JPS585431A - Angular velocity changing rotary engine - Google Patents

Abstract

PURPOSE:To reduce vibration and noise, by constituting working chambers, in which the internal peripheral surface of a cylinder and the peripheral surface of pistons are relatively slided by a crank to change volume, and mounting gas seals of closed loop state. CONSTITUTION:Forces F1, F2 are generated by combustion pressure F in a combustion stroke respectively in a crank pin 42, with an internal rotary piston 20 through a connecting rod 44, and a crank main shaft 41, with an external cylinder 10, to drive a planetary gear 45, rotate the cylinder 10 and rotate also the piston 20 while spreading volume of a working chamber 29. Its working chambers 29A, 29B are symmetrically formed with respect to one piston 20, and dynamic balance can be obtained. There are provided a gas seal 71 to the rotary piston 20 and gas seal 72A to the rotary cylinder 10. Through these shape is complicated, concentrically rotating motion is performed around a fixed center shaft 30, and adjustment of a gap can be easily performed. Further cooling and lubricating oil is circulated through the shaft 30 to perform cooling and lubrication.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rotary piston engine. The general KE2-Taly piston engine has a dynamic balance of 4111 points compared to a reciprocating piston engine, and has a vibration-free
It is believed that the engine will produce less noise. However, on the other hand, gas seal and cooling problems are considered to be overlapping issues, especially in internal combustion engines.The four-tary engine of the present invention provides a practical solution to the gas seal cooling problem, and also has a structural It has a structure that can withstand the large force exerted during gas combustion.

The present invention will be described below with reference to one embodiment.

(2) Construction of the Embodiment In this embodiment, the cylinder is constructed as an outer rotary cylinder 10 consisting of one half 10A and an IOB, as shown in FIGS. 1 and 2.

10A and 10B are of the same shape. In principle, the rotary motor and stone engine mentioned above operate by means of a pair of rotary rotors, namely an outer rotary cylinder and an inner rotary piston, one of which rotates at a uniform angular velocity. Since the other rotor has an angular velocity that varies periodically, it belongs to a so-called angular velocity variable type rotary engine that expands and contracts the working chamber formed between the two rotors.

3 to 7 show one half 10 of the outer rotating cylinder 10.
Indicates A. FIG. 4 is a view of 10A seen from the inside, FIG. 3 is a view of 10A seen from the left, and FIG. 5 is a view of 10A seen from the right. An intake/exhaust opening 13 is provided on the circumference of the IOA. 18mm is left and right outer synchronous cylinder 1
Connecting bolt hole 1 on the sliding surface where 0A and 10B touch
6m, 16m, etc. are provided. 11A
is the half of the fixed center shaft bearing, and the outer rotating cylinder 1
Together with the bearing 11B of 0'B, it constitutes a fixed center shaft bearing. 12A, 12A are halves of the crank main shaft bearing, which together with the bearing 12B of the outer rotary cylinder 10B constitute the crank main shaft bearing. 82m, 82b, @2e are coolant passages for cooling the outer rotating cylinder. FIG. 7 shows a left half 10At of the outer rotary cylinder 10 viewed from the circumferential direction. A closed loop gas seal 12 is attached to the outer circumferential surface. 14 mu.

14 is an oil passage cover. No. 6 WA shows a sectional view taken along the line Vl--Vl in FIG. 7, where 17 mm is a hollow part for weight reduction, and 15 mm is an oil discharge port.

8-10 illustrate the inner rotating piston 20. FIG. FIG. 9 is a front view of the inner rotating piston 20, FIG. 8 is a left side view, and FIG. A cross-sectional view of IKf85 is shown. The inner rotary piston 20 is integrally molded and has a symmetrical shape with respect to the central axis. 21.21 is piston bi/,
22 is a fixed center shaft bearing. A closed loop gas seal 71.71 is attached to the inner rotating piston 20.

The rotary engine of the present invention has a pair of crank mechanisms 40A, 4
It has 0B. 40mu and 40B are the same shape. The crank mechanism 40 has a crank main shaft 41A and a crank bin 42.
A, a crank arm 43A and a connecting rod 44A are provided, the crank main shaft 41A is supported by the crank main shaft bearings 12A and 1211 of the outer rotating cylinder 10, and the crank pin 42A is connected to the connecting rod 44A. Crank main shaft 41
An idling gear 45 is fixed to A. The housing SO consists of an upper crank 51 and a lower housing 5Ii. The 12th @ is the upper No. 1 Uzing 51
The view from the inside, Figure 11 is on the M-M line of Figure 12?
85 is a sectional view. An intake port s2 and an exhaust port 53 are opened at the outer circumference of the upper housing 51. 54 is a support portion for supporting the fixed central shaft 30. No crank 50
An output shaft 63 is supported on the output shaft 63, and an output car 62 is attached to the end of the output shaft 63. ss, ss... are bolt sizes for bolts (not shown) connecting the upper housing 51 and the lower housing 56.

