JP2019167945A - Three-divided connecting rod type stroke volume and compression ratio continuous variable device - Google Patents

Abstract

To provide a compression ratio continuous variable device in which crank angles between a top dead center and a bottom dead center and between a bottom dead center and a top dead center are kept constant and crank phases of the top dead center and the bottom dead center are not changed in the entire range of a continuously variable compression ratio.SOLUTION: A connecting rod cooperatively connecting a piston with a crank is divided into three types of a piston connecting rod, a crank connecting rod and a link oscillatably connecting them in a direction perpendicular to a crank journal shaft, an oscillation shaft of an oscillation arm for stroking a small end of the crank connecting rod in a circular arc-shaped manner is fixed and an oscillation shaft position of the oscillation arm for stroking a large end of the piston connecting rod in a circular arc-shaped manner is variably controlled in a two-dimensional manner.SELECTED DRAWING: Figure 1

Description

The present invention relates to an engine in which a stroke volume and a compression ratio are arbitrarily and continuously variable at any time in an engine of an automobile, a ship, an outboard motor, etc., and a crank side of an arm that divides a connecting rod into three parts and swings a connecting part in an arc shape Crank angle between upper, lower dead center and lower, upper dead center over the entire range of stroke volume and compression ratio variable range by fixing the swing shaft and controlling the position of the piston swing shaft in two dimensions. Constant, can be set to 180 ° or any angle before and after, there is no change in crank phase at top dead center and bottom dead center, VVT for valve timing adjustment is unnecessary, crank balance is good and vibration reduction is achieved, and normal use By aligning the top dead center side arc-shaped locus of the piston side connecting rod large end in the region with the cylinder core axis, the piston side pressure can be greatly reduced and low mechanical loss can be achieved. ratio Limiting the circumference, stroke volume without power, fixed compression ratio, it is intended to also enable retention.

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, rotation speed, etc., the thermal efficiency in a wide operating range Improve and reduce pumping loss.
It has been proposed to convert piston reciprocating motion to crankshaft rotational motion on the swash plate (slanting shaft), change the tilt angle of the swash plate (slanting shaft) and crankshaft direction position, and change the stroke volume and compression ratio. However, the mechanical loss in the part that converts the piston reciprocating force to the rotational force of the output shaft is large, and it is difficult to achieve high rotation, greatly increasing the processing equipment of the engine that uses the conventional single connecting rod crank mechanism. However, if a single connecting rod crank mechanism can be applied, conventional processing equipment can be used and the engine layout will be similar, making it easier to install on conventional car bodies and barriers to practical use. Get smaller.
The connecting rod of the single connecting rod crank mechanism is divided into two parts, and the position of the swing axis of the arm is varied mainly to restrict the movement on the crank side with the arm. Patent Documents 1 and 2 are disclosed, in which a swing axis of an arm for restricting the movement of the crank side connecting rod is provided in the second quadrant inside the perpendicular.
JP 2003-129817 A JP 2003-201875 A Further, the crank side of the connecting rod divided into two is an L-shaped yoke provided with a variable control arm connecting shaft core at the opposite vertex that is substantially perpendicular to the side connecting the connecting rod connecting shaft and the crankpin shaft. The arm connecting shaft is stroked in an arc shape with the variable control arm, and the locus is close to the top dead center side with respect to the line passing through the crank journal shaft core and parallel to the cylinder core shaft, and the bottom dead center side expands to both sides Patent Document 3 discloses that the position of the swing axis of the variable control arm is variably controlled linearly or two-dimensionally so that the position and angle change radially within a range.
JP 2017-106428 A

In Patent Document 1, the swing axis of the control rod and the swing tip axis are provided in the second quadrant, and the locus of the tip axis determines the piston stroke. The trajectory of the tip axis spreads on the side farther from the crank journal axis (top dead center side) and narrows on the side close to the axis (bottom dead center side), above the minimum stroke side, between the bottom dead center and below The crank angle difference between the top dead centers is small, but on the maximum stroke side, the crank angle between the top and bottom dead centers is significantly larger than the bottom and top dead centers, and the crank balance is not achieved, which is disadvantageous in terms of vibration. At the same time, the top dead center phase changes greatly as the stroke changes, and VVT for adjusting the valve timing is essential. If the valve timing is also variable, a VVT with a larger phase variable width is required.

In Patent Document 2, it has been proposed to change the position of the swing axis of the control rod in a two-dimensional manner, so that the compression ratio with respect to the stroke can be arbitrarily changed, and the locus of the tip axis is separated from the crank journal axis. It is possible to expand on the side (top dead center side) and the side close to the axis (bottom dead center side), and the top dead center phase change due to the stroke change can be reduced, but other defects are not solved. 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 core axis of the connecting rod connecting shaft is kept small, and the piston side pressure can be greatly reduced, but the compression ratio with respect to the stroke is fixed. Both plans have good crank balance with small crank angle difference between top, bottom dead center and bottom, top dead center over the entire stroke volume variable range, top dead center phase change is small, VVT is unnecessary, and piston side pressure is greatly increased. It cannot be reduced and the mechanical loss can be reduced.

（位相はクランクジャーナル軸芯を通りシリンダ芯軸に平行な線からの時計回り角度）四気筒エンジンの様に隣合う気筒が１８０°クランクの場合、従来の単コンロッドクランク機構であれば隣合う気筒の平均ピストン位置は、図１３ピストンストロークカーブ点線の様に変動し、上、下死点クランク角が１８０°なので上、下死点時には上、下死点中央位置（一点鎖線上）となり一次クランクバランスが取れるが、二分割コンロッドのクランク側をＬ形ヨークとした特許文献３の例では、下、上死点間に対し上、下死点間のクランク角が大きく差が５０〜７０°にもなり、図１３実線の様に平均ピストン位置が大きく変動し、上死点及び上死点より１８０°回転時では中央位置からずれてしまい、吸気、膨張行程のクランク角を大きくとれるが、クランクバランスが悪く振動対策としてエンジン懸架ダンパにて対策できない場合はバランサが必要になったり、一軸クランクの対向ピストンエンジンではバランスが取れないので、二軸クランクを互いに逆転させる工夫が必要となり、エンジン幅、重量が増加する欠点があった。対策として、シリンダ芯軸を可変制御アーム揺動軸芯とクランクジャーナル軸芯の間に配置すれば下表例の様に、最小、最大ストローク間の上死点位相変化が大きくなるが、限られた行程容積、圧縮比可変範囲で１８０°にできると共に、下、上死点間に対する上、下死点間のクランク角差を最大２０°程度に抑えられるが差を無くすことはできない。

