrically opposite 
oil ports 10 are provided in the cylinder 3. Each oil port is so arranged 
that the oil ports open upon the peripheral surface of the piston below 
the piston ring 8b during the reciprocation of the piston. The lubrication 
oil ports 10 communicate with an annular oil groove 12 which is provided 
on the crank case 11 at the portion joined to the cylinder block 1 and the 
oil groove 12 in turn communicates with the discharge port of an oil pump 
16 through an oil passage 13 as shown in the dotted line in FIG. 1. The 
oil pump 16 consists of a plunger 18 slidably provided in a pump chamber 
17 which is formed in the crank case 11 and a coil spring 19 set in the 
pump chamber 17 so as to urge the plunger 18 against a pump driving cam 21 
provided on a cam shaft 20 which is rotated in synchronism with the crank 
shaft (not shown) of the engine. A check valve 23 loaded by a spring 22 is 
provided on each of the intake and discharge ports of the oil pump 16 
respectively (the intake port check valve being not shown). The intake 
port of the oil pump 16 is communicated through an intake tube 24 and an 
oil strainer 25 to an oil tank 26 provided in the bottom of crank case 11. 
In the embodiment shown in the drawings although at least two oil ports 10 
are provided in the peripheral wall portion of the cylinder 3, the number 
of the ports may be varied. 
As shown in FIGS. 1 and 3, a first oil return hole 14 is provided at the 
bottom of the annular groove of the oil ring 8b communicating with the 
interior of the piston 4 and a second oil return hole 15 is provided 
between the oil ring 8b and the lowermost gas ring 8a communicating with 
the interior of the piston. The first and second oil return holes 14, 15 
may be provided in the piston 4 circumferentially at one or more 
positions. 
Further, as shown in FIGS. 3 and 4, there is provided a pair of oil guide 
grooves 27 on the periphery of the piston skirt 4a extending in the axial 
direction and communicating with the oil ports 10 respectively. 
In operation, the plunger 18 is operated in reciprocal motion in the pump 
chamber 17 by the function of the coil spring 19 and protrusion 21a of the 
cam 21 to effect an oil pumping operation in synchronism with the crank 
shaft, so that lubricating oil is fed through the oil groove 13 and 
injected into the space (piston clearance) from the oil ports 10 when the 
piston 4 is in the bottom dead center. The lubricating oil which is 
injected into the clearance flows in the grooves 27 and overflows to 
spread in the piston clearance to form a relatively thick oil film. 
Therefore inclination caused by the change of direction of the piston 
motion can be limited. 
While the piston moves toward the top dead center, lubricating oil is 
injected to the oil guide grooves 27 the same as when the piston is in the 
bottom dead center, and diffused over the relatively wide area. 
Further, when the piston is in the top dead center, the injected oil forms 
a relatively thick high pressure oil film over a wide area of the piston 
clearance, as it does at the bottom dead center. Thus, inclination of the 
piston at the change of direction at the top dead center can be prevented 
to reduce the slapping sound of the piston 4. 
The lubricating oil which is injected from the oil port 10 is prevented 
from directly entering into the combustion chamber, because each oil port 
10 is arranged in the position outside of the sliding area of the piston 
rings 8. 
Oil injected in the piston clearance is scratched off by the effect of oil 
ring 8b into the crank case 11 below, and oil entering into the groove of 
the oil ring 8b is returned back to the crank case through the first oil 
return hole 14. However, since the provision of the oil return hole 14 is 
not enough to scratch off a great deal of oil, it may still arise that a 
portion of oil may pass rising over the oil ring 8b and remain in the 
space between the wall of cylinder and the land formed between the oil 
ring 8b and the gas ring 8a. Therefore, this invention provides a second 
oil return hole 15 to send the oil in the space between the cylinder wall 
and the land rapidly back into the crank case 11 without remaining in the 
space and entering into the combustion chamber. 
FIG. 5 shows a part of the cylinder 1 having a cylinder liner 30. In such 
an engine, the oil port 10 is provided in the liner 30 and the annular oil 
groove 12 is formed in the cylinder wall outside of the liner. 
FIG. 6 shows a modification of piston 8. On the periphery of the piston, a 
pair of annular oil spreading grooves 31 are provided to communicate with 
the guide groove 27. In accordance with the grooves 31, lubricating oil 
may widely spread in the piston clearance. The number and direction, and 
the sectional shape of the oil spreading grooves 31 may be suitably 
selected. FIGS. 7 to 13 show different examples of the oil spreading 
grooves, although the invention is not limited thereto. 
Thus, in accordance with the present invention, a portion of lubricating 
oil is injected into the space between the piston and the wall of the 
cylinder, whereby the swing of the piston at the change of direction 
positions can be prevented by the injected lubricating oil, thereby 
minimizing the noise caused by piston slapping. Further, because a great 
deal of lubricating oil is injected into the space between the piston and 
the wall of cylinder, advantages, such as minimum wear, improved 
durability as well as the high cooling efficiency of the members may be 
obtained. 
While I have disclosed several embodiments of the invention it is to be 
understood that these embodiments are given by example only and not in a 
limiting sense.