JP2018115647A - Two-piece housing connecting rod l-shaped yoke type cylinder capacity continuous variable device with piston top dead center and bottom dead center and compression ratio limiter - Google Patents

Abstract

PROBLEM TO BE SOLVED: To eliminate a default that although there is provided a device for changing an arm oscillation shaft position to restrict a motion of a connecting shaft of two-piece housing and connected and for continuously varying its stroke, this device was not a cylinder capacity and compression ratio continuous variable device showing a small amount of its top dead center phase during variable time and capable of substantially reducing a piston side pressure and also restricting the piston top dead center and the piston bottom dead center as well as a range of compression ratio.SOLUTION: One of the two-piece housing connecting rods is applied as L-shaped yoke, a connecting rod connecting shaft core is arranged in a range where it is arranged on an extended line of an arm oscillation and connecting shaft core from a position on vertical line passing through the connecting shaft core in respect to a side connecting a crank pin with a variable control arm connecting shaft at the time of maximum oscillation of the arm top dead center side where an arm oscillation arranging center at any one of minimum or maximum stroke capacity is near a right angle in respect to a cylinder axis, the arm connecting shaft is oscillated by the arm in an arcuate state, the arm oscillation shaft position is variably controlled in a two-dimentional manner in such a way that its locus approaches at a side spaced apart from a crank journal shaft core and its position and angle are changed in a range of a shape of lower spread shape where it is wide spread at both sides and then a journal shaft is arranged in the shape of lower spread shape.SELECTED DRAWING: Figure 1-1

Description

The present invention, in engines such as automobiles, ships, outboard motors, etc., greatly reduces the piston side pressure, and with low mechanical loss, the stroke volume and compression ratio can be arbitrarily varied continuously and continuously, and the piston top dead center phase change when variable The present invention relates to a continuously variable stroke volume device that can limit the piston, bottom dead center position, and compression ratio range with a small size.

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 US Pat. No. 4,433,596 which converts piston reciprocating motion into crankshaft rotational motion with a swash plate (slanted shaft), changes the tilt angle and crankshaft direction position of the swash plate (slanted shaft), and varies the stroke volume and compression ratio. No. 2004-245092, etc., however, the mechanical loss at the part that converts the piston reciprocating force into the rotational force of the output shaft is large, and it is difficult to achieve high rotation. Since the cylinder head and the like are arranged in order and the axial engine length becomes long, it is difficult to arrange the crankshaft and transmission in the left-right direction of the vehicle body, so it is arranged in the front-rear direction. There are disadvantages that obstruct the driver's and passenger's seats, and the engine processing equipment that uses the conventional single crank mechanism has to be changed significantly, leading to practical application. Ino is the status quo.

If a single crank mechanism is applied, conventional processing equipment can be used, and the engine layout is similar, so that it can be easily mounted on a conventional vehicle body and the barrier to practical use is reduced.
Dividing the connecting rod into two parts, mainly restricting the movement on the crank side with the arm, and changing the position of the swing axis of the arm, or making the swing axis move circularly with 1/2 rotation of the crank, variable compression ratio Many proposals have been made to realize a so-called Atkinson cycle in which the stroke is variable for each rotation of the crank.
Among them, in the second quadrant inside the perpendicular to the core shaft passing through the cylinder core shaft and the crank journal shaft, a swing shaft core of an arm for restricting the movement of the crank side connecting rod is provided. No. 2003-129817 and JP-A-2003-201875, the piston stroke can be continuously changed by changing the pivot axis position one-dimensionally or two-dimensionally, and the compression ratio is also matched to the stroke volume. There has been proposed one that can be set or arbitrarily continuously variable at any time.

In Japanese Patent Application Laid-Open No. 2003-129817, a control shaft swing shaft and a swing tip shaft are provided in the second quadrant, and the locus of the tip shaft determines the piston stroke. The two-way connecting rod connecting shaft runout in the direction perpendicular to the cylinder is equivalent to the crankpin rotation diameter, but the crankpin rotation diameter can be made somewhat smaller than the maximum piston stroke, so the piston side pressure can be reduced compared to the conventional single crank mechanism. The crank-side connecting rod (intermediate arm) is extended in the direction perpendicular to the cylinder. This causes an increase in reciprocating motion weight, resulting in increased vibration and reduced strength. It spreads on the side away from the crank journal axis (top dead center side) and narrows on the side close to the axis (bottom dead center side), and the top dead center phase of the piston stroke changes greatly as the stroke changes. VVT for adjusting the timing is essential, and if the valve timing is also variable, VVT with a larger phase variable width is required. In the cornerstone, in which the compression ratio with respect to the stroke is also immobilized. Japanese Patent Application Laid-Open No. 2003-201875 proposes that the position of the swing axis of the control rod can be varied two-dimensionally, and the compression ratio with respect to the stroke can be arbitrarily varied, and the locus of the tip shaft can be changed to the crank journal axis. It is possible to expand on the side farther away (top dead center side) and closer to the shaft center (bottom dead center side), and the top dead center phase change due to stroke change can be reduced, but other defects have been resolved Absent. There has also been proposed a method of changing the pivot axis position in an arc shape, and under some conditions where the locus of the tip axis is nearly parallel to the cylinder axis (in the case of JP, only near the top dead center on the maximum stroke side) The displacement in the direction perpendicular to the cylinder axis of the connecting rod connecting shaft can be kept small and the piston side pressure can be greatly reduced. However, the compression ratio to the stroke is fixed, and the swing of the moving arm that changes the position of the swing axis is fixed. It is necessary to arrange the lower end of the piston at the bottom dead center (bottom end of the cylinder skirt) to avoid the moving range. When overlapping in the crankshaft direction, the top dead center piston top surface height from the crank journal axis increases. Longer connecting rods and intermediate arms cause problems in terms of vibration and strength, and there is a drawback that the dimensions in the crankshaft direction become longer if they do not overlap. Hirakian, together with the piston side pressure at the top dead center phase change small over stroke volume variation throughout can be greatly reduced, stroke volume, was not the compression ratio can be optionally continuously steplessly variable from time to time.

The present invention has been made in view of the above-described problems. The crank side of a connecting rod, which is divided into two parts and is swingably connected in a direction perpendicular to the crankshaft, is connected to the side connecting the connecting shaft and the crankpin axis. An L-shaped yoke with a variable control arm connection shaft core at the opposite vertex with the angle set to an appropriate range, and the arm connection shaft is stroked in an arc shape with the variable control arm, and the locus is the piston direction from the crank journal shaft core The variable control arm swings so that the position and angle are changed radially within a square-shaped range that approaches the crank journal shaft side (bottom dead center) and spreads on both sides. When the crankshaft shaft is arranged in a C-shaped range by variably controlling the moving shaft core position, the inner angle angle with the variable control arm connecting shaft at the apex of the L-shaped yoke and the fluctuation of the connecting shaft. Suitable for moving trajectory It is possible to suppress the displacement width in the direction perpendicular to the cylinder axis of the connecting rod connecting shaft core locus on the side of the minimum or maximum stroke volume, and to make the stroke volume continuously variable in accordance with the engine usage characteristics, The compression ratio is set according to the stroke volume, or can be arbitrarily continuously variable at any time, improving the thermal efficiency in a wide operating range, reducing the pumping loss, and can greatly reduce the piston side pressure, with low mechanical loss, and higher when the stroke volume is variable. There is little dead center phase change, VVT is not required for phase alignment, and the increase in reciprocating motion part weight is suppressed, and the stroke volume and compression ratio control motor drive force transmission mechanism are partly equipped with an irreversible transmission mechanism. The present invention provides a continuously variable stroke volume device that can save and save power by fixing and maintaining the stroke volume and compression ratio without power.

The invention of claim 1 for solving the above-mentioned problem is that the crank journal shaft is arranged between the cylinder shaft and the variable control arm swing shaft as viewed in the crank journal shaft direction, and is divided into two parts in a direction perpendicular to the crank journal shaft. The crank side of the connecting rod that is pivotally connected to the L-shaped yoke, the variable control arm connecting shaft is stroked in an arc shape by the variable control arm, the locus approaches on the side away from the crank journal axis in the piston direction, The position of the swing axis of the variable control arm is variably controlled in a two-dimensional manner so that the position and angle change radially in a square-shaped range spreading on both sides on the journal axis side, and within the square-shaped range. In this example, the connecting rod core of the L-shaped yoke is connected to the side connecting the crank pin shaft and the variable control arm connecting shaft. From the position on the vertical line, either the minimum or maximum stroke volume side of the variable control arm swing distribution center is near the right angle to the cylinder axis. It is provided within a range where it is arranged on an extension line of a line connecting the dynamic shaft core and the connecting shaft core.

