JPS5951102A - Lubricating and sealing mechanism of rotary piston engine - Google Patents

Abstract

PURPOSE:To improve the lubricating and sealing abilities and improve the combustion efficiency by providing an oil ring between compression rings inserted into a piston section. CONSTITUTION:Multiple pistons 2a-2d are provided in an annular cylinder 11 having a circular orbit. An oil ring 20d formed to introduce lubricating oil is inserted between compression rings 20a, 20b. The oil ring 20d section adequately lubricates the wall face of the cylinder 11 and the airtightness to a combustion chamber is maintained by a pair of rings. Accordingly, the lubricating ability and sealing ability of mainly rotors 2, 2' provided with the pistons 2a-2d, casings 1a, 1b, the pistons 2a-2d and cylinder 11 can be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a cat-and-mouse rotary piston engine that utilizes the so-called cat-and-mouse effect of a torus-shaped piston that slides inside an annular cylinder. A, regarding the lubrication and sealing mechanism of the parts.

Engines that are currently in practical use have a piston with a ring connected to the crank mechanism by a rod that slides back and forth within a straight cylinder, making one revolution (two-stroke engine) or one revolution (two-cycle engine). This reciprocating engine is a so-called reciprocating engine that uses a crank mechanism to convert the reciprocating motion of the piston into rotary motion by generating one cycle of two revolutions (four-cycle engine) as a power source.Reciprocating engines have been extensively researched since ancient times. Currently, it is used for various purposes, but its unique structure is 1. Although we have increased the number of cylinders and added various devices to address the problems, such as loss of inertia and power loss, uneven piston wear due to thrust, and vibration, mechanical problems still remain. The loss is large and the energy efficiency is poor, and the structure is also complicated.

For this reason, rotary piston engines that rotate the piston itself to simplify the addendum and improve efficiency have been developed in the past.
A variety of other products have been developed. These include eccentric rotary engines, cat and mouse engines, multi-rotor engines, and rotating block engines. Of these, the Wankel engine, which is an eccentric rotary engine, has been put into practical use, and because it can apply explosive force directly to the piston and cause it to rotate, it eliminates the need for a crank mechanism, a koshi rod, and even a valve mechanism, resulting in less vibration. Although it has many excellent effects such as high speed rotation, high output, and simple structure, the combustion chamber has a complicated trochoid curve shape in order to cause the piston to move eccentrically. Since the volume must be changed, there are many problems in terms of sealing mechanism, fuel consumption, and exhaust gas countermeasures.

Furthermore, two sets of rotors each having a pair of rotary pistons that rotate in an annular cylinder while maintaining a phase relationship of 180 degrees are arranged, one of which is rotated at an inconstant speed, and the other rotor is rotated at an equal speed. While rotating at high speed, the non-uniform type (
A piston is formed between the pistons by shortening or widening the relative distance between the rotating screws (cat-and-mouse effect) by using a type such as a cowl type), a mare type, or a both-inconsistent velocity type (mayer type), etc. A can-nod-and-mouth type rotary engine (also called a scissor engine) is a rotary engine that changes the volume of the combustion chamber so that the four strokes of intake, compression, expansion, and exhaust proceed smoothly. Although good results have been obtained in the test stage, there are problems with inertia during high-speed rotation, especially with the sealing mechanism and lubrication mechanism.As for the sealing mechanism, Lahillin packing is used, but it has not been put into practical use at all. The castle has not been reached.

Kowarani%h'% The applicant of this application has installed the aforementioned cat-and-mouse type engine (hereinafter referred to as A with rotary screws 1 to 1):
By incorporating the techniques and advantages of the previous J:RI reciprocating engine, we took advantage of the advantages of the rotating piston type, eliminated the valve mechanism, and designed it into a small cabin, reducing vibration and fuel consumption. We previously proposed a rotary piston engine in Japanese Patent Application No. 162281/1983, which can reduce energy consumption, provide excellent energy efficiency, and provide high speed rotation and high output.

