JP2016109109A - Stroke volume continuous variable device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To resolve disadvantages found in the prior art stroke volume continuous variable engine that a part receiving a reaction force of a slant plate [an inclined shaft] for converting a piston stroke into rotation shows a large mechanical loss due to its sliding and a structure of making its contact speed fast, and an inertia force and an inertia moment at a reciprocating motion part may become easily an unbalanced state due to arrangement of multi-cylinder at an outer periphery of a crank shaft.SOLUTION: This invention relates to a double-cylinder stroke volume continuous variable mechanism that is added with another double-cylinder stroke volume continuous variable mechanism in parallel with an oscillation plane co-operated under the same number of rotation in a reverse direction to have four cylinders in total constituted in such a way that cylinder shafts are arranged at both sides of a crank shaft in a symmetrical and substantial parallel manner, an oscillating extremity end of a swing arm connecting a large end shaft of a connecting rod connected to a piston to stroke it is connected to a cross joint rotatably supported at both end shafts of a rocker arm rotatably and axially attached to a slant shaft of which inclination angle and position are variable against the crank shaft, and both end shafts of the rocker arm are oscillated on a plane including the crank shaft.SELECTED DRAWING: Figure 1-1

Description

The present invention relates to a device for continuously changing a stroke volume in an engine such as an automobile, and also to a device capable of setting a compression ratio according to the stroke volume, or arbitrarily continuously changing as needed.

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, and the mechanical loss is large, which makes it difficult to adopt as an automobile engine. 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. Further, when a cylinder is arranged on the outer periphery of one swash plate and the output shaft as in Patent Documents 1 and 2, it is often difficult to balance the moment of inertia of the reciprocating motion part.
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. However, the mechanism for changing the tilt angle of the swash plate (slant axis) is not sufficient in terms of accuracy and safety, and has not been put into practical use.

The present invention has been made in view of the above-described problems. A swing in which cylinder holes are arranged substantially in parallel on both sides of a crankshaft and connected to a large end shaft of a connecting rod connected to a piston to stroke the piston. Rotating, axially fixed cross supported on both ends of the rocker arm, which is pivotally supported by a roller bearing on a tilting shaft provided with a variable tilt angle and position on the crankshaft. A two-cylinder stroke volume continuously variable device that connects the joint with a joint link and swings both ends of the rocker arm on a plane that includes the crankshaft is provided in parallel with the plane. This is a four-cylinder stroke volume continuously variable device that is linked by the same rotation speed and reverse rotation, and the piston position on both planes on one side of both crankshafts is shifted to the top dead center. When converting the force of movement into the rotational force of the output shaft, the cross joint, joint link, and swing arm receive the reaction force perpendicular to the piston reciprocating direction, so the sliding speed of the load receiving surface is received by the piston and swash plate. Compared to Patent Documents 1 and 2, the mechanical loss can be significantly reduced, and high rotation can be achieved by using a roller rotary bearing for the rocker arm. In addition, the inertial force and moment of inertia of the reciprocating motion part can be balanced by using four cylinders in which the piston positions on both sides of the crankshaft are shifted to the top and bottom dead centers. Furthermore, the present invention provides a continuous stroke volume variable device that can arbitrarily change the compression ratio at any time by providing a mechanism for shifting the swing axis position of the swing arm.

The invention according to claim 1 for solving the above-mentioned problem is a swing arm in which cylinder holes are arranged substantially in parallel on both sides of the crankshaft and connected to the large end shaft of the connecting rod connected to the piston to stroke the piston. The tilting axis of the oscillating tip and the ear shaft, which is arranged at right angles on the shaft shaft of the crankshaft and can be moved in the axial direction, can be tilted with the shaft shaft aligned with the ear shaft axis. The rocker arm is rotatably supported by a roller bearing on the oblique axis, and is fixed to both ends of the rocker arm that is supported in the axial direction by a joint link. Set the shaft on a line that passes through the intersection of the axis of the crankshaft, ear shaft, and oblique shaft, and swing the swing arm and joint link in parallel to both end shafts so that both end shafts of the rocker arm are on the plane including the crankshaft. Swing stroke Characterized by the product continuously variable device.
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, the sliding speed is reduced by receiving the reaction force in the perpendicular direction when converting the piston reciprocating motion into the rotational force at the swinging cross joint, joint link, shaft of the swing arm and the shaft end, By using a rocker arm rotary bearing on a slanted shaft with a fast peripheral speed as a roller bearing, the mechanical loss can be greatly reduced and high rotation 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.