Conventional two-division connecting rod stroke volume variable mechanisms such as Japanese Patent Application Laid-Open Nos. 2003-129817 and 2003-201875 have a control rod tip position located on the piston side of the connecting rod connecting shaft, and a swing shaft position is also a crank. It is closer to the piston top dead center side than the journal shaft, and it is necessary to prevent contact with the cylinder skirt during the stroke, and the top surface position of the piston at the top dead center relative to the crank journal shaft becomes higher and the connecting rod on the piston side becomes longer. There is a drawback, and the crank side connecting rod is also extended long in the direction perpendicular to the cylinder core axis. This causes an increase in vibration and strength due to an increase in weight and an increase in engine block.
Although the crankpin rotation diameter can be made somewhat smaller than the piston stroke, the deflection width in the direction perpendicular to the cylinder core axis of the connecting rod connecting shaft is equal to the crankpin rotation diameter. The side pressure due to piston slap can be reduced, but not greatly reduced, and the top dead center phase of the piston stroke is the stroke other than the two-dimensional variable of the control rod swing axis position disclosed in Japanese Patent Laid-Open No. 2003-201875. Since VVT changes greatly with change, VVT is indispensable for adjusting the valve timing, and if the valve timing is also variable, VVT having a larger phase variable width is required.

In the present invention, the crank journal shaft is disposed between the cylinder shaft and the variable control arm swing shaft as viewed in the crank journal shaft direction, and is divided into two parts and connected to the crank side of the connecting rod that is swingably connected in the direction perpendicular to the crank journal shaft. When the connecting rod connecting shaft core satisfies the requirements of claim 1, the connecting rod connecting shaft swings with respect to the arm connecting shaft on the arcuate locus of the arm connecting shaft. Set the arc-shaped locus of the arm connection shaft on the engine normal range side on either the minimum or maximum stroke volume side to be approximately parallel to the cylinder core axis, and connect the crank pin axis and variable control arm. By selecting the connecting rod connecting shaft core position with respect to the side connecting the shaft cores to an appropriate position, the connecting rod connecting shaft core locus with respect to the cylinder core shaft Shake angular direction becomes low mechanical loss can be significantly reduced lateral pressure due to very small suppressed and piston slap.
Furthermore, it approaches on the side away from the crank journal axis in the piston direction (top dead center side) and spreads on both sides on the crank journal axis side (bottom dead center side). By arranging the crank journal axis within the range of the variable control arm connecting shaft arcuate stroke trajectory, the displacement of the connecting rod connecting shaft core trajectory in the direction perpendicular to the cylinder core axis is kept narrow, while The character trajectory can be widened and the stroke volume ratio can be increased.
The position of the arm connecting shaft on the top dead center side at the minimum and maximum stroke volume is close to the perpendicular position of the cylinder core axis, but in order to set the compression ratio according to the stroke amount, the perpendicular position is shifted slightly. Become. However, since the amount of displacement is small, the crank phase change at the top dead center due to the stroke amount is small and is within a few degrees, and VVT for timing adjustment becomes unnecessary.
In addition, since the arm connecting shaft is sandwiched between the crankpin shaft and the cylinder skirt in the vicinity of the top dead center, the height of the cylinder head mating surface with respect to the crank journal shaft is higher than that of the single crank mechanism, The crank pin rotation radius of the single crank mechanism is 1/2 of the stroke, but it can be reduced to about 1/3 to 1/4 of the maximum stroke, so it is not so high, and the connecting rod connecting shaft position is also at the bottom dead center side. Since the crankpin rotation radius is not lowered, the length of the connecting rod can be made shorter than that of the single crank mechanism, which is advantageous in terms of strength and weight over the patent document example.
In addition, by making the variable control arm's pivot axis position variable in a planar shape (two-dimensional), the compression ratio can be varied continuously and steplessly at any time over the entire stroke range. High compression ratio in the low load and low rotation region on the stroke volume) side to improve combustion efficiency, and low compression ratio to prevent knocking in the high load and low rotation region on the maximum stroke (maximum stroke volume) side In addition to being able to change the compression ratio in a stepless manner, the variable range of the compression ratio can be set to a large value, so it is not necessary to continuously and continuously adjust the compression ratio of a supercharged gasoline engine to the compression ratio of a diesel engine or HCCI engine with a single engine. The stage can be changed.

According to a second aspect of the present invention, in the first aspect of the present invention, the variable control arm swing distribution center on the minimum stroke volume side is disposed substantially perpendicular to the cylinder axis, and within the range from the minimum compression ratio to the maximum compression ratio. The crank journal shaft core is arranged on the tangent line of the variable control arm coupling shaft core locus at the variable control arm swing distribution center on the minimum stroke volume side.

二点鎖線の軌跡となる。右図の円は従来の単クランク機構時における実線と同行程容積相当クランクピン回転軌跡を示し、小円が最小、大円が最大行程容積時を示す。
尚、右図におけるＹ軸のＹ’軸からのＸ軸（Ｏ軸芯を通りＹ軸に直角な軸）方向位置は、本例では最小、最大行程容積時の上死点Ｘ軸方向位置の中間付近に設定しており、各ヨーク形状により異なり、単クランク機構時はＯ軸芯を通るＹ’軸上となる。1-8, on the axis Y ′ (hereinafter referred to as Y ′ axis) passing through the crank journal axis O (hereinafter referred to as O axis) and parallel to the cylinder core axis Y (hereinafter referred to as Y axis), the Y axis The variable control arm connecting shaft center at the center of the variable control arm swing distribution side on the minimum stroke volume side arranged substantially at right angle to the variable control arm top dead center side maximum swing (O shaft core and variable control arm connection) When the crankpin shaft core P comes on the line connecting the shaft cores B), an L-shaped yoke having the connecting rod connecting shaft core C arranged on the extension line of the line connecting the variable control arm swing shaft cores A and B is used. The stroke trajectory of C is the solid line in the right figure (the left stroke on the Y axis is the minimum stroke volume and the right stroke is on the maximum stroke volume side), and the variable control arm on the maximum stroke volume side is at the top dead center side maximum swing (with the O axis When the crankpin shaft core P ′ comes on the line connecting the variable control arm connecting shaft core B ′) If the L-shaped yoke has the connecting rod connecting shaft core C ′ disposed on the extended line of the line connecting the pivot shafts A ′ and B ′, the locus of the dotted line in the right figure is obtained.
When the connecting rod connecting core C ″ is an L-shaped yoke arranged on a perpendicular line passing through B with respect to the side connecting P and B (the internal angle of the opposite vertex B of sides P and C ″ is a right angle), the dashed line on the right diagram In the claims, the connecting rod connecting shaft core is within the range of C to C ″, and the locus is a solid line, a one-dot chain line, and

It becomes a locus of a two-dot chain line. The circle on the right shows the crank stroke rotation locus corresponding to the same stroke volume as the solid line in the conventional single crank mechanism, and the small circle indicates the minimum and the large circle indicates the maximum stroke volume.
In the right figure, the position of the Y axis from the Y ′ axis to the X axis (the axis passing through the O axis and perpendicular to the Y axis) is the minimum and maximum top dead center X axis direction position in this example. It is set near the middle and differs depending on the shape of each yoke. When a single crank mechanism is used, it is on the Y ′ axis passing through the O axis.

