JP2022107973A - Rotary revolution conversion mechanism and reciprocating engine - Google Patents

Abstract

To provide a rotary revolution conversion mechanism which has high flexibility of design of a revolving track of revolving motion, and to provide a reciprocating engine.SOLUTION: A rotary revolution conversion mechanism 20 mutually converts rotative motion of a rotary shaft 21 and revolving motion of a revolving shaft 22 to transmit power and includes: an annular groove 23 which encloses the rotary shaft 21; and a node 24 which is fixed to the rotary shaft 21 and rotationally moves around the rotary shaft 21. The annular groove 23 forms an annular shape, and the node 24 has: a revolution arm part 24a; and a revolution elongated hole 24c which is placed at one end part on the side of the annular groove 23 of the revolution arm part 24a, arranged in a manner that its longitudinal direction is set in an extensin direction of the revolution arm part 24a, and overlaps with the annular groove 23 constantly. The revolving shaft 22 is inserted into the annular groove 23 and the revolution elongated hole 24c.SELECTED DRAWING: Figure 1

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotation/circulation conversion mechanism and a reciprocating engine, and more particularly, a rotation/circulation conversion mechanism that mutually converts and transmits the rotary motion of a rotary shaft and the rotary motion of a rotary shaft that revolves around the rotary shaft. It relates to a reciprocating engine provided with the rotation rotation conversion mechanism.

A reciprocating engine such as an internal combustion engine is equipped with a mechanism that mutually converts the reciprocating linear motion of the piston and the rotary motion of the rotating shaft. A crankshaft having a pin structure is essential (see, for example, Patent Document 1).

Patent No. 5632962

In the crankshaft, the orbit of the crankpin is limited to a perfect circular orbit when viewed in the axial direction of the rotating shaft. Therefore, in the mechanism having the crankshaft, there is a problem that the degree of freedom in designing the orbit of the crankpin is low.

An object of the present disclosure is to provide a rotation orbit conversion mechanism and a reciprocating engine with a high degree of freedom in designing the orbit of the orbital motion.

A rotation orbit conversion mechanism according to one aspect of the present invention that achieves the above objects converts the rotational motion of a rotating shaft and the orbital motion of a orbiting shaft that revolves around the rotating shaft when viewed in the axial direction of the rotating shaft. a rotation rotation conversion mechanism for transmitting power through a rotary shaft, comprising: an annular groove surrounding the rotation shaft when viewed in the axial direction of the rotation shaft; and a node fixed to the rotation shaft and rotating around the rotation shaft, The annular groove has an annular shape, and the node is disposed at a winding arm extending beyond the annular groove from the rotating shaft and at one end of the winding arm on the annular groove side. and an elongated circling hole whose longitudinal direction is oriented in the extending direction of the arm portion and which overlaps with the annular groove, and the circulating shaft is inserted through both the annular groove and the elongated circulating hole. characterized by

A reciprocating engine according to one aspect of the present invention that achieves the above object comprises the above-described rotation/circulation conversion mechanism, a piston arranged inside a cylinder and performing reciprocating linear motion, the reciprocating linear motion of the piston and the reciprocating motion. a direct-acting orbital conversion mechanism for mutually converting the orbital motion of the shaft.

According to one aspect of the present invention, the orbital motion of the orbital shaft along the annular groove and the rotational motion of the rotating shaft can be mutually converted by the rotational motion of the nodes, and the shape of the annular groove allows the orbital path of the orbital shaft to be true. Can be constrained to trajectories other than circular trajectories. As a result, it is possible to increase the degree of freedom in designing the circling orbit of the circulating shaft.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view illustrating a rotation cycle conversion mechanism of an embodiment and a reciprocating engine of an embodiment provided with the rotation cycle conversion mechanism; It is the front view which looked at the rotation rotation rotation conversion mechanism of FIG. 1 in the axial direction of the rotating shaft. 3 is a cross-sectional view indicated by arrow III in FIG. 2; FIG. FIG. 3 is a front view of a rotation rotation conversion mechanism illustrating a first modified example of the node in FIG. 2; FIG. 3 is a front view of a rotation rotation conversion mechanism illustrating a second modified example of the node in FIG. 2; FIG. 2 is a relationship diagram illustrating the relationship between the rotation angle of a rotating shaft and the position of a piston in the X-axis direction in the reciprocating engine of FIG. 1; FIG. 4 is a front view of a rotation rotation conversion mechanism illustrating a first modified example of the annular groove of FIG. 2; FIG. 10 is a front view of a rotation rotation conversion mechanism illustrating a second modified example of the annular groove of FIG. 2; FIG. 2 is a perspective view of a reciprocating engine illustrating a modification of the linear motion rotation conversion mechanism of FIG. 1;

