JP3108903B2 - Piston engine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a piston engine, and more particularly, to a piston engine capable of increasing the output without changing the height and the physique of the engine body.

[0002]

2. Description of the Related Art In recent years, in order to increase the output of a piston engine (hereinafter simply referred to as an engine) by increasing the displacement, a cylinder having a larger cylinder bore and a longer cylinder is required. However, there is a problem that simply increasing the cylinder bore increases the overall length of the engine body in the front-rear direction in a multi-cylinder engine, and simply increasing the cylinder length increases the height of the engine body in a vertical engine.

[0003] In order to solve the above problems, the present applicant has previously developed an engine shown in FIG. 2 (hereinafter referred to as a prior invention example). This prior invention example is a cylinder block 1
The cylinder 2 and the crankcase 5 are integrally formed. A piston 10 is provided in the cylinder 2 so as to be reciprocally slidable. The crankshaft 7 provided in the crankcase 5 and the piston 10 are connected by a connecting rod 15. , The cylinder 2
End 2A of the cylinder 2 protrudes toward the crank chamber 6 side, and avoids interference with the connecting rod large end 16 at the left and right neighboring portions 2a, 2a of the one end 2A of the cylinder 2 where the connecting rod large end 16 approaches. A pair of left and right cutout recesses 3 are formed.

[0004] The prior invention is directed to an end portion 2A of a cylinder 2.
Is protruding toward the crank chamber 6 side, the one end 2
A pair of left and right cutout recesses 3 formed in A avoids interference between the one end 2A and the connecting rod large end 16.
The one-end portion 2A of the cylinder 2 protrudes toward the crank chamber 6 to increase the cylinder length, thereby increasing the displacement, thereby increasing the output of the engine.

However, since the ridge portions 4a at both ends of the cutout recesses 3 are in sliding contact with the outer surfaces of the left and right skirt portions 13 receiving the side pressure of the piston 10, the left and right skirt portions 13 Deep scratches occur on the outer surface. In addition, metal powder is interposed between the piston and the cylinder with this, and this metal powder causes wear of the piston ring, the piston, and the cylinder, and deteriorates the gas sealing property of the piston ring, and in the worst case, It causes various adverse effects such as burning of the engine.

[0006]

SUMMARY OF THE INVENTION The present invention has been made to solve the problems of the prior art and the above-mentioned prior art example at the same time, and it is possible to increase the output of the engine without changing the height and the physique of the engine body. It is an object of the present invention to prevent the scratches from being generated on the outer surface of the skirt portion of the piston.

[0007]

The present invention is configured as follows to solve the above-mentioned problems. That is, the cylinder 2 and the crankcase 5 are integrally formed in the cylinder block 1, and the piston 10 is provided in the cylinder 2 so as to be reciprocally slidable, and the crankshaft 7 pivotally supported in the crankcase 5 and the piston 10 Are connected by a connecting rod 15, one end 2 A of the cylinder 2 is protruded toward the crank chamber 6, and the large right end 16 a of the connecting rod of the one end 2 A of the cylinder 2 approaches the right and left neighboring portions 2 a.・ In 2a, the connecting rod large end 16
And a pair of left and right skirt portions 13 of the piston 10 are formed.
Oil grooves 14 are formed on the outer surface of each of the notch concave portions 3 and 3 at opposite ends of the notch ridge portions 4a and 4a, respectively. The oil grooves 14 are parallel to the cylinder axis.

[0008]

According to the present invention, even if one end 2A of the cylinder 2 is protruded toward the crank chamber 6, the one end 2A of the cylinder 2 is provided.
A pair of left and right cutout recesses 3 formed in the one end 2
Since the interference between A and the large end portion 16 of the connecting rod is avoided, the exhaust amount is increased by an amount corresponding to the increase in the cylinder length by protruding the one end 2A of the cylinder 2 toward the crank chamber 6 side. Also, the left and right skirt portions 13.1, which receive the lateral pressure of the piston 10,
3 are formed on the outer surface of the skirt portion 13 and the ridge portions 4a at both ends of the cutout recess 3.
Lubricating the sliding surface of the piston 10 while avoiding sliding contact with 4a.