1-10 is a piston stroke curve according to the connecting rod connecting shaft arrangement example of FIG. 1-8, the horizontal axis is the clockwise crank phase from the cylinder side Y ′ axis, and the vertical axis is the piston top surface from the O axis. The position is shown, the thin line shows the standard compression ratio and minimum stroke (stroke volume), and the thick line shows the standard compression ratio and maximum stroke (stroke volume). Clockwise crank rotation from the cylinder side Y 'axis For the solid line, the top dead center is 21 ° at the minimum stroke volume, the crank rotation angle is 208 ° between the top and bottom dead points, the top dead center is 20 ° at the maximum stroke volume, and the crank rotation angle is 220 ° between the top and bottom dead points. In the case of the one-dot chain line, the top dead center is 27 ° at the minimum stroke volume, the crank rotation angle is 207 ° between the top and bottom dead points, the top dead center is 23 ° at the maximum stroke volume, and the crank rotation angle is 217 ° between the top and bottom dead points. Dotted line is 13 ° top dead center at minimum stroke volume, crank rotation between top and bottom dead center 210 °, top dead center at maximum stroke volume 15 °, crank rotation angle 226 ° between top and bottom dead centers, minimum in solid line of dashed line, one-dot chain line, top dead center phase difference between maximum stroke volumes is 1 to Although there is almost no 4 ° and a VVT for matching the top dead center phase is unnecessary, the crank rotation angle between the top dead center and the bottom dead center (intake and expansion stroke) 180 as shown in FIG. It is about 30-40 ° wider than the angle, and the top dead center (compression, exhaust stroke) is narrower by that amount, and the intake and expansion strokes can be taken longer. Since it is difficult to balance the primary, when the vibration cannot be suppressed to an allowable range by a damper or the like, a device for suppressing the vibration is required by providing a secondary balancer.
Note that the maximum stroke volume / minimum stroke volume = stroke volume ratio is a solid line 1.51, a one-dot chain line 1.48, and a dotted line 1.60.

様に単クランク機構に近い変位幅になりピストン側圧大で、しかもコンロッド連結軸部をシリンダ筒内に臨ませることができなくなり、シリンダスカート部をコンロッド連結軸よりＯ軸芯に対し離して設定する必要があり、ヘッド高の高いエンジンになってしまうので、点線、二点鎖線の軌跡となるヨーク形状条件は請求範囲から除外した。The invention of claim 2 is intended to greatly reduce the piston side pressure by suppressing the displacement width in the X-axis direction of the connecting rod connecting shaft core locus on the minimum stroke volume side to be small. The L-shaped yoke shape and its variable control arm connecting shaft By satisfying the requirements of claim 2, the trajectory satisfies the minimum stroke volume side connecting rod connecting shaft core trajectory as a solid line, an alternate long and short dash line, and an intermediate trajectory thereof, thereby minimizing the displacement width in the X-axis direction and increasing the maximum stroke. The volume side is also relatively small, and the maximum runout width W in the X-axis direction at the minimum and maximum stroke volume is also suppressed to the same level as the crankpin radius at the minimum stroke volume of the single crank mechanism. It should be suitable for the engine.
The L-shaped yoke with the internal angle of the apex B at a right angle makes the displacement in the X-axis direction of the connecting rod connecting shaft core locus on the minimum stroke volume side extremely narrow, resulting in a substantially linear stroke, but on the maximum stroke volume side, the X-axis direction As the displacement width becomes wider, the slope of the side BC ″ on the bottom dead center side becomes larger, and in order to avoid contact between the connecting rod and the variable control arm connecting shaft, it is necessary to lengthen the span of the side BC ″. Therefore, the piston stroke can be increased, but the weight of the L-shaped yoke is increased and the strength is decreased. On the other hand, the L-shaped yoke arranged on the extended line connecting C and A and B has a slightly larger displacement width in the X-axis direction on the minimum stroke volume side than the above-mentioned yoke, but the X-axis on the maximum stroke volume side is slightly increased. The directional displacement width can be kept small, and the span of the side BC can be shortened to further reduce the weight and increase the strength. It can be selected according to the design policy of the engine.
In addition, the displacement width in the X-axis direction increases as the dotted line and the two-dot chain line indicate, and the effect of reducing the piston side pressure decreases. The cylinder skirt should not be contacted by the displacement of the connecting rod connecting shaft portion in the X-axis direction. If the connecting rod connecting shaft core position is about the displacement width in the X-axis direction of the top dead center side of C ′, the connecting shaft is Since it can face the cylinder and the skirt lower end can be brought close to the position where it does not come into contact with the variable control arm connecting shaft, the piston bottom dead center (skirt lower end) position relative to the O-axis is charged, and the connecting shaft core position is claimed. The height can be the same as that of the invention range of Item 2, but the deflection width at both ends in the X-axis direction is large at the minimum and maximum stroke volume on the bottom dead center side.

In this way, the displacement is close to that of a single crank mechanism, the piston side pressure is large, and the connecting rod connecting shaft cannot be exposed to the cylinder cylinder, and the cylinder skirt is set away from the connecting rod connecting shaft to the O axis. Since it is necessary and the engine has a high head height, the yoke shape condition that becomes the locus of the dotted line and the two-dot chain line is excluded from the claims.

ン軸芯が辺Ａ、Ｐｕ（Ａ’、Ｐ’ｕ）を半径とする円弧上を移動するのであれば、コンロッド

クランクピン軸芯は半径ｒの円上を回転するので、クランクピン軸芯は可変制御アーム連結軸芯を軸に辺Ａ、Ｐｕ（Ａ’、Ｐ’ｕ）を半径とする円弧上を左右に揺動し、コンロッド連結軸芯の軌跡は辺Ａ、Ｃｕ（Ａ’、Ｃ’ｕ）を半径とする円弧よりＡ（Ａ’）寄りの軌跡を描くことになる。
図１−１４は上、下死点側最大揺動間を４等分した図で、例えば可変制御アーム連結軸芯Ｂ_１（Ｂ’_１）にある時のクランクピン軸芯はＰ_１Ｒ（Ｐ’_１Ｒ）又はＰ_１Ｌ（Ｐ’_１Ｌ）となる。
辺Ａ、Ｐｕ（Ａ’、Ｐ’ｕ）を半径とする円弧上のＰ_１ｃ（Ｐ’_１ｃ）にあれば、辺Ａ、Ｃｕ（Ａ’、Ｃ’ｕ）を半径とする円弧上にコンロッド連結軸芯がくるが、辺Ｂ_１、Ｐ_１ｃ（Ｂ’_１、Ｐ’_１ｃ）に対する傾斜分だけコンロッド連結軸芯はＡ（Ａ’）に近づき、最少行程容積側ではＬ側の傾きが小さく円弧に近い軌跡となり、Ｒ側の傾きが大きくＡに近づき円弧から離れた軌跡となる。対して最大行程容積側ではＲ、Ｌの傾斜の差が少なく、クランクピン軸芯Ｐ’_１Ｒ、Ｐ’_１Ｌ時における、Ａ’、Ｂ’_１を結ぶ線の延長線に対するコンロッド連結軸芯とＢ’_１を結ぶ線の傾きのＲ、Ｌ差が小さい為に、Ａ’、Ｃ’ｕを半径とする円弧より直線的でＡ’中心方向変位差の小さな軌跡となる。The reason why the displacement width in the X-axis direction of the connecting rod connecting axis trajectory can be reduced by using the claims will be described with reference to FIG. 1-14. The left figure shows the minimum, the right figure shows the maximum stroke volume side, and when the variable control arm top dead center side maximum swing is Y ", the line connecting O and Bu (B'u) is the crankpin shaft on the line When the core Pu (P'u) comes, the top dead center side maximum swing time occurs, and the L shape with Cu (C'u) arranged on the extension of the line connecting A (A ') and Bu (B'u) Assuming that the yoke is the side A, Pu (A ′, P′u) is rotated around the point A (A ′), and the point where Pu (P′u) intersects the crankpin axis rotation path again.

If the center axis moves on an arc whose radius is the side A, Pu (A ′, P′u), the connecting rod

Since the crankpin axis rotates on a circle having a radius r, the crankpin axis is set to the left and right on an arc having sides A and Pu (A ′, P′u) as radii with the variable control arm connecting axis as the axis. It swings and the locus of the connecting rod connecting shaft core draws a locus closer to A (A ′) than an arc having a radius of side A, Cu (A ′, C′u).
FIG. 1-14 is a diagram in which the upper and lower dead center side maximum swings are divided into four equal parts. For example, when the variable control arm coupling axis B ₁ (B ′ ₁ ) is located, the crankpin axis is P _1R (P ' _1R ) or _P1L ( _P'1L ).
If there is P _1c (P ′ _1c ) on the arc whose radius is the side A, Pu (A ′, P′u), the connecting rod is on the arc whose radius is the side A, Cu (A ′, C′u). Although the connecting shaft comes, the connecting rod connecting shaft approaches A (A ') by the amount of inclination with respect to the sides B ₁ and P _1c (B ′ ₁ , P ′ _1c ), and the L-side inclination is small on the minimum stroke volume side. The locus is close to an arc, and the R-side inclination is large, approaching A and away from the arc. On the other hand, the difference between the inclinations of R and L is small on the maximum stroke volume side, and the connecting rod connecting shaft core and B are connected to the extension line of the line connecting A ′ and B ′ ₁ at the time of the crankpin shaft cores P ′ _1R and P ′ _1L. 'Since the difference between the slopes R and L of the line connecting ₁ 's is small, the trajectory is more linear than the arc having radii A' and C'u and has a small displacement difference in the A 'center direction.

