JP4845989B2 - engine - Google Patents

Description

  The present invention relates to a reciprocating engine that eliminates a crankshaft in a conventional reciprocating internal combustion engine and converts a reciprocating motion of a piston into a rotational motion using a gear.

  Conventionally, in a reciprocating internal combustion engine (reciprocating engine) such as a gasoline engine or a diesel engine, a reciprocating motion of a piston sliding in a cylinder is converted into a rotational motion of a crankshaft via a connecting rod (connecting rod), The energy from the explosion is extracted as rotational force.

  In order to convert the reciprocating motion of the piston using this crankshaft into a rotational motion (crank means), the crankshaft is not only heavy and expensive, but it is necessary to provide a balance weight, a balance web, etc. to obtain a smooth rotation Various conversion mechanisms have been studied in view of engine space and conversion efficiency.

  For example, a cam engine (Patent Documents 1 and 2) in which a piston that moves up and down along the cam surface of the cam is arranged around a cam arranged around the engine output shaft, or arranged around the output shaft. An engine (Patent Document 3) is proposed in which a piston disposed in a star shape around a rotating disk is reciprocated by a rotating disk that moves eccentrically.

  In addition, an engine (Patent Document 4) in which a viscous disc having an eccentric cam groove is fixed concentrically with the engine output shaft and a large end portion of the connecting rod is engaged with the eccentric cam groove, or an end portion of the connecting rod is provided. An engine (Patent Documents 5 and 6) supported by a rocking member connected to a cross bearing or a spherical bearing has also been studied.

  Furthermore, as a structure (converting means) for converting the reciprocating motion of the piston into a rotational motion using a gear mechanism (gear), for example, a small gear that rolls while meshing the inner periphery of a ring-shaped internal gear, An engine (Patent Documents 7 and 8) that pivotally supports the large end of the connecting rod connected to the shaft, a small gear arranged around the engine output shaft, and a ring-shaped inner ring that is eccentric while meshing around the small gear An engine (Patent Document 9) has been proposed in which a toothed gear (large gear) is used to reciprocate a piston that is eccentrically supported by an annular pivot disposed around a disc-shaped receiving body. .

  In addition, the large end of the connecting rod is supported by a chain that is spanned between one gear fitted to the output shaft of the engine and the other gear arranged at a distance. The engine (Patent Document 10), the engine (Patent Document 11) that converts the reciprocating motion of the piston into the rotational motion of the output shaft by two intermittent gears that mesh with the spur gear and rotate in reverse to each other, or the engine output shaft There has been proposed an engine (Patent Document 12) that reciprocates a piston in a cylinder disposed in a tangential direction around the output shaft by rotation of a fixed large gear (intermittent teeth).

  In addition, as an internal combustion engine that does not use a crankshaft and a piston, it is well known that a rotary engine composed of a saddle type rotor housing and a triangular rotor has been put into practical use.

JP-A-8-4553 JP 2008-25491 A JP 2000-303852 A Japanese Patent Laid-Open No. 3-185221 Japanese Patent Laid-Open No. 3-149319 JP-A-4-255501 Japanese Utility Model Publication No. 60-118344 Japanese Utility Model Publication No. 4-119333 JP-A-6-307256 JP-A 63-97831 JP-A-10-103441 JP 2001-227355 A

  However, the conventional attempts (converting means) for converting the reciprocating motion of the piston into the rotational motion without using the crankshaft in the above-mentioned reciprocating engine have not yet reached the practical use area except for the rotary engine. The current situation is not widespread. In the current automobile market, there is a demand for a lighter, more compact and fuel-efficient engine.

  The present invention has been made in view of such circumstances, and provides a novel engine capable of efficiently converting the reciprocating motion of a piston into a rotational motion without using a complicated and expensive crankshaft. Objective.

