JP2017025895A - Opposing piston-shaft crank stroke volume continuous variable device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To resolve some defaults found in a prior art stroke volume continuous variable engine that a part receiving a reaction force of a slant plate [a slant shaft] converting a piston stroke into a rotation shows a high mechanical loss due to its sliding and a fast contact speed and an inertia force and a moment of inertia at a reciprocating motion part may become easily unbalanced state due to arrangement of multi-cylinders at an outer circumference of one crank shaft.SOLUTION: This invention relates to four-cylinder stroke volume continuous variable device in which a cross-shaped joint rotatably and pivotally supported so as to be fixed in an axial direction at both end shafts of a motion converting rocker arm rotatably held to be attached in an axial direction at a slant shaft arranged at one shaft crank in variable slant angle and axial position and another oscillation end of L-shaped direction converting rocker arm as seen from an oscillation shaft for oppositely stroking a piston while a connecting rod large end shaft at one side oscillation end are connected by a double link mechanism, both end shafts are oscillated on a plane perpendicular to a cylinder hole including a crank shaft and there is provided a balance weight oscillated in an opposing direction of both end shafts.SELECTED DRAWING: Figure 1-1

Description

The present invention provides a low-vibration and compact crankshaft direction apparatus capable of continuously changing a stroke volume in an engine such as an automobile and simultaneously setting a compression ratio according to the stroke volume or continuously changing the compression ratio arbitrarily. is there.

The stroke volume and compression ratio of the internal combustion engine with respect to the output are the main factors that determine the thermal efficiency and pumping loss.If the stroke volume and compression ratio can be selected continuously according to the load, the rotational speed, etc. Increases thermal efficiency and reduces pumping loss.
Patent Document 1 that can change the stroke volume and the compression ratio by converting the piston reciprocating motion into the crankshaft rotational motion on the swash plate (slanted shaft) and changing the tilt angle of the swash plate (slanted shaft) and the crankshaft direction position. There are two.

The swing plate carrier is held by an ear shaft provided at a right angle to the output shaft core and a link provided rotatably on the crankcase and rotatably on an anchor member fixed in the axial direction, and the output shaft is displaced in the axial direction. Japanese Patent Application Laid-Open No. H10-228707 can change the tilt angle of the swing plate carrier to vary the stroke volume and set the compression ratio in accordance with the stroke volume.
US Pat. No. 4,433,596

The first rotation support body and the second rotation support body are provided so as to be axially movable on the same axis as the output shaft, and the swash plate can be swung by the support shaft of the first rotation support body provided at a right angle to the output shaft core. The second rotary support and the swash plate are connected via a joint, the first and second rotary supports are moved in the axial direction, the swash plate tilt angle is changed according to the relative positional relationship, and the stroke volume is variable. In addition, there is Patent Document 2 in which the compression ratio can be arbitrarily changed at any time.
Japanese Patent Application Laid-Open No. 2004-245092

In Patent Document 1, when converting the force of the piston reciprocating motion into the rotational force of the output shaft, the sliding force is fast because the piston receives the reaction force in the direction perpendicular to the piston sliding shaft with the piston of the bearing piston holding portion. Enormous frictional resistance is generated and mechanical loss is increased. In addition, the race for preventing the swing plate from rotating and the swing plate arm portion on the center line of the output shaft are linearly moved in the same manner as the race, but the other arm portions have an 8-shaped locus. Therefore, it is necessary to move the arm part with respect to the bearing piston, and the rocking plate cannot move unless the clearance of the wrist pin holding hole part of the arm part is secured. Therefore, the piston is rattled by the clearance and the compression ratio fluctuates and noise is generated. Further, since the positional relationship between the pivot axis of the ear shaft and the link is determined by the feed screw and the anchor member holding portion on both sides of the crankcase, it is likely to fluctuate due to the thermal expansion and rigidity of the case. Further, thrust bearings are used for each part, and when it is made of metal, it is difficult to increase the rotation speed at the peripheral speed surface and the centrifugal force surface acting on the roller as a needle, which makes it difficult to adopt as an automobile engine.

In the embodiment of Patent Document 2, when converting the piston reciprocating force into the rotational force of the output shaft, the piston outer periphery of the rail and the cylinder are not slid in contact as in Patent Document 1, so the piston sliding shaft The reaction force in the direction perpendicular to the surface acts as a bending moment at the contact portion between the piston and the cylinder, generating a huge frictional resistance and making the reciprocating motion difficult due to the wedge effect.
In addition, since the swash plate and the rail are in sliding contact with each other, the peripheral speed is high, and it is difficult to increase the rotation speed. In addition, the first rotational support that holds the swash plate with a variable tilt angle and the second rotational support that connects the swash plate via a joint are interlocked to change the axial position and change the stroke volume and compression ratio. Therefore, if there is a difference in response between both motors, there is a danger that the compression ratio will change greatly and breakage will occur.
Moreover, when the displacement generating mechanism is deviated from both rotating supports as in the embodiment, smooth displacement is difficult due to the wedge effect due to the moment, and a huge load due to the combustion pressure tends to be applied as a moment and the strength tends to be insufficient. is there.
As in the above example, the conventional stroke volume variable device using the swash plate (slant shaft) has a large mechanical loss in the part that converts the force of the piston reciprocating motion into the rotational force of the output shaft, and it is difficult to increase the rotation speed. The structure for changing the inclination angle of the swash plate (slant shaft) is also inadequate in terms of accuracy and safety. If the multi-cylinder hole shaft is placed parallel to the crankshaft, the inertial force and moment of inertia of the reciprocating motion part are likely to be unbalanced, and balancing with a single-shaft crank is very difficult, so vibration countermeasures are also insufficient. It becomes. In addition, cylinders, cylinder heads, etc. are arranged in order in the crankshaft direction, and the axial engine length becomes longer. Therefore, it is difficult to arrange the crankshaft and transmission in the left-right direction of the vehicle body. However, the actual situation is that it has not been put into practical use because there are many disadvantages that obstruct the driver's and passenger's seats due to the overhang of the transmission portion into the cab.
As a method of balancing, the cylinder shaft is arranged symmetrically in parallel on both sides of the crankshaft, connected to the large end shaft of the connecting rod connected to the piston, and the swinging tip of the swing arm that strokes the piston is tilted to the crankshaft. The angle and position can be freely rotated on a slanted shaft, and can be rotated on both end shafts of a motion conversion rocker arm held fixed in the axial direction. A two-cylinder stroke volume continuously variable mechanism that swings both end shafts on a plane including the crankshaft, and another two-cylinder stroke volume continuously variable mechanism is provided in parallel to the swing plane, and linked at the same rotation speed and reverse rotation. A device with four cylinders can be considered, but the crankshaft direction becomes long, and the crank becomes two shafts, and the mechanism becomes complicated.