（Ｐ_１Ｌ〜Ｐ_３Ｌ）のＹ’軸に対する傾斜がほぼ同じとなり、Ｐ_１Ｒ〜Ｐ_３Ｒ（Ｐ_１Ｌ〜Ｐ_３Ｌ）では傾斜分だけコンロッド連結軸芯がＡに近づくが、可変制御アーム連結軸芯が振分中心に近づき傾斜が大きくなるにつれ、可変制御アーム連結軸芯の円弧状軌跡がＡより遠ざかり、コンロッド連結軸芯がＡに近づく分を吸収し直線に近いＸ軸方向変位差の極小さな軌跡となる。
但し、最大行程容積側では、Ｙ’軸に対し可変制御アーム連結軸芯の円弧状軌跡が下死点側になるに従い離れており、辺（Ｂ’_１〜Ｂ’_３）、（Ｐ’_１Ｒ〜Ｐ’_３Ｒ）と辺（Ｂ’_１〜Ｂ’_３）、（Ｐ’_１Ｌ〜Ｐ’_３Ｌ）のＹ’軸に対する傾斜が、Ｒ、Ｌ同じ側では似た傾斜となるがＲ、Ｌでの差が大きく、Ｘ軸方向変位差が大きくなってしまう。In the case of the L-shaped yoke having the right angle of the inner angle of the vertex Bu (B′u) which is the other claim, the distribution center line of the circular arc locus of Bu on the minimum stroke volume side is substantially perpendicular to Y ′, By placing the center point on the approximate Y 'axis, the side connecting the connecting rod connecting shaft and the variable control arm connecting shaft

The inclination of (P _{1L to} P _3L ) with respect to the Y ′ axis is substantially the same, and in P _{1R to} P _3R (P _{1L to} P _3L ), the connecting rod connection axis approaches A by the inclination, but the variable control arm connection axis As the inclination approaches the distribution center and the inclination increases, the arc-shaped trajectory of the connecting shaft of the variable control arm moves away from A, and the connecting rod connecting shaft approaches A and absorbs the amount of displacement near the straight line. It becomes a trajectory.
However, on the maximum stroke volume side, the arcuate locus of the variable control arm connecting shaft core is separated from the Y ′ axis as it becomes the bottom dead center side, and the sides (B ′ _{1 to} B ′ ₃ ), (P ′ _1R to P _'3R) and side _{(B' 1 ~B '3)} , (P' inclined with respect to the axis 'Y of _{3L)' 1L} to P is, R, although the inclined similar in L same side R, with L Is large, and the X-axis direction displacement difference is large.

According to a third aspect of the present invention, in the first aspect of the present invention, the variable control arm swing distribution center on the maximum stroke volume side is disposed substantially perpendicular to the cylinder axis, and within the range from the minimum compression ratio to the maximum compression ratio. The crank journal shaft core is arranged on the tangent line of the variable control arm coupling shaft core locus at the variable control arm swing distribution center on the minimum stroke volume side.

As shown in the left figure of FIG. 1-9, the variable control arm swing distribution center on the maximum stroke volume side is arranged substantially perpendicular to the Y-axis, and the variable control arm swing distribution center on the minimum stroke volume side is variable. Near the tangent line of the control arm connecting shaft core locus (This figure shows the non-supercharged (standard) compression ratio in the supercharged engine application example, and the O-axis core is used when the normal range is supercharged (low compression ratio). The O-axis core is placed on the tangential line so that it slightly deviates to the high compression ratio side, and the variable control arm on the maximum stroke volume side at the top dead center side maximum swing (the O-axis core and B 'are connected) (When the crankpin axis P 'comes on the line), the L-shaped yoke with C' arranged on the extended line connecting A 'and B' is used to make the locus of C 'a solid line ( The left side of the Y-axis is the minimum stroke volume and the right side is the maximum stroke volume side, and the maximum stroke on the variable control arm top dead center side on the minimum stroke volume side (on the line connecting the O-axis core and B) When comes crank pin axis P), by the L-shaped yoke disposed C on an extension of a line connecting A and B, the dotted line trajectory at right. The connecting rod connecting axis C ″ is arranged on a perpendicular line passing through B ′ with respect to the side connecting the crankpin axes P ′ and B ′ (the inner angle of the opposite vertex B ′ of the sides P ′ and C ″ is a right angle) L If it is a shape yoke, it becomes a locus of a one-dot chain line in the right figure, and the claims are within the range of C ′ to C ″ of the connecting rod connecting shaft, and the locus is an intermediate locus including a solid line, a one-dot chain line and a dotted line. The circle in the figure shows a crankpin rotation locus corresponding to the same stroke volume as the solid line in the conventional single crank mechanism, and the small circle indicates the minimum stroke and the large circle indicates the maximum stroke volume.
In addition, the X-axis direction position from the Y 'axis of the Y axis in the right figure is set near the middle of the top dead center X-axis direction position at the minimum and maximum same stroke volume, and differs depending on each L-shaped yoke shape. At the time of a single crank mechanism, it is on the Y ′ axis passing through the O axis.

FIG. 1-12 is a piston stroke curve according to the connecting rod connecting shaft core arrangement example of FIG. 1-9. The clockwise crank rotation angle from the cylinder side Y ′ axis is 37 ° at the top stroke at the minimum stroke volume in the solid line. Top, bottom dead center crank rotation angle 209 °, maximum stroke volume top dead center 35 °, top, bottom dead center crank rotation angle 224 °, dotted line is minimum stroke volume top dead center 44 °, top, Crank rotation angle between bottom dead center 207 °, top dead center 39 ° at maximum stroke volume, top, crank rotation angle 218 ° between bottom dead center, top dead center 48 ° at minimum stroke volume, up, down Crank rotation angle between dead centers is 205 °, top dead center is 40 ° at maximum stroke volume, and crank rotation angle is 215 ° between top and bottom dead centers. Although the point phase difference is a little wide as 8 °, it does not require VVT. On the crank mechanism, between the bottom dead center crank angle (intake, expansion stroke) wider than 180 ° about 25 to 45 °, has the same features as claimed in claim 2.
The stroke volume ratio is a solid line 1.60, a dotted line 1.53, and an alternate long and short dash line 1.48.
As a feature common to the piston stroke curves of FIGS. 1-10 and 1-12, the top dead center phase approaches the Y ′ axis as the internal angle with the variable control arm coupling axis of the L-shaped yoke as the apex becomes larger than the right angle. At the same time, the crank angle between the top and bottom dead centers becomes wider and the piston stroke becomes shorter, but the stroke volume ratio (stroke ratio) tends to increase. Therefore, the L-shaped yoke shape may be selected in accordance with the engine design policy.

According to the invention of claim 3, the piston side pressure is greatly reduced by suppressing the displacement width in the X-axis direction of the connecting rod connecting shaft core on the maximum stroke volume side, and the L-shaped yoke satisfies the requirements of claim 3. The maximum stroke volume side connecting rod connecting shaft core trajectory is an intermediate trajectory including a solid line, a one-dot chain line, and a dotted line, thereby minimizing the displacement width in the X-axis direction, and the minimum stroke volume side is also relatively small. The maximum runout width in the X-axis direction at the minimum and maximum stroke volume is also kept to the same level as the crankpin radius at the minimum stroke volume of the single crank mechanism, and is suitable for engines such as ships and outboard motors that have the maximum stroke volume side as the normal range. It is intended.
The solid line shows the maximum stroke volume side rise and fall strokes with very little difference in the X-axis direction but is almost linear, but the minimum stroke volume side displacement in the X-axis direction is slightly larger. The alternate long and short dash line is the maximum stroke volume side. The X-axis direction displacement width near the bottom dead center is slightly larger, but the maximum runout width in the X-axis direction at the minimum and maximum stroke volume is within the same range as the solid line. A dotted line within these ranges is an intermediate trajectory of both.
The maximum stroke volume side C ′ locus of the solid stroke with C ′ arranged on the extended line of the line connecting A ′ and B ′ at the time of maximum swing on the variable control arm on the maximum stroke volume side at the top dead center is substantially on the Y axis. The locus is close to a parallel straight line, and the reason will be described with reference to the right diagram of FIG.
The left figure shows the minimum stroke, the right figure shows the maximum stroke volume side, and the line connecting O and Bu (B'u) is Y "and the Y" axis is the reference at the maximum swing on the variable control arm top dead center side. If it does so, it will become the same connecting rod connection axis | shaft locus | trajectory which can say the same as FIG. 1-14. On the minimum stroke volume side, the O-axis is slightly deviated from the tangent line of the variable control arm coupling axis trajectory at the center of the variable control arm swinging distribution. 14 is a connecting rod connecting shaft core locus similar to the left drawing, and since the variable stroke of the variable control arm connecting shaft core on the maximum stroke volume side is substantially the same as the Y ″ axis, The reason for this is the same as in FIG. 1-14 with reference to the Y ″ axis, and a detailed description thereof will be omitted.