The invention of claim 2 is characterized in that, in the invention of claim 1, the position of the swing pivot axis of the swing 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 third aspect of the present invention, in the first aspect of the present invention, the ear shaft for holding the oblique shaft with a variable inclination angle is provided at right angles to the key-shaped plate and slides in the key groove provided on the crank shaft for axial movement. It is characterized by being performed.
In a structure such as Patent Documents 1 and 2 in which an output shaft for a transmission is provided separately from a shaft provided with an ear shaft that supports a swash plate (slant shaft) with a variable tilt angle, the output shaft becomes thin and rotates at a large speed. Inertia, difficult to withstand high rotational torque.
Like the present invention, the output shaft can be shared with the shaft provided with the ear shaft that supports the tilt angle of the slant axis with a single crankshaft, so that the output shaft can be made to have high rigidity, high rotation inertia, high rotation Can withstand torque.

According to a fourth aspect of the present invention, in the first aspect of the present invention, the inclined shaft fixing link that holds the inclined shaft together with the ear shaft is pivotally supported by the crank shaft.
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.

According to a fifth aspect of the present invention, in the first aspect of the present invention, the rotation of the oblique shaft with respect to the crankshaft is fixed at the inclined shaft hole and the flat portion provided in the crankshaft.
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). 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.
As in the present invention, by rotating and fixing at the flat part provided in the inclined shaft hole and the crankshaft, it is possible to suppress the backlash in the rotational direction due to the clearance of one flat part, and the rigidity is also high. The strength to withstand the torque can be secured, and the burden on the ear shaft and the oblique shaft fixing link can be lightened, so the weight can be reduced.

The invention of claim 6 is characterized in that, in the invention of claim 1, balance weights in the rotational direction are provided on the crankshaft and the oblique shaft.
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.

According to a seventh aspect of the present invention, in the first aspect of the present invention, another two-cylinder stroke volume continuously variable device is provided in parallel with the rocking planes of the rocker arm end shafts, and the other crankshaft with respect to one crankshaft is provided. The crankshaft rotation phase that is shifted by 180 ° at a position perpendicular to the swing plane is interlocked by the same rotation speed and reverse rotation, and the inclination angle of the oblique axis and the axial position are the same for both crankshafts. A four-cylinder stroke volume continuously variable device that can be varied as described above.
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, the crankshaft rotation phase is shifted by 180 ° to the position perpendicular to the swing plane with respect to the other crankshaft, and the piston positions on both planes on one side with respect to both crankshafts are raised and lowered. A four-cylinder stroke volume continuously variable device that is linked with the same rotational speed and reverse rotation, and that the inclination angle of the oblique axis and the axial position are the same for both crankshafts, with the arrangement shifted to the dead center. By doing so, the inertial force and the moment of inertia can be balanced, and the engine has less vibration.

The invention of claim 8 is characterized in that, in the invention of claim 7, the positions of the ear shafts of both crankshafts are varied by one motor.
Although the total displacement can be varied by changing the stroke volume for each crankshaft, that is, every two cylinders, burning all the cylinders will put a burden on the cylinder with a large stroke volume and cause damage such as seizure. Unless a so-called deactivation mechanism that does not burn these two cylinders is adopted, it is better to vary all cylinders with the same stroke volume, and the response speed is slower when varying with one motor than when varying with separate motors. Therefore, although it is necessary to increase the motor capacity, there is no variation due to the difference in motor response, so that it is possible to vary with a smaller stroke volume difference.

The invention of claim 9 is characterized in that, in the inventions of claims 1 and 7, the accessory drive shaft is disposed between the cylinders at right angles to the crankshaft and transmits power to the camshaft.
When a swash plate (slant shaft) stroke volume variable device is used in an automobile engine, a cylinder head is disposed on one side in the crankshaft direction and a transmission is disposed on the opposite side. Will be placed in the direction. If an oil pump is placed there, and it is mechanically driven from the crankshaft so as not to interfere with the arrangement of transmissions, cylinders, and cylinder heads, the space between the cylinders on the opposite side of the transmissions It is reasonable to dispose the drive shaft at a right angle from the crankshaft. As a result, space can be used effectively, and the camshaft for lifting the intake and exhaust valves is generally disposed at a right angle to the cylinder hole. Because it is parallel, the camshaft can be driven by providing a drive sprocket of chain drive, which is a general drive method of the camshaft, on the drive shaft, and a drive pulley of auxiliary equipment etc. on the other end of the oil pump of the drive shaft Can also be provided.

The invention of claim 10 is the invention of claims 1 and 7, wherein the displacement of the swing pivot axis position of the swing arm is performed by one motor, and a nonreciprocal transmission mechanism is used as a part of the driving force transmission mechanism. It is characterized by that.
Providing the swing pivot shaft of the swing arm on the crankshaft side is difficult because the crankshaft and the inclined shaft are obstructed, so they are arranged on both sides away from the crankshaft.
If a shaft displacement mechanism is provided for each of the left and right pivot shafts, the degree of freedom in layout increases. However, a difference in the compression ratio between the left and right cylinders due to a difference in response occurs, and two displacement mechanisms are required. Cause an increase. If one motor is used to displace the left and right pivot shafts, the transmission distance of the driving force transmission mechanism will be longer. However, for the other hand, the motor can be powered by providing a nonreciprocal transmission mechanism in part of the driving force transmission mechanism. The swing pivot axis position can be maintained without passing through.