The present invention has been made in view of the above-described problems, and is a motion conversion rocker arm which is rotatably and axially fixedly held on a slant shaft provided with a variable tilt angle and axial position on a single-shaft crank. Rotating on both end shafts of the shaft, a cross joint that is supported in a fixed axial direction, and a cylinder hole is arranged at substantially right angles on both sides with respect to the crankshaft and both end shafts. The other rocking tip of the L-shaped direction change rocker arm as viewed in the rocking shaft direction is made up of a link rocking at right angles to each other and a holder that holds them and strokes parallel to the crankshaft. The four-cylinder stroke capacity is provided with a balance weight that swings in the opposite direction of both end shafts while swinging both end shafts on a plane perpendicular to the cylinder hole including the crankshaft. In a continuously variable device, in the power transmission process that converts the piston reciprocating force into the rotational force of the output shaft, the direction is changed by swinging the rocker arm, link, cross joint, etc. Compared with Patent Documents 1 and 2 where the reaction force is received by a piston or swash plate, the sliding speed of the load receiving surface is significantly smaller and the mechanical loss can be reduced. By using it, the mechanical loss can be further reduced and the rotation speed can be increased.
Also, because the two-cylinder opposed piston engine in which the cylinder holes are arranged at substantially right angles on both sides of the crankshaft and the motion converting rocker arm is arranged at the same position in the crankshaft direction, the crankshaft is arranged. Two cylinders on one side are arranged side by side, and the dimension in the crankshaft direction is shorter than that of the conventional four-cylinder opposed piston engine, which is shorter than that of the in-line four-cylinder engine. In addition, in terms of vibration countermeasures, both the inertial force and the moment of inertia are balanced in the cylinder hole axial direction even with a single-shaft crank because of the opposed piston. In the right-angled direction, unbalance occurs due to the swinging of both end shafts, cross joints, double link mechanisms, etc., but by providing a balance weight that swings in the opposite direction, a simple and compact device can be easily balanced. realizable. Furthermore, it is possible to provide a stroke volume continuous variable device that can arbitrarily change the compression ratio at any time by providing a mechanism for shifting the pivot axis position of the direction changing rocker arm.

In order to solve the above-mentioned problems, the invention of claim 1 is characterized in that the shaft of both ends of the motion conversion rocker arm which is rotatably and axially fixedly held on a slant shaft provided with a variable tilt angle and axial position on a single shaft. A cross joint that is pivotally supported in an axially fixed manner, and a cylinder hole is arranged at substantially right angles on both sides with respect to the crankshaft and both end shafts. A multi-link composed of a link that swings in a direction perpendicular to each other and a holder that holds them and strokes parallel to the crankshaft, with the other swing tip of the L-shaped direction change rocker arm as viewed in the swing axis direction The balun is connected by a mechanism, and both end shafts are swung on a plane perpendicular to the cylinder hole including the crankshaft to convert the reciprocating motion of the piston into rotation of the crankshaft and swing in the opposite direction of both end shafts. Characterized by a four-cylinder stroke volume continuously variable device provided with a weight.
The conventional swash plate (slanted axis) stroke volume variable mechanism has a multi-cylinder shaft arranged around the crankshaft holding one swash plate (slanted shaft) as in Patent Documents 1 and 2, and piston reciprocating motion In the swash plate type, the swash plate sliding contact part has a high peripheral speed, and the swash plate type has a high piston stroke sliding speed and a large mechanical loss. It was a structure in which an imbalance of moment of inertia was likely to occur.
As in the present invention, a four-cylinder counter-piston engine in which two-cylinder counter-piston engines in which cylinder holes are arranged at substantially right angles on both sides with respect to both end axes of the crankshaft and the motion conversion rocker arm are arranged at the same position in the crankshaft direction. The two-cylinder side cylinders are arranged side by side in the crankshaft direction, and the crankshaft direction dimension can be made shorter than that of the in-line four-cylinder engine. On the anti-vibration side, even with a single-shaft crank, because of the opposed piston, the cylinder bore axial direction balances both the inertial force and moment of inertia, and the right-angled direction is unbalanced due to swinging of both end shafts, cross joints, double link mechanisms, etc. By providing a balance weight that swings in the direction, the balance can be easily achieved. The four-cylinder stroke volume continuously variable device can be realized such.
In a single-shaft crank with cylinder bores arranged at substantially right angles on both sides of the crankshaft, if both ends of the motion conversion rocker arm are placed parallel to the cylinder hole, the cylinder pitch can be reduced, and the cross joint and direction change rocker arm It can be connected with links, and there is no need for multiple links, but even with two or four cylinders, all pistons stroke in the same direction and become unbalanced as with single cylinders, so they can be mounted on automobiles with low vibration In order to make a device, it is indispensable to use an opposed piston.
In addition, the mechanism that converts the direction of the reciprocating motion of the piston with the L-shaped arm-shaped direction conversion rocker arm and converts it into a rotational motion with the motion conversion rocker arm. Therefore, if the arm length on the connecting rod large end shaft mounting side of the direction conversion rocker arm is changed The stroke volume can be changed arbitrarily to some extent. If the length of the connecting rod is adjusted, the stroke volume can be freely selected with the same crankcase and cylinder.

Further, the invention of claim 2 is the invention of claim 1, wherein the rocker arm is pivoted at both ends of the motion converting rocker arm and supported in a fixed manner in the axial direction, and the rocking tip of the direction converting rocker arm is swung at each rocker arm. A link that can swing in parallel to the moving surface and that regulates displacement in the right-angle direction is provided, and a guide roller that rotates in contact with a swing guide that is parallel to the crankshaft is pivotally supported and strokes parallel and linearly to the crankshaft. By linking one of the links with a guide roller holder to form a multi-link mechanism, the rocker arm swing is converted to a right angle.
It is possible to convert the reciprocating motion of the opposed piston into the rotational motion of the crankshaft by swinging the both end shafts of the motion converting rocker arm on the plane including the crankshaft and restricting the motion in the perpendicular direction. The other arm end of the direction-changing rocker arm in the shape of an L-shaped arm as viewed in the direction of the oscillating shaft that supports the large end shaft of the connecting rod connected to the opposed piston orthogonal to the crankshaft and changes the direction to a right angle is Oscillates on a plane perpendicular to the oscillating surface of both end shafts, can rotate on both end shafts, and oscillates in a circular arc on the oscillating surface together with a cruciform joint that is supported in a fixed axial direction. A rocker that can swing in parallel to the rocking surface of each rocker arm, and a link that restricts displacement in the right-angle direction is provided on the cross joint and the other rocking tip of the direction change rocker arm, and contacts the rocking guide that is parallel to the crankshaft. A rotating guide roller is pivotally supported, and one of the links is connected by a guide roller holder that strokes parallel and linearly to the crankshaft to form a multi-link. While restricting the movement, it absorbs the arc-shaped movement of the other rocking tip of the cross joint and the direction change rocker arm, enabling the linear stroke of the guide roller holder, and the reciprocating movement of the opposed piston perpendicular to the crankshaft is cranked It can be converted into rotational movement of the shaft.