If the device can simply reduce the piston side pressure by changing the compression ratio, a pair of connecting rods that are divided and connected to each other on the crank side of the connecting rod that connects the connecting rod connecting shaft core and the crankpin shaft core will have a diagonal at right angles. If the compression ratio is varied by moving the apex parallel and linearly to the cylinder core axis and moving the stroke of the opposite apex parallel to the cylinder core axis, the connecting rod connecting axis is almost on the cylinder core axis. Draw a small trajectory of the cylinder core axis perpendicular displacement in parallel and linearly, but the crankpin axis and the connecting rod connecting axis swing by rotation of the crank with the opposite vertex as the axis, so between the top and bottom dead centers Is a locus in which the connecting rod connecting shaft is displaced in a direction perpendicular to the cylinder core axis in a direction away from the cylinder core shaft.
Further, when a slide mechanism is used to linearly stroke the apex, a moment is applied and it becomes difficult to move due to the wedge effect, resulting in a large mechanical loss and difficult to put into practical use.
By pivotally supporting the top of the pair with a swinging arm and making a stroke in the shape of a circular arc in the direction of the cylinder core axis, the sliding amount of the paired top and the swinging shaft can be reduced, and mechanical loss can be reduced. The displacement of the connecting rod connecting shaft in the direction of the cylinder core due to the swing of the crankpin shaft and the connecting rod connecting shaft between the bottom dead centers as an axis can be absorbed as described above to make a more linear trajectory. . In addition, in order to obtain a device in which the crankpin phase change at the top dead center side is small and the stroke volume can be varied, the arc stroke with respect to the peak at the minimum and maximum stroke volume is made closer on the side away from the crank rotation axis in the piston direction. In addition, it is necessary to make the shape of the letter C widened on the crank rotation shaft side, and the connecting rod connecting shaft core trajectory at all stroke volumes is a trajectory that is parallel and linear near the cylinder core shaft and has a small perpendicular displacement width. I can't do that.
In addition, if the crank journal axis is placed outside the C-shaped locus on the minimum stroke volume side of the opposite vertex, the displacement width in the X-axis direction of the connecting rod connecting axis locus can be narrowed, and the maximum stroke with respect to the crankpin radius can be increased. In order to prevent contact between the connecting rod and the variable control arm connecting shaft, it is necessary to increase the connecting rod connecting shaft of the L-shaped yoke, the span between the variable control arm connecting shafts and the connecting rod length, and the variable control arm and the L-shaped yoke. In order to prevent contact with the crank pin boss, it is necessary to lengthen the variable control arm and make the arm bent. This increases the weight and decreases the strength, making it difficult to achieve high rotation, making it difficult to put it to practical use in automobiles. It becomes.
When placed outside the C-shaped locus on the maximum stroke volume side at the top of the apex, the displacement width in the X-axis direction of the connecting rod connecting shaft core locus on the minimum stroke volume side increases, and the maximum stroke with respect to the crankpin radius decreases and the stroke volume ratio Will also get smaller.
By arranging the crank journal shaft core within the C-shaped range, it becomes possible to widen the width of the C shape in the vicinity of the journal shaft core, to increase the stroke volume ratio and to narrow the displacement width in the X-axis direction. . Therefore, by making the crank side connecting rod and its trajectory satisfy the requirements of claims 1 to 3, the piston side pressure in the normal range can be reduced in accordance with the usage characteristics of the engine, and mechanical loss and noise can be reduced. .

According to a fourth aspect of the present invention, in the first aspect of the present invention, the variable control arm swinging shaft is variable in position and fixed to the two driving links which are swingable with respect to the crankcase as a stationary link. A 5-bar link mechanism with a variable control arm swinging shaft as the pair that connects the two driven links connected at the, and a motor and a drive force transmission mechanism that swing the two driving links separately are provided. An irreversible transmission mechanism is used as a part of the mechanism.
According to the present invention, a variable control arm swinging shaft is pivotally supported by two driven links in a V-shape as viewed in the crankshaft direction, and the two driving links in which the V-shaped tip portions are connected in pairs are used as a stationary link. The relative phase of the drive link can be adjusted by fixing the two shafts to a pair of shafts arranged parallel to the crankshaft in the case and controlling the swinging of the two shafts separately using separate motors and drive force transmission mechanisms. The position of the variable control arm rocking shaft, which is the pair of the two driven links, can be varied in a wide range two-dimensionally while changing the V-shaped angle of the two driven links freely. The variable compression ratio range can be varied over a wide range. By providing a nonreciprocal transmission mechanism in a part of the driving force transmission mechanism, the variable control arm swing shaft position can be fixed and held without power, and the stroke Fixed volume and compression ratio In which power saving during holding.

Further, the invention of claim 5 is characterized in that, in the invention of claim 1, the upper and bottom dead center positions of the piston are limited and an arbitrary compression ratio range is limited for each stroke.
According to the present invention, even if the stroke volume and compression ratio control motor becomes uncontrollable and runs away, the piston collides with the cylinder head, valves and cranks by limiting the upper dead center side stroke range. Can prevent damage and avoid damage, and can limit the compression ratio within a predetermined range for each stroke volume, enabling fuel supply control with the minimum necessary computer capacity, preventing unauthorized combustion and stopping the engine And seizure can be prevented.

According to a sixth aspect of the present invention, in the fifth aspect of the invention, the variable control arm swing shaft is extended in the axial direction, and the two-dimensional movement range of the shaft portion protruding from the driven link is limited by the limiter plate. It is characterized by.
Since the stroke volume and compression ratio can be varied by controlling the position of the variable control arm swing shaft in two dimensions, it is ideal to limit the movement range of that part, and it is possible to accurately limit it. . By limiting the moving range and relative span of the two pairs that couple the driving link and the driven link, or limiting the moving range of the irreversible transmission mechanism of the driving force transmission mechanism, the stroke volume and compression ratio variable range can be reduced. Although it is possible to limit to some extent, in order to accurately limit the compression ratio within an arbitrary range for each stroke volume, there is no choice but to limit the movement range of the swing shaft, and limit the portion where the swing shaft is extended. Limiting with a plate is a cost-effective way to minimize additional parts.

According to a seventh aspect of the present invention, in the fifth aspect of the present invention, the contact between the limiter plate and the extension shaft of the variable control arm swing shaft is performed through a rotating body.
A non-reciprocal transmission mechanism is used in the driving force transmission mechanism to hold the variable control arm swing shaft position without power, and if the stroke volume or compression ratio control motor is out of control, it will run out of control. When the extension shaft portion of the variable control arm swing shaft and the limiter plate come into contact with each other, the swing shaft alignment is deformed and locked, and the resistance becomes large, so that a large amount of power is required to come out.
The contact between the limiter plate and the swinging shaft can be reduced by moving the swinging shaft in the tangential direction of the contact part via a rotating body such as a bearing as shown in this figure to reduce the frictional resistance of the contact part. The lock state can be released with

The invention according to claim 8 is the invention according to claim 5, wherein the limiter plate is provided in a cylinder closest to the variable arm.
The variable control arm swinging shaft position is variable and fixed. The variable arm that swings the driving link by rotating the shaft, which is the pair of two driving links, is limited. The farther the limiter plate is in the axial direction, the weaker the strength and rigidity, and the greater the alignment error and variation, and the deviation from the target stroke volume and compression ratio limit range increases with variation. By moving closer, the amount of deviation can be reduced and the strength and rigidity are advantageous. If the variable arm is arranged between the central cylinders in the same way as shown in this figure, the axial distance between the variable arm and the cylinders at both ends can be shortened as much as possible, while increasing the bending, torsional strength and rigidity, It is possible to control the stroke volume and the compression ratio with high accuracy while suppressing errors and variations.