A spark plug 59 is provided at a predetermined location on the lower housing 56.

FIG. 2 shows an assembled sectional view taken along the line MM in FIG. 12.

An inner rotary piston 20 is rotatably supported on a fixed central shaft 30. The outer rotating cylinder 10A and IOB are installed inside the 71 housing 50. The bearings 11 and 11B are rotatable around the fixed central shaft 30, and the crank main shaft bearing 1
2A.

A 12BK crank main shaft 41mm and 41B are supported. Connect the crank pin 42mm, 42B and the piston pin 21, 21B of the inner rotating piston 2o with the connecting rod 44mm, 44BK
Therefore, each is connected. Outer rotating cylinder 10mm, 1
There are 48 people in the crank chamber between 0B and inner rotating piston 2G.

41B and working chamber 29mm, 28mtl-consisting.

(2) Operating Mechanism In FIG. 1, the center fixed gear 31 and half the number of planetary gears 45A and 45B mesh with each other. Play 1
Gears 45A and 451m are crank main shafts 41A and 41, respectively.
It is attached to B.

When the outer rotary cylinder 1om and IOB rotate once, the crank shafts 41A and 4111 perform one revolution around the fixed central shaft 30 and two rotations. The inner rotating piston 20 has a piston pin 21,
Connecting rod 44A1 crank pin 42mm, crank main shaft 41
The outer rotary cylinders 10A and 10B are connected to each other through the outer rotary cylinders 10A and 10B. Therefore, the outer rotating cylinder is 10 mm.

When 10B rotates once, the inner rotary piston 20 makes two reciprocating movements.

As a result, the working chamber 29m, 29B formed between the outer rotary cylinder 1om, 10B and the inner rotary piston 2o
The volume of the outer rotating cylinder is 10 mm, per 1011 revolutions,
Expansion/reduction is repeated 211 times. This operation can correspond to each cycle of suction→compression→combustion→exhaust in a four-stroke engine.

An explanatory diagram of the operation is shown in FIG. 14. During the combustion cycle, the pressure F applied to the surface of the inner rotary piston 20 is transmitted through the connecting rods 44m, 44B to the crankbins 42m, 42m.
BKF, generates the force. On the other hand, the pressure F applied to the outer rotating cylinder 10m and IOB is
A force F is generated at B.

As a result, the planetary gears 4SA and 45BK generate clockwise rotational torque, and the outer rotating cylinders 10A and IOB rotate clockwise. In addition, the inner rotating piston 20 also has a working chamber 21.
Rotate clockwise while expanding the volumes of 1A and 29B.

Each cycle of exhaust, exposure, and compression acts as a braking force on this rotation, but since the force of the combustion cycle is sufficiently large, it overcomes these braking forces and mechanical losses, and the outer rotating cylinder 10A as a whole.

10B rotates clockwise. During the period in which the greatest force is generated in the combustion cycle, the crankshaft 41
The line of action of the force from the angle of 41B is the planetary gear 4SA, 4
It passes near the central axis of 5B. Therefore, the force applied to the gear is not so large, and the strength required for the gear is within a practical value.

Further, since a pair of working chambers 211A and 211B are formed symmetrically to the rotational axis of each inner rotary piston 20, a perfect dynamic balance can be achieved. Intake・
The function of evacuation is performed automatically by 100 revolutions of the outer rotating cylinder.

Next, problems in coupling the inner rotating piston and the outer rotating cylinder will be described. The inner rotating piston has two connecting rods, each with a crankshaft and connected to the outer rotating cylinder. Therefore, unless some connections are made loose, smooth rotation will not be possible. One possible method is to loosely connect the connecting rod on one side. In this case, the force generated in the working chamber is always 1
The transmission is carried out by a pair of connecting rods, the crankshaft, and the loosely coupled connecting rod, the crankshaft, simply acts as a balance weight.

Another method is to make the inner rotating piston a hinge-like mechanism in which two plates can rotate independently around the shaft. In this case, the two sets of connecting rods and crankshafts each serve to transmit the generated force.

