JPH01142216A - Double pistion device having fluid control groove on outer circumference of piston shaft - Google Patents

Abstract

PURPOSE: To make machining of a fluid control groove easier by forming the circular fluid control groove that controls inflow of new gas in periphery of the middle part of a shaft of an engine in which a pair of pistons connected by a shaft slides oppositely to each other. CONSTITUTION: A multi-piston arrangement (engine) is so constituted that the upper and lower pistons 4, 64 are slidingly inserted in coaxial upper and lower cylinders 2, 62, and the two pistons 4, 64 are connected by a single piston shaft 7. In this constitution, a fluid control groove 15 having a half moon shaped axial cross section is formed in the middle part of the piston shaft 7 like a ring relative to the shaft 7. Sucking apertures for each cylinder chambers 1, 61 are respectively formed between the upper and lower sealing rings 54, 55 in each cylinders 2, 62 by the fluid control groove 15. And a single inflow path 9 connected to the space between the pistons 4, 64 is formed inside the housing 40.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a double piston device used in internal combustion engines, etc. The present invention relates to a dual piston device having a fluid control groove on the outer periphery of a histoshaft, which allows both pistons to effectively reciprocate within a cylinder while giving opposite functions to each other.

(Prior art) As a double piston device, the present applicant has disclosed Japanese Patent Application Laid-Open No.
There is one disclosed in Japanese Patent No. 265327.

This is a system in which pistons are connected to each end of a single piston shaft so that their axes are common, and fluid controls are installed on the outer periphery of both ends of the piston shaft to control the intake and exhaust of fluid into each combustion chamber, etc. A groove is formed, and an inflow passage communicates with the fluid control groove. For example, when the upper piston is in the exhaust stroke, the lower piston acts in the compression stroke, thereby By reciprocating the upper and lower pistons as an integrated piston,
It is used between internal combustion engines, etc. (Japanese Patent Application Laid-open No. 1983-
Figures 14, 15, and 51 of Publication No. 265327,
(See Figures 52, 57, and 58).

However, since each piston is provided with a fluid control groove and a gas inflow passage, it is difficult to accurately position the multiple fluid control grooves relative to each other. There are problems that need to be improved, such as timing adjustment, turbulence due to the large number of fluid control grooves and inflow passages, and resistance to inflow into the cylinder. (Purpose) The present invention has been made in view of the above-mentioned points to be improved.
It is possible to improve the machining accuracy of the fluid control groove that controls the fluid flowing into the cylinder, improve the timing of fluid inflow and discharge, prevent turbulence in the inflow path, and improve the resistance to flow into the cylinder. The object of the present invention is to provide a dual-piston device that does the following.

(Structure) In order to solve the above problems, the present invention provides pistons at both ends of a single piston shaft, and makes the piston shaft reciprocate within the cylinder while giving opposite functions to both pistons. In a dual piston device equipped with a fluid control groove on the outer circumference of the piston shaft, a fluid control groove is provided on the outer circumference of the piston shaft.
At the center of the piston shaft, which is located between both pistons, there is one annular control groove with an approximately half-moon-shaped axial cross section, and a single fluid inflow path is provided in the space between both pistons. In addition, two or more of the devices described in item 1 above each having a piston shaft having the two pistons are arranged in parallel, and these devices are linked to a common crankshaft, and adjacent devices on this crankshaft are connected to each other by 90 degrees. The feature is that a phase angle difference of degrees is provided.

(Example) Hereinafter, the present invention will be described in detail based on the illustrated example.

FIG. 1 shows a case where a multiple piston device according to an embodiment of the present invention is used in an engine, in which upper and lower pistons 4.64 are arranged in upper and lower cylinders 2.62 having a common axis. Each cylinder 2 can slide back and forth on a common axis.
．． The strike cylinder 52 is fitted into a piston ring groove 51 provided on each piston 4.64 to maintain airtightness between the inner surface of the cylinder and the piston 4.64.