[0009]

According to the present invention, the following effects can be obtained. A pair of left and right cut-out recesses are formed at one end of the cylinder to avoid interference between the one end and the large end of the connecting rod, so that one end of the cylinder protrudes toward the crank chamber side to increase the cylinder length. It becomes possible to do. Thus, the displacement can be increased without changing the height and the physique of the engine body, and the output of the engine can be increased. Oil grooves parallel to the cylinder axis are formed on the outer surfaces of the left and right skirt portions that receive the side pressure of the piston so that the outer surfaces of the skirt portions do not slide on the ridge portions at both ends of the cutout recess. Therefore, it is possible to improve the slidability of the piston 10 while preventing the scratch on the outer surface of the skirt portion of the piston.

[0010]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows an embodiment of the present invention. FIG. 1 (A) is a vertical sectional front view of a main part of a vertical diesel engine, and FIG. 1 (B) is a vertical sectional side view of a main part of the engine.

Cylinder block 1 of this vertical engine
As shown in FIGS. 1 (A) and 1 (B), a plurality of cylinders 2 are arranged in front and rear, and adjacent cylinders 2 are connected to a continuous wall portion 21.
To form a siamese cylinder, and the crankcase 5 is also integrally formed. A piston 10 is provided in each of the cylinders 2 so as to be slidable back and forth,
A crankshaft 6 is pivotally supported in the crankcase 5, and the crankpin 8 of the crankshaft 7 and the piston 10 are connected by a connecting rod 15. Reference numeral 9 in FIG.
Reference numeral 0 denotes a cylinder jacket formed so as to surround the outer periphery of the siamese cylinder, and reference numeral 24 denotes a flow path forming member cast into the continuous wall portion 21 for flowing cooling water.

Hereinafter, the characteristic configuration of the apparatus of this embodiment will be described. Each of the cylinders 2 is set so that its lower end 2A protrudes toward the crank chamber 6 to increase the cylinder length, and that the movement stroke of the piston 10 is increased by the length of the cylinder length. That is,
In this embodiment, the crank radius R of the crankshaft 7 is increased by the length of the cylinder, and the connecting rod 15 is shortened by the length of the crank radius R to increase the movement stroke of the piston 10. It is configured such that the displacement is increased as a whole.

A pair of left and right cut-out recesses 3 for avoiding interference with the connecting rod large end 16 are formed in the left and right neighboring parts 2a of the lower end 2A of the cylinder 2 where the connecting rod large end 16 approaches. Have been. That is, cylinder 2
By forming the notched recesses 3 in the lower end 2A, the lower end 2A of the cylinder 2 can protrude toward the crank chamber 6 to increase the cylinder length.

On the outer surfaces of the left and right skirt portions 13 receiving the lateral pressure of the piston 10, the notch recesses 3 are formed.
At the opposite ends of each notch ridge line portion 4a
Oil grooves 14 are formed parallel to the cylinder axis. Each of the oil grooves 14 prevents sliding contact between the outer surface of the skirt portion 13 and each of the ridge portions 4a at both ends of the cutout recess 3, and scratches occur on the outer surface of the skirt portion 13 of the piston 10. To prevent In this embodiment, the lower end of each oil groove 14 is formed to the lower edge of the skirt portion 13, and the lubricating oil scraped down by the lower rings 11b and 11c flows down the oil grooves 14 and 14. Thus, the sliding surface of the skirt portion 13 is lubricated to improve the slidability of the piston 10.

A large amount of cooling water for the cylinder jacket 20 is circulated through the flow path forming member 24 cast into the continuous wall portion 21 so that the continuous wall portion 21 can be strongly cooled. Thereby, the thickness of the continuous wall portion 21 can be reduced, and the cylinder bore can be set larger by the reduced thickness. Therefore, in combination with the increase in the cylinder length, the engine displacement can be further increased and the output can be increased without changing the height and the physique of the engine body.

Further, the head-side portion 2 of the continuous wall portion 21
By strongly cooling the piston ring 2, the piston rings 11 a to 11 c can be strongly cooled via the head side portion 22. Thereby, the top ring 11a can be brought as close as possible to the top surface of the piston, and a ring-shaped dead space that does not contribute to the combustion on the outer periphery of the piston top portion can be minimized to improve the air utilization rate. In addition, the sticking of the top ring 11a due to the carbonization of the unburned portion of the fuel can be eliminated.