According to a third aspect of the present invention, in the first aspect of the present invention, the swing guide is provided with a flat surface on both sides parallel to the crankshaft and perpendicular to the swing surface of the direction changing rocker arm on both sides. The guide roller holder is provided with a plurality of guide rollers and is held by the guide roller holder, thereby enabling a stroke that keeps the posture of the guide roller holder with respect to the crankshaft constant, and the stroke position of each opposed piston is synchronized and stroked. .
As a method of enabling a stroke for keeping the posture of the holder holding the multiple links constant with respect to the crankshaft, a cylindrical shaft is provided in parallel to the crankshaft, and the holder having a cylindrical bearing hole that allows the cylindrical shaft to slide is used. When the links are connected, the structure can be simplified, but the sliding resistance tends to increase, and the positions of the left and right opposed pistons cannot be adjusted.
As in the present invention, the guide roller parallel to the crankshaft is contact-rolled by the guide roller and the guide roller itself is also pivotally supported by the roller bearing, so that mechanical loss can be greatly reduced and the outer diameter of the guide roller can be reduced. This is a necessary function for a high compression ratio engine with a structure that allows adjustment of the left and right opposed piston positions (synchronization of compression ratio) by selective assembly.

According to a fourth aspect of the present invention, in the first aspect of the present invention, the balance weight is arranged on the side of the cylinder that overlaps the piston bottom dead center position when viewed in the direction perpendicular to the cylinder hole.
The inertial force and inertial moment in the cylinder hole axial direction are balanced by using an opposed piston. However, an unbalance is generated in the perpendicular direction due to swinging of both end shafts, cruciform joints, double link mechanisms, etc. It is necessary to provide a balance weight that swings.
Although it is reasonable to provide a weight on the arm portion of the direction change rocker arm that supports the connecting rod large end shaft, it is difficult to balance because the cylinder skirt portion obstructs the swing radius of the weight center of gravity. .
Like the present invention, the balance weight is integrated with the direction change rocker arm on the side of the cylinder that overlaps the piston bottom dead center position when viewed in the direction perpendicular to the cylinder hole, thereby increasing the rocking radius of the weight center of gravity and reducing the weight. It is possible to balance it.

The invention of claim 5 is characterized in that, in the invention of claim 1, the position of the swing pivot axis of the direction changing rocker arm is displaced.
As in Patent Document 2, the first rotational support body that holds the swash plate with a variable inclination angle and the second rotational support body that connects the swash plate via a joint are interlocked to displace the axial position so that the stroke volume is obtained. In the case of a variable compression ratio, if the response difference occurs in both support axial position displacement mechanisms or one of them stops or runs out of control, the compression ratio changes greatly or the stroke volume cannot be changed. In addition, there is a danger of the piston hitting the cylinder heads and causing damage.
As in the present invention, by adopting a mechanism that can change the compression ratio independently, even if it stops or runs away, it does not hit the cylinder heads due to a change in the compression ratio within a certain range. It becomes a safer mechanism that can be varied.

According to a sixth aspect of the present invention, in the first aspect of the present invention, the accessory drive shaft is disposed substantially perpendicularly to the crankshaft and the cylinder hole substantially on the centerline of the crankshaft and the cylinder hole.
When the opposed piston oblique shaft type variable stroke volume device is used in an automobile engine, it is reasonable to arrange the cylinder and crankshaft in the horizontal direction and the cylinder on one side of the crankshaft direction and the transmissions on the opposite side. Therefore, the oil reservoir chamber is disposed in the radial direction of the crankshaft and below the cylinder. If an oil pump is placed there, and it is attempted to drive mechanically from the crankshaft so as not to interfere with the arrangement of the transmissions and cylinders, the crankshaft is placed in the space between both cylinders on the opposite side of the transmissions. It is reasonable to arrange the drive shaft at right angles, and as a result, space can be used effectively, and the camshaft that lifts the intake and exhaust valves is generally arranged at right angles to the cylinder holes and parallel to the cylinder rows. Because it is parallel to the shaft, the camshaft can be driven by installing a chain-driven drive sprocket, which is a common drive method for the camshaft, on the driveshaft, and auxiliary equipment is driven on the other end of the oil pump on the driveshaft. A pulley or the like can also be provided.

The invention of claim 7 is characterized in that, in the invention of claim 1, the bearings of the crankshaft, the oblique shaft, the ear shaft lifter, and the guide roller are roller bearings.
As shown in Patent Document 1, when the piston reciprocating motion of the piston is converted into a rotational force, the sliding force received by the piston of the bearing piston holding portion by the piston of the bearing piston holding part has a high sliding speed and a large friction. Resistance is generated and mechanical loss is large. As in Patent Document 2, when the piston outer periphery of the rail part and the cylinder are not in sliding contact with each other, the piston and cylinder contact part acts as a bending moment, resulting in a large frictional resistance. As a result, the reciprocating motion becomes difficult due to the wedge effect, and the swash plate and the rail are in sliding contact with each other. Therefore, the peripheral speed is high, and it is difficult to increase the rotation speed. As it is difficult to adopt. One way to solve these problems is to use spherical bearings at the large and small ends of the connecting rod, but it is difficult to manufacture and assemble spherical bearings, and a piston that withstands high rotation because a slap load is applied to the piston in all directions. It was difficult to do so, and the feasibility of an automobile engine in the conventional plan was low.
As in the present invention, in the power transmission process in which the piston reciprocating force is converted to the rotational force of the output shaft, the direction change is performed by rocking the rocker arm, link, cross joint, etc. Compared with Patent Documents 1 and 2, where the piston and swash plate receive the reaction force perpendicular to the piston reciprocating direction, the mechanical loss can be reduced and the peripheral speed and sliding speed are increased. By using this, it is possible to further reduce mechanical loss and increase the rotation speed, and by swinging the connecting rod on a single plane, it is possible to adopt the same piston as the conventional engine, and the swing angle of the connecting rod is higher than that of the conventional engine. The slap load and noise can be reduced and the weight can be reduced, so that it can be used in automobile engines.

According to the present invention, the piston reciprocating motion is converted into the crankshaft rotational motion on the oblique shaft, and the stroke volume and the compression ratio are changed by changing the inclination angle of the oblique shaft and the position in the crankshaft direction. Therefore, the mechanical loss is greatly reduced by reducing the sliding contact speed of the motion converter, the vibration is reduced by balancing the inertial force and moment of inertia of the reciprocating part, and the engine is rotated at a higher speed. An axial dimension can be shortened and the stroke volume continuous variable apparatus suitable for a motor vehicle engine can be provided.
In addition, the compression ratio can be arbitrarily changed at any time, and the stroke volume and the compression ratio can be changed by separate variable control mechanisms, so that the stroke volume and the compression ratio can be changed more stably. Because the variable range of the compression ratio is mechanically limited, even if the variable control mechanism runs out of control, the piston and cylinder head related parts are not in contact with each other and are safe, and the irreversible transmission mechanism is part of the variable mechanism. Since the stroke volume and the compression ratio can be kept constant without power, the power consumption can be suppressed and the fuel consumption can be reduced.