Embodiments of the rotation rotation conversion mechanism and the reciprocating engine in the present disclosure will be described below. In the figure, the direction of reciprocating linear motion of the piston 11 of the reciprocating engine 10 is the X direction, the axial direction of the output shaft 12 of the reciprocating engine 10 is the axial direction of the rotating shaft 21 of the rotation rotation conversion mechanism 20, and the Z direction is the axial direction. and the direction perpendicular to both the X and Z directions is the Y direction. In the drawings, the side of the piston 11 in the Z direction is the front side, and the opposite side is the back side. In the figure, solid line arrows indicate the operation of each member, and dotted line arrows indicate the dimensions of each member. In the drawings, the dimensions are changed so as to make the configuration easier to understand, and the ratios do not necessarily match the ratios of those actually manufactured.

In the present disclosure, reciprocating linear motion refers to linear reciprocating motion of an object, and in this embodiment, it is motion performed by the piston 11 . Rotational motion refers to a motion in which an object rotates in a perfect circle around its own axis. This is the motion performed by the joint 24 that rotates as Orbital motion is different from rotary motion in that an object revolves around an axis that exists at a distance from itself, and in this embodiment, it is the motion performed by the orbital axis 22 . It should be noted that the orbit of the orbiting object is not limited to a perfect circle.

As illustrated in FIG. 1, the reciprocating engine 10 of the embodiment is a prime mover powered by the reciprocating linear motion of a piston 11, and includes a piston 11, an output shaft 12, a linear motion rotation conversion mechanism 13, a transmission device 14, and a , and a rotation rotation conversion mechanism 20 . As the reciprocating engine 10, an internal combustion engine such as a gasoline engine or a diesel engine is exemplified.

The piston 11 is arranged inside a cylinder (not shown) and has a cylindrical shape with its axial direction directed in the X direction. I do. The output shaft 12 extends in the Z direction and is a rotation shaft with a specific bending that does not bend in the X direction or the Y direction, and outputs rotational power to a drive mechanism such as a transmission or a propulsion shaft (not shown) or rotates from the drive mechanism. Power is input. The linear motion rotation conversion mechanism 13 is a mechanism that is connected to each of the piston 11 and the rotation shaft 22 and converts the reciprocating linear motion of the piston 11 and the rotation motion of the rotation shaft 22 to each other.

The transmission device 14 connects the output shaft 12 and the rotary shaft 21 so that their respective rotary powers can be mutually transmitted. As the transmission device 14, a gear transmission device and a winding transmission device are exemplified. The gear transmission has at least two gears, which are fixed to the output shaft 12 and the rotary shaft 21, respectively, and mesh directly or indirectly with each other. The winding transmission device consists of pulleys or sprockets fixed to the output shaft 12 and the rotating shaft 21, respectively, and endless belts or chains. A belt is wound around each pulley or a chain is wound around each sprocket. consists of

The linear motion rotation conversion mechanism 13 includes a connecting rod 15 , a support member 16 , a first sliding member 17 and a second sliding member 18 . The connecting rod 15 extends in the X direction and has one end fixed to the lower end of the piston 11 and the other end fixed to the first sliding member 17 . The support member 16 supports the first slide member 17 in a slidable cantilever manner. The first sliding member 17 has at least an arm extending in the Y direction, and linearly reciprocates along the support member 16 in the X direction. The second sliding member 18 is slidably supported by the arm portion extending in the Y direction of the first sliding member 17, and is loosely fitted with the rotating shaft 22. As shown in FIG. The second sliding member 18 linearly reciprocates along the first sliding member 17 in the Y direction while linearly reciprocating in the X direction together with the first sliding member 17 .