下死点側では行程容積を可変させる為に軌跡を両側に広げているが、軌跡のハの字状の範囲内にクランクジャーナル軸芯を配置することで、少ない広がり量で行程容積変化量を大きくでき、可変制御アーム連結軸芯ストローク軌跡のシリンダ芯軸直角方向変位を小さく抑えられるが、クランクピン軸芯がクランクの回転により円形軌跡を描くことで、可変制御アーム連結軸芯を揺動軸芯にコンロッド連結軸芯が揺動しつつ可変制御アーム連結軸芯が円弧状軌跡を描きストロークするので、コンロッド連結軸芯軌跡はシリンダ芯軸直角方向に振れ幅を有する軌跡となるが、直角方向変位は小さく抑えられ、ピストン側圧が大幅低減し低メカロスにできる。又、Ｌ形ヨークの可変制御アーム連結軸芯を頂点とする内角角度と可変制御アーム連結軸芯の円弧状軌跡を選択することにより、限られた可変範囲でのシリンダ芯軸直角方向振れ幅の狭いコンロッド連結軸芯軌跡にでき更にピストン側圧を大幅低減できるが、幅のある軌跡となり可変制御アーム連結軸芯の軌跡の様な円弧の線状軌跡にはならない。On the other hand, in Patent Document 3, the crank journal shaft core is disposed between the variable control arm swing shaft core and the cylinder core shaft as viewed in the crankshaft direction, and passes through the crank journal shaft core and is parallel to the cylinder core shaft. On the other hand, the variable control arm connecting shaft is approached on the top dead center side, and the bottom dead center side is a square-shaped range spreading on both sides, and the stroke is changed radially and the angle is changed. The top dead center height changes by slightly shifting the trajectory in the direction perpendicular to the cylinder core axis, and the compression ratio can be adjusted to correspond to the stroke volume (piston stroke). The point phase changes slightly as shown in the table below.

(Phase is a clockwise angle from a line passing through the crank journal axis and parallel to the cylinder axis.) When the adjacent cylinder is a 180 ° crank like a four-cylinder engine, the adjacent cylinder is a conventional single connecting rod crank mechanism. The average piston position fluctuates as shown in Fig. 13 piston stroke curve dotted line, and the top and bottom dead center crank angles are 180 °, so at the top and bottom dead center, the top and bottom dead center position (on the one-dot chain line) is the primary crank. Although the balance can be taken, in the example of Patent Document 3 in which the crank side of the two-part connecting rod is an L-shaped yoke, the crank angle between the upper and lower dead points is greatly different from 50 to 70 ° with respect to the upper and lower dead points. As shown in FIG. 13, the average piston position fluctuates greatly, and when it rotates 180 ° from the top dead center and top dead center, it shifts from the center position, and the crank angle of the intake and expansion strokes can be increased. When the engine suspension damper cannot cope with the vibration due to poor crank balance, a balancer is necessary, or the counter-piston engine with a single-shaft crank cannot be balanced. There was a drawback that the width and weight increased. As a countermeasure, if the cylinder core shaft is placed between the variable control arm swing shaft core and the crank journal shaft core, the top dead center phase change between the minimum and maximum strokes will increase as shown in the table below. In addition, the stroke angle and the compression ratio variable range can be 180 °, and the crank angle difference between the top and bottom dead centers can be suppressed to about 20 ° at the maximum, but the difference cannot be eliminated.

On the bottom dead center side, the trajectory is widened on both sides in order to vary the stroke volume, but the stroke volume change can be reduced with a small amount of spread by placing the crank journal shaft core within the C-shaped range of the trajectory. Although the displacement of the variable control arm connecting shaft core stroke trajectory in the direction perpendicular to the cylinder core axis can be kept small, the crank pin shaft draws a circular locus by the rotation of the crank. Because the connecting rod connecting shaft core swings on the core and the variable control arm connecting shaft core draws an arc-like locus and strokes, the connecting rod connecting shaft core locus is a locus having a swing width in the direction perpendicular to the cylinder core axis. Displacement is kept small, piston side pressure is greatly reduced, and low mechanical loss can be achieved. In addition, by selecting the internal angle with the variable control arm connection axis of the L-shaped yoke as the apex and the arc-shaped trajectory of the variable control arm connection axis, the deflection of the cylinder core axis perpendicular to the limited variable range can be reduced. Although the connecting rod connecting shaft core can be narrowed and the piston side pressure can be greatly reduced, it becomes a wide track and does not become a circular linear track like the variable control arm connecting shaft track.

The present invention has been made in view of the above-described problems. A connecting rod for connecting a piston and a crank is connected to a piston-side connecting rod (piston rod) and a crank-side connecting rod (connecting rod) in the direction perpendicular to the crank journal axis. Divided into three links (connecting links) that can be pivoted, the pivot shaft of the pivot arm (connect rod arm) that strokes the small end of the connecting rod in an arc shape is fixed, and the large end of the piston rod is stroked in an arc shape By controlling the swing axis position of the swing arm (variable control arm) to be two-dimensionally variable, the crank phase of the top dead center and bottom dead center does not change over the entire range of stroke volume and compression ratio. VVT for adjusting the valve timing is no longer necessary, the crank angle between the top and bottom dead centers, the bottom and top dead centers can be made constant, and the upper end of the connecting rod If the axis of the bottom dead center at the bottom end of the connecting rod is placed on the line connecting the axis of the center of time and the crank journal axis, the crank angle between the bottom dead center will be 180 °, and the axis of the bottom dead center at the bottom of the connecting rod will be 180 °. Can be set to an arbitrary angle of about 180 ° by shifting the line from the line, and the piston rod large end draws a linear trajectory of the arc, so that the top dead center side trajectory in the normal range is substantially aligned with the cylinder core axis, Piston side pressure is greatly reduced, and mechanical loss can be reduced. Also, in the widest possible range, the distance between the circular arc path between the piston rod large end and the connecting rod small end is not widened while the piston rod large end and the connecting rod small end are stroked from the bottom dead center to the top dead center side. By arranging the swing control cores of the variable control arm and connecting rod arm, it is possible to prevent the reversal of the tilt of the connecting link in the cylinder core direction as much as possible, and the piston speed difference between the top dead center side and the bottom dead center side during the stroke is reduced. By reducing it, the crank balance is improved and vibration is reduced. The stroke volume is continuously variable continuously according to the engine usage characteristics, and the compression ratio is set according to the stroke volume, or arbitrarily continuously variable continuously. Variable, can improve heat efficiency and reduce pumping loss in a wide operating range, and further limit the piston, bottom dead center position and compression ratio range, stroke without power Product, fixed compression ratio, stroke volume also allows retention, and provides a compression ratio continuously variable device.