Embodiments of a continuously variable stroke volume device according to the present invention will be described below in detail with reference to the drawings. The continuously variable stroke volume device according to the present invention can be applied to a power device using various gasoline engines and diesel engines mounted on an automobile or the like.

The piston reciprocating motion is converted to the crankshaft rotational motion by the slant shaft provided in the single shaft crank, and the cylinder volume is changed to the crankshaft by changing the tilt angle of the slant shaft and the crankshaft direction position to change the stroke volume and compression ratio. And the other oscillating tip of the L-shaped arm of the direction changing rocker arm, which is arranged at substantially right angles on both sides with respect to the shafts on both ends of the motion converting rocker arm and connects the large end shaft of the connecting rod at the oscillating tip on one side and makes the piston face the opposite stroke. Rotating on the slant shaft, rotating on both ends of the motion conversion rocker arm held fixed in the axial direction, cruciform joints pivotally supported on the fixed axial direction, and links that swing perpendicular to each other and crankshaft holding them Are connected by a multi-link mechanism composed of a holder that strokes parallel to the shaft, and both end shafts are swung on a plane perpendicular to the cylinder hole including the crankshaft. The four-cylinder stroke volume continuously variable device is provided with a balance weight that swings in the opposite direction to the swing direction of both end shafts. The crank mechanism 10, the stroke volume variable mechanism 20, the stroke volume control mechanism 30, and the compression ratio variable. A mechanism 40 and an accessory driving mechanism 50 are included.

In the crank mechanism 10, the crankshaft 18 is axially fixed and rotatably supported by the front and rear crankcases 2 and 4 by the front and rear bearings 18-1 and 18-2, and is symmetrically positioned on both sides of the crankshaft. The cylinder holes of the R and L cylinders 1R and 1L are arranged substantially at right angles. In this embodiment, a solid needle roller bearing is used for the front bearing and a combined angular contact ball bearing is used for the rear bearing, and the outer race nut 18 The outer race is fixed to the rear crankcase at -3, and the inner race is sandwiched between the washer 18-4 inserted into the stepped portion of the crankshaft and the boss portion of the transmission engaging boss 19, and the crankshaft is tightened with the bolt 19-1. By tightening and fixing to the shaft, the backlash in the axial direction is minimized, and a strong radial and axial load due to combustion pressure and the like can be withstood. (See Figures 1-1 and 2)

The piston 11 is rotatably supported on the mating surfaces of the front and middle crankcases 2 and 3 at a cylinder hole on both sides of the crankshaft and at right angles to the crankshaft. One hole at the tip of the rocker that swings around the eccentric shafts 41Rb and 41Lb of the R and L direction conversion rocker arm pivot shafts 41R and 41L and that is parallel to the pivot shaft of the R and L direction conversion rocker arms 13R and 13L. The large end shaft 12-1 that is rotatably inserted and press-fitted into the large end hole of the connecting rod 12 and the piston pin 11-1 inserted into the hole of the piston are connected by a connecting rod, and the swing angle of the connecting rod The stroke can be stroked in the cylinder hole with little change. In this embodiment, in order to reduce the weight of the large end including the swinging tip of the direction changing rocker arm and simplify the lubrication path of the large end shaft part, the connecting rod can be loaded even if the large end width is narrowed. It is press-fitted to withstand large end holes and eliminate the need for lubrication. (See Figures 1-2 and 3)

The direction change rocker arm is an L-shaped arm that is substantially perpendicular to the swing axis direction, and is rotatable to the swing tip parallel to the pivot axis on the opposite side that pivotally supports the large end shaft. And the primary link 13-3 is press-fitted into the upper and lower ends thereof, so that the primary link is swingable in the direction parallel to the swing surface of the L-shaped arm, and the displacement is supported in the right-angle direction by restricting the displacement.
By inserting the shaft portion into the other hole of the upper and lower primary links, the shaft portion is freely rotatable, the axial direction is restricted, and the R and L guide roller holders 13-4R and 13-4L are held by the primary link. In the R and L guide roller holders, a hole perpendicular to the shaft portion is provided in the middle portion on the center line of the shaft portion supporting the pair of upper and lower primary links, and the secondary link shaft 13-5 is press-fitted. The R and L secondary links 14R and 14L are pivotally supported by the L guide roller holder so as to be restricted in the axial direction by the L guide roller holder and swingable on the secondary link shaft. In this embodiment, the secondary link shaft axis is arranged on the cylinder hole core, and the L-shaped arm of the direction changing rocker arm is formed in a single plane, thereby reducing the couple force and improving the strength. Is improving. The left and right pistons are stroked by the R and L direction conversion rocker arms and connecting rods connected to the primary link pivotally supported by the R and L guide roller holders integrated with the secondary link shaft. The counter piston is used to balance the cylinder bore. By disposing the opposed pistons on both end shafts of the motion conversion rocker arm, which will be described later, a 4-cylinder opposed piston engine in which the piston position is shifted to the top and bottom dead center in the upper and lower cylinder rows, each cylinder hole has a crankshaft and motion conversion The rocker arms are arranged on the same plane perpendicular to the rocking surfaces of both end shafts.
In addition, the cylinder skirt on the opposite side of the primary link shaft, that is, the piston position at the bottom dead center, overlaps the swing axis on the line connecting the primary link shaft axis and the swing axis when viewed from the swing axis direction. The weight center of gravity is arranged on the side of the cylinder skirt, and the R and L balance weight portions 13Rw and 13Lw are integrally provided on the side of the cylinder skirt portion when viewed in the direction perpendicular to the swing axis. In this embodiment, the balance weight part is molded separately from the L-shaped arm, and the shaft part is press-fitted and integrated to improve the moldability. After press-fitting in order to improve the strength and accuracy, There is also a method of welding and final finishing. Shim 13-1 is inserted between both ends of the swing shaft between the case and the axial clearance is adjusted to prevent friction and wear.
In this embodiment, the connecting rod large end shaft mounting side and the primary link shaft mounting side arm length of the direction change rocker arm are set to the same length, but if the arm length on the connecting rod large end shaft mounting side is changed, it is arbitrary to some extent. It is possible to change the stroke volume, and if the connecting rod length is adjusted, the stroke volume can be freely selected with the same crankcase and cylinder. (See Figures 1-1 to 5 and 5)