A plurality of supporting members 16 may be provided, and may be arranged at both ends of the first sliding member 17 in the Y direction to slidably support both ends of the first sliding member 17 . Further, when the first sliding member 17 is cantilevered, it is not limited to an L shape when viewed in the Z direction, and may be a T shape. good.

According to the linear motion rotation conversion mechanism 13 , the connecting rod 15 connected to the piston 11 performs only reciprocating linear motion, so that inclination of the posture of the piston 11 can be suppressed. Therefore, the side pressure of the piston 11 acting on the cylinder can be reduced. This is advantageous for reducing the frictional resistance in the reciprocating linear motion of the piston 11 . In addition, the connection between the piston 11 and the connecting rod 15 can be fixed, eliminating the need for a piston pin and simplifying the structure of the piston 11 .

The rotation orbit conversion mechanism 20 is provided in the reciprocating engine 10, and is a link mechanism capable of mutually converting the orbital motion of the orbital shaft 22 obtained by converting the reciprocating linear motion of the piston 11 and the rotational motion of the rotating shaft 21. . The rotation orbit conversion mechanism 20 includes an annular groove 23 , a node 24 , an adjustment shaft 25 , a bearing 26 , a lid 27 and a retaining member 28 .

The rotating shaft 21 extends in the Z direction and rotates about the axis. One end of the rotating shaft 21 on the front side in the Z direction is fixed to a node 24 , the midway position is rotatably supported by a bearing 26 , and the other end on the back side in the Z direction supplies rotational power to the output shaft 12 via the transmission device 14 . communicatively coupled. The rotating shaft 21 is arranged at the midpoint of the X-direction reciprocating linear motion of the first sliding member 17 and the midpoint of the Y-direction reciprocating linear motion of the second sliding member 18 in the linear motion rotation conversion mechanism 13 .

The rotating shaft 22 extends in the Z direction and is a member that rotates along the annular groove 23 around the rotating shaft 21 as viewed in the Z direction. One end on the front side in the Z direction of the circulating shaft 22 is loosely fitted in the second sliding member 18 of the direct-acting circulating conversion mechanism 13, and an elongated circulating hole 24c formed in the circulating arm portion 24a of the node 24 is formed in the intermediate position. It is inserted into both of the annular grooves 23 and has a retaining member 28 at the other end on the back side in the Z direction. The circling shaft 22 has an enlarged diameter portion at an intermediate position that is larger in diameter than the shaft diameter. It may have a function of suppressing.

As illustrated in FIG. 2, the annular groove 23 is a groove that surrounds the rotating shaft 21 as viewed in the Z direction and is recessed from the front side to the back side in the Z direction. The annular groove 23 is formed by fixing the lid 27 to the bearing 26, and is a gap between the outer peripheral surface of the protrusion 26a of the bearing 26 and the inner peripheral surface of the through hole 27a of the lid 27, which face each other in the annular radial direction. Configured. The annular groove 23 has an annular shape other than a perfectly circular annular shape when viewed in the Z direction. In the present disclosure, a perfect circle means a perfect circle around the rotation axis 21 . The annular groove 23 of this embodiment has an elliptical ring shape with a short axis directed in the X direction and a long axis directed in the Y direction when viewed in the Z direction.

The annular groove 23 is divided into a top dead center section 23a, a bottom dead center section 23b, and sections 23c and 23d other than those sections. The top dead center section 23a is a section including at least a section in which the rotation shaft 22 moves while the piston 11 is positioned near the top dead center. The bottom dead center section 23b is a section including at least a section in which the rotation shaft 22 moves while the piston 11 is positioned near the bottom dead center. In the present disclosure, positioning the piston 11 near the top dead center (or bottom dead center) includes positioning the piston 11 at the top dead center (or bottom dead center). For example, the term "while the piston 11 is positioned near the top dead center (or bottom dead center)" refers to 30 degrees before the top dead center (or bottom dead center) in terms of the rotation angle of the rotary shaft 21 with respect to the top dead center (or bottom dead center). ~ 30° after top dead center (or bottom dead center) and including top dead center (or bottom dead center) is exemplified. The annular groove 23 of this embodiment has an elliptical ring shape with a minor axis directed in the X direction and a major axis directed in the Y direction. also forms an arc shape with a small curvature.