The present invention provides a rotary piston engine that is improved mainly by improving the lubricity and sealing properties of the rotor and casing having the piston, the piston and the cylinder, and achieving higher efficiency and combustion efficiency, as well as measures against exhaust gas. The purpose is to

The present invention firstly provides an appropriate number of rotors having a plurality of pistons fixed at appropriate intervals within an annular cylinder having a circular orbit and moving within the cylinder, disposed within a pair of casings; In order to supply oil from the lubricating oil supply mechanism to the piston part through the lubricating oil supply mechanism, there are at least two combination links on the piston part, and at least one oil ring between the compression rings. These two sets of rings are fitted to each other in order to properly lubricate the cylinder wall surface with the oil ring portion, and to maintain airtightness to the combustion chamber by these sets of rings. An appropriate number of rotors each having a plurality of pistons which are fixedly installed at appropriate intervals within an annular cylinder having a circular orbit and which move within the cylinders are disposed within a pair of casings, and a pair of rotors are provided near the cylinders of the casing. A ring groove is recessed in the rotor, and a pair of thrust rings are fitted therein so as to bias and abut the rotor disposed between the pair of casings, and a ring groove is formed in at least one of the rotors. Concave (70
The thrust ring is fitted between the cylinders, and the rotor is lubricated from the lubricating oil supply mechanism to appropriately lubricate between the rotors and between the rotor and the casing.Furthermore, while lubricating the piston, the airtightness between the cylinder and the casing is maintained. In order to make the gist of the present invention even clearer, one embodiment of the present invention will be described in detail with reference to the drawings.・It is Ri.

Reference numeral 1 denotes a housing for a rotary screw 1 to twin engine according to the present invention, which is composed of a pair of casing bodies I11 and lb, and has an annular cylinder 11 having a circular orbit, and an inlet hole 12 and an exhaust hole 18 that communicate with the cylinder 11. Further, on the opposing surfaces of the casing bodies 1a and 1b, U-shaped ring grooves], d, and 1d, which are concentric with the cylinder 11, are provided on the inside near the cylinder 11, and the ignition plug 14 is provided at a predetermined position. shall be established.

Further, a water passage space 15 is formed on the outer periphery of the cylinder 11, through which cooling water is introduced from the injection port 1-:I 151 and is circulated through the discharge port 152. At the center of 1b is the main bearing 161.16.
2 is a provision.

2.2' is a rotor assembly, and the rotor assembly 2 has pistons 2a12c fixed to the opposing diametrical outer edges of a disc-shaped rotor 21, and the pistons 2a, 2.
C has compression rings 20&, 20b, 20
C is fitted into the compression ring 20.
An oil link 20d formed to guide lubricating oil is fitted into the compression ring 20b, and a U-shaped oil reservoir groove 202 is provided inside the oil ring 20d.
Furthermore, on the outer periphery, there is a semicircular oil sump outer groove 201d whose rotational front side is chamfered at a corner 2o1'd, between the oil sump inner groove 202d and the oil sump outer groove 2'o ta. The oil hole 20 is a conical shape with a smaller diameter toward the outside, and the diameter gradually becomes smaller from the bottom to the top (in the outer circumferential direction when fitted to the cylinder) as shown in Fig. 3.
0d is bored tl, a relatively large chamfered corner 203d is provided on the front side of the rotation, and the piston part 2
Further, the inner surfaces of the piston parts 2b and 2d, which will be described later, are provided with semicircular gouges T extending inward from the top to widen the ignition range.

Further, in the rotor assembly 2', like the rotor assembly 2, a biston 2b12d is fixed to a disc-shaped rotor 22, and the rings of the above-mentioned set are fitted.

The rotor assembly 2.2' formed in this way is placed between the casing bodies 1a and 1b on the output shaft 3, which will be described later.
I'1, each piston 2a, 2b, 2
A combustion chamber is formed between C and 2d.