In order to solve the above-mentioned problem, the invention according to claim 1 includes three connecting rods that connect the piston and the crank to the piston-side connecting rod, the crank-side connecting rod, and a link that slidably connects them in the direction perpendicular to the crank journal axis. Dividing and fixing the swing axis of the swing arm that strokes the crank end connecting rod small end in an arc shape, and two-dimensionally changing the swing axis position of the swing arm that strokes the piston end connecting rod large end in an arc shape It is characterized by controlling.

In Patent Document 3 of the conventional example, a connecting rod connecting shaft core, a variable control arm connecting shaft core, and a yoke in which a crankpin shaft core is arranged in an L shape are used, and a variable control arm connection corresponding to the connecting rod small end shaft core in the present invention is used. By slightly shifting the shaft core in the direction perpendicular to the cylinder core axis on the top dead center side, the top dead center height is changed and the compression ratio is adjusted to correspond to the stroke volume. In order to slightly change the point phase and to change the stroke volume, the variable control arm swing axis is expanded in a C shape on the crank journal axis side. Because the three-point position of the variable control arm connecting shaft core, connecting rod connecting shaft core, and crankpin shaft core of the L-shaped yoke is fixed, the crank top, bottom dead center phase and stroke volume, compression The variable ratio also changes in conjunction with it It was.
The present invention connects the small end of the connecting rod and the large end of the piston rod with a connecting link pivotally supported at both ends of the small end of the connecting rod and the large end of the piston rod so that the top dead center phase on the crank The stroke volume and variable compression ratio can be determined separately. The top dead center phase is determined by the arc-shaped locus at the small end of the connecting rod, and the stroke volume and compression ratio are determined by the arc-shaped locus at the large end of the piston rod. If the position of the pivot axis of the arm is appropriately determined and fixed, the upper, lower dead center phase and the angle between the upper, lower dead center and the lower, upper dead center are constant over the entire stroke volume and variable compression ratio range. VVT for timing adjustment is not necessary, and the angle between the top and bottom dead centers can be set to 180 ° or around that, so that a single connecting rod crank mechanism or higher crank balance can be obtained, and vibration can be reduced as compared with Patent Document 3.

According to a second aspect of the present invention, in the first aspect of the invention, the crank-side connecting rod small end is located on a line connecting the top dead center axis of the crank-side connecting rod small end and the crank journal shaft when viewed from the crank journal axis direction. The bottom dead center axis is arranged.

As shown in FIG. 12, the bottom dead center axis (on the line Y ′ (hereinafter referred to as the Y ′ line) connecting the top dead center axis (St) and the crank journal axis O (hereinafter referred to as the axis O) at the small end of the connecting rod. By arranging Sb), as shown in the piston stroke curves of FIGS. 14 to 17, the angle between the top dead center and the bottom dead center can be set to 180 °, vibration can be reduced, and an opposed piston engine with a single-shaft crank can be realized. However, in order to keep the cylinder height as low as possible, the linkage ratio λ = 2 in the embodiment of FIG. 14, the minimum stroke λ = 3.97 when the single connecting rod crank mechanism is used (dotted line), the maximum stroke Since the linkage ratio is small with respect to λ = 3.33, the difference in piston speed between the top dead center side and the bottom dead center side becomes large, and further, the small end of the connecting rod draws an arc-shaped locus and strokes up and down. The difference between the top dead center and the top dead center becomes larger than that between the dead centers, which is disadvantageous in terms of vibration compared to the single connecting rod crank mechanism, but compared with Patent Document 3, the vibration can be greatly reduced. However, as the piston rod large end and the connecting rod small end stroke from the bottom dead center to the top dead center, the distance between the circular arc locus between the piston rod large end and the connecting rod small end becomes narrower. By devising the pivot axis arrangement, the stroke ratio increase is halved as shown in FIGS. 16 and 17, but the piston stroke curve can be made closer to a sine curve, and vibration can be reduced by a single connecting rod crank mechanism. By shifting the axis of the bottom dead center from the Y 'line, the angle between the top and bottom dead centers can be easily set to an arbitrary angle around 180 °. The angle between the top and bottom dead centers can also be selected.

Further, the invention according to claim 3 is the invention according to claim 1, wherein the piston side connecting rod is larger than the line connecting the upper dead center at the crank end connecting rod small end and the crank journal axis when viewed from the crank journal axis direction. The swing axis of the end and crank side connecting rod small end swing arm is provided on the same quadrant side, and on the maximum stroke side, the arc side locus on the piston side connecting rod large end is compared to the arc side locus on the crank side connecting rod on the crank side. The connecting rod small-end swing arm is arranged on the opposite side of the swing axis.