■ Structure of the working chamber In order to prevent high-pressure gas from leaking, the working chamber is made up of two components, like the piston, cylinder, and piston ring in a reciprocating piston engine.
In addition, a closed loop sealing material must be fitted into one of the components. It is known that this sealing material is pressed against the wall of the other component by gas pressure or spring pressure, and that a satisfactory gas seal is obtained by the action of the oil present on the surface of the sealing material.

The angular velocity variable rotary engine of the present invention has a working chamber 211A.
, 29B is the outer rotation shi'J//10A.

The gas sealing problem is solved by fitting a closed-loop sealing material into the inner rotating piston 20.

The gas seal is divided into two parts. One is the seal between the inner rotary piston 20 and the outer rotary cylinders 10A, 10B, and the other is the seal between the outer rotary cylinders 10A, IO
It is a seal between B and the housing so, s@. FIG. 8 shows a gas seal 71 provided on the inner rotary piston 20. FIG. 7 shows a gas seal 72m provided on the outer rotary cylinder 10m. The gas seals 71 and 72 can sufficiently prevent gas leakage from the working chambers 29 and 28B. Gas Sea Rua 1. ．． The shape of 72A does not have a simple piston ring 4 shape, but the inner rotating cylinder 10A.

10B rotate concentrically around the fixed central axis 30, the gap can be easily adjusted and there are few technical problems.

(2) Cooling and Lubrication As for cooling, since the outer rotary cylinder 10 and the inner rotary piston 20 rotate together, it is difficult to provide independent passages for the bearing lubricating oil and the cooling fluid.

Therefore, a common passage for cooling and lubricating oil is provided here for 5K. The passages are shown in FIGS. 1, 3, 4, and 5. Oil enters from the fixed central shaft 30081m, and enters the outer rotating piston 82aK from 81b.

From 112m, it passes through 82b * 82c, returns to the fixed central shaft 30 again, and is taken out from 511e * 81d. The heated oil is cooled and circulated by a radiator.

■ Features The features of the engine of the present invention are as follows.

(1) Since the engine is perfectly dynamically balanced, vibration and noise can be reduced compared to reciprocating piston engines.

(2) Suction and discharge valves are no longer needed, and rotary valves take their place. This simplifies the suction and discharge mechanism and reduces vibration and noise. Furthermore, there is no restriction on the engine rotational speed due to the kinetic inertia of the suction and discharge valves.

(3) The shape of the working chamber is more similar to a reciprocating piston engine than a Wankel engine, and its thermodynamic properties are better than a Wankel engine.

(4) Since the outer rotating cylinder and inner rotating piston both rotate around a fixed central axis, their walls do not rub against each other (only the gas seal piece is in contact with the other wall. For this reason, there is little damage to the cylinder wall and the engine has a long lifespan.

(6) The materials that make up the engine do not necessarily need to be special or expensive; existing materials can be used.

■Second Embodiment Next, a mechanical modification of the engine described above will be described. Until now, a fixed gear on a fixed central shaft had been nationally specified, so the mechanism was one in which an outer rotating cylinder rotated. On the contrary, if the fixed gear on the fixed central shaft is allowed to freely rotate around it, the outer rotary cylinder can be fixed. In this case, the inner rotary piston performs an arcuate motion that reciprocates over a certain section.

In FIG. 13, cylinder 11G is fixedly provided and consists of halves 110A and 110B. 110A and 110B have coolant passages 1111A and 181, respectively.
B is provided, and spark plugs 15 iA, 15! An IB will be established. Fixed central shaft 130 allows inner rotating piston 12
0A, 12011' supports. Inner rotating piston 120
A and 120B include pistons 121A and 121B.

As in the case of the first embodiment, the crank main shaft 141A.

141B is supported by cylinders 110A and 110B, crank pin 142mm, 14211 piston pin 12
1A and 12111 respectively to connecting rods 144A and 144B
Concatenate by.

Cylinder 110mm, 110B and inner rotating piston 120
A, working chamber 129A by 120B.

129B and crank chambers 149A and 149B. The pair of working chambers and the pair of crank chambers are arranged axially symmetrically.

An intake/exhaust valve, such as a cylindrical rotary valve, having an intake port 152A and an exhaust port 153A is provided in the cylinder 110B, and an intake port 152B and an exhaust port 153 are provided in the cylinder 110B.
An intake/exhaust valve 192B having B is provided.

The features of the second embodiment of the present invention are as follows.