The invention of claim 11 is characterized in that, in the invention of claim 7, a mechanism for displacing the swing pivot axis position of the swing arm is disposed between both crankshafts.
In the four-cylinder stroke volume variable device, it is possible to arrange a mechanism for displacing the swing pivot axis position by effectively using the space between the two crankshafts and to shorten the distance between the gear part and both eccentric shaft parts. Therefore, the torsional rigidity can be increased, and the pivot shaft strength and the positional accuracy can be improved.

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. The mechanical loss is greatly reduced by reducing the sliding contact speed, and the vibration is reduced by balancing the inertial force and moment of inertia of the reciprocating motion part, so that the engine can be rotated at a high speed, and the stroke volume continuously variable device can be adopted for an automobile engine. Become. 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. Furthermore, if a continuously variable valve lift such as a three-dimensional cam is employed as in this embodiment, an ultimate engine that can continuously vary all of the intake, exhaust lift, compression ratio, and stroke volume can be realized.

Hereinafter, preferred embodiments of a continuously variable stroke volume device and an engine including the same according to the present invention will be described 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.

Piston reciprocating motion is converted to crankshaft rotational motion on the slant shaft, and the cylinder bore is symmetrically parallel to both sides of the crankshaft in order to change the tilt angle of the slant shaft and the position in the crankshaft direction to vary the stroke volume and compression ratio. The swinging tip of the swing arm that connects and connects the large end shaft of the connecting rod connected to the piston and strokes the piston, and the slant shaft that is variable in inclination angle and position on the crankshaft are rotatably held A two-cylinder stroke volume continuously variable mechanism that is connected to a cruciform joint that is rotatable on both end shafts of the rocker arm and supported in a fixed axial direction by a link, and that swings both end shafts of the rocker arm on a plane including the crankshaft, Another two-cylinder stroke volume continuous variable mechanism is provided in parallel with the swing plane, and is linked with the same rotational speed and reverse rotation to form four cylinders. The crank mechanism 10 and the stroke volume variable mechanism 2 , Including stroke volume control mechanism 30, variable compression ratio mechanism 40, auxiliary machinery driving mechanism 50.

The crank mechanism 10 has upper and lower crankshafts 18U and 18L supported on the front and rear crankcases 2 and 3 so that the front and rear bearings 18-1, 18U-2 and 18L-2 are axially fixed and rotatable. Cylinder holes of the cylinder 1 are arranged on both sides of each crankshaft substantially parallel to the symmetrical position. 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 18U is used. -3, 18L-3, the outer race is fixed to the rear crankcase 3, and the inner race is sandwiched between the washer 18-4 inserted in the stepped portion of the crankshaft and the upper, the bosses of the lower crankshaft gears 19U, 19L, The bolts 19-1 and nuts 19-2 are fastened to the crankshaft to minimize axial backlash and to withstand strong radial and axial loads caused by combustion pressure. .
The piston 11 is parallel to the pivot axis of the swing arm 13 that swings around the eccentric shaft portions 41Rb and 41Lb of the R and L swing arm pivot shafts 41R and 41L disposed outside the cylinder hole with respect to the crankshaft. A large end shaft 12-1 that is rotatably inserted into a hole at the tip of a swinging shaft and a piston pin 11-1 that is inserted into a hole of the piston 11 are connected by a connecting rod 12 to change the swinging angle of the connecting rod. The stroke inside the cylinder hole is made possible by keeping it small. (See Figures 1-1 and 2)
In the present invention, in order to reduce the swing inertia weight of the swing arm 13, the cylinder hole arrangement is substantially parallel to both sides of each crankshaft. However, in order to make the crankshaft direction compact, The shape of a rocker arm in the shape of a letter, and the large end shaft 12-1 is pivotally supported by a swinging tip different from the pivoting tip of the joint link 14, and the piston is stroked. However, the cylinder arrangement can be freely selected from the V type to the opposed engine.

The slant shaft 15 is press-fitted and fixed to the slant shaft fixing pin 15-2 press-fitted into the holes of the link holding portions 18Ua and 18La of the upper and lower crank shafts 18U and 18L, and the link holding portion 15a of the slant shaft 15. In the axial direction of the oblique shaft fixing link 15-1 held by the oblique shaft fixing pin 15-2 so as to be swingable and fixed in the axial direction at the hole end face of each link holding portion, and the upper and lower crankshafts 18U and 18L. The ear shaft 15-3a of the ear shaft holder 15-3, which is slidably inserted into the provided key groove-shaped groove, is held on the crankshaft, and the oblique shaft is moved by the axial movement of the ear shaft holder 15-3. The inclination angle of 15 is changed. The oblique axis portion 15b axis of the oblique axis passes through the axis line of both ear shafts, and the axis of the ear axis is set to move perpendicularly to the crankshaft and move in the axial direction of the crankshaft.
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 axis of the joint link 14 of the cruciform joint 17 due to the inclination angle change of the oblique shaft can be arbitrarily set to some extent. Therefore, the compression ratio in the maximum and minimum stroke volume can be arbitrarily set to an appropriate compression ratio without providing a variable compression ratio mechanism that changes the phase of the swing arm pivot shaft as an eccentric shaft as in this embodiment. . 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, 2 and 5)