Further, a single piston shaft 7 is provided between both pistons 4 and 64, and a central portion of the piston shaft 7 has a
A fluid control groove 15 having a substantially semicircular cross section in the axial direction is provided in an annular shape with respect to the shaft 7 . For this reason, fluid control groove 1
5 The diameter of the shaft in the center is smaller than the shaft diameter in other parts, and a suction hole to each cylinder chamber 1.61 is formed between the upper and lower seal rings 54.55 on the side of each cylinder 2 and 62. can do.

This fluid control groove 15 has only one location compared to the conventional one, so it can be easily and accurately processed, and together with the single inflow passage 9 described later, the gas inflow path is also simplified. This prevents the occurrence of turbulent flow in the inflow path, and further reduces the resistance to gas inflow into each cylinder.

Further, an exhaust hole 6 is provided near the upper and lower ends of each cylinder 2.62, and when the upper piston 4 is at the top dead center as shown in FIG. Groove 15
Both end portions 81.82 are separated from the upper and lower seal rings 54.55 to form a suction hole with less resistance.

Furthermore, the positional relationship between each exhaust hole 6 and the fluid control groove 15 is as follows:
When the exhaust hole 6 is closed by the piston 4, the end 81 of the fluid control groove 15 comes into contact with the upper seal ring 54, so that the suction hole formed by the fluid control groove 15 is closed, and at the same time, the lower end 81 contacts the upper seal ring 54. The lower cylinder chamber 61 has been compressed together with the lower cylinder head 63 by the histoscope 4.
The other end 82 of the fluid control groove 15 is provided at a position where the fluid control groove 15 is formed.

Therefore, easily improving the machining accuracy of the shape and position of the fluid control groove 15 makes it possible to accurately manage the timing of the compression stroke, etc. of each cylindrical chamber 1.degree. 61.

The reference numeral 40 in the figure is a housing, which is connected to each cylinder 2, 62 and a bolt 21 through each upper and lower cylinder head 3.638.
etc., each cylinder head 3.6
A seal groove 53 into which upper and lower seal rings 54 and 55 are fitted is provided in the portion facing 3.

These upper and lower seal rings 54, 55 are in contact with the outer circumferential surface of the piston shaft 7 to maintain air pressure in each cylinder chamber 1.61, and the pressure passages 41 provided in each cylinder head 3. The high pressure in the cylinder chambers 1, 61 acts on the outside of each seal ring 54, 55, which tightens each seal ring 54, 55 more strongly against the piston shaft 7, improving the airtightness between them. .

The interior of the housing 4o forms a single inlet passage 9 into which the piston shaft 7 together with the fluid control groove 15 is exposed and supplies each cylinder 1.61 with a mixed gas. .

Note that 10 indicates a mounting portion for mounting a spark plug 11, etc., and 13 indicates a bottle.

Roughly speaking, each piston 4, 64 is firmly assembled to the piston shaft 7 and connecting rod 14 using rivets 17, threaded portions 16, and the like.

Next, the action of the fluid control groove 15, which is a feature of the present invention, during the operation of the above-mentioned multiple piston device will be explained.

When the top and stone 4 rise to near the top dead center, the fluid control groove 15
The inflow passage 9 and the upper cylinder chamber 1 are in communication with each other, and the new mixed gas flows into the upper cylinder chamber 1 through the fluid control groove 15.At the same time, the exhaust hole 6 is opened by the passage of the upper piston 4, and the gas after combustion is opened. Exhaust gas is released.

During this gas inflow, since the gas inflow path is also simplified, generation of turbulent flow in the gas inflow path is prevented, and the gas inflow resistance to each cylinder is also roughly reduced, so that the gas can be inhaled efficiently.

In this case, if the mixed gas supercharged by a turbo charger (not shown) is introduced to the inflow passage ts9, intake and exhaust can be performed more efficiently.

In the upper and lower piston positions shown in FIG. 1, the lower cylinder chamber 61 enters the combustion expansion stroke by the spark plug 11 and lowers the lower piston 64. At the same time, the upper piston 4 begins to lower to close the exhaust hole 6, and at the same time the fluid control groove 15 end 8
1 reaches the upper seal ring 54, and the upper cylinder chamber 1 is sealed to perform a compression stroke.