The slant shaft 15 includes a slant shaft fixing pin 15-2 that is press-fitted and fixed in the hole of the link holding portion 18a of the crankshaft, and a slant shaft fixing pin 15-2 that is press-fitted and fixed to the hole of the link holding portion 15a of the slant shaft. The slidably inserted into the inclined shaft fixed link 15-1 held in the axial direction at the end face of each link holding portion hole and the key groove shaped groove provided in the axial direction of the crankshaft. The ear shaft 15-3a of the ear shaft holder 15-3 is held on the crankshaft, and the inclination angle of the oblique shaft is changed by the axial movement of the ear shaft holder.
The oblique axis portion 15b axis of the oblique axis is set so as to pass on the axis line of the both ears, and the axis of the ear axis is set to move perpendicularly to the crankshaft and move in the axial direction of the crankshaft. A patent that varies the stroke volume and compression ratio by linking the first rotary support that holds the swash plate with a variable tilt angle and the second rotary support that connects the swash plate via a joint to displace the axial position. Compared with Document 2, Patent Document 1 changes the inclination angle of the oblique axis by axially fixing one swinging pivot shaft of the oblique axis fixing link that holds the oblique axis together with the ear axis and displacing the ear axis in the axial direction. Since the stroke volume and compression ratio are automatically determined by the axial position of the ear shaft, more stable control is possible. Due to the arrangement of the oblique shaft on both sides of the crankcase, variations are likely to occur due to the thermal expansion and rigidity of the crankcase.
As in the present invention, by fixing one swing pivot shaft of the inclined shaft fixing link in the axial direction with the crankshaft, the holding of the inclined shaft is completed on the rigid crankshaft with a low coefficient of thermal expansion. Variations in stroke volume and compression ratio can be reduced.
In addition, by setting the center position of the inclined shaft fixing pin hole of the link holding portion of the crankshaft and the inclined shaft, the change position of the swing shaft core of the multi-link mechanism connected to the cruciform joint 17 due to the inclination angle change of the inclined shaft can be changed. Since it can be arbitrarily set to some extent, a compression ratio suitable for the maximum and minimum stroke volume can be obtained without using a variable compression ratio mechanism for changing the phase of the direction change rocker arm pivot shaft as an eccentric shaft as in this embodiment. Can be arbitrarily set. In addition, a shaft with an ear shaft that can be supported by a single crankshaft with a variable tilt angle and an output shaft that transmits power to the transmission can be used in common. It can withstand high rotational torque, and by holding the pivot shaft of one of the slanted shaft fixed links in the axial direction on the crankshaft, the slanted shaft can be held on a rigid crankshaft with a low coefficient of thermal expansion. Therefore, variation in stroke volume and compression ratio can be reduced. (See Figures 1-1 to 4)

The rotation of the swash plate (slanted shaft) to the crankshaft can be fixed by the ear shaft and the swash plate (slanted shaft) fixed link (joint), but the weight increases to ensure the strength to withstand the rotational torque, and each bearing There is a drawback that the stroke volume varies greatly due to the phase change caused by the backlash in the rotational direction due to the clearance of the portion. The oblique shaft hole shape of the oblique shaft 15 is an oval shape, and the oblique shaft 15 is rotated and fixed with respect to the crankshaft at both plane portions perpendicular to and parallel to the axis of the ear shaft 15-3a provided with the crankshaft. Because it can be held back and forth in the rotational direction due to the clearance of only one flat part, and because it has high rigidity, it can secure the strength to withstand high torque, and the burden on the ear shaft and oblique shaft fixed link can be reduced. Weight can be reduced.
The motion converting rocker arm 16 is inserted into the outer race side, the bearing 16-1 fastened and fixed by the outer race nut 16-3 is inserted into the inclined shaft portion 15b, and the inner race is fastened and fixed by the inner race nut 16-2. Thus, the motion converting rocker arm is axially fixed and rotatably supported with respect to the oblique axis. The motion conversion rocker arm is provided with both ends 16a on the line passing through the intersection of the crankshaft, ear axis, and oblique axes, and the cross joint 17 can be rotated on both ends. Thrust washer 17-1, nut It is pivotally supported by fixing in the axial direction at 17-2. By making the other hole of the secondary link face the shaft provided at right angles to the shaft hole at both ends of the cross joint, the secondary link is fixed to the shaft in the axial direction, and the motion is converted by supporting it rotatably. A rocker arm and a direction change rocker arm are connected to form a multi-link mechanism. (See Figures 1-1, 2 and 4)

The R and L guide roller holders are provided with a stepped shaft beside the primary link swinging shaft, and can be freely rotated by a bearing 16-6. The shaft is fixed in the axial direction by a thrust washer 16-7 and a circlip 16-8. Two supported guide rollers 16-5 are provided side by side in front and rear, positioned by a knock pin 16-9, and clamped between the front and rear cases and fixed to the crank of the motion converting rocker arm swing guide 16-4. Four guide rollers on the top and bottom, front and rear, contact and roll on both sides that are parallel to the shaft and perpendicular to the cylinder hole, and the stroke axis of both ends of the motion conversion rocker arm is perpendicular to the cylinder hole including the crankshaft core. It is possible to make a stroke that keeps the posture of the R and L guide roller holders constant while swinging on a flat plane, and reciprocating the piston by synchronizing the left and right piston positions. It is converted into rotation of the crankshaft. (See Figures 1-1, 2, 3, and 5)

By receiving the reaction force when converting piston reciprocating motion into rotational force at the shaft and shaft end of the oscillating cross joint, double link mechanism, direction change rocker arm, the sliding speed is reduced and the peripheral speed is high. By using roller bearings for the crankshaft, motion conversion rocker arm, and guide roller, mechanical loss can be greatly reduced and high rotation speeds can be achieved. The piston can be used, and the connecting rod has a smaller swing angle than the conventional engine, so that the slap load and noise can be reduced, and the weight can be reduced. Most of the internal combustion engines that are currently mass-produced are single-crank multi-cylinder engines, which use an integral crank to withstand high rotational torque and large rotational inertia, and structurally use bearings around the crank as metal bearings. . In this example, the shaft and shaft end of the cross joint, double link, and direction change rocker arm that receive the reaction force in the perpendicular direction are in sliding contact. However, if it is a roller bearing, all the bearings of the continuous stroke volume variable mechanism can be made a roller bearing. Further, mechanical loss can be reduced.
Therefore, in this proposal, a stroke volume continuous variable mechanism that can change the tilt angle and position of the oblique axis is proposed, but even if the oblique axis is integrated with the crankshaft and the stroke volume is not variable, the mechanical loss is greatly reduced compared to the conventional engine. A possible variable compression ratio engine can be provided.
In addition, in order to axially fix and rotate the motion conversion rocker arm on the oblique axis, a combined angular contact ball bearing is adopted as a bearing in this embodiment, minimizing axial play and minimizing radial motion. To withstand axial loads.