The connecting rod arm swing axis C (hereinafter referred to as axis C) in FIG. 1 (solid line on the left in FIG. 12), which is an embodiment of claim 3, is positioned in the quadrant opposite to the Y ′ line as shown by the dotted line in FIG. If it is arranged near the symmetrical position, it will not overlap with the position variable range of the shaft core C and the variable control arm swing shaft core V (hereinafter referred to as shaft core V) and the swing range of the variable control arm as viewed in the crank journal axial direction. Therefore, it is not necessary to dispose the connecting rod arm and its swing shaft outside the variable control arm and its swing shaft in the direction of the crank journal axis. The shaft can be supported by a single shaft, which simplifies the structure and facilitates processing and assembly. However, the connecting rod small-end shaft core S (hereinafter referred to as shaft core S) and piston rod large-end shaft core B (hereinafter referred to as shaft) The convex shape of the arc-shaped locus of the core B) is reversed. At the same time, the arcuate locus of the axis B is on the same side as the axis C with respect to the arcuate locus of the axis S on the maximum stroke side, and the axis S and the axis B stroke from the bottom dead center to the top dead center side. A section where the interval widens is generated between the pistons, and a piston stroke curve having a large crank rotation angle on the bottom dead center side as shown in FIG. Thus, the difference in piston speed between the top dead center side and the bottom dead center side increases, which is disadvantageous in terms of vibration.
When the shaft core C and the shaft core V are arranged on the same quadrant side with respect to the Y ′ line, as shown in the left diagram in FIG. 12, the shaft core C and the shaft core V can be seen in the axial direction of the crank journal. Since the position variable range and the swing range of the variable control arm overlap, the connecting rod arm and its swing shaft are arranged outside the variable control arm and its swing shaft in the direction of the crank journal axis, and the structure is complicated. However, machining and assembly takes time, but by arranging the arcuate locus of the axis B on the opposite side of the axis C with respect to the arcuate locus of the axis S in the widest possible variable range on the maximum stroke side, Y ′ The convex shape of the arcuate locus of the axis S and the axis B is the same direction with respect to the line, and the interval when the axis S and the axis B stroke from the bottom dead center to the top dead center side is at least narrowed without widening. Since it can be arranged, the Y-axis direction inclination of the connecting link is As shown in FIG. 14, the piston speed difference between the top dead center side and the bottom dead center side during the stroke can be reduced as shown in FIG. 14, the crank balance is improved, the vibration is reduced, and the stroke ratio (maximum / minimum stroke). Also, it is possible to ensure the same level as Patent Document 3 (this example is 1.45 in comparison with the compression ratio of 12:00).

るが、クランクケースのコンパクト化と、可変制御アームのアーム部とシリンダスカート下端との接触を避けできる限りシリンダ高を低く抑える為に、最小弦長時のＢｔ、Ｖｓを結んだ線とＹ軸の交点の内角αを略直角以下にすると共に、Ｙ’線に対し軸芯Ｖと軸芯Ｃを同象限側に配置し、軸芯Ｓと軸芯Ｂの円弧状軌跡が殆どの可変範囲で同象限側になるよう配置している。本実施例では、Ｙ軸を自動車用エンジンの常用域である最高圧縮比、最小ストローク時の上死点付近を通り、下死点時連結リンクの軸芯Ｓｂ回りのピストンロッド大端軸芯円弧の接線付近を通る配置とすることで、常用域の上死点側での軸芯Ｂ円弧状軌跡をＹ軸に沿わせ、最大ストローク側での軸芯Ｂ円弧状軌跡の弦をＹ軸に略平行としストローク減少を抑えると共に、可変範囲における軸芯Ｂ円弧状軌跡のＸ軸方向最大振れ幅の中央付近を通しピストン側圧を抑えている。
軸芯Ｏと軸芯Ｖの軸間が広がりクランクケースが増大するが、図１２右図の様に軸芯Ｓと軸芯Ｂの円弧状軌跡を配置することで、ピストンストロークカーブを単コンロッドクランク機構より正弦カーブに近づけることが可能となる。（図１２参照）The chord length (≈piston stroke) of the piston rod large end arcuate locus is the line connecting the connecting rod large end axis (crankpin axis) P and the small end axis S at the top and bottom dead centers (= Y ' Is determined by the swing angle around the bottom dead center axis St, Sb above the connecting link, and the piston rod large end axis Bt, Bb at the top dead center is at a position where it is on the Y ′ line. If the core Vs is disposed, the swing angle difference between the top and bottom dead centers is zero, and the minimum chord length is obtained. The maximum chord length swings around the axis Sb of the connecting link with respect to the line connecting the connecting rods P and S at the bottom dead center as long as the connecting rod large end and the connecting rod arm do not come into contact with each other. The top dead center is at the top dead center position where the connecting link is swung from the top dead center at the minimum chord length and the target compression ratio is the maximum chord length.

However, in order to make the crankcase compact and to keep the cylinder height as low as possible to avoid contact between the arm of the variable control arm and the lower end of the cylinder skirt, the line connecting the Bt and Vs at the minimum string length and the Y axis The internal angle α of the intersection point is made substantially equal to or smaller than the right angle, and the axis V and the axis C are arranged on the same quadrant side with respect to the Y ′ line, and the arc-shaped locus of the axis S and the axis B is in the most variable range. Arranged to be on the same quadrant side. In this embodiment, the piston rod large end axis arc around the axis Sb of the connecting link at the bottom dead center passing through the vicinity of the top dead center at the minimum stroke and the maximum compression ratio, which is the normal range of the engine for automobiles, in the present embodiment. By placing the tangent line near the axis, the axis B arcuate locus on the top dead center side in the normal range is along the Y axis, and the chord of the axis B arcuate locus on the maximum stroke side is the Y axis. It is substantially parallel to suppress stroke reduction, and the piston side pressure is suppressed through the vicinity of the center of the maximum deflection width in the X-axis direction of the axis B arcuate locus in the variable range.
The space between the shaft core O and the shaft core V increases and the crankcase increases. By arranging the arcuate locus of the shaft core S and the shaft core B as shown in the right figure of FIG. It is possible to approximate a sine curve from the mechanism. (See Figure 12)

According to a fourth aspect of the present invention, in the first aspect of the invention, the piston-side connecting rod is larger than the line connecting the upper dead center axis at the small end of the crank-side connecting rod and the crank journal shaft when viewed from the crank journal axis direction. The swing axis of the end and crank side connecting rod small end swing arm is provided in the quadrants opposite to each other, and on the maximum stroke side, the arc side locus of the piston side connecting rod large end is cranked against the arc shape locus of the crank side connecting rod small end. The side connecting rod small end swinging arm is arranged on the opposite side of the swing axis.

The axis V and the axis C are arranged in opposite quadrants with respect to the Y ′ line, and the convex shape of the arc-shaped locus of the axis S and the axis B is reversed, and the right side of FIG. As shown by the solid line, if the arc V of the axis B is within the variable range of the axis V where the arc B of the axis B is opposite to the axis C with respect to the arc of the axis S, the axis S and the axis B are dead. As the stroke moves from the point to the top dead center side, the interval is narrowed, and the inclination of the connecting link in the Y-axis direction becomes tighter according to the stroke, resulting in a piston stroke curve as shown in FIG. ) Can reduce the piston speed difference between the top dead center side and the bottom dead center side. On the maximum stroke side, the average piston position of the adjacent cylinders rises and becomes a curve with little fluctuation at the bottom dead center position. A single connecting rod club approaching the chain line) The difference can be reduced and the vibration reduction effect is large compared to the case where the transmission mechanism (continuous ratio λ = 3.62) is used (dotted line), but the stroke ratio cannot be taken large (this example is 1.21 compared with the compression ratio of 12:00). Although there are drawbacks, it is possible to adopt it if importance is attached to variable compression ratio and vibration reduction.