Further, as the top ring 11a is brought as close as possible to the top surface of the piston, the position of the piston pin 12 is brought as close as possible to the top surface of the piston. The radius R) can be increased, the size of the engine can be relatively reduced without changing the physical size of the engine, the piston stroke can be further increased, and the displacement can be increased. Furthermore, by applying the present invention to a multi-cylinder engine or the like equipped with a turbocharger, it is possible to reduce the size of the engine and increase the output.

FIGS. 3 to 14 are front views showing the pistons according to the second to thirteenth embodiments, respectively, partially cut away, and each will be briefly described below. In the second embodiment (FIG. 3), the upper ends of the oil grooves 14 formed on the outer surface of the skirt 13 extend to the lower edge of the lower ring groove 12. Thereby, the lower ring 11b
The lubricating oil scraped down in 11c is
To lubricate the sliding surface of the skirt portion 13. Also,
At the position of the lower edge boundary line of the lower ring groove 12,
The lubricating oil scattered from the crank chamber 6 side to the inside of the piston (to the piston pin 12) flows out through the through oil hole 18 into the lower ring groove 12, and passes through the lower ring 11c. Lubricate the sliding surface. This through oil hole 18
Is similarly formed for the piston of FIG. 3, reference numeral 19 denotes a pin hole for inserting the piston pin 12, and 19a denotes a ring groove of a ring for preventing the piston pin 12 from being removed.

In the third embodiment (FIG. 4), each oil groove 14.1
4 intersect above the skirt 13, and the upper end thereof extends to the lower edge of the lower ring groove 12. Other points are the same as those of the second embodiment (FIG. 3). In the fourth embodiment (FIG. 5), in addition to the oil grooves 14
A plurality of oil grooves 14b, 14b are separately provided in the upper half part of the first embodiment, and the other points are the same as those of the first embodiment (FIG. 1).

In the fifth embodiment (FIG. 6), a plurality of oil grooves 14
b and 14b communicate with the lower ends of the oil grooves 4b and 14b near the center of the skirt portion 13, and are otherwise the same as in the fourth embodiment (FIG. 5). Sixth
In the embodiment (FIG. 7), each oil groove 14 intersects above the skirt portion 13 and the upper end portion is a boss cut step portion 12c.
The lubricating oil that has been extended down to the lower side and collected by the boss cut step 12c is collected and flows down into the oil grooves 14. Other points are the same as those of the third embodiment (FIG. 4).

In the seventh embodiment (FIG. 8), each oil groove 14.1
No. 4 does not intersect, and its upper end is extended below the boss cut step 12c. The other points are the same as in the sixth embodiment (FIG. 7). In the eighth embodiment (FIG. 9), the upper ends of the oil grooves 14
And a through oil hole 18b is formed at the junction. The lubricating oil flowing out through the through oil holes 18b flows down the oil grooves 14 and lubricates the sliding surface of the skirt portion 13. Other points are the same as those of the third embodiment (FIG. 4).

In the ninth embodiment (FIG. 10), each oil groove 14
14 crosses over the skirt portion 13 and extends at the upper end to the lower side of the lower ring groove 12, and a through oil hole 18b is formed at each of the intersection and the upper end. Other points are the same as those of the third embodiment (FIG. 4). First
Example 0 (FIG. 11), Example 11 (FIG. 12) and Example 1
In each of the two embodiments (FIG. 13), a through oil hole 18 is formed at a substantially central portion of each of the lower ring grooves 12 in order to facilitate drilling. Other points are the second embodiment (FIG. 3), the third embodiment (FIG. 4), and the fifth embodiment (FIG. 6), respectively.
It is configured similarly to.

In the thirteenth embodiment (FIG. 14), each of the oil grooves 14 is formed in a U-shape in the upper half of the skirt portion 13, and the upper end thereof is located below the lower ring groove 12. Has been extended to Other points are the same as those in the tenth embodiment (FIG. 1).
It has the same configuration as 1). In the above embodiment,
Although the vertical diesel engine has been exemplified, the present invention can be similarly applied to a horizontal diesel engine and a spark ignition type engine.