Reference numeral 3 denotes an output shaft, which has a lubricating oil passage P2 provided on the shaft center, and an oil port G that is supplied with oil via an oil filter F, etc. provided in the casing body 1a(J)'l;
It is connected to the lubricating oil passage 1'1 that leads to the lubricating oil, and is also connected to the passages P3 and P4, and is rotatably supported on the main bearings 161 and 162 of the casing bodies 1a and 1b.

Furthermore, the oil passage P2 is a series of oil passages (not shown), and includes a fixed arm 31, 32 (described later), a rotating sliding portion of the crankshaft 5, and a sliding shaft (not shown) protruding from the fixed arm 31. The transmission gear 41 and other parts that require lubrication, such as rotating tank moving parts, are communicated so that they can be supplied with oil.

The lubricating oil discharged into the casing after lubrication is collected in the oil collecting part S1.82 at the inner bottom of the casings Ia and 1b, and is supplied to the oil filter F through the oil collecting part. The oil is circulated to each part via the oil pump G again to form a passageway for supplying oil.

4 is a fixed gear formed integrally with the casing body 1b, and includes a transmission gear 41 that makes planetary motion around the outer periphery of the fixed gear, and a planetary gear 42 that engages with this and makes planetary motion around the fixed gear 4. , each gear 4.41.42 in a straight line through a fixed arm 81 extending from the output shaft 8 and having I'1
They are arranged side by side in mesh with each other.

Furthermore, the planetary gear 42 is placed on the crankshaft 5 on the solid rotor body 21.22 surface, and the crank arm is rotatable within the through hole 211.221 of the rotor body 21.22. , and the crankshaft 5 is rotatably engaged with the fixed arm 31 and the fixed arm 32 extending from the output shaft 8 at its other end, and has a flywheel 6 fixed thereto.

In addition, both ends of the crank arm are connected to rotor assembly 2.
．． The positions of the pistons 2a12c, 2b, and 2d of the rotor assembly 2.2' are connected to arbitrary points on a straight line by links 7a and lb, and the rotor combination 2.2' is designed to rotate in conjunction with the movement of the crank arm. This allows the vinyl
l-:/2a, 21), 2c, and 2d have a cat-and-mouse effect.

The above-mentioned planetary gear mechanism, crankshaft 5, crank arm, etc. are also provided at symmetrical positions and perform the same functions. A thrust ring assembly 8 consisting of a rectangular ring 82 with a cross-sectional shape and a spring-like waveform ring 81 configured to bias the ring outwardly is fitted in an opposing manner. , and circular ring grooves 21d and 22d with a cross-sectional shape are recessed in the facing surfaces of the pair of rotor bodies 21 and 22 to face the thrust ring combination 8, and a thrust intermediate ring with a cross-section with a cross-section is provided here. 9 is a fitting device 7, and inside the rotor body 21.22, the thrust ring combination 8.8, the intermediate ring 9, and the rotor body 21 are connected to the oil passages P8 and P4 from the output shaft 8.
5.22 and other lubricating surfaces, and the oil rings 20d of the pistons 2a, 2b, 2c, 2d.
Oil passages P6 and P7 to introduce oil are bored into this ring 20d from the axis side of the groove, and these oil passages P6 and P7
is shown in FIG. 2. Taking the case of 1-rotor 21 as an example, the oil passage P6 indicated by the broken line is connected to the oil ring 2Od of the piston 2a.
A similar oil passage P7 is also formed in the rotor 22, which is extended to the bottom of the groove to supply oil from the center side thereof.

Incidentally, the oil passages P6 and P7 are formed in an arbitrary number not only to the piston portion but also to the thrust ring combination 8 and the thrust intermediate ring 9 so that oil can be uniformly supplied all around.