The joint 24 is a plate-like member that is fixed to one end of the rotating shaft 21, rotates around the rotating shaft 21, and has a thickness direction in the Z direction. The node 24 is configured with a winding arm portion 24a, an adjusting arm portion 24b, a winding slot 24c, and an adjusting slot 24d. The shape of the node 24 of this embodiment as viewed in the Z direction is a rectangle, and the rotating shaft 21 is fixed at the center thereof. The shape of the node 24 as viewed in the Z direction is not limited to a rectangle, and can be modified as appropriate. It is desirable that the node 24 be separated from the bearing 26 and the lid 27 .

Each of the circulating arm portion 24a and the adjusting arm portion 24b is a portion that extends from the rotating shaft 21 toward the outside in the axial radial direction of the rotating shaft 21 until it exceeds the annular groove 23 as viewed in the Z direction. A plurality of arm portions of the winding arm portion 24a and the adjusting arm portion 24b are arranged at equal intervals in the rotational circumferential direction of the node 24. As shown in FIG. When the plurality of arms are composed of two arms, ie, the rotating arm portion 24a and the adjusting arm portion 24b, the rotating arm portion 24a and the adjusting arm portion 24b are arranged point-symmetrically with respect to the rotation shaft 21. .

Each of the rounding slot 24c and the adjustment slot 24d is a slot whose longitudinal direction is oriented in the axial radial direction of the rotating shaft 21 when viewed in the Z direction and which always overlaps the annular groove 23 and passes through the node 24 in the Z direction. . The winding elongated hole 24c is arranged at the end of the winding arm portion 24a on the annular groove 23 side, and the winding shaft 22 is inserted therethrough. The adjustment slot 24d is arranged at the end of the adjustment arm 24b on the annular groove 23 side, and the adjustment shaft 25 is inserted therethrough.

It is desirable that both longitudinal ends of the winding elongated hole 24c and the adjusting elongated hole 24d are not in contact with the winding shaft 22 and the adjusting shaft 25, respectively. Specifically, it is desirable that the longitudinal length La of the rotation slot 24c and the adjustment slot 24d is longer than the difference between the maximum value Lmax and the minimum value Lmin of the distance from the rotation shaft 21 . By adjusting the length La in this way, the winding elongated hole 24c and the adjusting elongated hole 24d always overlap the annular groove 23, and both ends in the longitudinal direction are out of contact with the winding shaft 22 and the adjusting shaft 25. . As a result, the contact between the winding shaft 22 or the adjustment shaft 25 and the node 24 is only in the winding direction, which is advantageous in reducing transmission efficiency and noise caused by contact.

The adjustment shaft 25 extends in the Z direction, one end in the Z direction protrudes from the annular groove 23 , the midway position is inserted into the annular groove 23 , and the other end has a retaining member 28 . The adjustment shaft 25 functions as a counterweight. The weight of the adjustment shaft 25 can be appropriately adjusted depending on the shaft length and material. One end of the adjusting shaft 25 may have a shape with an enlarged diameter relative to the shaft.

As illustrated in FIG. 3, the bearing 26 is a member that rotatably supports the rotating shaft 21 and constitutes a part of the annular groove 23, and has a protrusion 26a, an inner recess 26b, and a shaft hole 26c. consists of The projecting portion 26a is arranged in the central portion when viewed in the Z direction, and protrudes from the back side in the Z direction toward the front side. The inner recess 26b is formed over the entire circumference of the Z-direction back side of the outer peripheral surface of the projecting portion 26a, and is recessed inward from the outer peripheral surface. The shaft hole 26c is arranged in the center of the protrusion 26a and passes through the bearing 26 in the Z direction.

The lid 27 is a member that is fixed to the bearing 26 and constitutes a part of the annular groove 23, and has a through hole 27a and an outer recess 27b. The through hole 27a is arranged in the central portion when viewed in the Z direction and penetrates the lid 27 in the Z direction. The outer recess 27b is formed over the entire circumference of the Z-direction back side of the inner peripheral surface of the through hole 27a, and is recessed outward from the inner peripheral surface.