[Brief description of the drawings]

1A and 1B show an embodiment of the present invention, in which FIG. 1A is a longitudinal sectional front view of an essential part of a vertical diesel engine, and FIG. 1B is a longitudinal sectional side view of an essential part of the engine.

FIG. 2 shows an example of the prior invention, wherein FIG. 2A is a vertical sectional front view of a main part of a vertical diesel engine, and FIG. 2B is a vertical sectional side view of a main part of the engine.

FIG. 3 is a front view showing a piston according to a second embodiment, partially broken away.

FIG. 4 is a diagram corresponding to FIG. 3 according to a third embodiment.

FIG. 5 is a diagram corresponding to FIG. 3 according to a fourth embodiment.

FIG. 6 is a diagram corresponding to FIG. 3 according to a fifth embodiment.

FIG. 7 is a diagram corresponding to FIG. 3 according to a sixth embodiment.

FIG. 8 is a diagram corresponding to FIG. 3 according to a seventh embodiment.

FIG. 9 is a diagram corresponding to FIG. 3 according to an eighth embodiment.

FIG. 10 is a diagram corresponding to FIG. 3 according to a ninth embodiment.

FIG. 11 is a diagram corresponding to FIG. 3 according to a tenth embodiment.

FIG. 12 is a diagram corresponding to FIG. 3 according to an eleventh embodiment.

FIG. 13 is a diagram corresponding to FIG. 3 according to a twelfth embodiment.

FIG. 14 is a diagram corresponding to FIG. 3 according to a thirteenth embodiment.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Cylinder block, 2 ... Cylinder, 2A ... One end of cylinder, 2a ... Right and left vicinity part, 3 ... Notch recess, 4a ...
Notch ridges at both ends of the notch recess, 5 ... crankcase, 6
... Crank chamber, 7 ... Crank shaft, 8 ... 10 Piston, 13 ... Piston skirt part, 14 ... Oil groove, 15 ...
Connecting rod, 16 ... Large end of connecting rod.

──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Yasumichi Kamata 64, Ishizukitamachi, Sakai City, Osaka Prefecture Inside Kubota Sakai Works, Inc. (72) Inventor Seiji Yukawa 64, Ishizukitamachi, Sakai City, Osaka Prefecture Inside Kubota Sakai Works, Ltd. 72) Inventor Nobuhiro Yamamoto 64 Ishizukita-cho, Sakai-shi, Osaka Prefecture Inside Kubota Sakai Factory (72) Inventor Hideyuki Koyama 64 Ishizukita-cho, Sakai-shi, Osaka Prefecture Inside Kubota Sakai Factory Co., Ltd. (72) Inventor Toshiyuki Yotsutsuji Sakai-shi, Osaka Ishizu Kitamachi 64 Inside Kubota Sakai Works (56) References JP-A-54-35509 (JP, A) JP-A 62-119451 (JP, U) JP-A 1-1131847 (JP, U) JP-A 61-120061 (JP, U) Actually open 1987-156 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F02F 1/00-7/00 F01M 1/06 F16J 1 / 08

Claims (1)

(57) [Claims] A cylinder (2) and a crankcase (5) are integrally formed in a cylinder block (1), and a piston (10) is provided in the cylinder (2) so as to be reciprocally slidable. 5) In a piston engine constructed by connecting a crankshaft (7) pivotally supported in the piston and the piston (10) with a connecting rod (15), one end (2A) of the cylinder (2) is connected to a crank chamber (6). )
Side (2a) of the connecting rod large end (16) of one end (2A) of the cylinder (2) approaching the connecting rod large end (16). A pair of left and right cutout recesses (3) and (3) are formed to avoid interference, and the left and right skirt portions (13) and (13) of the piston (10) are formed.
Oil grooves (14) (14) formed parallel to the cylinder axis on the outer surface of each of the notch recesses (3) and (3) at the opposite faces of the notch ridge portions (4a) and (4a) at both ends. A piston engine characterized in that: