JP6874413B2 - engine - Google Patents

Description

The present invention relates to an engine that transmits a force from a piston to a planetary gear mechanism via a first connecting rod, a reciprocating part and a second connecting rod.

Some engine lubricating oil supply mechanisms supply lubricating oil to connecting rod bearings provided between the connecting rod and the crankshaft. As such a lubricating oil supply mechanism, for example, lubricating oil is supplied to a bearing for supporting a crankshaft interposed between a crankcase and a crankshaft, and this lubricating oil is passed through an oil passage in the crankshaft to a bearing for supporting a connecting rod. Is known to supply to.

According to such a lubricating oil supply mechanism, when the crankshaft is rotated, the lubricating oil enters the oil passage in the crankshaft, and the lubricating oil that has entered the oil passage is supplied to the bearing for supporting the connecting rod.

Japanese Unexamined Patent Publication No. 2016-075208 Japanese Unexamined Patent Publication No. 05-09218 Japanese Unexamined Patent Publication No. 10-0778919 Japanese Unexamined Patent Publication No. 2015-057570

However, the engine described in Patent Document 1 is different from a normal engine in that a force from a piston is applied to a planetary gear mechanism via a first connecting rod, a reciprocating portion that slides in the same direction as the piston, and a second connecting rod. It transmits and does not have the bearing for supporting the crankshaft described above. Therefore, the above-mentioned lubricating oil supply mechanism cannot be adopted, and there is a problem that there is no effective means for supplying lubricating oil to the bearing for supporting at least one of the first and second connecting rods.

Therefore, the present invention was conceived in view of such circumstances, and an object of the present invention is that even an engine that transmits a force from a piston to a planetary gear mechanism via a first connecting rod, a reciprocating rod, and a second connecting rod has a first purpose. And to provide an engine capable of supplying lubricating oil to bearings for supporting at least one of the second connecting rods.

According to one aspect of the invention
A reciprocating piston provided in the cylinder, a first conrod having one end coupled to the piston, and a reciprocating reciprocating engine rotatably coupled to the other end of the first conrod via a first bearing. A moving part, a guide part provided on the crank case that guides the reciprocating part in the reciprocating direction of the piston, and a second conrod rotatably coupled to the reciprocating part via a second bearing. An engine provided with a planetary gear mechanism coupled to the other end of the second conrod and converting the reciprocating motion of the second conrod into a rotary motion, provided between the crank case and the reciprocating portion. A spring that expands and contracts in response to the reciprocating motion of the reciprocating engine, an oil passage in the spring formed on the spring and for supplying lubricating oil supplied from the crankcase side to the reciprocating engine, and the reciprocating engine. Provided is an engine characterized in that at least one of the first bearing and the second bearing provided in a moving portion is provided with an oil passage in a reciprocating moving portion for supplying lubricating oil from the oil passage in the spring. To.

Preferably, the spring is formed in the shape of a hollow coil.

Preferably, one end of the spring is provided with a first fastening member to be fastened to the crankcase, and a tapered first crimping portion to be crimped to the crankcase is formed, and the other end of the spring is formed with a tapered first crimping portion. It is preferable that a second fastening member to be fastened to the reciprocating moving portion is provided and a second crimping portion to be crimped to the reciprocating moving portion is formed.

Further, the crank case is provided with a first piping portion for supplying lubricating oil, the reciprocating moving portion is provided with a second piping portion for receiving lubricating oil, and one end of the spring is described as described above. It may be connected to the first pipe portion via the first pipe joint, and the other end of the spring may be connected to the second pipe portion via the second pipe joint.

Preferably, the spring is formed in a central portion in the longitudinal direction and expands and contracts in response to the reciprocating movement of the reciprocating portion, and is formed adjacent to both ends of the large elastic portion and expands and contracts from the large elastic portion. It is preferable to provide a small expansion / contraction portion having a small amount.

Preferably, the reciprocating portion is provided with a hydraulic absorption mechanism for absorbing fluctuations in flood pressure due to expansion and contraction of the spring.

According to the present invention, even an engine that transmits a force from a piston to a planetary gear mechanism via a first connecting rod, a reciprocating portion, and a second connecting rod can supply lubricating oil to a bearing for supporting the connecting rod.

It is a schematic perspective view which shows the lubricating oil supply path of the engine which concerns on one Embodiment of this invention. It is a perspective view of the spring connected to the reciprocating part. It is a side sectional view of FIG. FIG. 1 is a cross-sectional view taken along the line AA of FIG. It is sectional drawing of a planetary gear. It is sectional drawing of the spring which concerns on other embodiment. It is sectional drawing of the spring which concerns on other embodiment. It is sectional drawing of the main part of the spring and the crankcase which concerns on other embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. In the embodiment described later, for convenience, the moving direction of the piston in the compression stroke of the engine is upward, the movement direction of the piston in the expansion stroke is downward, and the extension direction of the output shaft is the left-right direction. Each direction in the present embodiment is relative and does not necessarily match each direction of the actual engine.

FIG. 1 is a schematic perspective view schematically showing an engine according to an embodiment of the present invention and a lubricating oil supply path thereof. As shown in FIG. 1, the engine (internal combustion engine) E is a compression ignition type internal combustion engine mounted on a vehicle, that is, a diesel engine. The illustrated example shows a single-cylinder engine, but the cylinder arrangement type, the number of cylinders, and the like of the engine are arbitrary. The engine may be a reciprocating piston engine (reciprocating engine) or a spark-ignition internal combustion engine such as a gasoline engine.

The engine E is rotatably connected to a piston 2 provided in the cylinder 1 so as to be reciprocating, a first connecting rod 3 whose upper end is rotatably coupled to the piston 2, and a lower end of the first connecting rod 3. The combined reciprocating part 4, the pair of left and right guide parts 6 provided on the crank case 5 that slidably guide the reciprocating part 4 in the reciprocating direction of the piston, and the lower end portion of the reciprocating part 4 can be rotated. A second connecting rod 7 that is coupled and a planetary gear mechanism 8 that is coupled to the upper end of the second connecting rod 7 and converts the reciprocating motion of the second connecting rod 7 into a rotary motion are provided.

The planetary gear mechanism 8 includes a pair of internal gears 9, a pair of planetary gears 10 meshed with the internal gears 9, a crank pin 11 connecting the planetary gears 10, and an output for output provided on one of the planetary gears 10. A gear 12 and a sun gear 13 that meshes with an output gear 12 are provided. The pair of internal gears 9 are fixed to the crankcase 5 and arranged coaxially, and are arranged apart from each other in the axial direction. The planetary gears 10 are arranged coaxially and spaced apart in the axial direction. The crank pins 11 are provided between the planetary gears 10 eccentrically with respect to the center of the planetary gears 10. The crank pin 11 is rotatably coupled to the upper end of the second connecting rod 7 via the third bearing 17c. The output gear 12 is coaxially fixed to the side surface of one planetary gear 10. The sun gear 13 is arranged coaxially with the internal gear 9. The output shaft 14 is coaxially provided on the sun gear 13. The output shaft 14 is supported by the crankcase 5 so as to be rotatable and to keep the position of the sun gear 13 constant. Although the sun gear 13 is assumed to mesh with the output gear 12, it may be meshed with a planetary gear. In this case, the diameter of the planetary gear may be set to be less than the radius of the internal gear 9.

The reciprocating portion 4 includes a shaft portion 15 extending in parallel with the rotation center axis 2a of the piston 2, and slider portions 16a and 16b provided at both ends of the shaft portion 15 and sliding up and down with respect to the left and right guide portions 6. Be prepared.

As shown in FIGS. 1 and 4, the lower end of the first connecting rod 3 is rotatably coupled to the outer circumference of the shaft portion 15 via a first bearing 17a (not shown), and the lower end of the second connecting rod 7 is formed. The portions are rotatably coupled via the second bearing 17b. The second bearing 17b is for rotatably supporting the second connecting rod 7, and is composed of a pair of half-split plain bearings 17d. The half-split plain bearing 17d is formed in a semicircularly curved plate shape and has holes 17e penetrating in the radial direction. The hole 17e functions as an oil passage for circulating the lubricating oil supplied from the shaft portion 15 side (inner peripheral side) to the second connecting rod 7 side (outer peripheral side). The half-split plain bearing 17d is arranged on the outer periphery of the shaft portion 15 in a state where both ends in the circumferential direction are butted against each other. Further, the half-split plain bearing 17d is fixed by being squeezed into the second connecting rod 7. The first bearing 17a and the third bearing 17c described above are configured in the same manner as the second bearing 17b. Therefore, the description of the first bearing 17a and the third bearing 17c will be omitted.

The slider portions 16a and 16b are formed in a block shape and symmetrically. Both sides of the slider portions 16a and 16b are slidably guided by the guide portion 6. The guide portion 6 is integrally provided with the crankcase 5. The guide portion 6 extends in the vertical direction (reciprocating direction of the piston 2).

A spring (omitted in FIG. 1) is provided between each of the slider portions 16a and 16b and the crankcase 5 above the slider portions 16a and 16b.

The spring will be described. Since the springs are formed in the same manner, those arranged on the first connecting rod 3 side will be described, and those arranged on the second connecting rod 7 side will be omitted. In the present embodiment, the slider portion 16a arranged on the first connecting rod 3 side is also referred to as a first slider portion 16a, and the slider portion 16b arranged on the second connecting rod 7 side is also referred to as a second slider portion 16b. The first slider portion 16a and the second slider portion 16b are configured by arranging the same members symmetrically.

As shown in FIGS. 2 and 3, the spring 18 is formed in a substantially hollow coil shape, and expands and contracts in response to the reciprocating movement of the first slider portion 16a. The upper end of the spring 18 is fixed to the ceiling portion 5a of the crankcase 5, and the lower end is fixed to the upper surface portion 39 on the center of gravity of the first slider portion 16a.

The spring 18 includes a base portion 18a formed at both upper and lower ends and extending coaxially and linearly in the vertical direction, and a coil portion 18b formed between the base portions 18a and formed in a spiral shape centered on the axis of the base portion 18a. The coil portion 18b is formed in the central portion in the vertical direction or the longitudinal direction and expands and contracts according to the reciprocating movement of the reciprocating portion 4, and the large elastic portion 19a is formed adjacent to both ends of the large elastic portion 19a. It is provided with a small expansion / contraction portion 19b having a smaller expansion / contraction amount. The small expansion / contraction portion 19b is formed by increasing the number of turns of the spring 18 per unit length in the expansion / contraction direction as compared with the large expansion / contraction portion 19a. The spring 18 is set to have a natural length when the piston 2 is located at bottom dead center. Although the spring 18 is provided between the crankcase 5 and the first slider portion 16a, it may be provided between the crankcase 5 and the shaft portion 15.

The small expansion / contraction portion 19b is provided with a clip 20 for restricting the expansion of the small expansion / contraction portion 19b. The clip 20 is formed in a substantially C shape and is hung on springs 18 at a plurality of height positions.

Further, in the spring 18, an oil passage in the crankcase formed in the crankcase 5 and an oil passage in the spring for connecting the oil passage 21 in the reciprocating portion 4 formed in the reciprocating portion 4 are connected. 22 is formed. An oil pump (not shown) is connected to the oil passage 21 in the crankcase. The oil pump supplies lubricating oil to the oil passage 21 in the crankcase. The oil passage 22 in the spring is formed over both ends of the spring 18 and is formed along the shape of the spring.

Further, the upper base portion 18a is provided with a first fastening member 23a to be fastened to the crankcase 5, and a first crimping portion 24a to be crimped to the crankcase 5 by the fastening force of the first fastening member 23a. .. The first crimping portion 24a is formed on the base portion 18a above the first fastening member 23a, and is formed in a tapered shape having a circular cross section whose diameter increases from the upper side to the lower side. The first fastening member 23a is formed in a tubular shape that is rotatably fitted to the outer periphery of the base portion 18a. The first fastening member 23a is restricted from moving upward by the first crimping portion 24a. A head 38a projecting outward in the radial direction is formed at the lower end of the first fastening member 23a. The head 38a is formed in a hexagonal shape in a plan view and functions as the head of a bolt. A male screw (not shown) is formed on the first fastening member 23a above the head 38a.

Further, the crankcase 5 is formed with a first receiving surface 25a for receiving the first crimping portion 24a and a female screw (not shown) screwed with the first fastening member 23a. The first receiving surface 25a is formed by increasing the diameter of the inner peripheral surface of the crankcase inner oil passage 21 formed in a circular cross section toward the downward direction. The female screw is formed on the inner peripheral surface of the oil passage 21 in the crankcase below the first receiving surface 25a. By screwing and tightening the male screw of the first fastening member 23a to the female screw of the crankcase 5, the upper base portion 18a is fixed to the crankcase 5, and the first crimping portion 24a is attached to the first receiving surface 25a. It is crimped. As a result, the oil passage 21 in the crankcase and the oil passage 22 in the spring are liquid-tightly connected.

Further, the lower base portion 18a is provided with a second fastening member 23b to be fastened to the first slider portion 16a, and a second crimping member to be crimped to the first slider portion 16a by the fastening force of the second fastening member 23b. Part 24b is provided. The second crimping portion 24b is formed on the base portion 18a below the second fastening member 23b, and is formed in a tapered shape having a circular cross section whose diameter increases from the lower side to the upper side. The second fastening member 23b is formed in a tubular shape that is rotatably fitted to the outer periphery of the base portion 18a. The second fastening member 23b is restricted from moving downward by the second crimping portion 24b. A head 38b protruding outward in the radial direction is formed at the upper end of the second fastening member 23b. The head 38b is formed in a hexagonal shape in a plan view and functions as the head of a bolt. A male screw (not shown) is formed on the second fastening member 23b below the head 38b.

Further, the first slider portion 16a is formed with a second receiving surface 25b for receiving the second crimping portion 24b, and a female screw (not shown) screwed with the second fastening member 23b is formed. , The oil passage 26a in the first slider portion is formed. The oil passage 26a in the first slider portion is formed so as to extend vertically, the upper end is opened by the upper surface portion 39, and the lower end is connected to the oil passage 27a in the first shaft portion, which will be described later. The second receiving surface 25b is formed by expanding the inner peripheral surface of the oil passage 26a in the first slider portion having a circular cross section toward the upper side. The female screw is formed on the inner peripheral surface of the oil passage 26a in the first slider portion above the second receiving surface 25b. By screwing and tightening the male screw of the second fastening member 23b to the female screw of the first slider portion 16a, the lower base portion 18a is fixed to the first slider portion 16a and the second crimping portion 24b is fixed to the first slider portion 16a. 2 It is crimped to the receiving surface 25b. As a result, the oil passage 26a in the first slider portion and the oil passage 22 in the spring are liquid-tightly connected. The second slider portion 16b is also provided with the spring 18 in the same manner.

As shown in FIG. 1, the reciprocating part 4 is formed with an oil passage 4a in the first reciprocating part for supplying lubricating oil to the first bearing 17a, and the second bearing 17b (see FIG. 4) is formed. An oil passage 4b in the second reciprocating part for supplying lubricating oil is formed.

As shown in FIGS. 1, 2 and 3, the oil passage 4a in the first reciprocating moving portion includes the oil passage 26a in the first slider portion formed in the first slider portion 16a and the shaft portion on the first connecting rod 3 side. An oil passage 27a in the first shaft portion formed in the 15 is provided. The oil passage 26a in the first slider portion is formed so as to extend in the vertical direction, and the upper end is connected to the oil passage 22 in the spring and the lower end is connected to the oil passage 27a in the first shaft portion. The oil passage 27a in the first shaft portion includes the first axial oil passage 28a extending from the oil passage 26a in the first slider portion to the axial position of the first bearing 17a, and the oil passage 28a in the first axial direction outward in the radial direction. It is provided with a first radial oil passage 29a which extends to and is opened at a position facing the first bearing 17a.

The oil passage 4b in the second reciprocating part is also formed in substantially the same manner as the oil passage 4a in the first reciprocating part. The oil passage 4b in the second reciprocating part is formed in the oil passage 26b in the second slider portion 16b formed in the second slider portion 16b (indicated by the reference numerals in parentheses in FIG. 3) and in the shaft portion 15 on the second connecting rod 7 side. The oil passage 27b in the second shaft portion formed in the above is provided. The oil passage 26b in the second slider portion is formed so as to extend in the vertical direction like the oil passage 26a in the first slider portion, the upper end is connected to the oil passage 22 in the spring portion, and the lower end is connected to the oil passage 27b in the second shaft portion. Will be done. The oil passage 27b in the second shaft portion includes the oil passage 28b in the second axial direction extending from the oil passage 26b in the second slider portion to the axial position of the second bearing 17b, and the oil passage 28b in the second axial direction outward in the radial direction. It is provided with a second radial oil passage 29b that extends to and is opened at a position facing the second bearing 17b.

As shown in FIGS. 1 and 4, the second connecting rod 7 is formed with an oil passage 30 in the second connecting rod for supplying the lubricating oil supplied to the second bearing 17b to the above-mentioned third bearing 17c. .. The crank pin 11 is formed with an oil passage 31 in the crank pin for supplying the lubricating oil supplied to the third bearing 17c to the planetary gear 10 side.

As shown in FIGS. 1 and 5, the planetary gear 10 is formed with an oil passage 32 in the planetary gear for supplying the lubricating oil supplied from the oil passage 31 in the crank pin to the tooth surface.

As shown in FIG. 3, each of the slider portions 16a and 16b is provided with a hydraulic absorption mechanism 33 for absorbing fluctuations in flood pressure due to expansion and contraction of the spring 18. Since the hydraulic absorption mechanism 33 provided in each of the slider portions 16a and 16b is the same, the one provided in the first slider portion 16a will be described, and the description of the one provided in the second slider portion 16b will be omitted.

The hydraulic absorption mechanism 33 provided in the first slider portion 16a is formed in the first slider portion 16a and extends in a direction intersecting the oil passage 26a in the first slider portion, and is connected to the oil passage 26a in the first slider portion. A sealing piston 36 provided in the oil sump portion 34, a bladder 35 provided in the oil sump portion 34, and a seal piston 36 provided on the oil passage 26a side in the first slider portion of the bladder 35 and slidably formed along the extension direction of the oil sump portion 34. And. The oil sump portion 34 is formed by forming a hole penetrating in the horizontal direction in the first slider portion 16a and then closing both ends of the hole with a plug 37. The oil sump portion 34 is formed to have a circular cross section. The cross-sectional shape of the oil sump portion 34 is not limited to a circle, but may be another shape such as a rectangle or an ellipse. The bladder 35 is formed of a bag that can be expanded and contracted, and compressed air is sealed therein. The bladder 35 is provided adjacent to the plug 37.

Next, the operation of this embodiment will be described.

When the engine E is driven, the piston 2 moves up and down along the cylinder 1, and the reciprocating portion 4 that receives a vertical force from the first connecting rod 3 moves up and down along the guide portion 6. Further, the ascending / descending movement of the reciprocating unit 4 is transmitted to the crank pin 11 via the second connecting rod 7. Since the crank pin 11 is provided eccentrically on the planetary gear 10, the force from the second connecting rod 7 acts on the planetary gear 10 as a force in the rotational direction. As a result, the planetary gear 10 revolves along the internal gear 9 while rotating on its axis, and rotates the sun gear 13 meshed with the output gear 12. The rotational force of the sun gear 13 is output via the output shaft 14.

When the engine E is driven in this way, lubricating oil is supplied to the oil passage 21 in the crankcase. The lubricating oil supplied to the oil passage 21 in the crankcase is supplied to the oil passage 26a in the first slider portion and the oil passage 26b in the second slider portion through the oil passage 22 in the spring of each spring 18. The spring 18 repeatedly expands and contracts in response to the ascending / descending movement of the reciprocating portion 4, and the lubricating oil pulsates when flowing from the oil passage 22 in the spring to the oil passage 26a in the first slider portion and the oil passage 26b in the second slider portion. However, since the bladder 35 of the hydraulic absorption mechanism 33 expands and contracts according to the pressure fluctuation of the lubricating oil and the volume in the oil sump portion 34 expands and contracts, the pressure fluctuation of the lubricating oil is absorbed and eliminated or reduced.

The lubricating oil supplied to the oil passage 26a in the first slider portion is supplied to the first bearing 17a via the oil passage 27a in the first shaft portion, and the lubricating oil supplied to the oil passage 26b in the second slider portion is the second. It is supplied to the second bearing 17b via the oil passage 27b in the shaft portion. As can be seen from FIG. 4, the lubricating oil supplied to the first bearing 17a and the second bearing 17b lubricates the inner peripheral side of the half-split plain bearing 17d and the outer circumference of the half-split plain bearing 17d through the hole 17e. It flows to the side, flows from the outer peripheral side of the half-split plain bearing 17d to the oil passage 30 in the second connecting rod, and is supplied to the third bearing 17c through the oil passage 30 in the second connecting rod. Then, as shown in FIG. 1, the lubricating oil supplied to the third bearing 17c is supplied to the tooth surface of the planetary gear 10 via the oil passage 31 in the crank pin and the oil passage 32 in the planetary gear. After that, the lubricating oil lubricates the meshing portion between the planetary gear 10 and the internal gear 9. Lubrication between the output gear 12 and the sun gear 13 is performed by the same method as before, that is, lubrication is performed on a bearing for supporting the output shaft (not shown) interposed between the crankcase 5 and the output shaft 14. It is preferable to supply oil and supply this lubricating oil to the tooth surface of the output gear 12 through an oil passage (not shown) in the output shaft 14.

As described above, the spring 18 provided between the crank case 5 and the reciprocating portion 4, the in-spring oil passage 22 formed in the spring 18, and the first bearing 17a and the second bearing formed in the reciprocating portion 4. Since the 17b is provided with the oil passages 4a and 4b in the reciprocating part for supplying the lubricating oil from the oil passage 22 in the spring, the force from the piston 2 is applied to the first connecting rod 3, the reciprocating part 4 and the second connecting rod. Even the engine E transmitted to the planetary gear mechanism 8 via the 7 can supply the lubricating oil to the first bearing 17a and the second bearing 17b.

Further, since the spring 18 is formed in the shape of a hollow coil, the oil passage 22 in the spring can be formed with a simple structure.

A first fastening member 23a to be fastened to the crankcase 5 is provided at one end of the spring 18, and a tapered first crimping portion 24a to be crimped to the crankcase 5 is formed. A second fastening member 23b to be fastened to the reciprocating moving portion 4 is provided, and a second crimping portion 24b to be crimped to the reciprocating moving portion 4 is formed. Therefore, the outer periphery of the tip portion of the spring 18 can be fastened to the crankcase 5 and the reciprocating moving portion 4 while being crimped to the crankcase 5 and the reciprocating moving portion 4, and the oil passage 21 in the crankcase and the oil passage 26a in the slider portion can be fastened. The 26b can be liquid-tightly connected via the oil passage 22 in the spring.

The spring 18 has a large expansion / contraction portion 19a formed in the central portion in the longitudinal direction and expands / contracts according to the reciprocating movement of the reciprocating movement portion 4, and a spring 18 formed adjacent to both ends of the large expansion / contraction portion 19a and has a larger expansion / contraction amount than the large expansion / contraction portion 19a. Since it is provided with a small small expansion / contraction portion 19b, vibration transmitted to both ends of the spring 18 can be reduced, and the connection portion between the spring 18 and the crankcase 5 and the connection portion between the spring 18 and the slider portions 16a and 16b can be separated from the vibration. Can be protected.

Since the reciprocating portion 4 is provided with a hydraulic absorption mechanism 33 for absorbing the fluctuation of the hydraulic pressure due to the expansion and contraction of the spring 18, the pulsation of the hydraulic pressure can be eliminated or reduced, and the first bearing 17a and the second bearing 17b can be eliminated. Lubricating oil can be stably supplied to the vehicle.

The second connecting rod 7 is formed with an oil passage 30 in the second connecting rod for supplying lubricating oil from the second bearing 17b to the third bearing 17c, and the crank pin 11 is on the planetary gear 10 side from the third bearing 17c. An oil passage 31 in the crank pin for supplying lubricating oil to the planetary gear 10 is formed, and an oil passage 32 in the planetary gear is formed in the planetary gear 10. Therefore, the third bearing 17c can be lubricated, and the meshing portion between the planetary gear 10 and the internal gear 9 can be lubricated.