According to a fifth aspect of the present invention, in the first aspect of the invention, the piston-side connecting rod is larger than the line connecting the upper dead center at the top end of the crank-side connecting rod and the crank journal shaft when viewed from the crank journal axis direction. The pivot axis of the end and crank side connecting rod small end swing arm is provided on the same quadrant side, and on the maximum stroke side, the arc side locus of the crank side connecting rod small end is lower than the arc side locus of the piston side connecting rod large end. The point position is arranged on the crank side connecting rod small end swinging arm swinging shaft core side.

The invention of claim 5 is a plan in which the convex shape of the arc-shaped locus of the shaft core S is opposite to the Y ′ line with respect to the invention of claim 4. Since the locus is convex toward the crank rotation direction side, the crankpin phase is at an angle advanced near the piston stroke center position, and the shaft core S and shaft core B are stroked from the bottom dead center to the top dead center side. Since the interval is suddenly narrowed, a sharp piston stroke curve is obtained. However, in the invention of claim 5, the arcuate locus of the shaft core S has a convex shape on the opposite side to the crank rotation direction. Since the crankpin phase becomes an angle delayed and the interval between the shaft core S and the shaft core B is gradually narrowed from the bottom dead center to the top dead center side as compared with the invention of claim 4, a gentle piston stroke curve is obtained. Can be. Furthermore, the average piston position curve is the same as that of the single connecting rod crank mechanism on the minimum stroke side, and vibration can be reduced on the minimum stroke side.
If the curvature and arrangement of the arcuate trajectories of the shaft core S and the shaft core B are appropriately selected, it is possible to further approximate a sine curve, and even in the case of claim 3 (solid line on the left in FIG. 12) The piston stroke curve shown in FIG. 17 can be obtained by devising the arc S of the axis B closer to the axis S at the top dead center of the core S or by changing the inclination of the arc B of the axis B with respect to the Y ′ axis. Can be approached.

Further, the invention of claim 6 is the invention according to claims 1 and 3, wherein in the crank journal axial direction, the crank side connecting rod small end swing is formed by connecting the arm part to both outer sides of the link and the crank side connecting rod small end with a bridge. An arm and a swing shaft are provided, and the piston-side connecting rod swing arm and the swing shaft are arranged on the inner side in the crank journal axis direction so that the swing shaft position can be varied.

When the invention according to claim 3 is adopted, the connecting rod arm and the swinging range of the connecting rod arm and the swinging range of the connecting rod arm overlap with the variable control arm swinging shaft position variable range and the swinging range of the arm when viewed from the crank journal axis direction. The moving shaft is arranged outside the variable control arm and its swing shaft in the direction of the crank journal axis.
In this embodiment, both ends of the connecting rod small end shaft are press-fitted into the left and right connecting rod arms, the connecting rod small end and the connecting link are swingable inside the connecting rod arm, and are axially supported by the connecting rod small end shaft. The swinging shaft hole of the connecting rod arm is swingable by the connecting rod arm swinging shaft and the end face of the crankcase shaft hole, and is pivotally supported by axial restriction, and the connecting rod arm press-fitting portion twist strength at both ends of the connecting rod small end shaft If the load is weak, there is a risk that the connecting rod arm swing shaft hole core will be displaced due to the load, increasing the swing resistance of the connecting rod arm or making it impossible to swing. Because the inner width of the left and right counterweights is increased to prevent contact during rotation, the left and right connecting rod arms are connected by a bridge and twisted without increasing the press-fit width. It is intended to ensure increased sex.

According to a seventh aspect of the present invention, in the first, third, and fourth aspects of the invention, the axial length of the swing shaft of the crank-side connecting rod small end swing arm is shorter than the outer end face width of the swing shaft hole of the swing arm. It is characterized by doing.

During assembly, the connecting rod arm swinging shaft can be stored in the connecting rod arm swinging shaft hole, so the connecting rod arm swinging shaft is shifted after aligning the connecting rod arm swinging shaft hole core with the crankcase shaft hole core. Thus, the assembly time can be reduced by being accommodated in the nearest crankcase shaft hole.

According to an eighth aspect of the present invention, in the first aspect of the present invention, the driving link and the variable arm for two-dimensionally changing the swinging shaft position of the piston-side connecting rod large end swinging arm are connected to the variable shaft by a knock screw. The axial position and phase are determined, and the nut is used to prevent loosening.

Only the Knox screw can control the phase and axial direction of the drive link, variable arm, and limit detection drive link with respect to the variable shaft, and by tightening the fastening bolt, the shaft of the variable shaft, each link, and the shaft hole of the arm It can be assembled by absorbing the gap and the gap between the knock screw hole of the variable shaft and the knock screw. If nuts are eliminated and only bolts are tightened, even if the knock bolts are tightened before tightening the fastening bolts, there will be a gap in the fastening bolt head contact seating surface due to deformation of the link and arm shaft mounting hole bosses due to fastening bolt tightening. However, if the knock bolt is tightened after the tightening bolt is tightened, the shaft core hole is displaced due to deformation of the shaft mounting hole boss portion, and the shaft cannot be inserted. Even if it is inserted in advance, the resistance increases due to the misalignment of the core of the hole, and the specified tightening torque is reached in a state where there is a gap in the head contact seating surface, which makes it easy to loosen. By using a screw and nut system like a rocker arm tappet, loosening can be prevented by tightening the fastening bolt after temporarily tightening the screw at a specified position, and then tightening the nut with a nut to prevent loosening.