(1) Since a pair of axially symmetrical cranks are placed inside the cylinder 110, even if the inner rotary piston 120 makes a rocking motion, the output shaft is located at the center, so the effect of vibration is minimal on the output shaft. I can't get it across. Therefore, the life of the output shaft is not only extended (but also gives good results to the output output mechanism from the output shaft.) By providing two cylinders, the operating phase of the crank/connecting rod mechanism of each cylinder is adjusted to 18-09. If it is shifted, the vibration canceling effect will be further improved.

(2) Since the output shaft is centrally located, the distance to the valve mechanism and cooling fan is short, which is advantageous in terms of drive mechanism design.

■ Application examples This engine can be used not only as a compressor or an odd cycle engine (but also as a diesel engine with low vibration and noise).

Furthermore, it can be used as a capacity type gas turbine as follows. If this rotary engine is made to have multiple cylinders, for example, it has two internally rotating pistons, one of the four-cylinder engines is used as a compressor, the other is used as an output chamber, and both are connected by a combustion chamber. It can be a capacity type gas turbine engine. In this case, the rotary engine used as the power chamber can, after exhausting the combustion gases, draw in and exhaust fresh, cold air to cool the walls of the power chamber. Therefore, the temperature of the combustion gas can be raised to the same level as that of a reciprocating piston, making it possible to realize an engine with high thermal efficiency and clean exhaust gas.

[Brief explanation of the drawing]

Figure 1 is an overall perspective view of the main components (however, the housing is not drawn). Figure 2 is a sectional view of the main components, Figure 3 is a left side view of the outer rotating cylinder (one half), and Figure 4 is a left side view of the outer rotating cylinder (one half). The figure is a front view of the outer rotating cylinder, Figure 5 is a right side view of the outer rotating cylinder, Figure 6 is a sectional view of the outer rotating cylinder taken along the line ■-■ in Figure 7, and Figure 7 is a cross-sectional view of the outer rotating cylinder. Rear view, Figure 8 is the left side view of the inner rotating piston, No. 9
The figure is a front view of the inner rotating piston, Figure 10 is a cross-sectional view of the inner rotating piston, and Figure 11 is an X of the housing (one half).
12 is a view of the housing (one half) seen from the inside, FIG. 13 is a sectional view of the second embodiment, and FIG. 14 is an explanatory diagram of the operation. 10=outer rotating cylinder, 10A, 10B=outer rotating cylinder (one half), 11A, 11B=fixed center shaft bearing, 12A, 12B=crank main shaft bearing, 13
A, 13B = intake/exhaust opening, 20 = inner rotating piston, 21: = piston pin, 2! IA, 29B=working chamber, 31=fixed center gear, 30=fixed center shaft, 4
0A, 40B=crank mechanism, 41 A, 41
B=crank main shaft, 42A, 42B=crank bin,
44A. 44B=Connecting rod, 45A, 45B=Planetary gear, 4$
1A, 4! IB=crank chamber, 50=housing,
51=upper housing, 52=intake port, 53=
Exhaust port, 56; Lower housing, 59 = Spark plug, 61 = Output extraction gear, 62 = Output gear,
71=Inner rotating piston gas seal, ? 2=2=Outer cylinder gas seal, 81=Fixed central axis coolant passage, 82=Outer rotating cylinder reproductive liquid passage, 110
;Outer fixed cylinder, 120=inner rotating piston,
129A, 129B = Working chamber 140mm, 140B = Crank mechanism, 149mm, 14! iB=crank chamber,
159A. 159B=Spark plug, 1112A, 1!12B=Intake/exhaust valve. Figure 14

Claims (1)

[Claims] 1 The following (1), (II), (III),
An angular velocity variable lid rotary engine with the conditions of IV). (i) The piston is formed axially symmetrically and is rotatable around the central axis. (It) The cylinder cooperates with the piston to form a crank chamber and a working chamber, the two crank chambers are arranged axially symmetrically, and the two working chambers are arranged axially symmetrically. (-) A crank whose main shaft is supported by a cylinder is built into the crank chamber, and the crank connects the cylinder and the piston, and each crank operates axially symmetrically with respect to the other. The inner peripheral surface of the cylinder and the outer peripheral surface of the piston constitute a working chamber whose volume changes by sliding relative to each other by a crank,
To enable the installation of closed loop gas seals. 2. The angular velocity variable rotary engine according to claim 1, wherein the cylinder continuously rotates on one side. 3. The angular velocity variable rotary engine according to claim 1, wherein the cylinder is fixed and the piston makes a reciprocating circular arc motion.