Although the embodiments of the present invention have been described in detail above, the present invention can also be modified as follows.

(1) Deformation Example of Base 18a As shown in FIG. 6, the upper base 41 of the spring 40 may be bent at a substantially right angle. In this case, the upper end of the spring 40 may be fixed to the side surface 5b of the crankcase 5.

(2) First Deformation Example of Small Telescopic Part 19b The small stretchable portion 19b may be formed by partially changing the spring material to a high-strength material regardless of the number of turns per unit length in the expansion / contraction direction of the spring. .. In this case, the large expansion / contraction portion 19a and the small expansion / contraction portion 19b may be formed separately in advance, and the small expansion / contraction portions 19b may be welded to both ends of the large expansion / contraction portion 19a to form the spring 18. Further, the additive material may be changed between the large expansion / contraction portion 19a and the small expansion / contraction portion 19b while integrally forming the large expansion / contraction portion 19a and the small expansion / contraction portion 19b.

(3) Second Deformation Example of Small Stretchable Part 19b As shown in FIG. 7, the small stretchable portion 50 may be formed by being wound around the inner peripheral side of the large stretchable portion 19a. In this case, the springs 51 adjacent to each other in the radial direction may be fastened with the clip 52.

(4) Deformation Example of Overall Spring The spring may be composed of a leaf spring that connects the crankcase 5 and the reciprocating portion 4 while allowing the reciprocating movement of the reciprocating portion 4.

(5) Deformation Example of Lubricating Part In this embodiment, lubricating oil is supplied to both the first bearing 17a and the second bearing 17b. However, when it is not necessary to supply the lubricating oil to one of the first bearing 17a and the second bearing 17b with the structure according to the present embodiment, the lubricating oil is supplied only to the other bearing with the structure according to the present embodiment. May be good.

(6) Deformation Example of Spring Connection Structure As shown in FIG. 8, the spring 18 may be connected to the piping portion 61 on the crankcase 5 side via the piping joint 60. In this case, the piping portion 61 may be integrally provided with the crankcase 5 by welding or the like so as to be connected to the oil passage 21 in the crankcase, or may be integrally cast with the crankcase 5. Further, the piping portion 61 has a structure shown in FIG. 3, that is, the piping portion 61 is provided with the first fastening member 23a and the first crimping portion 24a, and the crankcase 5 is provided with the first receiving surface 25a and the female screw. It may be connected to the oil passage 21 in the crankcase with a structure in which the first crimping portion 24a is crimped to the first receiving surface 25a by fastening the first fastening member 23a to the screw. The pipe joint 60 is preferably a coupler type coupling. Specifically, the pipe joint 60 includes a female connector 62, a male connector 63 inserted into the female connector 62, a lock mechanism 64 for locking the male connector 63 and the female connector 62, and the male connector 63 and the female connector 62. Each of the above is provided with a valve mechanism 65 that opens the valve when the male connector 63 and the female connector 62 are connected and closes the valve when the male connector 63 and the female connector 62 are disconnected.

The lock mechanism 64 has a lock groove 66 formed on the outer periphery of the insertion portion of the male connector 63, a ball 67 provided on the female connector 62 so as to appear and disappear in the radial direction, and slidable axially on the outer periphery of the female connector 62. Lock sleeve 68, which is provided in the above and holds the ball 67 in a posture of protruding inward in the radial direction when moved in one direction in the axial direction, and releases the holding of the ball 67 when moved in the other direction. A locking spring 69 that urges the sleeve 68 in one direction is provided.

The valve mechanism 65 includes a mushroom-shaped valve body 70 provided so as to be slidable in the axial direction in the flow paths 63a and 62a of the male connector 63 and the female connector 62, and the flow paths 63a and 62a of the male connector 63 and the female connector 62. An annular valve seat 71 provided in the valve seat 71 and a valve closing spring 72 that presses the valve body 70 against the valve seat 71. The valve seat 71 is formed so as to face the open ends of the flow paths 63a and 62a, and the valve body 70 is arranged with the mushroom-shaped tip facing the open end side, and the tip is opened when seated on the valve seat 71. It is formed so as to protrude from the edge. As a result, when the male connector 63 is inserted into the female connector 62, the tip of the valve body 70 of the female connector 62 and the tip of the valve body 70 of the male connector 63 come into contact with each other and are pressed against each other with the same spring force. Has been done.