At this time, the lower piston 64 opens the exhaust hole 6, the end 82 of the fluid control groove 15 separates from the lower seal ring 55, and the fluid control groove 15 functions as a suction hole for the lower cylinder chamber 61, as described above. The same effect as in the intake/exhaust stroke of the upper piston 4 is performed.

FIG. 2 shows an embodiment of the second invention, which is similar to the first embodiment described above.
It is a combination of two invented engines in parallel.

The two connecting rods 114, 214 coupled to each lower piston 164, 264 have a phase angle difference of 9
At 0 degrees, eccentricity of crankshaft 19 &326,12
6 to a common crankshaft 19, and this 90 degree phase angle difference allows the timing of the intake and exhaust strokes of each cylinder chamber to be performed smoothly.

In the figure, reference numeral 8 is a crank case, 25 is a bearing for supporting the crankshaft, and 27 and 127 are balancers.

In addition, the crankshaft 19 is divided into two fitting parts 2.
They are connected into one at 8.

Note that a turbocharger (not shown), which is rotated by exhaust gas from the exhaust hole 106, is connected to the inlet 30 of the inflow passage 109.
It can also be provided in

The right engine section shown in FIG. 2 is in the same state as in FIG. 1.

Furthermore, this engine forms four cycles, with the first cylinder chamber 20 showing intake and exhaust strokes, the second cylinder 261 just before ignition, the third cylinder 101 showing compression, and the fourth cylinder 161 showing combustion and expansion strokes. .

Arrows indicate the flow of gas, etc., and 231 indicates the flow of the mixed gas from the inlet passage 109 to the exhaust hole 106;
133 indicates the expansion of combustion, and 133 indicates gas in a compressed state.

The engine of the second invention described above has a higher output than the first invention, and the effect on the conventional drawback regarding the inflow of gas from the inflow passage 109 is more efficient than that of the first invention. .

(Effects) As explained above, according to the present invention, two pistons that are connected by a single shaft and have a common axis are given opposite functions, thereby reciprocating the entire piston. In a motion device, a fluid control groove for controlling the inflow of a new mixed gas, etc. is provided at one location in the center of the shaft located between both pistons, and the new mixed gas flows from a single inflow passage through this fluid control groove. In addition, it is possible to effectively install additional devices such as a turbo charger in the inflow passage, which improves the machining accuracy of the fluid control groove that controls the fluid flowing into the cylinder, and improves the flow of fluid in and out. Improving swimming, preventing turbulence in the inflow path, and improving resistance to inflow into the cylinder can be achieved more efficiently than in the past.

Furthermore, according to the second invention, in which a plurality of engines and the like of the multiple piston device are arranged in parallel, the effects of the first invention described above can be efficiently exerted, and the advantages of the present device can be greatly increased.

[Brief explanation of the drawing]

FIG. 1 shows a multiple piston device 1F of an embodiment of the present invention.
FIG. 2 is a sectional view showing an embodiment of a multiple piston device according to another invention. 1.61, 101, 161, 201, 261... Cylinder chamber 2.62... Cylinder 3.63... Cylinder head 4.64, 164.264... Piston 6.106.
...Exhaust hole, 7...Piston shaft 9.109...Inflow passage 15...Fluid control groove 40...Housing 54.55...Seal ring

Claims (2)

[Claims] (1) Pistons are provided at both ends of a single piston shaft, and the piston shaft is reciprocated within the cylinder while giving mutually opposite functions to both pistons, and a fluid control groove is provided on the outer periphery of the piston shaft. being given,
In a dual piston device equipped with a fluid control groove on the outer periphery of the piston shaft, one control groove is provided in the center of the piston shaft located between both pistons and has a substantially half-moon-shaped axial cross section and is annular with respect to the shaft, and A dual piston device having a fluid control groove on the outer periphery of a piston shaft, characterized in that a single fluid inflow path is provided in a space between both pistons. (2) Two or more of the devices described in item 1 above each having a piston shaft having two pistons are arranged in parallel, and these devices are linked to a common crankshaft, and adjacent devices on this crankshaft are connected at an angle of 90 degrees. A dual piston device equipped with a fluid control groove on the outer periphery of a piston shaft, characterized in that a phase angle difference of .