When the lid 27 is fixed to the bearing 26, a gap is formed between the outer peripheral surface of the protrusion 26a of the bearing 26 and the inner peripheral surface of the through hole 27a of the lid 27, which face each other in the ring radial direction of the annular groove 23. This gap becomes the annular groove 23 . Also, the inner recess 26b and the outer recess 27b are arranged to face each other with the annular groove 23 interposed therebetween.

The retaining member 28 is a member that is fixed to the other end portion on the back side in the Z direction of the rotating shaft 22 and the adjusting shaft 25 . The retaining member 28 has a diameter larger than that of the rotating shaft 22 and the adjusting shaft 25, and is accommodated in the inner recess 26b and the outer recess 27b. The retaining member 28 may have a diameter larger than the diameter of each shaft, and the retaining member 28 may be composed of a roller bearing.

The action of the reciprocating engine 10 will be described. When pressure acts on the crown surface of the piston 11, power is transmitted to the piston 11, the direct-acting rotation conversion mechanism 13, the rotation rotation conversion mechanism 20, and the output shaft 12 in this order.

Specifically, when pressure acts on the crown surface of the piston 11, the piston 11 performs reciprocating linear motion in the X direction. Next, the first sliding member 17 linearly reciprocates in the X direction, and the second sliding member 18 reciprocates linearly along the first sliding member 17 in the X direction along with the first sliding member 17 in the Y direction. reciprocating linear motion. The reciprocating linear motion of the first sliding member 17 in the X direction and the reciprocating linear motion of the second sliding member 18 in the Y direction cause the reciprocating linear motion of the piston 11 to revolve around the revolving shaft 22 . Convert to exercise.

The circling shaft 22 then circulates along the annular groove 23 . Next, the joint 24 rotates around the rotary shaft 21 as the rotary shaft 22 rotates, and as the rotary shaft 24 rotates, the rotary shaft 21 rotates and the adjusting shaft 25 rotates along the annular groove 23. . The circulating shaft 22 circulates in the annular groove 23 while longitudinally reciprocating through the circulating elongated hole 24c, and the adjusting shaft 25 similarly circulates in the annular groove 23 while reciprocatingly longitudinally reciprocating through the regulating elongated hole 24d. The rotary orbit conversion mechanism 20 constrains the orbit of the orbital shaft 22 to an elliptical orbit and converts the orbital motion into the rotational motion of the rotary shaft 21 . Next, the rotational power of the rotary shaft 21 is transmitted to the output shaft 12 by the transmission device 14 to rotate the output shaft 12, and the rotational power is transmitted to a drive mechanism (not shown).

When no pressure is applied to the crown surface of the piston 11 and rotational power is transmitted from the drive mechanism to the output shaft 12, the rotating shaft 21, the node 24, the orbiting shaft 22, and the linear motion shaft 21, the joint 24, the orbiting shaft 22, and the direct-acting Power is transmitted to the rotation conversion mechanism 13 and the piston 11 in this order.

As described above, in the rotary rotation conversion mechanism 20 of the present embodiment, the rotary motion of the rotary shaft 22 along the annular groove 23 and the rotary motion of the rotary shaft 21 can be mutually converted by the rotary motion of the joints 24. The shape of 23 can constrain the orbit of the orbital shaft 22 to an orbit other than a perfect circular orbit. This makes it possible to increase the degree of freedom in designing the orbit of the orbital motion. It should be noted that the rotary orbit conversion mechanism 20 can also make the orbit of the orbital shaft 22 a perfect circle by configuring the shape of the annular groove 23 in a perfect circle.

In addition, since the rotary rotation conversion mechanism 20 converts the rotary motion of the rotary shaft 21 and the rotary motion of the rotary shaft 22 only by the rotation of the joints 24, it becomes a simple link mechanism with a small number of links and joints. As a result, compared to a mechanism that converts rotary motion and orbital motion using gears or a complicated link mechanism with a large number of links and joints, in addition to being able to reduce the cost required for manufacturing, it is advantageous for reducing the kinetic mass. As a result, power transmission efficiency can be improved.