Further, the spring 18 may be connected to the piping portion (not shown) on the reciprocating portion 4 side (see FIG. 2) via the piping joint 60. In this case, the piping portion is connected to the oil passage 26a in the first slider portion (or the oil passage 26b in the second slider portion) with a structure similar to the structure for connecting the piping portion 61 and the oil passage 21 in the crankcase. It is good.

As described above, the crank case 5 is provided with a piping portion 61 for supplying the lubricating oil, and the reciprocating moving portion 4 is provided with a piping portion (not shown) for receiving the lubricating oil, and the spring 18 When one end of the spring 18 is connected to the piping portion 61 via the piping joint 60 and the other end of the spring 18 is connected to the piping portion (not shown) via the piping joint 60, the spring 18 is attached / detached and replaced. Can be easily performed.

The valve mechanism 65 may be omitted. In this case, the pipe joint can be inexpensive.

The configurations of each of the above embodiments can be combined partially or wholly, unless otherwise inconsistent. The embodiment of the present invention is not limited to the above-described embodiment, and all modifications, applications, and equivalents included in the idea of the present invention defined by the scope of claims are included in the present invention. Therefore, the present invention should not be construed in a limited manner and can be applied to any other technique belonging to the scope of the idea of the present invention.

E Engine 1 Cylinder 2 Piston 3 First connecting rod 4 Reciprocating part 4a Oil passage in the first reciprocating part (Oil passage in the reciprocating part)
4b Oil passage in the second reciprocating part (oil passage in the reciprocating part)
5 Crankcase 6 Guide part 7 Second connecting rod 8 Planetary gear mechanism 17a 1st bearing 17b 2nd bearing 18 Spring 22 In-spring oil passage

Claims (5)

A piston that can be reciprocated in the cylinder and
A first connecting rod whose one end is coupled to the piston,
A reciprocating portion rotatably coupled to the other end of the first connecting rod via a first bearing, and a reciprocating portion.
A guide portion provided on the crankcase to guide the reciprocating portion in the reciprocating direction of the piston, and a guide portion.
A second connecting rod whose one end is rotatably coupled to the reciprocating portion via a second bearing.
An engine provided with a planetary gear mechanism that is coupled to the other end of the second connecting rod and converts the reciprocating motion of the second connecting rod into rotary motion.
A spring provided between the crankcase and the reciprocating portion and expanding and contracting according to the reciprocating movement of the reciprocating portion.
An oil passage in the spring for supplying the lubricating oil formed on the spring and supplied from the crankcase side to the reciprocating portion side.
At least one of the first bearing and the second bearing formed in the reciprocating portion is provided with an oil passage in the reciprocating portion for supplying lubricating oil from the oil passage in the spring.
The engine is characterized in that the spring is formed in the shape of a hollow coil. A first fastening member to be fastened to the crankcase is provided at one end of the spring, and a tapered first crimping portion to be crimped to the crankcase is formed, and the reciprocating portion is formed at the other end of the spring. The engine according to claim 1 , wherein a second fastening member to be fastened to the moving portion is provided and a second crimping portion to be crimped to the reciprocating moving portion is formed. The crank case is provided with a first piping portion for supplying lubricating oil, the reciprocating portion is provided with a second piping portion for receiving lubricating oil, and one end of the spring is the first. The engine according to claim 1 , wherein the engine is connected to the piping portion via a first piping joint, and the other end of the spring is connected to the second piping portion via a second piping joint. The spring has a large expansion / contraction portion formed in the central portion in the longitudinal direction and expands / contracts according to the reciprocating movement of the reciprocating movement portion, and is formed adjacent to both ends of the large expansion / contraction portion and has a smaller expansion / contraction amount than the large expansion / contraction portion. The engine according to any one of claims 1 to 3, further comprising a small expansion / contraction portion. The engine according to any one of claims 1 to 4 , wherein the reciprocating portion is provided with a hydraulic absorption mechanism for absorbing fluctuations in flood pressure due to expansion and contraction of the spring.

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