In order to balance the rotation of the crankshaft as much as possible, the link holding portion 18a is lightened and lightened, and the crankshaft on the link holding portion side is notched and a weight portion 18w is provided on the opposite side, and the missing portion is inclined. A weight portion 15w is provided and balanced on the opposite side of the shaft to the link holding portion 15a. The unbalanced axial moment can be kept small by providing the crankshaft and the oblique shaft with the oblique shaft fixing link and its mounting portion on the crankshaft and the oblique shaft with the oblique shaft portion (crankshaft) sandwiched between the generating portion. (See Figures 1-1 and 4)

R, L direction conversion rocker arm pivot shaft, direction conversion rocker arm, large end shaft, double link mechanism, cross joint, motion conversion rocker arm both end shafts are provided with oil passages, and through the oil filter, R, L direction Forced lubrication with oil supplied from the center hole of the conversion rocker arm pivot shaft. (See Figures 1-2, 3, and 5)

The stroke volume variable mechanism 20 determines the phase of the female feed screw 21 with the knock pin 21-2, fixes it to the rear crankcase 4 with the bolt 21-1, and engages the male feed screw 22 with it. A bearing 22-1 is inserted in the inner diameter portion of the male feed screw so that the male feed screw can rotate freely on the ear shaft lifter 23 and is supported in the axial direction, and the outer race is fixed by the outer race nut 22-3. The inner race is fixed to the ear lifter at 22-2. As for the connection between the ear shaft holder and the ear shaft lifter, an ear shaft 15-3b similar to the ear shaft 15-3a that holds the oblique shaft is provided on the lifter side of the ear shaft holder, and the lifter has a hole core on the axis thereof. Even if the ear shaft holder is slid to the ear shaft lifter until the ear shaft 15-3b is aligned with the core of the boss hole, it is inserted into the boss hole and press-fitted into the ear shaft 15-3b. The inner end face of the boss hole and the outer end face of the ear shaft 15-3b are not interfered with each other, and the assembly is made possible by press-fitting the joint collar after matching.
The joint collar may be press-fitted into the boss hole of the ear shaft lifter.
The male / female feed screw and the ear shaft lifter are provided concentrically with the crankshaft, and the ear shaft lifter is supported by the crankshaft so as to be rotatable and slidable. ing. (See Figures 1-1 and 2)
In the present embodiment, a four-point contact ball bearing is adopted as the bearing 22-1 to enable high rotation, but a needle bearing or the like can also be used if it can cope with a low-rotation engine or centrifugal force. Moreover, trapezoidal screws, square screws, sawtooth screws, etc. can be considered as feed screws, but the screw lead angle should be less than the dynamic friction coefficient of the material used in order to make the screw part reliable irreversible transmission. Must be less than or equal to the static friction coefficient.

In the stroke volume control mechanism 30, a secondary idle gear 33 meshing with a driven gear provided integrally with a male feed screw is rotatably supported by a secondary idle gear shaft 33-1 via a bearing 33-2. A primary idle gear 32 meshing with the secondary idle gear is rotatably supported by a primary idle gear shaft 32-1 via a bearing 32-2, and a thrust washer 32-3 is interposed between the middle crankcase 3 and the rear crankcase 4. 33-3 and spacer 33-4 are arranged to determine the axial position while reducing rotational friction and wear, and are fixed to each case in the axial direction to prevent contact between the secondary idle gear and the driven gear of the primary idle gear. It is out. The driven gear provided integrally with the primary idle gear meshes with the drive pinion gear portion 31a of the stroke volume control motor 31, and the ear shaft connected to the female feed screw via the ear shaft lifter by forward and reverse rotation of the stroke volume control motor. By moving the holder in the direction of the crankshaft, the inclination angle of the oblique axis and the axial position are changed to change the stroke volume. The stroke volume is controlled by bringing the measurement contact portion into contact with the gear outer peripheral side surface of the male feed screw and detecting the axial displacement of the gear outer peripheral side surface with the lifter position detection sensor 35.
By setting the lead of the lead screw part to be equal to or less than the friction coefficient, non-reciprocal transmission is achieved, and an arbitrary stroke volume can be maintained without the need for electric power. (See Figures 1-2 and 3)

The variable compression ratio mechanism 40 is provided between the crankshaft and the R and L cylinders at the end of the oil reservoir chamber side of the R and L direction conversion rocker arm pivot shaft disposed at right angles to the crankshaft and the cylinder bore and parallel to each other. The gear portions 41Ra and 41La are engaged with the rack gears of the R and L rack shafts 45R and 45L provided at substantially right angles, and the R and L rack shafts are moved in opposite directions by the rotation of the feed screw shaft 44. The L-direction conversion rocker arm pivot shaft is rotated in the opposite direction, and the axial center positions of both side eccentric shaft portions 41Rb and 41Lb are displaced to symmetrical positions with respect to the swing planes of the axial shaft cores on both ends of the motion conversion rocker arm including the crankshaft core. Thus, the swing trajectory of the direction change rocker arm is changed symmetrically so that the left and right cylinders are variable at the same compression ratio.
In addition, the left and right screws of the feed screw portion 44b of the feed screw shaft are reversed to each other so that the R and L rack shafts can be moved in the reverse direction by rotating the feed screw shaft in one direction. Also, since the distance between the R and L direction conversion rocker arm pivot shafts is short relative to the stroke amount of the R and L rack shafts, the feed screw and the rack are arranged in the axial direction to ensure the stroke and the stroke chamber oil The rack shaft is provided with an oil relief hole that prevents the rack shaft from being locked and the resistance from increasing. Trapezoidal screws, square screws, sawtooth screws, etc. can be considered as the feed screws of the feed screw shaft and rack shaft feed screw portions 44b, 45Ra, 45La, but the swing pivot axis position is fixed without passing electric power to the motor. In order to keep the compression ratio constant, it is necessary to make the screw part surely irreversible transmission, and the screw lead angle should be less than or equal to the dynamic friction coefficient of the material used, and it is necessary to make it the minimum or less static friction coefficient.
Shafts provided on both sides of the driven gear portion 44a arranged at substantially the center of the feed screw shaft can be freely rotated and fixed in the axial direction by half-cap-shaped R and L feed screw shaft holders 47R and 47L and a middle crankcase. The pinion gear of the drive gear shaft 43, which is connected to the drive pinion gear portion 42a of the compression ratio control motor 42 and is integrally rotated with the driven gear portion 44a, is engaged with the driven gear portion 44a by the forward / reverse rotation of the compression ratio control motor. Variable compression ratio.
In this embodiment, the R and L rack shafts are arranged on the motion conversion rocker arm side with respect to the gear portion of the R and L direction conversion rocker arm pivot shafts, and the strokes in the direction in which the R and L rack shafts are arranged closer and widened at the lowest compression ratio. Thus, the eccentric shaft center phase of the pivot shaft is shifted by about 180 ° around the motion converting rocker arm side to change to the maximum compression ratio. Little change in compression ratio at °. Therefore, although it is possible to make the rack shaft stroke about half, it is possible to vary the pivot shaft phase of about 180 ° in order to accurately control the vicinity of the maximum compression ratio. Conversely, at the maximum low compression ratio, the R and L rack shafts are arranged close to each other and stroked in the direction of expansion, and the eccentric shaft center phase of the pivot shaft is shifted by about 180 ° around the opposite side of the motion conversion rocker arm to change to the minimum compression ratio. Thus, the vicinity of the minimum compression ratio can be controlled with high accuracy. (See Figures 1-2, 3, and 6)