  In order to achieve the above object, the present invention includes a cylinder, a piston that reciprocates in the cylinder, a connecting means having one end pivotably connected to the piston via a pin, and the connecting means. An engine having a converting means connected to the other end of the output shaft for rotating the output shaft, the pinion gear fitted and fixed to the output shaft as the converting means, and the pinion gear meshing with the pinion gear. An internal ring gear that circulates while decentering, a first planetary gear that is disposed inside the internal ring gear and revolves around the pinion gear while meshing with the pinion gear, and the first planetary gear and the internal ring gear The second planetary revolving on the track centering on the pinion gear while meshing with the first planetary gear and the internal ring gear. And one end side is rotatably fitted to the output shaft, and the other end side is provided with a support member that pivotally supports the planetary gears at a predetermined interval. An engine in which the other end of the connecting means is connected to the connecting portion is a first gist.

  In order to achieve the same object, the present invention includes a cylinder, a piston that reciprocates in the cylinder, a connecting means having one end pivotably connected to the piston via a pin, An engine having a conversion means connected to the other end of the means and imparting rotational movement to the output shaft, the conversion means as a pinion gear fitted and fixed to the output shaft, and an axial direction of the output shaft A wide ring-shaped inner tooth is formed on the inner circumferential surface of the pinion gear, and outer teeth are formed in both axial end regions of the outer circumferential surface. A connecting portion with the coupling means is formed in the region, and meshes with the pinion gear and meshes with the external teeth of the internal and external tooth ring gears rotating around the pinion gear while being eccentric. While the two guide gears revolving around the inner and outer tooth ring gears, one end side is rotatably fitted to the output shaft, and the other end side is pivotally supported with the guide gears engaged with the outer teeth of the inner and outer tooth ring gears. An engine having a support member and having the other end of the coupling means connected to a connecting portion provided on the outer peripheral surface of the inner and outer toothed ring gear is a second gist.

  That is, the present inventor has intensively studied to solve the above problems, and as a result, as a reciprocation-rotation conversion mechanism replacing the crank means, a small-diameter external gear fixed to the output shaft, and an eccentricity around the outer gear. The present inventors have found that the rotation conversion function of the crankshaft can be replaced by combining a large-diameter internal gear that moves and providing a gear structure that can stably support the eccentric motion of the internal gear.

  The present invention has been made on the basis of the above knowledge. In the engine of the present invention, the vertical movement of the connecting means caused by the reciprocating movement of the piston is converted into the eccentric movement of the ring gear. However, by being transmitted to the pinion gear fixed to the output shaft, energy from the explosion of the fuel can be efficiently extracted as a rotational force. In addition, since a heavy and expensive crankshaft is not used, it is possible to reduce the weight and cost of the engine.

  Further, in the present invention, among them, the connecting means is formed integrally with the ring gear by extending the connecting portion of the ring gear, and the piston is connected to the tip of the connecting portion. The number of engine parts can be reduced, which is preferable. Moreover, the engine in which the connecting means is integrated with the ring gear distributes stress without receiving the force due to the reciprocating movement of the piston at one point, unlike the connecting point (crank pin) of the conventional crankshaft and connecting rod. Has the advantage of being able to.

  And in the present invention, among them, in particular, the ring gear side base portion of the connection portion extended from the ring gear is formed in an arc shape covering a part of the outer peripheral surface of the ring gear in the circumferential direction. The stress due to the reciprocating motion of the piston can be dispersed and supported on the outer peripheral surface of the ring gear over a wide range, which is preferable.

It is a perspective view showing typically the structure of the engine in a 1st embodiment of the present invention. It is a schematic structure figure explaining the operation of the engine in a 1st embodiment of the present invention, and shows the state where the piston went up most. It is a schematic structure figure explaining the operation of the engine in a 1st embodiment of the present invention, and shows the state where a piston is going down. It is a schematic block diagram explaining the operation | movement of the engine in 1st Embodiment of this invention, and shows the state which the piston fell down most. It is a schematic structure figure explaining the operation of the engine in a 1st embodiment of the present invention, and shows the state where a piston is going up. It is sectional drawing of the output-shaft direction which shows schematic structure of the engine in 1st Embodiment of this invention. It is a figure which represents typically the relationship between the reciprocating motion of the piston in the engine of 1st Embodiment of this invention, and the eccentric motion of a connection means and a ring gear. It is a schematic block diagram explaining the movement of the engine in 2nd Embodiment of this invention, and shows the state which the piston went up most. It is a schematic block diagram explaining the motion of the engine in 2nd Embodiment of this invention, and shows the state in which a piston is going down. It is a schematic block diagram explaining the operation | movement of the engine in 2nd Embodiment of this invention, and shows the state which the piston fell down most. It is a schematic block diagram explaining the movement of the engine in 2nd Embodiment of this invention, and shows the state in which a piston is going up. It is sectional drawing of the output-shaft direction which shows schematic structure of the engine in 2nd Embodiment of this invention. It is a figure which represents typically the relationship between the reciprocating motion of the piston in the engine of 1st Embodiment of this invention, and the eccentric motion of a connection means and a ring gear.