According to the present invention, the crank side of the split connecting rod is controlled by the arm, and the piston stroke can be continuously varied by changing the position of the pivot axis of the arm two-dimensionally. In accordance with the characteristics of the engine, the piston side pressure can be greatly reduced according to the operating characteristics of the engine, and the piston side pressure can be greatly reduced. VVT is also unnecessary, and the increase in the weight of the reciprocating motion part can be suppressed to a small extent, and the upper and lower dead points of the piston stroke and the compression ratio range for each stroke are limited to prevent piston damage, unauthorized combustion, engine stop, It is possible to provide a continuously variable stroke volume device that prevents sticking and the like.
In addition, since the irreversible transmission mechanism is provided in a part of the stroke volume / compression ratio variable mechanism, the stroke volume and the compression ratio can be kept constant without electric power, so that power consumption can be suppressed and 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 is applicable to power devices such as various gasoline, diesel, and HCCI engines mounted on automobiles, ships, outboard motors and the like.

The variable control arm connecting shaft centered on the opposite side of the connecting rod and the crankpin shaft with the opposite side of the connecting rod and crankpin shaft core set to an appropriate range. The arm connecting shaft is stroked in an arc shape with a variable control arm, and the locus approaches on the side away from the crank journal axis in the piston direction (top dead center side), and the journal axis side ( Two-dimensional variable control is performed on the pivot axis position of the variable control arm so that the position and angle of the variable control area change radially, with a C-shaped range extending on both sides at the bottom dead center side). In the case where the crank journal shaft is placed inside, the internal angle angle with the variable control arm connecting shaft of the L-shaped yoke as the apex and the swinging trajectory of the connecting shaft are set appropriately, and the stroke volume is continuously matched to the engine usage characteristics Stepless With a variable to set the combined compression ratio in the stroke volume, or one that continuously infinitely variable at any time optionally includes a crank mechanism 10, the stroke volume, the compression ratio varying mechanism 20, the stroke volume, the compression ratio control mechanism 30.

In the crank mechanism 10, a crankshaft 15 of a four-cylinder 180 ° phase crank is rotatably supported by a journal shaft 15b by a half-split journal metal bearing 15-1 in upper and lower crankcases 2 and 3, The axial direction is regulated with an appropriate gap by inserting a half shim 15-2 and adjusting the thickness between the journal bearing side surfaces and the side surfaces of the counterweight portion 15w and the transmission engaging boss portion 15c. The opposite crankshaft stepped shaft is provided with a camshaft, a camshaft drive sprocket 15d for transmitting power to the oil pump, and an oil pump drive sprocket 15e. Rotate clockwise. The crank pin shaft 15a is divided into two parts, and the connecting rod connecting shaft 12-1 on the crank side (L-shaped yoke) of the connecting rod connected in a swingable manner in a direction perpendicular to the crank shaft is connected to the crank pin shaft 15a. From the vertical position passing through the connecting axis to the side connecting the axes of the control arm connecting shaft 13-4, the variable control arm swing distribution center on either the minimum or maximum stroke volume side is perpendicular to the Y axis. The variable control arm on the side close to the top dead center side is within the range where it is placed on the extension line of the line connecting the variable control arm swing shaft core and the connecting shaft core, and three shaft cores are L-shaped The L-shaped yoke 13 is arranged, and a half-pin yoke metal bearing 13-2 and a yoke cap 13-1 are fastened to the yoke with a bolt 13-3 to form a crank pin hole, and the yoke is rotatably supported. doing. Note that the mating surface of the yoke and yoke cap is inclined to the connecting rod connecting shaft side from the surface perpendicular to the line connecting the crank pin hole and the variable control arm connecting shaft core, and is variable with the tightening boss portion of the yoke cap fixing bolt during crank rotation. While avoiding contact with the control arm 14, rigidity and strength are secured by fastening bolts between the connecting rod connecting shaft and the crank pin hole, and the mating surface is perpendicular to the line connecting the crank pin hole and the core of the variable control arm connecting shaft. Vibration is reduced by making the yoke lighter than the direction.
Also, by shifting the arm part of the variable control arm to the side where the crank pin boss part of the yoke escapes with respect to the line connecting the hole core of the connecting shaft and the swinging shaft, the span between the crank pin hole of the yoke and the variable control arm connecting shaft is increased. In addition to shortening and reducing weight, the length of the variable control arm is shortened, and the engine block is made compact accordingly. (See Figures 1-1 to 5 and 5)

A piston 11 is inserted into a cylinder 1 that is arranged with the Y axis perpendicular to the crankcase mating surface (X axis) and offset in the crank rotation direction with respect to the O axis, and the piston pin 11-1 and connecting rod The connecting rod on the piston side that is pivotally supported by the yoke so as to be swingable in a direction perpendicular to the crankshaft on the connecting shaft and the variable control arm connecting shaft of the yoke that is rotatably supported on the crankpin shaft are variable to restrict the movement of the connecting shaft. The control arm is pivotally supported and oscillated by the variable control arm oscillating shaft 16 so that the variable control arm connecting shaft oscillates in an arc shape mainly in the Y axis direction to regulate the X axis direction and perform the piston reciprocating motion. This is converted into crank rotation motion, and the position of the variable control arm swing shaft is two-dimensionally variably controlled so that the arm connecting shaft trajectory is away from the O axis in the piston direction (top dead center side) Approach and change the position and angle radially in a square-shaped range spreading on both sides on the O-axis core side (bottom dead center side), and arrange the O-axis core in the square-shaped range By connecting the internal angle of the variable control arm connecting shaft of the L-shaped yoke as the apex and the swinging trajectory of the connecting shaft, the connecting rod connecting shaft core locus on the minimum or maximum stroke volume side according to the engine usage characteristics is set. It is possible to minimize the displacement width in the direction perpendicular to the cylinder axis of the cylinder, and the side pressure due to the piston slap can be greatly reduced, resulting in low mechanical loss.

Furthermore, the position in the X-axis direction of the Y-axis relative to the trajectory of the connecting rod connecting shaft is minimized near the top dead center on the side where the frequency of use is high, and then as shown in the example of this figure, due to the high frequency of the engine normal range. The piston side pressure is located at the middle of the position of the top dead center in the X-axis direction at the maximum stroke volume, then at the minimum, and at the approximate center of the maximum swing width in the X-axis direction of the connecting rod connecting shaft center swing locus at the maximum stroke volume. It is possible to widen the operation time zone that keeps the value small. (See Figs. 1-1 to 3, 8 and 9) The position of the arm connecting shaft at the top dead center in the X-axis direction is slightly shifted to set the compression ratio according to the stroke volume. Since it is small, the crank phase change at the top dead center due to the stroke volume is small and is within several degrees as shown in FIG. 1-10, the difference between the 12 thin line and the thick line, so that the timing matching VVT is unnecessary.
In this embodiment, the connecting rod, the connecting rod connecting shaft, the variable control arm and the variable control arm connecting shaft are press-fitted and fixed, and each shaft is rotatably supported by both side bearing holes of the L-shaped yoke. The crankshaft counterweight is widened as much as possible, and the crankpin radius with respect to the stroke is reduced, so that the cross-sectional overlap of the crankpin shaft and journal shaft can be increased, thereby improving the rigidity and strength of the crankshaft. The rocking bearing portion is lubricated by oil supplied through oil holes communicating with the crank pin hole portion on both side bearing holes of the L-shaped yoke.
(See Figures 1-1 to 5 and 5)

The stroke volume and compression ratio variable mechanism 20 is a variable control arm swinging shaft that regulates the movement of the L-shaped yoke, and the position of the swinging shaft is fixed and fixed by a five-bar linkage mechanism. ) Arrange the shaft of the lower variable shaft 23L, which is the opposite of the lower drive link 21L, and the shaft parallel to the crank journal shaft. The lower drive link determines the phase of the lower drive shaft with the key 21-2 and bolts It is fixed at 21L-3, the axial direction is restricted by the end face of the shaft hole boss part of the crankcase, and is swingable together with the lower variable shaft. On the other hand, the upper drive link 21U determines the phase with a key 21-2 at the upper variable shaft 23U, which is a pair, and is rotatably inserted into the shaft hole of the upper crankcase opened parallel to the crank journal axis. The upper variable shaft is sandwiched and fixed with bolts 21U-3 so that it can swing together with the upper variable shaft. Since the lower drive link can be temporarily assembled before setting the lower variable shaft in the crankcase, one side of the shaft hole is divided in half, and after setting, the half drive is tightened and fixed with bolts. Since it can only be assembled after the upper variable shaft has been inserted into the crankcase, the shaft hole is divided in half into an arm portion and a cap, enabling assembly and fixing after insertion of the shaft.