According to the present invention, the connecting rod that connects the piston and the crank is divided into three parts, the piston rod, the connecting rod, and the connecting link that connects the piston rod and the connecting rod so as to be swingable in the direction perpendicular to the crank journal axis, and the connecting rod small end is stroked in an arc. By fixing the swing axis of the connecting rod arm and variably controlling the swing axis position of the variable control arm that strokes the piston rod large end in an arc shape, the stroke volume, the compression ratio variable range over the entire range, The top dead center and bottom dead center crank phases do not change, VVT is not required to match the valve timing, the crank angle between the top dead center, the bottom dead center, the bottom dead center, and the top dead center can be made constant. If you place the bottom dead center axis on the small end of the connecting rod on the line connecting the top dead center axis and the crank journal axis, the top dead center crank angle will be 180 °, If the axis of the bottom dead center at the small rod end is shifted from the line, it can be set to an arbitrary angle of around 180 °, and the large end of the piston rod draws a circular arc-like locus, so the top dead center side locus in the normal range is roughly omitted. By following the cylinder core, the piston side pressure is greatly reduced, and the mechanical loss can be reduced. Also, in the widest possible range, the distance between the circular arc path between the piston rod large end and the connecting rod small end is not widened while the piston rod large end and the connecting rod small end are stroked from the bottom dead center to the top dead center side. By arranging the swing control cores of the variable control arm and connecting rod arm, it is possible to prevent the reversal of the tilt of the connecting link in the cylinder core direction as much as possible, and the piston speed difference between the top dead center side and the bottom dead center side during the stroke is reduced. By reducing it, the crank balance is improved and vibration is reduced. The stroke volume is continuously variable continuously according to the engine usage characteristics, and the compression ratio is set according to the stroke volume, or arbitrarily continuously variable continuously. Variable, can improve thermal efficiency and reduce pumping loss in a wide operating range, and further limit on piston, bottom dead center position and compression ratio range, stroke volume without pressure, pressure Fixed ratio, stroke volume also allows retention, and provides a compression ratio continuously variable device.

The stroke volume and compression ratio continuously variable device according to the present invention can be applied to power devices such as various gasoline, diesel, and HCCI engines mounted on automobiles, ships, outboard motors, etc., and the embodiments will be described in detail below with reference to the drawings. To do.

The connecting rod that connects the piston and crank is divided into three parts: the piston rod, connecting rod, and connecting link that allows them to swing freely in the direction perpendicular to the crank journal axis. Two-dimensional variable control of the oscillating shaft position of the variable control arm that fixes the shaft and strokes the piston rod large end in an arc shape, and the stroke volume is continuously variable continuously according to the engine usage characteristics, and the compression ratio Is set in accordance with the stroke volume or arbitrarily continuously variable at any time, and includes a crank mechanism 10, a stroke volume, a compression ratio variable mechanism 20, a stroke volume, and a 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. A camshaft, a camshaft drive sprocket 15d for transmitting power to the oil pump, and an oil pump drive sprocket 15e are provided on the crankshaft stepped shaft on the opposite side. 1 and 2, in this embodiment, it is rotated in the cylinder direction (clockwise), but the crank phases of the top dead center and the bottom dead center do not change over the entire variable stroke, and the top and bottom dead centers. Since the crank angle between the middle and bottom and top dead center can be set to an arbitrary constant angle of about 180 ° or about 180 °, it is possible to make it counterclockwise. (See Figures 1-3)

A crank pin hole is formed by fastening a half connecting rod metal bearing 13-2 and a connecting rod cap 13-1 to the large end of the connecting rod 13 with a bolt 13-3. The connecting rod is connected to the crank pin shaft 15a in the direction of the crank journal axis. It is pivotally supported in a regulated and rotatable manner.
Note that the connecting surface of the connecting rod and connecting rod cap swings the variable control arm from the plane perpendicular to the line connecting the crank pin hole and the connecting rod small end hole core in order to avoid contact with the swing shaft of the variable control arm. It is tilted away from the shaft.
A connecting rod small end shaft 17-1 whose both end shaft portions are press-fitted and fixed to the tip hole of the connecting rod arm 18 is connected to a connecting rod small end which is bifurcated into a U-shape in the axial direction and a connecting link 17 disposed in the middle. The connecting rod arm front end inner end surface, the connecting rod small end, and the end surface of the connecting link are axially restricted and rotatably supported.
The connecting rod arm has an arm and a swinging shaft hole boss portion divided into both sides as viewed in a direction perpendicular to the crank journal axis, and is rotatably supported by connecting rod arm swinging shafts 18-1 and 18-2. The axial direction is regulated by the outer surface of the hole boss part and the end face of the swing shaft hole of the crankcase, and the small end of the connecting rod can be swung in an arcuate shape. The connecting rod arm swinging shaft core C is disposed at the center position of the arc where the bottom dead center shaft core Sb is disposed on the line connecting the crank journal shaft core O and the crank journal shaft core O.
If the torsional strength of the connecting rod arm press-fitting parts on both ends of the connecting rod small end shaft is weak, the core of the connecting rod arm swinging shaft hole on both sides may be displaced due to the load, and the swinging resistance of the connecting rod arm may increase or be unable to swing I want to increase the press-fit width to improve strength, but to increase the inner width of the left and right counterweights to prevent contact during rotation, connect the left and right connecting rod arm arms with a bridge 18a. Torsional rigidity is ensured without increasing the press-fitting width.
The connecting rod arm swinging shaft 18-1 disposed between the cylinders is prevented from coming off by fitting the circlip 18-3 into the grooves at both ends and sandwiching the inner surface of the connecting rod arm swinging shaft hole boss portion. By making N shorter than the width M of the outer end face of the connecting rod arm swinging shaft hole boss, it is possible to place the connecting rod arm swinging shaft in the swinging shaft hole of the connecting rod arm during assembly. By aligning the pivot shaft hole core of the connecting rod arm with the shaft hole core and then shifting the connecting rod arm rocking shaft, it can be accommodated in the nearest crankcase swing shaft hole and the number of assembly steps can be reduced. The connecting rod arm swing shaft 18-2 disposed outside the cylinder has a hook provided at one end and a circlip 18-3 in the groove at the other end, and an inner surface of the connecting rod arm swing shaft hole boss. The crankcase is prevented from coming off by pinching the end face of the pivot shaft hole. (See FIGS. 1-3, 6, and 12)