  Next, embodiments of the present invention will be described in detail with reference to the drawings. However, the present invention is not limited to this embodiment.

  FIG. 1 is a perspective view showing a schematic configuration of an engine according to the first embodiment of the present invention. 2 to 5 are cross-sectional views in the direction orthogonal to the output shaft showing the configuration of the engine in the first embodiment of the present invention. FIG. 6 is a view of the engine in the output shaft direction of FIGS. It is sectional drawing. In these figures, a fuel injection device and intake / exhaust valve drive devices required for engine operation, control means for performing air-fuel ratio control, ignition control, etc., lubrication means, cooling means, etc. The illustration is omitted.

  The engine in the present embodiment is a reciprocating engine mounted on a vehicle or the like, and while the piston 11 disposed so as to be capable of reciprocating in the cylinder 10 performs two reciprocations (four strokes), an intake process-a compression process-(ignition) ) -Expansion step-A so-called four-cycle engine that performs a series of steps consisting of an exhaust step.

  The engine rotates sequentially from the state shown in FIGS. 2 to 3, 4, and 5, and the rotation is continuously repeated from the state shown in FIG. 2. Therefore, FIG. 2 represents a state in which the piston 11 in the cylinder 10 has risen most (top dead center), and FIG. 4 represents a state in which the piston 11 in the cylinder 10 has descended most (bottom dead center). In addition, the thick line arrow in a figure shows the direction to which the "connection part 3b of the internal ring gear 3" as a connection means moves, and the white arrow shows the direction to which each gear moves. Reference numeral R in the figure indicates the center of the base portion on the ring gear 3 side of the connecting means, and is a maximum displacement point representing the amount of ring displacement due to the eccentric movement of the ring gear 3 (hereinafter the same).

  A cylindrical cylinder bore is formed in the cylinder 10 of the engine, and the upper part is a combustion chamber 13. On the upper side (cylinder head portion) of the combustion chamber 13 is an ignition plug 14 that ignites the fuel-air mixed gas (air mixture) in the cylinder 10 and an intake port (intake valve) that supplies the air-fuel mixture into the cylinder 10. 15) and an exhaust port (exhaust valve 16) for exhausting the air-fuel mixture after combustion. Reference numeral 1 in the figure is an output shaft, 12 is a piston pin, and 17 is a gear case corresponding to a conventional crankcase.

  A feature of the engine in the present embodiment is that a conventional crankshaft (crank means) is not used as a conversion means for converting the reciprocating motion of the piston 11 into a rotational motion. The engine of the present embodiment has a small-diameter pinion gear 2 fitted to the output shaft 1 and a large-diameter internal ring gear 3 that circulates around the pinion gear 2 while meshing with the pinion gear 2 as the reciprocation-rotation conversion means. A first planetary gear 4 and a second planetary gear 5 that support the eccentric movement of the internal ring gear 3 around the pinion gear 2, and a support plate 6 (support member) that pivotally supports the planetary gears 4 and 5. A conversion mechanism is formed.

  The pinion gear 2 is an external gear in which external teeth having a predetermined shape are formed on the outer peripheral surface, and the inner peripheral through hole is formed to have a diameter substantially equal to the outer diameter of the output shaft 1. Then, after being fitted to the outer periphery of the output shaft 1, the output shaft 1 is fixed to the output shaft 1 so as not to rotate by a key or the like (not shown).

  As shown in FIG. 1, the internal ring gear 3 includes a ring-shaped annular portion 3a and a triangular plate-shaped (Δ-shaped) connecting portion 3b (coupling means) extending so as to protrude from the outer peripheral surface of the annular portion 3a. It is composed of On the inner peripheral surface of the annular portion 3 a, inner teeth having a shape that meshes with the outer teeth of the pinion gear 2 are formed, and an eccentric movement around the pinion gear 2 is enabled.