The lower follower link 22L is rotatably inserted into the tip hole of the lower drive link and has a lower link pin 24L having a stepped shaft at both ends, and a variable control arm and an upper follower link 22U that are pivotally supported so as to be stepped at both ends. It is press-fitted into the stepped shafts on both sides of the variable control arm swing shaft with attached shaft, and the lower link pin and lower driven link for the lower drive link, and the upper driven link for the lower driven link and the variable control arm swing shaft The variable control arm is pivotally supported so as to be axially restricted and swingable. Also, an oil passage is provided on one side of the lower variable shaft, lower driving link, lower link pin, variable control arm swing shaft and at least the lower driven link, and press-fitted with oil supplied from the oil gallery to the lower variable shaft central oil passage. The bearings other than those are lubricated.
The upper driven link is inserted into the stepped shafts on both sides of the upper link pin 24U having a stepped shaft at both ends rotatably inserted into the tip hole of the upper driving link, and is inserted into the upper driving link by sandwiching the upper driving link. The other hole is pivotally inserted between the lower driven link and the variable control arm on the variable control arm swing shaft.
The variable control arm swinging shaft is pivotally supported in a V shape when viewed from the crankshaft direction with the upper and lower follower links, and the upper and lower driving links are fixed by connecting the V-shaped tip with the upper and lower link pin pairs. Fixed to the upper and lower variable shafts that are arranged in parallel to the crankshaft on the crankcase that becomes the link, and the two shafts are controlled separately and freely by separate motors and driving force transmission mechanisms. Thus, the position of the variable control arm swinging shaft, which is a pair of the upper and lower driven links, can be varied while freely changing the V-shaped angle of the upper and lower driven links by changing the relative phase of the upper and lower driven links. It is two-dimensionally variable, and the stroke volume and compression ratio variable range can be varied over a wide range. (See Figures 1-1 to 4)

The stroke volume / compression ratio control mechanism 30 includes a lower variable arm 37L that swings a lower variable shaft that is a pair of lower drive links of a five-bar linkage mechanism that varies, fixes, and holds the position of the variable control arm swing shaft. In the middle of the second and third cylinders in the lower variable shaft axial direction, the phase is determined by the key 37-2 and fixed by the bolt 37L-3, and the axial direction is restricted by the end face of the shaft hole boss part of the crankcase. It can swing freely with the lower variable shaft. On the other hand, the upper variable arm 37U is positioned in the middle between the second and third cylinders in the axial direction of the upper variable shaft, the phase is determined by the key 37-2, the upper variable shaft is sandwiched between the cap 37U-1 and fixed by the bolt 37U-3. The axial direction is restricted by the end surface of the crankcase shaft hole boss, and it can swing together with the upper variable shaft. The lower variable arm can be temporarily assembled before setting the lower variable shaft in the crankcase, so one side of the shaft hole is divided in half and the half is fixed with bolts after setting. Since it cannot be assembled unless the upper variable shaft is inserted into the crankcase, it can be divided into half at the shaft hole and divided into the arm and the cap so that the assembly can be fixed after inserting the shaft.

The joint 35 is rotatably inserted in the tip holes of the upper and lower variable arms and has joint pins 36 having stepped shafts at both ends, and holes in the joint holder portions 34Ua and 34La of the upper and lower male feed screws 34U and 34L. It is press-fitted to the stepped shafts on both sides of the joint pin 36 that is rotatably inserted so as to sandwich the upper and lower variable arm tips and upper and lower male feed screw joint holder side surfaces. When the joint is restricted to the axial direction of the joint pin and swingably supported with respect to the upper and lower male feed screws, and the upper and lower male feed screws are regulated in the direction perpendicular to the axis. The rotation of the male screw is stopped and the male screw moves in and out of the female screw in the axial direction by rotating the female screw. Upper, allowing swinging the lower variable arm.
The upper and lower female feed screws 33U and 33L are connected to the Y axis by engaging with the upper and lower male feed screws, axially restricted and rotatably supported by the crankcase. The driven gear portions 33Ua and 33La provided at the shaft ends are rotatably inserted into the holes of the parallel upper crankcase, and both side surfaces of the gear portion are connected to the end surfaces of the female feed screw insertion holes of the upper crankcase and the gasket 32-1. Is controlled by the mating surface of the control motor holder 32, which is fixed by a liquid sealing bolt 32-2.

The upper and lower control motors 31U and 31L having drive pinion gear portions 31Ua and 31La meshing with the driven gear portion are arranged in parallel with the axis of the female feed screw (Y axis) and liquid-sealed by an O-ring 31-2. The bolt is fixed to the control motor holder by a bolt 31-1.
The upper and lower control motors rotate forward and backward, and the lower male feed screw moves forward and backward. The upper and lower are fixed to the upper and lower variable shafts. The lower drive link can be swung while changing the relative phase to change the phase, the V-angle of the upper and lower follower links can be freely changed, and the variable control arm swing axis position can be varied in a wide range two-dimensionally. ing.
Plugs 23U-2 and 23L-2 are press-fitted or sandwiched in the case on the transmission shaft side journal shaft side of the upper and lower variable shafts, and are sealed in the center hole on the opposite side in the axial direction. 1 is press-fitted, and the protrusions of the upper and lower variable shaft phase detection sensors 39U and 39L, which are liquid-sealed to the cam chain cover 4 with an O-ring 39-2 and fastened with bolts 39-1, are inserted into the grooves. Then, by detecting the phase and phase difference of the upper and lower variable shafts, the variable control arm swing shaft position is obtained to control the stroke volume and the compression ratio. (See Figures 1-1 to 4, 6, and 7)

In the present invention, a feed screw is provided in a part of the power transmission mechanism of the control motor, the stroke volume, and the compression ratio variable mechanism so that the stroke volume and the compression ratio can be kept constant without power.
The lead screw may be a trapezoidal screw, square screw, sawtooth screw, etc., but in order to ensure reliable non-reversible transmission of the screw part, the screw lead angle should be less than or equal to the dynamic friction coefficient of the material used. Must be less than or equal to the static friction coefficient.

The variable control arm swing shaft of the cylinder adjacent to the upper and lower variable arms is a variable control arm swing shaft 16L with limiter, the shaft end is extended, and the bearing 16L-1 is inserted into the stepped shaft to the circlip 16L-2. To prevent the bearing from falling off. A limiter plate 38 that restricts the two-dimensional movement range of the swing shaft of the variable control arm with limiter by contacting with the outer ring of the bearing is accurately positioned on the upper crankcase with the knock pin 38-1 and then with the bolt 38-2. It is tightened and fixed to the case. In the hole of the limiter plate where the bearing enters, the arc-shaped solid line connecting the upper cross center and the lower cross center is the axis locus of the swing axis of the variable control arm with limiter at the standard compression ratio (compression ratio 12 in this embodiment). The one-dot chain line indicates the lowest compression ratio (compression ratio 10 in this embodiment), the two-dot chain line indicates the highest compression ratio (compression ratio 18 in this embodiment), and the upper cross center indicates the piston top dead center and the minimum compression ratio. Stroke volume limit, lower cross center is piston bottom dead center and maximum stroke volume limit position, lowest compression ratio lower cross center position is different from other compression ratios. This is to prevent the collision with the cranks so as not to protrude further. In this embodiment, the limiter plate hole shape that enables supercharging and HCCI combustion in a gasoline engine is possible in all of the minimum and maximum stroke volumes, but on the minimum stroke volume side, the minimum compression ratio and the maximum stroke On the volume side, it is easy to narrow the limit width in the direction of eliminating the maximum compression ratio side. (See Figures 1-3, 4, and 7)

In the following, the embodiment will be described mainly with reference to a crankcase block portion in which a continuously variable stroke volume device at the maximum and minimum strokes (stroke volume) at a standard compression ratio is accommodated. Oil pumps and auxiliary equipment are not shown or described.
The stroke volume continuously variable device described in this embodiment is a four-cylinder.
FIG. 1-1 shows the standard compression ratio at the top dead center and the maximum stroke (stroke volume), and FIG. 1-2 shows the standard compression ratio at the top dead center in the continuously variable stroke volume device according to the present embodiment. , Indicates the minimum stroke (stroke volume), and the two-dot chain line indicates the bottom dead center.
1-3 shows the case where the crank pin, the lower link pin and the joint pin are on the crankcase mating surface, the L-shaped yoke section is the crank pin, connecting rod connecting shaft section, the lower driven link section is the lower link pin, The cross section between the variable control arm swinging shafts is shown. 1-5 shows a section on the transmission engagement boss side from C and L in FIG. 1-3, and a camshaft drive sprocket side section is omitted. In each drawing, some drawings are omitted as necessary.
The present invention is not limited to four cylinders, and can be applied from a single cylinder to multiple cylinders.