The joint 24 of the rotation/circulation conversion mechanism 20 may have only the circulating arm portion 24a and the circulating elongated hole 24c. It is desirable to have an adjustment slot 24d. In the rotation rotation conversion mechanism 20, the joint 24 has an adjusting arm portion 24b and an elongated adjusting hole 24d, and the adjusting shaft 25 is inserted through the elongated adjusting hole 24d and the annular groove 23, thereby acting a couple of forces on the joint 24. can be made As a result, the rotation of the joint 24 is balanced, and the joint 24 can smoothly rotate around the rotary shaft 21 .

As illustrated in FIGS. 4 and 5, the shape of the node 24 when viewed in the Z direction is not limited to the shape of this embodiment.

The node 24 of the first modified example of FIG. 4 has a cross shape when viewed in the Z direction, and has one orbiting arm 24a and three adjusting arms 24b. When viewed from the direction, they are arranged at regular intervals in the winding direction of the node 24 . In the joint 24 of the first modification, each of the three adjusting arms 24b is formed with an adjusting elongated hole 24d, and an adjusting shaft 25 is inserted through each of the adjusting elongated holes 24d. The number of adjustment arms 24b is not particularly limited, but if the number is increased, the number of adjustment shafts 25 increases, resulting in an increase in weight, the number of parts, and frictional resistance in circular motion. Therefore, the number of adjusting arms 24b is preferably one.

In the node 24 of the second modification shown in FIG. 5, the space between the winding arm portion 24a having the winding elongated hole 24c and the adjusting arm portion 24b having the adjusting elongated hole 24d is filled, and when viewed in the Z direction, , and the winding elongated hole 24c and the adjustment elongated hole 24d are formed point-symmetrically with respect to the center of the circular node 24. As shown in FIG. In this way, the joint 24 may be configured in a circular shape or a regular polygonal shape in which the space between the arms adjacent to each other in the rotation circumferential direction is filled. When the node 24 is configured in a circular or regular polygonal shape and the rotating shaft 21 is arranged at its center of gravity, the node 24 functions as a force wheel (also called a flywheel). As a result, even if the piston 11 is positioned at the top dead center or the bottom dead center, the motion of each member can be smoothly stabilized by the moment of inertia of the joint 24 .

The annular groove 23 may be formed in the bearing 26 as a recess that is recessed in the Z direction without using the lid 27. It is desirable that the gap between the inner peripheral surface of 27a is formed. By forming the annular groove 23 with the bearing 26 and the lid 27 in this manner, a recess is formed in the annular groove 23 to accommodate the retaining member 28 fixed to the end of the rotating shaft 22 and the adjusting shaft 25 . can be formed. As a result, the circulating shaft 22 can be prevented from slipping out of the annular groove 23, and the circulating shaft 22 can be supported at both ends by the second sliding member 18 of the linear motion turning conversion mechanism 13 and the retaining member 28 housed in the recess. .

The reciprocating engine 10 of the present embodiment is provided with a rotation orbit conversion mechanism 20 that has a high degree of freedom in designing the orbit of the orbital motion, and by changing the orbit of the orbital motion to a trajectory other than a perfect circular orbit, the piston 11 can be The moving speed of the reciprocating linear motion can be decelerated in a predetermined section or increased in a predetermined section.

In the reciprocating engine 10, it is desirable that the annular groove 23 has an arc shape or a linear shape in which the shape of the top dead center section 23a as viewed in the Z direction has a smaller curvature than the other sections 23c and 23d. The annular groove 23 of this embodiment has an elliptical annular shape with a short axis directed in the direction of reciprocating linear motion of the piston 11 when viewed in the Z direction, and the curvature of the top dead center section 23a is the curvature of the other sections 23c and 23d. less than That is, while the rotary shaft 22 moves through the top dead center section 23a, the amount of reciprocating linear motion of the piston 11 is reduced, and the speed of the reciprocating linear motion of the piston 11 near the top dead center can be reduced. This is advantageous in suppressing the decrease in combustion efficiency that occurs as the piston 11 moves away from the top dead center, and a combustion cycle with a high degree of constant volume can be realized.