  The connecting portion 3b is formed in a shape reaching the piston pin 12 of the piston 11, and the piston pin 12 is inserted into a through-hole provided in the tip portion 3c thereof, whereby the piston 11 reciprocates. The movement (vertical movement) is supported. Since the annular portion 3a and the connecting portion 3b are integrally formed by casting or the like, the annular portion 3a side base portion 3d of the connecting portion 3b has an arc shape that covers a part of the outer peripheral surface of the annular portion 3a. (See FIG. 1 and FIG. 2).

  The first planetary gear 4 and the second planetary gear 5 are external gears having external teeth of a predetermined shape formed on the outer peripheral surface, and are rod-shaped fixed to a support plate 6 to be described later in through holes on the inner periphery. By inserting a member (pin: reference numerals 6a and 6b see FIG. 6), the support plate 6 is rotatably supported. The planetary gears 4 and 5 are configured such that the second planetary gear 5 meshes with the internal ring gear 3 and the first planetary gear so that the first planetary gear 4 meshes with the pinion gear 2 and the second planetary gear 5. The pinion gear 2 is rotated in synchronism (synchronization) with the rotation of the pinion gear 2 and the eccentric movement of the internal ring gear 3 around the pinion gear 2.

  The support plate 6 that pivotally supports the first planetary gear 4 and the second planetary gear 5 has a substantially rectangular shape made of a metal plate or the like, and has one end side (fixed side) in the longitudinal direction of the output shaft 1. A hole having a diameter slightly larger than the outer diameter is formed, and on the other end side (rotation side), the pins 6a and 6b that pivotally support the first and second planetary gears 4 and 5 described above are provided at predetermined intervals. Two small holes are provided for fixing. Then, the hole on one end side is inserted into the output shaft 1 and is rotatably fitted to the output shaft 1, so that the pinion gear 2 (output) of the first planetary gear 4 and the second planetary gear 5 is output. The revolution around the axis 1) and the rotation of each of the planetary gears 4 and 5 in synchronization with the eccentric motion of the internal ring gear 3 are simultaneously enabled.

Next, the operation of the engine having the above configuration will be described.
In this engine, when the piston 11 descends in the cylinder 10, the air-fuel mixture is sucked into the combustion chamber 13 through the intake port (intake valve 15) or the like (intake stroke: FIG. 2 → FIG. 3 → FIG. 4). ). Then, the air-fuel mixture is compressed by the piston 11 moving up through the cylinder 10 through the intake stroke bottom dead center (FIG. 4) (compression stroke: FIG. 4 → FIG. 5 → FIG. 2).

  When the piston 11 approaches the vicinity of the top dead center of the compression stroke (FIG. 2), the air-fuel mixture is ignited by the spark plug 14, the air-fuel mixture burns, and the piston 11 is lowered by the combustion pressure (expansion stroke: again in FIG. 2 → FIG. 3 → FIG. 4). The air-fuel mixture after combustion rises again toward the top dead center of the intake stroke (FIG. 2) through the expansion stroke bottom dead center (FIG. 4), and thus through the exhaust port (exhaust valve 16). The exhaust gas is discharged into the atmosphere (exhaust stroke: again FIG. 4 → FIG. 5 → FIG. 2).

  At this time, the reciprocating motion of the piston 11 in the cylinder 10 is transmitted to the annular portion 3a via the connecting portion 3b of the internal ring gear 3, and the eccentric motion (circulation) around the pinion gear 2 of the internal ring gear 3 is performed. Converted. Further, the rotation of the pinion gear 2 due to the eccentricity of the internal ring gear 3 is transmitted to the output shaft 1 located on the inner periphery thereof and can be taken out as the output of the engine.

  Further, the piston 11 reciprocates in the cylinder 10 as the internal ring gear 3 rotates by further rotating a gear mechanism (reciprocation-rotation conversion means) including the internal ring gear 3 by inertia force. to continue. Then, the internal ring gear 3 makes two rounds around the pinion gear 2 so that the piston 11 makes two reciprocations (four strokes). ) Is performed, and one ignition explosion is performed in the combustion chamber 13.