It is sectional drawing (sectional drawing which follows the AA line of FIGS. 1-3) which shows a standard compression ratio and the top dead center at the time of the maximum stroke. It is sectional drawing (sectional drawing in alignment with the AA line of FIGS. 1-3) which shows a top compression point at the time of a standard compression ratio and the minimum stroke volume. It is sectional drawing which follows the CC line of FIGS. 1-1. 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. 1-1. It is sectional drawing which follows the FF line | wire of FIGS. 1-3. It is sectional drawing which follows the GG line of FIGS. 1-4. They are a L-shaped yoke connecting rod connecting shaft arrangement example figure and a connecting rod connecting shaft core locus in a standard compression ratio variable control arm connecting shaft swing locus. FIG. 6 is an L-shaped yoke connecting rod connecting shaft arrangement example diagram and a connecting rod connecting shaft core locus in the standard compression ratio variable control arm connecting shaft swing locus. FIG. 9 is a piston stroke diagram by connecting rod connecting shaft arrangement example excluding the two-dot chain line in FIG. It is a piston stroke comparison figure at the time of setting it as the stroke with the example of the continuous line of FIGS. 1-10, and the conventional single crank mechanism. It is a piston stroke figure according to the connecting rod connection shaft arrangement example of Drawing 1-9. It is a piston stroke comparison figure at the time of setting it as the stroke with the example of the continuous line of FIGS. 1-12, and the conventional single crank mechanism. FIGS. 9A and 9B are diagrams showing each axis position and a connecting rod connecting axis locus with respect to the variable control arm connecting axis when the variable control arm swinging range is equally divided into four in FIGS. It is a figure which shows each axial center position with respect to the variable control arm connection axial center at the time of 4 equal division | segmentation of the variable control arm rocking | fluctuation range of FIG. 1-9, and a connecting rod connection axial locus.

1 cylinder 1-1 cylinder gasket 2 upper crankcase 3 lower crankcase 4 cam chain cover 10 crank mechanism 11 piston 11-1 piston pin 12 connecting rod 12-1 connecting rod connecting shaft 13 L-shaped yoke 13-1 yoke cap 13-2 yoke Metal bearing 13-3 Bolt 13-4 Variable control arm connecting shaft 14 Variable control arm 15 Crankshaft 15a Crankpin shaft
15b Journal axis
15w counterweight part
15c Transmission engaging boss
15d camshaft drive sprocket
15e oil pump drive sprocket 15-1 journal metal bearing 15-2 half shim 15-3 oil seal 16 variable control arm swing shaft 16-1 plug 16L variable control arm swing shaft with limiter 16L-1 bearing 16L-2 Clip 20 Stroke volume, compression ratio variable mechanism 21U Upper driving link 21U-1 Cap 21-2 Key 21U-3 Bolt 21L Lower driving link 21L-3 Bolt 22U Upper driven link 22L Lower driven link 23U Upper variable shaft 23-1-Groove Attached shaft 23U-2 Plug 23L Lower variable shaft 23L-2 Plug 24U Upper link pin 24L Lower link pin 24-1 Plug 30 Stroke volume, compression ratio control mechanism 31U Upper control motor 31Ua Drive pinion gear 31- Bolt 31-2 O-ring 31L Lower control motor 31La Drive pinion gear part 32 Control motor holder 32-1 Gasket 32-2 Bolt 33U Upper female feed screw 33Ua Driven gear part 33L Lower female feed screw 33La Driven gear part 34U Upper male feed screw 34Ua Joint holder Part 34L Lower male feed screw 34La Joint holder part 35 Joint 36 Joint pin 37U Upper variable arm 37U-1 Cap 37-2 Key 37U-3 Bolt 37L Lower variable arm 37L-3 Bolt 38 Limiter plate 38-1 Knock pin 38-2 Bolt 39U Upper variable shaft phase detection sensor 39-1 Bolt 39-2 O-ring 39L Lower variable shaft phase detection sensor Y Cylinder shaft Y 'Crank Naru axis perpendicular as Y axis parallel lines X crank journal axis as Y-axis shaft (crankcase mating surface)
A (A ') Variable control arm swing axis B (B') Variable control arm connection axis C (C ', C ") Connecting rod connection axis P (P') Crank pin axis O Crank journal axis L Span between crankpin shaft and variable control arm connecting shaft r Crankpin radius W Minimum, maximum runout in X-axis direction at maximum stroke volume

Claims (8)

The crank journal shaft is arranged between the cylinder shaft and the variable control arm swing shaft as viewed from the crank journal shaft direction, and the crank side of the connecting rod that is divided into two and is swingably connected in the direction perpendicular to the crank journal shaft is connected to the L-shaped yoke. The variable control arm connecting shaft is stroked in a circular arc shape with the variable control arm, and the locus approaches in the direction of the square away from the crank journal axis in the piston direction and spreads on both sides on the journal axis. The position of the swing axis of the variable control arm is two-dimensionally variably controlled so that the position and angle change radially, and the crank journal axis is disposed within the C-shaped range. Connect the connecting rod connecting shaft from the position on the vertical line passing through the connecting shaft core to the side connecting the crankpin shaft core and the variable control arm connecting shaft core. From the extension line of the line connecting the pivot axis of the variable control arm and the connecting axis when the center of the swing of the variable control arm swings at the top dead center near the right angle to the cylinder axis. Stroke volume continuously variable device provided within the range to be arranged. Variable control arm on the minimum stroke volume side The swing distribution center is arranged at a substantially right angle to the cylinder axis, and the crank journal shaft core is variably controlled on the minimum stroke volume side within the range from the minimum compression ratio to the maximum compression ratio. The stroke volume continuous variable device according to claim 1, wherein the stroke volume continuous variable device is disposed on a tangent line of a variable control arm coupling axis core locus at the center of arm swing distribution. Variable control arm on the maximum stroke volume side The swing distribution center is arranged at a right angle to the cylinder axis, and the crank journal shaft core is controlled on the minimum stroke volume side within the range from the minimum compression ratio to the maximum compression ratio. The stroke volume continuous variable device according to claim 1, wherein the stroke volume continuous variable device is disposed on a tangent line of a variable control arm coupling axis core locus at the center of arm swing distribution. Variable control arm swing shaft position variable and fixed, variable to couple the two driven links connected by the pair even to the two drive links that can swing to the crankcase that is the stationary link The motor according to claim 1, wherein a motor and a driving force transmission mechanism are provided to swing the two driving links separately, and a nonreciprocal transmission mechanism is used as a part of the transmission mechanism. The described stroke volume continuously variable device. The stroke volume continuous variable device according to claim 1, wherein the upper dead center position and the lower dead center position of the piston are limited and an arbitrary compression ratio range is limited for each stroke. 6. The stroke volume continuous variable device according to claim 5, wherein the variable control arm swinging shaft is extended in the axial direction, and the two-dimensional movement range of the shaft portion protruding from the driven link is limited by a limiter plate. The stroke volume continuous variable device according to claim 5, wherein the limiter plate and the extension shaft of the variable control arm swing shaft are contacted via a rotating body. The stroke volume continuous variable device according to claim 5, wherein the limiter plate is provided in a cylinder closest to the variable arm.

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