As illustrated in FIG. 6, the speed of the reciprocating linear motion of the piston 11 in the vicinity of the top dead center in the reciprocating engine 10 of the present embodiment indicated by the solid line is the top dead center of a conventionally known reciprocating engine using a crankshaft. It is slower than the speed of the reciprocating linear motion of the piston in the vicinity of the point. Therefore, according to the reciprocating engine 10 of the present embodiment, the combustion cycle has a higher degree of constant volume compared to a reciprocating engine using a crankshaft.

The minor axis of the ellipse of the annular groove 23 may be tilted from the reciprocating direction of the piston 11 so that the speed of the reciprocating linear motion of the piston 11 is reduced after the piston 11 is positioned at the top dead center. Alternatively, the long axis of the ellipse of the annular groove 23 may be oriented in the reciprocating direction of the piston 11 to increase the speed of the reciprocating linear motion of the piston 11 near the top dead center.

As exemplified in FIGS. 7 and 8, the shape of the annular groove 23 as viewed in the Z direction is not limited to an elliptical ring shape, and may be any shape that increases or decreases the reciprocating linear motion of the piston 11 in a predetermined interval. Just do it.

The annular groove 23 of the first modified example of FIG. 7 has an annular shape obtained by flattening a part of the perfectly circular annular shape. Specifically, in the annular groove 23 of the first modified example, the bottom dead center section 23b and the other sections 23c and 23d form an arc shape with a predetermined curvature, and the top dead center section 23a has a curvature smaller than the predetermined curvature. form an arc. In this manner, the annular groove 23 may reduce the curvature of the top dead center section 23a to reduce the speed of the reciprocating linear motion of the piston 11 in the vicinity of the top dead center.

The annular groove 23 of the second modified example of FIG. 8 has a rectangular annular shape with rounded corners. Specifically, the annular groove 23 of the second modification has a top dead center section 23a and a bottom dead center section 23b that are linear, and other sections 23c and 23d that are arc-shaped. In this manner, the top dead center section 23a forms a linear shape, and the piston 11 does not reciprocate linearly in the vicinity of the top dead center.

As illustrated in FIG. 9, the linear motion rotation conversion mechanism 13 is not limited to the configuration of this embodiment. A direct-acting rotation conversion mechanism 13 of this modification includes a connecting rod 15 , a support member 16 , a first sliding member 17 , and a swinging member 19 .

The connecting rod 15 extends in the X direction and has one end fixed to the lower end of the piston 11 and the other end fixed to the first sliding member 17 . The supporting member 16 slidably supports both ends of the first sliding member 17 . The first sliding member 17 has a columnar shape extending in the Z direction and linearly reciprocates along the support member 16 in the X direction. The rocking member 19 has one end arranged on the lower side in the X direction loosely fitted with the first sliding member 17 , and the other end arranged on the upper side in the X direction loosely fitted with the rotating shaft 22 . The swinging member 19 reciprocates linearly in the X direction together with the first sliding member 17, and the other end swings about one end thereof.

As in the embodiment, the direct-acting rotation conversion mechanism 13 of this modification can reduce the side pressure of the piston 11 acting on the cylinder, and the structure of the piston 11 is simplified. In the case of the linear motion rotation conversion mechanism 13 of this modified example, the rotating shaft 21 is arranged at the midpoint of the reciprocating linear motion of the swing member 19 in the X direction and the midpoint of the circular swing motion in the Y direction.

The reciprocating engine 10 of this embodiment may be configured as a multi-cylinder engine having a plurality of cylinders. In that case, the reciprocating engine 10 is provided with a piston 11, a rotary shaft 21, a linear motion rotation conversion mechanism 13, and a rotation rotation conversion mechanism 20 for each of the plurality of cylinders, and one of the rotation shafts 21 is provided. Each transmission device 14 is provided, and each transmission device 14 is configured to connect each rotating shaft 21 and one output shaft 12 so as to be capable of transmitting rotational power.

In a well-known multi-cylinder engine, a crankshaft is used to output the power generated in each cylinder as rotational power. can't Therefore, by providing the transmission device 14 for each rotating shaft, the power generated by each cylinder can be output from one output shaft 12 .