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.
By inserting the rocker arm 16 on the outer race side and inserting the bearing 16-1 tightened and fixed with the outer race nut 16-3 into the inclined shaft portion 15b, and fixing the inner race with the inner race nut 16-2. The rocker arm 16 is axially fixed and rotatably supported with respect to the oblique shaft 15. The rocker arm 16 is provided with both end shafts 16a on a line passing through the intersections of the crankshaft, ear shaft and oblique shaft. A cross joint 17 can be rotated on both end shafts 16a, a thrust washer 17-1, a nut 17-. 2 is axially fixed and fixed in the axial direction. The cruciform joint 17 and the swinging tip of the swing arm 13 are connected to each other by press-fitting the joint link 14 to the stepped shafts on both sides of the large end shaft 12-1, which is rotatably inserted into the hole at the swinging tip. On the other hand, the large end shaft and the joint link are fixed in the axial direction and supported rotatably, and the other hole of the joint link faces the shaft provided at right angles to the shaft holes at both ends of the cross joint 17 so that On the other hand, the joint link is fixedly supported in the axial direction and connected by pivotally supporting it, and the rotation of the rocker arm 16 is restricted, and the swing arm and the joint link are swung in parallel with the both end shafts. By swinging on a plane, the reciprocating motion of the piston is converted into the rotation of the crankshaft.
The slanted shaft, which has a fast peripheral speed, reduces the sliding speed by receiving the reaction force in the perpendicular direction when converting the piston reciprocating motion into the rotational force at the shaft and shaft end of the oscillating cross joint, joint link, swing arm. By making the rocker arm rotary bearing to the roller bearing, the mechanical loss can be greatly reduced and high rotation can be achieved, and the connecting rod can be swung on a single plane to adopt the same piston as the conventional engine, In addition, the connecting rod swing angle is smaller 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 adopted for an automobile engine. 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 embodiment, the cross joints, joint links, and swing arm shafts that receive a reaction force in the perpendicular direction are in sliding contact, but if they are made of roller bearings, all of the bearings around the crank can be made roller roller bearings, further reducing mechanical loss. It becomes. (See Figures 1-1, 2 and 5)
In addition, in order to support the rocker arm axially fixed to the oblique axis and to be rotatably supported, in this embodiment, a combined angular contact ball bearing is employed as a bearing, minimizing axial backlash and strong due to combustion pressure, etc. It can withstand heavy radial and axial loads.

In the lower crankshaft 18L, the swing planes of the both end shafts 16a of the rocker arm 16 are parallel to each other with respect to the upper crankshaft 18U, the shaft position is perpendicular to the swing plane, and the axial direction is also the same position. Are arranged 180 ° apart from each other, and the upper and lower crankshaft gears 19U and 19L are assembled at the crankshaft end to interlock with each other at the same rotational speed and reverse rotation to form a four-cylinder stroke volume continuously variable device. (FIG. 1-1 shows the upper crankshaft side, the link holding portion 18Ua is on the left side and the left side is the top dead center. The lower crankshaft side is shifted 180 ° so that the link holding portion 18La is on the right side and the right side is on the upper side. From this state, the upper and lower crankshaft gears are fluid-sealed from the transmission chamber in the gear case 4 and are not shown in the wall of the rear crankcase 3 (not shown). It is structured such that it is lubricated with engine oil taken from the crank chamber through the provided hole and returned to the crank chamber through the return hole.
By adopting a four-cylinder stroke volume continuously variable device in which the inclination angle of the oblique axis and the axial position of both crankshafts are the same, the inertia force and moment of inertia can be balanced, resulting in an engine with less vibration.
In order to balance the rotation of the crankshaft as much as possible, the link holding portions 18Ua and 18La are made lighter and lighter, and the crankshaft on the link holding portion side is notched and weight portions 18Uw and 18Lw are provided on the opposite side. A weight portion 15w is provided on the opposite side of the inclined shaft 15 to the link holding portion 15a for balancing. 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. In this embodiment, the transmission engaging boss portion 19Ua is provided on the crankshaft gear 19U on the upper crankshaft side, but it may be provided on the lower crank side according to the layout of the transmission. (See Figures 1-1 and 2)