  FIG. 7 schematically shows the relationship between the reciprocating motion of the piston 11, the eccentric motion of the internal ring gear 3, and the movement of the connecting portion 3b (connecting means) of the internal ring gear 3 as described above. FIG.

In this figure, points P _{0 to} P ₃ are points indicating the center of the piston pin 12 of the piston 11 and the tip 3c of the connecting means (connecting portion 3b of the internal ring gear 3). Motion trajectory). Points R _{0 to} R ₃ are points indicating the center of the base of the connecting means (the connecting portion 3 b of the internal ring gear 3) and the maximum displacement point of the internal ring gear 3, and the eccentric movement of the internal ring gear 3. Represents the trajectory. A point O is a point indicating the center of rotation of the output shaft 1 and the pinion gear 2, respectively point A ₀ to A ₃ and the point B ₀ .about.B ₃ is rotation of the first planetary gear 4 and the second planetary gear 5 This is a point indicating the center, and represents the revolution trajectory of the planetary gears 4 and 5 around the pinion gear 2. Note that the subscripts ₀ , ₁ , ₂ , and ₃ of each point code such as P ₀ , P ₁ , P ₂ , and P ₃ are the above-described FIG. 2 (top dead center), FIG. 3 and FIG. This corresponds to the state of FIG. 5 (the same applies hereinafter).

As can be seen from this figure, since the tip 3c of the ring gear connecting part 3b is connected to the piston pin 12 portion of the piston 11 as a connecting means, for example, the state of FIG. 2 (top dead center: R ₀ ) Thus, the internal ring gear 3 that has received the combustion pressure due to the combustion of the air-fuel mixture in the combustion chamber 13 via the piston 11 and the connecting portion 3b does not rotate and is displaced to the right in the figure (eccentricity: R ₀ → R ₁ → R ₂ ), and the pinion gear 2 and the output shaft 1 are rotated according to the displacement.

In addition, after the state of FIG. 4 (bottom dead center: R ₃ ) has elapsed, the tip 3c of the ring gear connection 3b is connected to the piston pin 12 portion of the piston 11 in the same manner. The tooth ring gear 3 does not rotate due to the eccentric motion inertia of the internal ring gear 3 and the rotational inertia force of the gears 2, 4, 5 (decentration: R ₂ → R ₃ → R). ₀ ), and the piston 11 connected to the tip 3c of the ring gear connecting portion 3b is pushed up according to the displacement.

  In this manner, in the engine according to the present embodiment, the piston 11 reciprocates twice (four strokes) while the internal ring gear 3 makes two revolutions around the pinion gear 2, and during this time, the intake stroke, the compression stroke, and the expansion stroke. , A series of four strokes (four cycles) including an exhaust stroke is performed. Since this engine converts the reciprocating motion of the piston 11 into the rotation of the pinion gear 2 by the eccentric motion of the internal ring gear 3, the conversion means (crank means) using a conventional crankshaft and its rotation ( When the radius is the same, the stroke (reciprocation stroke length) of the piston 11 is halved compared to the crank means.

  With the above configuration, the engine according to the present embodiment can efficiently convert the reciprocating motion of the piston 11 into a rotational motion without using a complicated and expensive crankshaft. In addition, since a heavy crankshaft is not used, it is possible to reduce the weight and cost of the engine.

  Further, in this engine, the connecting rod (connecting rod) in the conventional engine is integrally formed as a triangular plate-shaped (Δ-shaped) connecting portion 3b on the outer periphery of the internal ring gear 3, thereby reducing the number of parts of the engine. In addition, it is possible to disperse and support the stress without receiving at one point the force resulting from the reciprocating motion of the piston 11. Therefore, the engine according to the present embodiment can improve its life as well as cost reduction.

  Note that the gear mechanism (reciprocation-rotation conversion means) including the internal ring gear 3 in the engine of this embodiment is a multi-cylinder engine, particularly in the case of an in-line multi-cylinder engine, between the crank arm and the crank arm. Compared to a conventional crankshaft in which a crankpin portion must be provided, the axial length of the output shaft (shaft, journal) can be designed to be shorter. Therefore, the engine in the present embodiment can be configured compactly with a shorter output shaft direction length than a conventional engine.