10 reciprocating engine 11 piston 12 output shaft 13 direct-acting rotation conversion mechanism 20 rotation rotation conversion mechanism 21 rotating shaft 22 rotation shaft 23 annular groove 24 node 24a rotation arm 24b adjustment arm 24c rotation long hole 24d adjustment length Hole 25 Adjusting shaft 26 Bearing 27 Lid 28 Retaining member

Claims (9)

In a rotation/circulation converting mechanism for mutually converting and transmitting the rotational motion of a rotating shaft and the orbital motion of a rotating shaft that revolves around the rotating shaft when viewed in the axial direction of the rotating shaft, the An annular groove surrounding a rotating shaft and a node fixed to the rotating shaft and rotating around the rotating shaft, the annular groove forming an annular shape, and the node extending from the rotating shaft to the annular A winding arm extending beyond the groove and a winding arm disposed at one end of the winding arm on the side of the annular groove and having a longitudinal direction in the extending direction of the winding arm always in the annular groove. A rotation/circulation converting mechanism, characterized in that it has overlapping slots for rotation, and the rotation shaft is inserted through both the annular groove and the slots for rotation. The longitudinal length of the orbiting elongated hole is longer than the difference between the maximum value and the minimum value of the distance between the orbiting shaft and the rotating shaft when the orbiting shaft orbits along the annular groove. The rotation rotation conversion mechanism according to claim 1. The node comprises at least one adjusting arm extending from the axis of rotation beyond the annular groove and one end of the adjusting arm on the side of the annular groove for extending the adjusting arm. A plurality of arms formed of the moving arm and at least one of the adjusting arms extend in the circumferential direction of rotation of the joint, each having an adjusting elongated hole that always overlaps the annular groove with its longitudinal direction oriented in the forward direction. are arranged at regular intervals,
3. The rotation/circulation conversion mechanism according to claim 1, further comprising an adjustment shaft that is inserted through both the annular groove and the adjustment elongated hole and that rotates along the annular groove. 4. The joint according to claim 3, wherein a space between the arms adjacent to each other in the rotation circumferential direction of the joint is filled, and a circular shape or a regular polygonal shape is formed centering on the rotary shaft when viewed in the axial direction of the rotary shaft. Rotational rotation conversion mechanism. 5. The rotation/circulation conversion mechanism according to claim 3 or 4, wherein said joint has said slot for rotation and one said slot for adjustment arranged point-symmetrically with respect to said rotation axis. A bearing that rotatably supports the rotating shaft and a lid fixed to the bearing,
The bearing has a projection projecting in the axial direction of the rotating shaft, the lid has a through hole through which the projection penetrates,
6. The annular groove according to any one of claims 1 to 5, wherein the annular groove is constituted by a gap between an outer peripheral surface of the protrusion and an inner peripheral surface of the through hole which are opposed to each other when the cover is fixed to the bearing. 3. A rotating orbiting conversion mechanism according to the above paragraph. The protruding portion has an inwardly recessed recess formed along the entire circumference of the outer peripheral surface thereof, and the through hole has an outwardly recessed recess formed along the entire inner peripheral surface thereof,
The peripheral shaft has an end portion that is inserted into the annular groove and has an enlarged diameter in the shaft radial direction, and the end portion is free in both the recess formed in the protrusion and the recess formed in the through hole. 7. The rotation rotation conversion mechanism according to claim 6, which is fitted. A rotation/circulation conversion mechanism according to any one of claims 1 to 7, a piston arranged inside a cylinder and performing reciprocating linear motion, and mutually converting the reciprocating linear motion of the piston and the reciprocating motion of the revolving shaft. A reciprocating engine, comprising: a linear motion rotation conversion mechanism. The annular groove has a top dead center section including at least a section in which the piston is positioned near the top dead center, a bottom dead center section including at least a section in which the piston is positioned near the bottom dead center, and other sections other than those sections. 9. The reciprocating engine according to claim 8, wherein the top dead center section has a circular arc shape or a linear shape with a curvature smaller than that of the other sections.

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