The swing arm 13 finely adjusts the axial position by shims 13-1 disposed on both end faces of the swing pivot shaft so that the phases of both rocker arms 16 are matched and can swing smoothly. The lubrication of the R, L swing arm pivot shaft, swing arm, large end shaft, connecting rod large end, cross joint, rocker arm both end shaft is forcibly lubricated with oil supplied from the center hole of the R, L swing arm pivot shaft. .
In this embodiment, the pivot plane of the connecting rod 12 in the axial direction (that is, the center of the cylinder hole) is aligned with the pivot plane of the shaft core of both end shafts 16a of the rocker arm 16, but the cylinder pitch is reduced. It is also possible to dispose them in correspondence. Further, in this embodiment, the joint link and the swing arm are both supported, but can be cantilevered if the strength and rigidity can be supported.
In the case of a two-cylinder stroke volume variable device, the swing arm 13 has a rocker arm shape that swings by providing a balance weight that balances the reciprocating motion part on the opposite side of the swinging pivot axis of the swing arm to the large end shaft mounting part, Vibration can be reduced. (See Figures 1-1, 3 and 6)

The stroke volume variable mechanism 20 determines the phase of the upper and lower female feed screws 21U and 21L with the knock pin 21-2 and fixes it to the rear crankcase 3 with the bolt 21-1, and is linked to each other at the same rotational speed and reverse rotation. The upper and lower male feed screws 22U and 22L having gears for engaging are engaged. 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 at 22-2. The feed screw and gear are positioned so that the axial positions of the upper and lower male feed screws are the same when the gears are engaged. The feed screw moves to.
For the connection between the ear shaft holder 15-3 and the ear shaft lifter 23, an ear shaft 15-3b similar to the ear shaft 15-3a for holding the oblique shaft is provided on the lifter side of the ear shaft holder, and a hole core is provided on the axis thereof. The joint collar 23-1 is inserted into the boss hole of the lifter and pressed into the ear shaft 15-3 b, and the ear shaft holder 15 is inserted into the ear shaft lifter 23 until the ear shaft 15-3 b and the core of the boss hole are aligned. Even if -3 is slid, the inner end surface of the boss hole and the outer end surface of the ear shaft 15-3b do not interfere with each other, and assembly is 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 upper, lower male / female feed screw and the ear shaft lifter are provided concentrically with the crankshaft, and the ear shaft lifter is rotatably supported by the crankshaft but is rotated by the earshaft holder. Is regulated.
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.
(See Figures 1-1 and 2)

The stroke volume control mechanism 30 is rotatably supported on an idle gear shaft 33-1 via a bearing 33-2, and a pinion gear of the idle gear 33 fixed in the axial direction by the rear crankcase 3 and the idle gear shaft holder 34 is provided. A stroke gear control motor that meshes with the gear of the upper male feed screw 22U and meshes with a pinion gear of a drive pinion shaft 32 that is integrally connected to a drive pinion gear portion 31a of the stroke volume control motor 31 and rotates integrally. The stroke volume is varied by rotating forward and backward. The stroke volume is controlled by causing the measurement contact portion to contact the side surface of the outer periphery of the upper male feed screw 22U and detecting the axial displacement of the side surface of the outer periphery of the gear by the lifter position detection sensor 35.
With the mechanism described above, the stroke volume lifter moves at the same position in the axial direction for both the upper and rear shafts by the rotation of the stroke volume control motor, so that the stroke volumes of all the cylinders can be continuously varied at the same volume. Although the total displacement can be varied by changing the stroke volume for each crankshaft, that is, every two cylinders, burning all the cylinders will put a burden on the cylinder with a large stroke volume and cause damage such as seizure. Unless a so-called deactivation mechanism that does not burn these two cylinders is adopted, it is better to vary all cylinders with the same stroke volume, and the response speed is slower when varying with one motor than when varying with separate motors. Therefore, although it is necessary to increase the motor capacity, there is no variation due to the difference in motor response, so that it is possible to vary with a smaller stroke volume difference. In addition, any stroke volume can be maintained without the need for power.
(See Figures 1-1, 2 and 3)