Next, a second embodiment of the present invention will be described.
8 to 11 are sectional views in the direction orthogonal to the output shaft showing the configuration of the engine according to the second embodiment of the present invention, and FIG. 12 is a sectional view in the output shaft direction of the engine in FIG. In these figures, as in the first embodiment, supply / exhaust means such as a fuel injection device and intake / exhaust valve drive device necessary for engine operation, control means for performing air-fuel ratio control, ignition control, etc., and lubrication The means, the cooling means, etc. are not shown. Moreover, the same code | symbol is attached | subjected to the structural member which has the same function as 1st Embodiment, and the detailed description is abbreviate | omitted.

  The engine in the present embodiment is also a reciprocating engine mounted on a vehicle or the like, and while the piston 11 disposed in the cylinder 10 so as to be capable of reciprocating is reciprocated twice (four strokes), the intake process-compression process-(ignition) ) -Expansion step-A so-called four-cycle engine that performs a series of steps consisting of an exhaust step. The same is true in that the conventional crankshaft (crank means) is not used as the conversion means for converting the reciprocating motion of the piston 11 into the rotational motion.

  The engine in this embodiment is equipped with a reciprocating motion-rotating motion converting means different from the engine in the first embodiment. The engine of the present embodiment includes a small-diameter pinion gear 2 fitted to the output shaft 1, a large-diameter inner / outer tooth ring gear 7 that circulates around the pinion gear 2 and the inner / outer teeth as the conversion means. A conversion mechanism is formed which includes guide gears 8 and 8 for guiding the eccentric motion of the ring gear 7 around the pinion gear 2 and a support plate 9 (support member) for pivotally supporting the guide gears 8 and 8.

  The internal / external tooth ring gear 7 includes a ring-shaped annular portion 7a and a triangular plate-shaped (Δ-shaped) connecting portion 7b (connecting means) extending so as to protrude from the outer peripheral surface of the annular portion 7a. Similar to the internal ring gear 3 in the first embodiment, internal teeth having a shape that meshes with the external teeth of the pinion gear 2 are formed on the inner peripheral surface of the annular portion 7a, and eccentric movement around the pinion gear 2 is performed. (Refer to the connecting portion 3b in FIG. 1 for the shape of the connecting portion 7b).

  Further, as shown in FIG. 12, external teeth meshing with the respective guide gears 8 and 8 are respectively formed at the end portions 7e and 7e on both sides in the axial direction on the outer peripheral surface of the annular portion 7a. A connecting portion 7b reaching the piston pin 12 of the piston 11 is formed in the axial center portion 7f. By inserting the piston pin 12 through a through hole provided in the tip portion 7c, the piston 11 The reciprocating motion (vertical motion) is supported. Since the annular portion 7a and the connecting portion 7b are integrally formed by casting or the like as in the first embodiment, the annular portion 7a side base portion 7d of the connecting portion 7b is the outer peripheral surface of the annular portion 7a. It has an arc shape that covers a part of

  The guide gear 8 is an external gear having external teeth of a predetermined shape formed on the outer peripheral surface, and a rod-like member (pin: reference numeral 9a) fixed to a support plate 9 described later in an inner peripheral through hole. Are inserted into the support plates 9 and 9 so as to be rotatable. Since these guide gears 8 and 8 revolve around the pinion gear 2 while meshing with the internal and external tooth ring gear 7, according to the eccentricity of the internal and external tooth ring gear 7, as shown in FIG. 8 → FIG. 9 → FIG. 10 → FIG. Change its position to. For this reason, the guide gears 8 and 8 guide the eccentric motion of the inner and outer toothed ring gear 7 and also serve as a balancer for balancing the eccentric motion (rotation).

  The support plate 9 that pivotally supports the guide gear 8 has a substantially rectangular shape made of a metal plate or the like, and has a hole having a diameter slightly larger than the outer diameter of the output shaft 1 at one end side (fixed side) in the longitudinal direction. The other end (rotation side) is formed with a small hole for fixing the pin 9a that pivotally supports the guide gear 8 described above. Then, the pinion gear of the guide gear 8 is synchronized with the eccentric movement of the inner and outer toothed ring gear 7 by inserting the hole on the one end side into the output shaft 1 and being rotatably fitted to the output shaft 1. Two revolutions are possible.