By adopting a mechanism that can change the compression ratio independently, even if it stops or runs away, it does not hit the cylinder head due to a change in the compression ratio within a certain range, so it is safer to change the compression ratio arbitrarily at any time. It becomes a mechanism.
According to the present invention, even if the amount of change in the axial center position of the eccentric shaft portion of the direction-changing rocker arm pivot shaft is minimal, the compression ratio can be greatly varied. [In this embodiment layout, the shaft is about 2.5% of the maximum stroke. The amount of change in the center position (variable from 10.5 to 13 in the maximum stroke volume compression ratio and 10.5 to 15 in the minimum stroke volume compression ratio at 1/2 of the eccentric radius)], combustion pressure and reciprocating motion part The moment load on the eccentric shaft portion due to the load of inertial force is small, the compression ratio control motor can also change the compression ratio with a small capacity and low power, the load on the gear portion is small, and there is no problem in strength.
The R and L rack shafts are assembled to the middle crankcase by assembling the feed screw shaft to the middle crankcase with the R and L feed screw shaft holders, and then the R and L rack shafts to the compression ratio control motor and cap. 48 Insert through the left and right holes of the mounting part, rotate the feed screw shaft and mesh and assemble the feed screw part, then the R and L rack shaft racks and the gear part of the R and L direction change rocker arm pivot shaft are inserted into the left and right eccentric shafts. Assemble and assemble so that the parts phase match.
The compression ratio is applied to the direction change rocker arm pivot shaft phase detection sensor 46 which faces the groove in the grooved plug 41-1 which is press-fitted to the shaft end of the R direction change rocker arm pivot shaft. By detecting the phase change of the R direction change rocker arm pivot shaft, the change of the direction change rocker arm pivot shaft position with respect to the oblique axis is read and controlled. (See Figures 1-2, 3, and 6)

The auxiliary machinery drive mechanism 50 has an auxiliary machinery drive shaft 51 disposed on the crankshaft axis at a right angle to the crankshaft and the R and L cylinders on the opposite side of the transmission chamber, and splined to the stepped shaft of the crankshaft. The drive bevel gear 52, which is rotationally fixed and axially fixed by a nut 52-2, is engaged with a driven bevel gear 53 that is press-fitted and fixed to an accessory drive shaft so that power is transmitted to the auxiliary accessories. The lower side of the accessory drive shaft is rotatably supported by a lower bearing 51-1, and an accessory (not shown) such as an oil pump is disposed and driven at the tip. On the upper side, an auxiliary bearing drive shaft 51-2 that rotatably supports an accessory drive shaft and is axially fixed is inserted into a bearing holder 54 that is fixed to the front crankcase with bolts, and an outer race by a nut 51-4. Is fixed in the axial direction, and by adjusting the thickness of the shim 54-1 and shim 52-1, the axial position with respect to the accessory drive shaft and the crankshaft is changed, and the tooth contact of the bevel gear can be adjusted. .
Camshaft drive sprocket 55 Auxiliary machinery driving pulley 56 and the like are rotationally fixed by a spline and axially fixed by a bolt or the like (not shown), whereby the inner race of the upper bearing is axially fixed to the auxiliary machinery driving shaft. A middle bearing 51-3 is provided in the vicinity of the gear in order to prevent a swing of the accessory drive shaft due to the load of the bevel gear portion. (See Figures 1-1, 2 and 3)

When the opposed piston oblique shaft type variable stroke volume device is used in an automobile engine, it is reasonable to arrange the cylinder and crankshaft in the horizontal direction and the cylinder on one side of the crankshaft direction and the transmissions on the opposite side. Therefore, the oil reservoir chamber is disposed in the radial direction of the crankshaft and below the cylinder. If an oil pump is placed there, and it is attempted to drive mechanically from the crankshaft so as not to interfere with the arrangement of the transmissions and cylinders, the crankshaft is placed in the space between both cylinders on the opposite side of the transmissions. It is reasonable to arrange the drive shaft at right angles, and as a result, space can be used effectively, and the camshaft that lifts the intake and exhaust valves is generally arranged at right angles to the cylinder holes and parallel to the cylinder rows. Because it is parallel to the shaft, the camshaft can be driven by installing a chain-driven drive sprocket, which is a common drive method for the camshaft, on the driveshaft, and auxiliary equipment is driven on the other end of the oil pump on the driveshaft. A pulley or the like can also be provided.
In this embodiment, a solid needle roller bearing is used for the lower bearing, and a combined angular contact ball bearing is used for the upper bearing to minimize backlash in the axial direction and to cope with the noise and strength of the bevel gear section.
In the case of a 4-cycle engine, the camshaft only needs to make one revolution by reciprocating two pistons. Therefore, in this embodiment, the rotation of the accessory drive shaft is reduced to 4 / 3≈1.33 with respect to the crankshaft. By setting the shaft rotation to 3/2 = 1.5 relative to the accessory drive shaft and finally setting the reduction ratio to 2 relative to the crankshaft rotation relative to the crankshaft, the oil pump and water pump can be Even if it is directly connected to the drive shaft, it is possible to reduce the size by increasing the rotational speed to the range where cavitation does not occur at the maximum rotational speed of a general automobile gasoline engine. When the rotation is high with a small displacement, the reduction ratio can be increased from 1.5 etc. to 2.

In the following, the embodiment will be mainly described in the crankcase block portion in which the continuously variable stroke volume device at the minimum compression ratio is accommodated, and the cam chain related to the valve operating device, the oil pump, and the auxiliary machines are both shown and described. Omitted. The stroke volume continuously variable device described in this embodiment is a four-cylinder. Fig. 1-1 shows the maximum stroke volume at the minimum compression ratio of the upper cylinder (at bottom dead center), and the two-dot chain line shows the center line of the motion conversion rocker arm and secondary link at the minimum stroke volume at the minimum compression ratio. Is shown. Fig. 1-2 shows the maximum stroke volume at the lowest compression ratio of the lower cylinder (at top dead center). The two-dot chain line shows the direction change rocker arm, primary link, and connecting rod at the maximum stroke volume at the highest compression ratio. The center line is shown.
The present invention is not limited to four cylinders, but can be adopted for two cylinders. However, if it is desired to take unbalance in the direction perpendicular to the cylinder on the non-cylinder side in two cylinders, it is necessary to provide only a swing balance weight.
In each of the drawings, part of the drawing is omitted as necessary. In this embodiment, the crankshaft is arranged in the horizontal direction, and R and L used for reference numerals are on the right side when viewed from the transmission side. R, the left side is L, the transmission side is the rear, the cylinder side is the front, the oil reservoir chamber side is down, and the cam chain chamber side is up.