The variable compression ratio mechanism 40 is provided substantially at the center of the eccentric shaft portions 41Rb and 41Lb on both sides of the R and L swing arm pivot shafts 41R and 41L, which are arranged parallel to both outer sides of the upper and lower crankshafts 18U and 18L. By engaging the gear portions 41Ra and 41La with the rack gears of the R and L rack shafts 45R and 45L provided substantially at right angles, and rotating the feed screw shaft 44, the R and L rack shafts are moved in opposite directions to each other. By rotating the L swing arm pivot shaft in the opposite direction and displacing the shaft center positions of both eccentric shaft portions 41Rb and 41Lb to symmetrical positions with respect to the intersection of the crank shaft and the ear shaft, the swing trajectory of the swing arm is made symmetrical. The left and right cylinders can be varied at the same compression ratio by changing. In addition, the left and right screws of the feed screw portion 44b of the feed screw shaft 44 are mutually reverse screws, so that the R, L rack shafts 45R, 45L can be moved in the reverse direction by rotating the feed screw shaft in one direction. I have to. In addition, the lead screw 44b, 45Ra, 45La can be a trapezoidal screw, square screw, sawtooth screw, etc., but the screw lead angle is used to make the screw part reliable irreversible transmission. It is good to make it below, and it is necessary to make it below the coefficient of static friction.
The shaft portions provided on both sides of the driven gear portion 44a disposed at the substantially central portion of the feed screw shaft 44 can be freely rotated by the half-cap-shaped R, L feed screw shaft holders 47R, 47L and the front crankcase 2. The feed screw shaft is pivotally supported with the direction fixed, and is connected by the drive pinion gear portion 42a of the compression ratio control motor 42, and the pinion gear of the drive gear shaft 43 that rotates integrally is engaged with the driven gear portion 44a. The compression ratio is varied by rotation.
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.
Providing the swinging pivot shaft of the swing arm on the crankshaft side is difficult because the crankshaft and the inclined shaft are obstructed, so they are disposed at both side positions away from the crankshaft. If a shaft displacement mechanism is provided for each of the left and right pivot shafts, the degree of freedom in layout increases. However, a difference in the compression ratio between the left and right cylinders due to a difference in response occurs, and two displacement mechanisms are required. Cause an increase. If one motor is used to displace the left and right pivot shafts, the transmission distance of the driving force transmission mechanism will be longer. However, for the other hand, the motor can be powered by providing a nonreciprocal transmission mechanism in part of the driving force transmission mechanism. The swing pivot axis position can be maintained without passing through.
In the four-cylinder stroke volume variable device, it is possible to arrange a mechanism for displacing the swing pivot axis position by effectively using the space between the two crankshafts and to shorten the distance between the gear part and both eccentric shaft parts. Therefore, the torsional rigidity can be increased, and the pivot shaft strength and the positional accuracy can be improved.
The R and L rack shafts are assembled to the front crankcase by attaching the feed screw shaft to the front crankcase with the R and L feed screw shaft holders, and then attaching the R and L rack shafts to the compression ratio control motor 42 and Insert through the left and right holes of the cap 48 mounting part, rotate the feed screw shaft, and assemble the feed screw part.
The compression ratio is determined by the swing arm pivot shaft phase detection sensor 46 having a groove-shaped projection 41 facing the groove of the grooved plug 41-1 which is press-fitted to the shaft end of the R swing arm pivot shaft 41R. By detecting the phase change of the swing arm pivot axis, the change of the swing arm pivot axis position with respect to the oblique axis is read and controlled.
(See Figures 1-1, 2, 3, and 4)

The auxiliary machinery drive mechanism 50 has an auxiliary machinery drive shaft 51 disposed on the opposite side of the transmission chamber on the upper and lower crankshafts 18U, 18L at right angles and on both crankshafts. Auxiliary machinery drive shaft is rotatable on a drive bevel gear 52 fixed to a shaft by a spline and axially fixed by a nut 52-2. A driven bevel gear 53 that is fixed in the axial direction by a shaft flange and rotated and fixed by a spline is configured to transmit power to the meshing accessories. The lower side of the accessory drive shaft 51 is rotatably supported by a lower bearing 51-1, and an auxiliary device (not shown) such as an oil pump is disposed and driven at the tip. On the upper side, a camshaft drive sprocket 55 accessory drive pulley 56 and the like are rotationally fixed by a spline and axially fixed by a bolt or the like (not shown), whereby the upper bearing 51-2 is also axially fixed. The upper bearing 51-2 is inserted into the bearing holder 54 and fixed in the axial direction by the nut 51-3. By adjusting the thickness of the shim 54-1 and the shim 52-1, the auxiliary machine drive shaft In addition, the position of the bevel gear can be adjusted by changing the axial position of the upper crankshaft.
When the slant shaft type variable stroke volume device is used for an automobile engine, the cylinder head is arranged on one side in the crankshaft direction, and the transmissions are arranged on the opposite side, so the oil reservoir is arranged in the radial direction of the crankshaft. Will be. If an oil pump is placed there, and it is mechanically driven from the crankshaft so as not to interfere with the arrangement of transmissions, cylinders, and cylinder heads, the space between the cylinders on the opposite side of the transmissions It is reasonable to dispose the drive shaft at a right angle from the crankshaft. As a result, space can be used effectively, and the camshaft for lifting the intake and exhaust valves is generally disposed at a right angle to the cylinder hole. Because it is parallel, the camshaft can be driven by providing a drive sprocket of chain drive, which is a general drive method of the camshaft, on the drive shaft, and a drive pulley of auxiliary equipment etc. on the other end of the oil pump of the drive shaft 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 this embodiment, the shaft of the accessory drive shaft is used as the mating surface of the cylinder and the front crankcase, and the accessory drive shaft is extended to the oil reservoir on the lower side. Therefore, a seal tube 6 is provided. Liquid sealed.
(See Figures 1-1, 2 and 3)