  Also in the engine having the above-described configuration, the internal and external tooth ring gear 7 makes two rounds around the pinion gear 2 so that the piston 11 makes two reciprocations (four strokes). During this time, a series of intake strokes, compression strokes, expansion strokes, and exhaust strokes. Four strokes (four cycles) are performed, and one ignition explosion is performed in the combustion chamber 13.

  At this time, the reciprocating motion of the piston 11 in the cylinder 10 is transmitted to the annular portion 7a via the connecting portion 7b of the inner and outer tooth ring gear 7, and the eccentric motion (circulation) around the pinion gear 2 of the inner and outer tooth ring gear 7 is performed. Converted. The rotation of the pinion gear 2 due to the eccentricity of the inner and outer tooth ring gear 7 is transmitted to the output shaft 1 located on the inner periphery thereof and can be taken out as an engine output. As the gear mechanism (reciprocating motion-rotating motion converting means) including the motor further rotates by the inertial force, the cylinder 10 can continue to reciprocate with the rotation of the internal / external tooth ring gear 7, and the operation can be continued.

  FIG. 13 schematically shows the relationship between the reciprocating motion of the piston 11 and the eccentric motion of the internal / external tooth ring gear 7 and the movement of the connecting portion 7b (coupling means) of the internal / external tooth ring gear 7 as described above. FIG.

As in FIG. 6 in the first embodiment, in this figure, points P _{0 to} P ₃ are points indicating the center of the piston pin 12 and the tip 7c of the connecting means (connecting portion 7b). Indicates the movement (trajectory of vertical movement). Points R _{0 to} R ₃ are points indicating the center of the base of the coupling means (connecting portion 7 b) and the maximum displacement point of the internal and external tooth ring gear 7, and represent the locus of the eccentric motion of the internal and external tooth ring gear 7. Point O is a point indicating the rotation center of the output shaft 1 and the pinion gear 2, and points C _{0 to} C ₃ are points indicating the rotation center of the guide gear 8. The guide gear 8 has a revolution orbit around the pinion gear 2. It represents. The subscripts 0, 1, 2, and 3 for each point code correspond to the states shown in FIG. 8 (top dead center), FIG. 9, FIG. 10 (bottom dead center), and FIG. ).

Also in this figure, since the tip 7c of the ring gear connecting portion 7b is connected to the piston pin 12 portion of the piston 11 as a connecting means, for example, in the state shown in FIG. 8 (top dead center: R ₀ ), The internal and external tooth ring gear 7 that has received the combustion pressure due to the combustion of the air-fuel mixture in the combustion chamber 13 via the piston 11 and the connecting portion 7b does not rotate but is displaced to the right in the figure (eccentric: R ₀ → R ₁ → R ₂ ) is started, and the pinion gear 2 and the output shaft 1 are rotated according to the displacement.

Further, after the state of FIG. 10 (bottom dead center: R ₃ ) has elapsed, the tip 7c of the ring gear connecting portion 7b is connected to the piston pin 12 portion of the piston 11 in the same manner. The tooth ring gear 7 is displaced to the left in the figure without being rotated by the inertia of the eccentric motion of the inner and outer tooth ring gear 7 and the inertial force of the rotation of the gears 2 and 8 (eccentricity: R ₂ → R ₃ → R ₀ ). In accordance with the displacement, the piston 11 connected to the tip portion 7c of the ring gear connection portion 7b is pushed up.

  In this way, in the engine according to the present embodiment as well, the piston 11 reciprocates twice (four strokes) while the inner and outer tooth ring gear 7 makes two rounds around the pinion gear 2, and during this time, the intake stroke, the compression stroke, and the expansion stroke , A series of four strokes (four cycles) including an exhaust stroke is performed. This engine also converts the reciprocating motion of the piston 11 into the rotation of the pinion gear 2 by the eccentric motion of the internal and external toothed ring gear 7, so that the conversion means (crank means) using a conventional crankshaft and its rotation ( When the radius is the same, the stroke (reciprocation stroke length) of the piston 11 is halved compared to the crank means.