For the purpose of maximizing the piston side pressure in the normal range and reducing the displacement in the X-axis direction within the variable range to reduce the piston side pressure, it passes through the position at the top dead center of the piston rod near the normal range, The piston 11 is inserted into the cylinder 1 that is offset with respect to the shaft core O so as to be distributed through the large end arc-shaped locus of the variable range, and the piston pin 11− that is disposed in parallel with the crank journal shaft. The piston rod 12 is pivotally supported by 1 and the both ends of the piston rod large end shaft 12-1 are press-fitted and fixed in the holes of the piston rod large end divided into two forks in the axial direction. Two thin plate-like variable control arms 14 are connected to both ends of the connecting link at the center of the large end shaft of the rod, and are axially regulated by the respective end surfaces and the inner end surface of the piston rod large end hole, and are rotatably supported by the large end shaft. There.
In this embodiment, the X-axis direction position of the Y-axis with respect to the piston rod large end locus is set to the minimum stroke volume and the maximum compression ratio side, which are the normal range of the engine for automobiles. The operating time zone where the piston side pressure is suppressed should be widened by placing it near the top dead center.
The variable control arm that regulates the movement of the piston rod large end is pivotally supported by the variable control arm swing shaft to swing, so that the piston rod large end swings in an arc shape mainly in the Y axis direction. The direction displacement is reduced and piston reciprocating motion is converted into crank rotational motion. The position of the variable control arm swing shaft is variably controlled two-dimensionally, so that the minimum or maximum stroke volume side can be adjusted according to the engine usage characteristics. The displacement width in the X-axis direction of the piston rod large end locus is minimized, and the side pressure due to piston slap can be greatly reduced, resulting in low mechanical loss.
In addition, since the connecting link is rotatably supported by the piston rod large end shaft and the connecting rod small end shaft, the inclination of the piston rod and the connecting rod can be freely changed according to the change in the distance between the arcuate trajectories. Since the movements of the piston rod large end shaft and connecting rod small end shaft are not linked, the crank phases of the top dead center and bottom dead center do not change over the entire variable range, and the top dead center, top dead center, bottom dead center, and top dead center. The crank angle between them can also be set to an arbitrary constant angle of 180 ° or around 180 °.
The connecting rod and the connecting rod and the shaft support on the piston rod large end side of the variable control arm are connected to the connecting rod, connecting rod, and the oil passage of the connecting rod and piston rod large end shaft. Lubricated with oil supplied through a passage (see FIGS. 1 to 5)

The stroke volume and compression ratio variable mechanism 20 is a variable control arm swinging shaft that regulates the movement of the piston rod, and the position of the swing shaft is fixed and fixed by a five-bar linkage mechanism. The core of the lower variable shaft 23L, which is the opposite of the link 21L, is disposed and the shaft is disposed in parallel with the crank journal shaft. A tool is inserted into the head quadrangular column of the knock screw 21-1, and the lower end screw portion is variable. After temporarily assembling the shaft screw hole to an appropriate axial position, the bolt 21-3 is tightened, and then the nut 21-2 is tightened to prevent the loosening of the knock screw with a square pole, thereby preventing the loosening, and the lower driving link The phase and the axial position are determined so as to be swingable together with the lower variable shaft.
On the other hand, the upper drive link 21U is assembled in the same manner as the lower drive link to the upper variable shaft 23U, which is a pair, which is rotatably inserted into the shaft hole of the upper crankcase that is opened in parallel to the crank journal shaft, and is variable in the lower drive link. It can swing with the shaft. (See Figures 1-5)

The lower driven link 22L is axially restricted at one end at the inner side of the boss at both ends of the lower driving link, and has a lower link pin 24L that is press-fitted and fixed in the hole at both bosses. A pair of shafts that are movably supported, and that the other end of the upper driven link 22U is press-fitted and fixed at both ends, and the variable control arm swinging shaft 16 that is a mating pair, are disposed between the front end and the upper driven link. The upper driven link and the variable control arm are lower by sandwiching the both side surfaces of the tip part with the variable control arm and the upper driven link press-fitted into the arm swinging shaft. The axial direction is restricted with respect to the driven link.
Also, an oil passage is provided in the lower variable shaft, lower driving link, lower link pin, lower driven link, variable control arm swing shaft, and oil supplied from the oil gallery to the lower variable shaft central oil passage other than the press-fit portion. The bearing is lubricated.
The pair of upper driven links are press-fitted into both ends of the upper link pin 24U that is rotatably inserted into the hole of the upper driving link front end boss portion, and the boss portions on both ends of the upper driving link end are sandwiched so as to be axial with respect to the upper driving link. It is pivotally supported so as to be regulated and swingable. (See Figures 1-5)

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. (Refer to FIGS. 1 to 5 and 7 to 11) In addition, the V-shaped angle of the link with respect to the pair of the upper, lower link pin and variable control arm swinging shaft approaches the straight line in the total stroke volume and the variable compression ratio range, and the dead point ( It is necessary to have a layout that does not generate thought points.

The stroke volume / compression ratio control mechanism 30 is an upper of the five-bar linkage mechanism that performs variable position, fixing, and holding of the variable control arm swing shaft, an upper that is a pair of the lower drive link, and an upper that swings the lower variable shaft. The lower variable arms 37U and 37L are arranged in the cam chain chamber on the opposite side of the transmission chamber in the axial direction of the upper and lower variable shafts, and the phase and axial position of the upper and lower variable shafts by the knock screw 37-1. After tightening the end screw part of the Nox screw into the shaft screw hole and temporarily assembling it to an appropriate axial position, tighten the bolt 37-3, and then tighten the nut 37-2 to prevent loosening, together with the upper and lower variable shafts. It can swing freely. The upper and lower variable arm uppers, the mounting boss end surface and upper of the lower variable shaft, and the shaft end surface of the lower variable shaft are clamped between the crankcase upper, the lower variable shaft insertion hole end surface and the cam chain cover mating surface. The axial direction of the variable shaft is regulated. (See Figs. 4, 5, and 7)