The cylinder head is equipped with a SOHC roller rocker arm type three-dimensional cam continuous variable valve operating device. This valve operating apparatus is provided with R and L accelerator shafts provided in center holes of R and L camshafts 61R and 61L arranged in parallel to cylinder hole rows arranged parallel to both outer sides of both crankshafts and perpendicular to the crankshaft. 3D R, L intake cam lobes 64R, 64L whose height and working angle increase as the slide through the key 63 increases and the timing changes continuously in the axial direction, and height suitable for intake lift The three-dimensional R and L exhaust cam lobes 65R and 65L formed by continuously changing the working angle and timing in the axial direction are arranged side by side in the axial direction and fixed. The pin 66-1 and 67-1 are press-fitted and fixed to the pin 66-1 and 67-1 through the needle bearings 66-2 and 67-2. In the R and L suction and exhaust swing arms 66R, 66L, 67R, and 67L having the roller followers 66-3 and 67-3, the pressure is sucked through the adjustment screw at the swinging tip portion, and the exhaust valves 69in and 69ex are moved forward and backward. The rotation output transmitted from the accelerator motor 73 via the gear train to the joint bracket 71 pivotally supported by the bearing 62-1 fixed to one end of the accelerator shaft is converted into a reciprocating motion by the accelerator shaft slide actuator 72. By advancing and retracting, the R and L accelerator shafts 62R and 62L are advanced and retracted, and the displacement of the joint bracket 71 is detected by the accelerator shaft slide sensor 74, and the accelerator motor 73 is controlled and output controlled.
A swing arm shaft 68 for pivotally supporting the swing arm is fixed in the axial direction by a flange 68a and a bevel-shaped circlip 68-1 at a bearing portion on the accelerator shaft slide actuator 72 side, and at both ends of the swing arm swing shaft. The shim 68-3 is inserted between the circlip 68-2 or the collar 68a locked in the circlip groove of the swing arm shaft, and the thickness of the shim 68-3 is adjusted to adjust the axial clearance of the swinging shaft portion. The position of the swing arm in the axial direction is adjusted, and the lift amount of the intake valve between the cylinders is mainly adjusted to synchronize, and the change in the lift amount due to thermal expansion is minimized. (See Figures 1-3, 4, and 7)

In the following, the embodiment will be described mainly with respect to the crankcase block portion in which the continuously variable stroke volume device at the maximum 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 continuous variable device described in the present embodiment is a four-cylinder, and by mounting a SOHC roller rocker arm type three-dimensional continuous cam variable valve device on the cylinder head portion, the valve lift, compression ratio, stroke volume Realizing continuous variable without. FIG. 1-1 shows the maximum stroke volume at the maximum compression ratio of the upper crankshaft side cylinder, and the two-dot chain line indicating the swing center line locus of the swing arm indicates the swing range at the maximum stroke volume at the minimum compression ratio. The alternate long and short dash line indicates the arm position at the minimum stroke volume. The rotation direction of each shaft is clockwise when the upper crankshaft is viewed from the transmission chamber side, and the lower crankshaft is counterclockwise. Therefore, the accessory drive shaft and camshaft are counterclockwise when viewed from the upper side to the lower side (in FIGS. 1-1 and 1-4).
The piston position in Fig. 1-4 indicates the minimum stroke volume at the maximum compression ratio. By setting the center position of the inclined shaft fixing pin hole in the link holding part of the crankshaft and the inclined shaft, the maximum stroke volume is obtained. A higher compression ratio is set to improve combustion efficiency at low loads.
The present invention is not limited to four cylinders, and can be applied to a two-cylinder to multi-cylinder internal combustion engine. Since continuously changing the valve lift is not indispensable and not within the scope of the claims, it will be described briefly. In each drawing, some drawings are omitted as necessary. R and L used for reference numerals are R on the right side and L on the left side when viewed from the transmission side, the rear side on the transmission side, and the cylinder head side. The front.

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 and 1-3. It is sectional drawing which follows the CC line of FIGS. 1-4. It is sectional drawing which follows the DD line | wire of FIGS. 1-2. It is sectional drawing which follows the EE line of FIGS. 1-1. It is sectional drawing which follows the FF line of FIGS. 1-1. It is sectional drawing which follows the GG line of FIGS. 1-4.