In addition, although the case where the thrust intermediate ring 9 is provided with only a cross-sectional shape has been described above, this and the ring groove 21d
, 22d, or the intermediate ring 9 is fitted in the shape of a mouth and a chive split in the shape of a mouth, and a spring-like wave ring is placed between these. Fitting devices z-r: If both of them are biased outward, the sealing performance can be further improved, and it goes without saying that the use of these devices is also included in the present invention.

Next, the operation of the rotary piston engine formed as described above will be explained.

The output shaft 3 is rotated counterclockwise by the starter motor (not shown in the figure), and the spark plug 14 is ignited (thus, an explosion occurs in the combustion chamber, and both pistons 2a and 2d are Trying to shift the weight in the opposite direction.

However, both pistons 2a, 2d are connected to the crankshaft 5 and nine links 7a, 7b via a rotor assembly 2.2', and the crankshaft 5i: around the control gear 4 The transmission gear 41 and the planetary gear 42 rotate 1 inch in the opposite direction to the revolution direction, so when the crankshaft No. G revolves counterclockwise while rotating on its own axis [1. The piston 2a moves counterclockwise, while the piston 2d
will remain in a stopped state within cylinder ll.

Furthermore, the binuton 2a7J and the crank 11ll continue to rotate 51 times (J), and the force 5 between the pistons 2B and 2d becomes maximum, and the inertial force of the crankshaft 5, the pressure D in the combustion chamber, and the subsequent explosion occur between both pistons 2a12d. Coupled with the mutual relationship with other pistons 2C12b, the pistons rotate smoothly and approach each other, and the combustion gas is discharged from the exhaust hole 13.

On the other hand, the pistons 2)) and 2C, which are provided with symmetrical structures to the pistons 2a and 2d, are rotated in the same manner as the pistons 2a and 2d, respectively, together with the rotor assembly 2.2'. Fuel is sucked through the hole 12, and the compression stroke is completed.

Then, the pistons 2a, 2 (inflating and exhausting strokes are performed in the same manner as in the first period).

Masuko, between the pistons 2d and 20, and between the pistons 2a and 2
Since each stroke is similarly carried out between b and so on, four explosions are carried out for one rotation of the output shaft 8.

During the series of steps described above, the first lubricant ih supplied from the oil 1 imp G via the oil passage 1'l and P2 is first passed through the oil passage 1'l and P2 to the main support holder 161, 162 and the fixed Arm 81.82. ! : Lubricates between the crankshaft 5 and the rotating and sliding parts of the transmission gear 41, and also lubricates the oil passages P3 and P.
4 Through the oil passages P6 and P7 of the rotor body, the rotor 2
1.22 and between these and the casing bodies 1a and lb, as well as the pair of thrust ring combinations 8.8 and the thrust intermediate ring 9.
, 2 bs2c, from the groove bottom side into which the oil ring 20d of 2d is fitted, the oil sump inner groove 2 of the oil link 20d.
02d, oil is introduced into the oil sump outer groove 201d through the oil hole 200d, and this is used as the oil sump part] 7, while maintaining airtightness with the cylinder 11. When the 20d is fitted into the cylinder 11, the diameter is gradually reduced toward the outer periphery (J), so that oil can be evenly supplied into the cylinder 11 even against the centrifugal force caused by the rotation of the piston. Therefore, an oil film is appropriately formed on the cylinder 11, and each piston slides and rotates inside the cylinder 11, so the combination seal in-rings 20a, 20b
, 20c does not send excess lubricating oil to the combustion chamber, and the cylinder and casing are reliably sealed by the thrust link combination 8.8 and the thrust intermediate link 9, so unburned fuel is 1. As explained in detail above, the present invention achieves high rotation speed, high output, and reduced vibration by a rotary piston engine, and reduces the number of parts. In addition to the effects of reduction in size, size, and weight, it also has the following excellent effects.