  With the configuration described above, the engine in the present embodiment can also efficiently convert the reciprocating motion of the piston 11 into a rotational motion without using a complicated and expensive crankshaft. In addition, since a heavy crankshaft is not used, it is possible to reduce the weight and cost of the engine.

  Further, in this engine, the connecting rod (connecting rod) in the conventional engine is integrally formed as a triangular plate-shaped (Δ-shaped) connecting portion 7b on the outer periphery of the inner and outer toothed ring gear 7, thereby reducing the number of parts of the engine. In addition, it is possible to disperse and support the stress without receiving at one point the force resulting from the reciprocating motion of the piston 11. Therefore, the engine according to the present embodiment can improve its life as well as cost reduction.

  In the above-described two embodiments, the connecting portions 3b, 7c extending from the outer peripheral surfaces of the ring gears 3, 7 are used as connecting means between the piston 11 and the ring gears 3, 7. Instead of these connecting portions 3b and 7c, the outer peripheral surfaces of the ring gears 3 and 7 are provided with ear-like convex portions having holes through which pins can be inserted, and connecting rods (connecting rods) having the same shape as before. And the pin inserted into the hole of the convex portion and the piston pin 12 may be connected.

  In the above embodiment, only one cylinder of a 4-cycle reciprocating engine is illustrated. However, the present invention is applicable to any type of piston that reciprocates a piston, such as a 4-cycle engine, a 2-cycle engine, and a diesel engine. It can also be applied to multi-cylinder engines of the type.

  The engine of the present invention is suitable for an engine mounted on equipment that is lightweight, compact, and requires low fuel consumption, such as for vehicles and agricultural machinery.

1 Output shaft 2 Pinion gear 3 Internal ring gear 4 First planetary gear 5 Second planetary gear 6 Support plate 10 Cylinder 11 Piston

Claims (4)

  A cylinder, a piston that reciprocates in the cylinder, a coupling means having one end pivotably coupled to the piston via a pin, and a rotational movement of the output shaft connected to the other end of the coupling means An engine having a conversion means for providing a pinion gear fitted and fixed to the output shaft, an internal gear ring gear that meshes with the pinion gear and rotates around the pinion gear, A first planetary gear disposed inside the tooth ring gear and revolving around the pinion gear while meshing with the pinion gear, and disposed between the first planetary gear and the internal ring gear, and the first planetary gear A second planetary gear that revolves on a track centered on the pinion gear while meshing with an internal ring gear, and one end side of which is rotatable on the output shaft The other end of the connecting means is connected to a connecting portion provided on an outer peripheral surface or an end surface of the internal ring gear. Engine characterized by being.   A cylinder, a piston that reciprocates in the cylinder, a coupling means having one end pivotably coupled to the piston via a pin, and a rotational movement of the output shaft connected to the other end of the coupling means An engine having a conversion means for providing a pinion gear fitted and fixed to the output shaft, and a ring-shaped ring that is wide in the axial direction of the output shaft, and the inner peripheral surface of the pinion gear. Inner teeth meshing with the pinion gear are formed, outer teeth are formed in the regions on both ends in the axial direction on the outer peripheral surface, and a connecting portion with the coupling means is formed in the region in the axial central portion on the outer peripheral surface. An inner and outer tooth ring gear meshing with the pinion gear and rotating around the pinion gear, and revolving around the inner and outer tooth ring gear while meshing with each outer tooth of the inner and outer tooth ring gear 2 And a support member that pivotally supports one end of the guide gear in a state where the one end side is rotatably fitted to the output shaft and the other end side meshes the guide gear with the external teeth of the internal and external tooth ring gears. An engine characterized in that the other end of the coupling means is connected to a connecting portion provided on an outer peripheral surface.   The engine according to claim 1 or 2, wherein the connecting means is formed integrally with the ring gear by extending a connecting portion of the ring gear, and the piston is connected to a tip portion of the connecting portion.   The engine according to claim 3, wherein a ring gear side base portion of a connection portion extending from the ring gear is formed in an arc shape covering a part of an outer peripheral surface of the ring gear in a circumferential direction.

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