DESCRIPTION OF SYMBOLS 1 Cylinder 2 Front crankcase 3 Rear crankcase 4 Gear case 4-1 Oil seal 5 Camshaft drive chain cover 6 Seal tube 10 Crank mechanism 11 Piston 11-1 Piston pin 12 Connecting rod 12-1 Large end shaft 12-2 Plug 13 Swing Arm 13-1 Shim 14 Joint link 15 Oblique shaft 15a Link holding part
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 Rocker arm 16a Both end shaft 16-1 Bearing 16-2 Inner race nut 16-3 Outer race nut 17 Cross joint 17-1 Thrust washer 17-2 Nut 18 (U, L) (Upper, lower) crank axis
18 (U, L) a Link holding part
18 (U, L) w Weight part 18-1 Front bearing 18 (U, L) -2 Rear bearing 18 (U, L) -3 Outer race nut 18-4 Washer 19 (U, L) (Upper, lower) Crankshaft gear
19Ua Transmission engaging boss portion 19-1 Bolt 19-2 Nut 20 Stroke volume variable mechanism 21 (U, L) (Upper, lower) Female feed screw 21-1 Bolt 21-2 Knock pin 22 (U, L) (Upper , Lower) 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 Drive pinion shaft 33 Idle gear 33-1 Idle gear shaft 33-2 Bearing 33-3 Thrust washer 34 Idle gear shaft holder 34-1 Bolt 35 Lifter position detection sensor 35-1 Bolt 40 Variable compression ratio mechanism 41 (R, L) (R, L) swing arm pivot Shaft
41 (R, L) a Gear part
41 (R, L) b Eccentric shaft portion 41-1-Slotted plug 41-2 Plug 42 Compression ratio control motor 42a Drive pinion gear portion 43 Drive gear shaft 44 Feed screw shaft 44a Driven gear portion
44b Feed screw part 45 (R, L) (R, L) Rack shaft 45 (R, L) a Feed screw part 46 Swing arm pivot shaft phase detection sensor 47 (R, L) (R, L) Feed screw shaft holder 48 Cap 50 Auxiliary drive mechanism 51 Auxiliary drive shaft 51-1 Lower bearing 51-2 Upper bearing 51-3 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 61 (R, L) (R, L) Camshaft 62 (R, L) (R, L) Accelerator shaft 62-1 Bearing 63 Key 64 (R, L) (R , L) Intake cam lobe 65 (R, L) (R, L) Exhaust cam lobe 66 (R, L) (R, L) ) Intake swing arm 66-1 pin 66-2 Needle bearing 66-3 Roller follower 67 (R, L) (R, L) Exhaust swing arm 67-1 Pin 67-2 Needle bearing 67-3 Roller follower 68 Swing arm shaft 68a 鍔 68-1 Bevel type circlip 68-2 Circlip 68-3 Shim 69in Intake valve 69ex Exhaust valve 71 Joint bracket 72 Accelerator shaft slide actuator 73 Accelerator motor 74 Accelerator shaft slide sensor

Claims (11)

Cylinder holes are arranged symmetrically on both sides of the crankshaft, approximately parallel to each other, connected to the large end shaft of the connecting rod connected to the piston, and the swinging arm of the swing arm that strokes the piston is perpendicular to the axis of the crankshaft. An ear shaft with an axial core that can be moved in the axial direction. The oblique shaft with the axial core aligned with the axial shaft shaft is supported by a tilt variable shaft, and the oblique shaft can be rotated by a roller bearing. Both ends of the rocker arm that is fixedly supported are connected to a joint that is rotatable and supported in the axial direction by a joint link. The intersection of the rocker arm is the intersection of the axis of the crankshaft, ear shaft, and oblique shaft. A continuous stroke volume variable device that swings both ends of the rocker arm on a plane including the crankshaft by swinging the swing arm and joint link in parallel with the both ends. The stroke volume continuous variable device according to claim 1, wherein the swing pivot axis position of the swing arm is displaced. 2. The variable stroke volume continuously variable device according to claim 1, wherein an ear shaft for holding the oblique shaft so that the inclination angle can be varied is perpendicular to the key-shaped plate, and a key groove provided on the crank shaft for sliding in the axial direction is slid. 2. The variable stroke volume continuously variable device according to claim 1, wherein an oblique axis fixed link that holds the oblique axis together with the ear axis is pivotally supported by a crankshaft. 2. The variable stroke volume variable device according to claim 1, wherein the rotation of the oblique shaft with respect to the crankshaft is fixed by the inclined shaft hole and the flat portion provided on the crankshaft. The continuous stroke volume variable device according to claim 1, wherein the crankshaft and the oblique shaft are provided with balance weights in the rotational direction. Another two-cylinder stroke volume continuously variable device is provided in parallel to the rocking planes of the rocker arm both end shafts, and the crankshaft rotation phase is shifted by 180 ° so that the other crankshaft with respect to one crankshaft is perpendicular to the swinging plane. 2. The four-cylinder stroke volume continuous variable device which is arranged so as to be interlocked by the same rotation speed and reverse rotation, and to change the inclination angle of the oblique axis and the axial direction position to be the same for both crankshafts. The described stroke volume continuously variable device. The stroke volume continuous variable device according to claim 7, wherein the ear shaft positions of both crankshafts are varied by one motor. 8. A variable stroke volume continuously variable device according to claim 1, wherein the accessory drive shaft is disposed between the cylinders at right angles to the crankshaft and transmits power to the camshaft. 8. The stroke volume continuously variable device according to claim 1, wherein the swing arm pivot axis position of the swing arm is displaced by a single motor, and a nonreciprocal transmission mechanism is used as a part of the driving force transmission mechanism. 8. The stroke volume continuous variable device according to claim 7, wherein a mechanism for displacing the swing pivot axis position of the swing arm is disposed between both crankshafts.

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