(1) Lubrication supply mechanisms such as oil pumps and oil passages are appropriately arranged to positively and reliably supply lubrication to the pistons and rotors, which are the main moving parts, and the oil is designed to guide the lubrication oil in an appropriate manner. Since the link is fitted onto the screw 1, it is possible to efficiently form an oil film around the entire circumference, and it also prevents burnout even at high speeds and high loads. This arrangement prevents excess lubricating oil from entering the combustion chamber, thereby preventing the formation of unburned scum.

(2) Also, if the lubricating oil supply mechanism is used to supply oil to the piston part via the output shaft as described above, while guiding the oil inside the rotor, it will properly lubricate between the rotors and between the rotor and the casing, and Since the thrust link of the L is able to hold enough air, even if unburned waste from the cylinder flows in, it will form a g-song properly and will sufficiently prevent the generation of blowby gas into the atmosphere. and high speed rotation can be obtained.
Screws in exclusive Yat-and-mouse type rotary engines with adequate measures taken to prevent exhaust residue)
It provides ideal motion to the main moving parts such as ・ and operates smoothly, making it extremely efficient.

In addition, the oil supply structure to the piston, the shape of the screw link, the structure of the rotor and thrust ring, and the lubricating oil may be arbitrarily determined within the range of operation and effect, and any of these changes are not included in this document. Needless to say, this does not change the gist of the invention.

As is clear from the above description, the present invention simply and effectively achieves the desired lubrication and sealing in a rotary piston engine, and the present invention provides no practical benefits. I have to say that it is a great thing.

[Brief explanation of the drawing]

The drawings show one embodiment of the present invention, and FIG. 1 is a front view of the main parts of the rotary piston engine with one casing main body side removed, FIG. 2 is a front view of the loaf assembly, and FIG. Figure 3 (A) is a side view of the oil ring, (B) is a sectional view of the main parts of the oil ring, (C) is a side view of the combination long ring, Figure i4 is a longitudinal sectional view of the rotary piston engine, and Figure 5 1 is an enlarged longitudinal cross-sectional view of the main parts of the rotary piston engine, showing an exploded view of the vicinity of the cylinder section in the upper part of the rotary piston engine. 1a, 1b---Casing body, 11---Cylinder, 2.2'-m-Rotor combination, 2a, 2b, 2C, 2d---Piston, 20&, 20b, 20c---
Combination ring, 20d--11 oil ring, 21.22-m-rotor body, 8-m-thrust link combination, 9-m-thrust intermediate ring. Patent Applicant Yoshi Kei Kuroki Figure 1 2b 2c Figure 2 Figure 3 (A) (B) (C) Figure 4

Claims (2)

[Claims] (1) An appropriate number of rotors each having a plurality of pistons that are fixed at appropriate intervals within an annular cylinder having a circular orbit and move within the cylinder are disposed within a pair of casings, and The piston part is to be lubricated by a lubricating oil supply mechanism, and at least two combination rings are fitted in the piston part, and at least one oil ring is fitted between the compression rings. A lubrication and sealing mechanism for a rotary piston engine, characterized in that the oil ring portion is formed to appropriately lubricate the cylinder wall surface, and the set of rings is formed to maintain airtightness to the combustion chamber. . (2) An appropriate number of rotors each having a plurality of pistons that are fixedly installed at appropriate intervals within an annular cylinder having a circular orbit and move within the cylinders are disposed within a pair of casings, and the rotors are disposed in the vicinity of the cylinders of the casings. A pair of ring grooves are recessed in the
A pair of thrust rings are fitted in order to bias and abut the rotor disposed between the pair of casings, and a ring groove is recessed in at least one of the rotors, so that the thrust ring is provided between the rotors. A ring is fitted, and the rotor is supplied with oil from a lubricating oil supply mechanism to appropriately lubricate the space between the rotors and between the rotor and the casing, and is also formed to maintain airtightness between the cylinder and the casing while supplying oil to the piston. A lubrication and seal link mechanism for a rotary piston engine that is characterized by the following.