It is a top view (sectional view which meets an AA line of Drawing 1-2) which shows a stroke volume continuous variable device concerning this embodiment. It is sectional drawing which follows the BB line of FIGS. 1-1. It is sectional drawing which follows the CC line of FIGS. 1-2. It is sectional drawing which follows the DD line | wire of FIGS. 1-1. It is sectional drawing which follows the EE line of FIGS. 1-2. It is sectional drawing which follows the FF line | wire of FIGS. 1-3.

1 (R, L) (R, L) cylinder 2 Front crankcase 3 Middle crankcase 4 Rear crankcase 4-1 Oil seal 5-1 Camshaft drive chain upper cover 5-2 Camshaft drive chain lower cover 6 Bevel gear cap 10 Crank mechanism 11 Piston 11-1 Piston pin 12 Connecting rod 12-1 Large end shaft 13 (R, L) (R, L) direction change rocker arm
13 (R, L) w (R, L) balance weight part 13-1 shim 13-2 primary link shaft 13-3 primary link 13-4 (R, L) (R, L) guide roller holder 13-5 two Next link shaft 13-6 to 9 Plug 14 (R, L) (R, L) Secondary link 15 Oblique shaft 15a Link holding portion
15b Oblique shaft
15w Weight part 15-1 Oblique shaft fixing link 15-2 Oblique shaft fixing pin 15-3 Ear shaft holder 15-3a Ear shaft
15-3b Ear shaft 16 Motion conversion rocker arm 16a Both end shaft 16-1 Bearing 16-2 Inner race nut 16-3 Outer race nut 16-4 Motion conversion rocker arm swing guide 16-5 Guide roller 16-6 Bearing 16-7 Thrust Washer 16-8 Circlip 16-9 Dowel pin 17 Cross joint 17-1 Thrust washer 17-2 Nut 17-3 Plug 18 Crankshaft
18a Link holding part
18w Weight part 18-1 Front bearing 18-2 Rear bearing 18-3 Outer race nut 18-4 Washer 19 Transmission engaging boss 19-1 Bolt 20 Stroke volume variable mechanism 21 Female feed screw 21-1 Bolt 21-2 Knock pin 22 Male feed screw 22-1 Bearing 22-2 Inner race nut 22-3 Outer race nut 23 Ear shaft lifter 23-1 Joint collar 30 Stroke volume control mechanism 31 Stroke volume control motor 31a Drive pinion gear 31-1 Bolt 32 Primary idle Gear 32-1 Primary idler gear shaft 32-2 Bearing 32-3 Thrust washer 33 Secondary idler gear 33-1 Secondary idler gear shaft 33-2 Bearing 33-3 Thrust washer 33-4 Spacer 35 Lifter position Sensor 40 variable compression ratio mechanism 41 (R, L) (R, L) redirecting rocker arm pivot shaft
41 (R, L) a Gear part
41 (R, L) b Eccentric shaft portion 41-1-Slotted plug 41-2 Plug 41-3 C ring 41-4 Plug 42 Compression ratio control motor 42a Drive pinion gear portion 43 Drive gear shaft 44 Feed screw shaft 44a Driven gear Part
44b Feed screw portion 45 (R, L) (R, L) Rack shaft 45 (R, L) a Feed screw portion 46 Direction change rocker arm pivot shaft phase detection sensor 47 (R, L) (R, L) feed screw shaft Holder 48 Cap 50 Auxiliary machinery drive mechanism 51 Auxiliary machinery drive shaft 51-1 Lower bearing 51-2 Upper bearing 51-3 Middle bearing 51-4 Nut 52 Drive bevel gear 52-1 Shim 52-2 Nut 53 Driven bevel gear 54 Bearing Holder 54-1 Shim 55 Camshaft drive sprocket 56 Auxiliary machinery drive pulley

Claims (7)

A cruciform joint that is pivotally supported on an axis fixed to the axial direction, and can be rotated on both ends of a motion conversion rocker arm that is rotatably and axially fixed, on a slant shaft that is provided with a variable tilt angle and axial position on a single-axis crank, Cylinder holes are arranged at substantially right angles on both sides of the crankshaft and both end shafts, and the connecting rod large end shaft is connected at the one-side swinging tip, and the piston is stroked oppositely. One swinging tip is connected by a multi-link mechanism consisting of a link that swings in a direction perpendicular to each other and a holder that holds them and strokes in parallel to the crankshaft, and both end shafts are cylinder holes including the crankshaft. A four-cylinder stroke volume continuously variable device equipped with a balance weight that swings on a plane perpendicular to the shaft to convert the reciprocating motion of the piston into rotation of the crankshaft and swings in the opposite direction of the shafts at both ends. . A link that can rotate on both ends of the motion conversion rocker arm and is supported in a fixed axial direction, and a rocking tip of the direction conversion rocker arm that can swing in parallel with the rocking surface of each rocker arm. A guide roller that rotates in contact with a swing guide provided parallel to the crankshaft is supported, and one of the links is connected by a guide roller holder that strokes in parallel and linearly with the crankshaft. The stroke volume continuous variable device according to claim 1, wherein, by configuring, the swing of each rocker arm is converted to a right angle. The swing guide is provided with a flat surface on both sides parallel to the crankshaft and perpendicular to the swing surface of the direction change rocker arm on both sides, and a plurality of guide rollers are provided for each surface and held by the guide roller holder. The continuous stroke volume variable device according to claim 1, wherein a stroke for maintaining a constant posture of the guide roller holder with respect to the crankshaft is enabled, and a stroke position of each opposed piston is synchronized and stroked. 2. The stroke volume continuous variable device according to claim 1, wherein the balance weight is disposed on a cylinder side portion overlapping with a piston bottom dead center position when viewed in a direction perpendicular to the cylinder hole. The stroke volume continuous variable device according to claim 1, wherein the position of the swing pivot axis of the direction change rocker arm is displaced. 2. The stroke volume continuously variable device according to claim 1, wherein the accessory drive shaft is disposed at a right angle to the crankshaft and the cylinder hole substantially on the centerline of the crankshaft and the cylinder hole. The stroke volume continuous variable device according to claim 1, wherein the bearings of the crankshaft, the oblique shaft, the ear shaft lifter, and the guide roller are roller bearings.

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