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 on the stepped shafts on both sides of the joint pin that is rotatably inserted so as to sandwich the upper, lower variable arm tip and upper, and both side surfaces of the joint holder part of the lower male feed screw. The upper, lower variable arm, and upper When the joint holder is separated from the female screw, the joint is restricted to the axial direction of the joint pin and pivotally supported with respect to the lower male feed screw. In addition to preventing falling, the male screw stops rotating and the male screw moves in and out of the female screw in the axial direction by rotating the female screw. Path, and swing the lower variable arm.
The upper female feed screw 33U, which engages with the upper male feed screw, is axially restricted and rotatably supported by the upper control motor holder 32U, is provided parallel to the Y axis. The driven gear portion 33Ua, which is rotatably inserted into the hole of the upper control motor holder and provided at the shaft end, has both side surfaces of the gear portion mating surfaces with the upper control motor holder of the upper crankcase perpendicular to the Y axis, and liquid. It is liquid-sealed with a gasket, positioned with a knock pin 32-2, and is fixed with bolts 31-1, 32-1, and is regulated in the axial direction at the upper female feed screw hole end face of the upper control motor holder.
The lower female feed screw 33L, which engages with the lower male feed screw and is axially restricted and rotatably supported by the upper crankcase, allows the male feed screw to move in and out in the axial direction. The both sides of the gear portion of the driven gear portion 33La that is rotatably inserted into the hole of the upper crankcase and that is provided at the shaft end are liquid-sealed with a liquid gasket on the mating surface of the upper crankcase perpendicular to the Y axis, and a knock pin The axial direction is regulated by the case mating surface of the lower control motor holder 32L, which is positioned by 32-2 and fixed by bolts 31-1, 32-1, and the lower female feed screw hole end surface of the upper crankcase. (See FIGS. 4, 5, 7-10)

The upper and lower control motors 31U and 31L having drive pinion gear portions 31Ua and 31La that directly or indirectly mesh with the driven gear portion and transmit power are arranged with the rotation axis parallel to the axis of the female feed screw, and the O-ring 31-2. And is fixed to the upper crankcase together with the control motor holder by a liquid seal bolt 31-1.
The mating surface of the control motor holder and the upper crankcase is provided as much as possible on the variable shaft side in order to make the crankcase more compact, so avoid contact with the upper male feed screw at the minimum stroke volume and maximum compression ratio. In order to avoid contact between the control motor holder cover and the control motor that protrudes, a hole provided in the upper crankcase and the control motor holder is provided between the drive pinion gear of the upper control motor and the driven gear of the upper female feed screw. An upper feed screw idle gear 33Ui that is rotatably supported and whose axial direction is regulated by the end face of the hole is provided to widen the space between the upper female feed screw and the upper control motor. (See FIGS. 7 to 10)

Upper and lower by the forward and reverse rotation of the lower and lower control motors, and the upper and lower variable arms fixed to the upper and lower variable shafts by the forward and backward movement of the lower male feed screw. 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 46U and 46L that are liquid-sealed to the cam chain cover 4 with an O-ring 46-2 and fastened with bolts 46-1 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 Figs. 4 and 5)

In the present invention, by providing a feed screw that is a nonreciprocal transmission mechanism in a part of the power transmission mechanism of the control motor, stroke volume, and compression ratio variable mechanism, the stroke volume and compression ratio can be kept constant with no power. Power consumption can be suppressed and fuel consumption can be reduced.
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.

Next to the upper and lower variable arms, the limit detection upper and lower driving links 41U and 41L having the same inter-axis length as the upper and lower driving links are fastened to the upper and lower variable shafts in the same manner as the upper and lower variable arms. The limit detection upper and lower driven links 42U and 42L, which have the same inter-axis length as the upper and lower driven links, are press-fitted into the end holes of the limit detection upper and lower driving links by pressing the link pins 43 with the flanges. The limit detection upper follower link is pivotally supported by the pin, and the limit detection upper follower link one end hole is inserted into the limiter bearing shaft 44-1, which is press-fitted into one end hole of the limit detection lower follower link. A limiter bear on the opposite side of the limit detection upper driven link. Ring shaft has axially restricted and prevented from falling off the bearing by circlip 44-2 Insert the limiter bearings 44, and the same variable during the movement of the limiter bearing shaft and the variable control arm pivot shaft.
The limiter plate 45 that limits the two-dimensional movement range of the limiter bearing shaft by contacting with the outer ring of the bearing is accurately positioned on the cam chain cover with the knock pin 45-1 and tightened with the bolt 45-2 to the cover. It is fixed.
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 limiter bearing shaft at the standard compression ratio (compression ratio 12 in this embodiment) (= variable control arm swing shaft) The one-dot chain line indicates the lowest compression ratio (compression ratio 10), the two-dot chain line indicates the highest compression ratio (compression ratio 18), the upper cross center indicates the piston top dead center and the minimum stroke volume limit, The lower cross center is at the piston bottom dead center and the maximum stroke volume limit position, and the lower cross center position height varies depending on the compression ratio. This is to prevent the collision.
By limiting the two-dimensional variable range of the swing axis of the variable control arm with a limiter device, the upper and lower dead centers of the piston stroke and the compression ratio range for each stroke are limited, and the piston breaks illegal combustion, engine stop, seizure, etc. It is possible to provide a device for continuously changing the stroke volume and compression ratio. 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 Figs. 4, 5, and 11)

In the following, the present embodiment will be described mainly with reference to the minimum stroke volume, the maximum compression ratio and the maximum stroke volume, the stroke volume at the minimum compression ratio, and the crankcase block portion in which the compression ratio continuously variable device is accommodated. The illustration of the cam chain related to the drive, the oil pump, and the auxiliary machinery are omitted in the drawing and description.
The stroke volume and compression ratio continuously variable device described in the present embodiment is a 180 ° crank four cylinder.
FIG. 1 shows the maximum compression ratio and minimum stroke volume (minimum piston stroke) at the top dead center, and FIG. 2 shows the minimum compression at top dead center in the continuous stroke volume and compression ratio variable device according to this embodiment. The ratio and maximum stroke volume (maximum piston stroke) are shown, and the two-dot chain line shows the bottom dead center.
FIG. 3 shows a cross section through the connecting portion axis of the connecting rod divided into three parts from the piston to the crank journal axis. 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 in alignment with the AA line of FIG. 3) which shows the top dead center at the time of the maximum compression ratio (compression ratio 18) and minimum stroke volume. It is sectional drawing (sectional drawing which follows the AA line of FIG. 3) which shows the minimum compression ratio (compression ratio 10) and the top dead center at the time of the maximum stroke volume. It is sectional drawing which follows the BB line of FIG. It is sectional drawing which follows the CC line of FIG. It is sectional drawing which follows the DD line | wire of FIG. It is sectional drawing which follows the EE line | wire of FIG. It is sectional drawing which follows the FF line of FIG. It is sectional drawing which follows the GG line of FIG. It is sectional drawing which follows the HH line of FIG. It is sectional drawing which follows the JJ line of FIG. It is sectional drawing which follows the KK line | wire of FIG. FIG. 5 is a diagram showing arcuate trajectories of the shaft cores S and B according to arrangement examples of the shaft cores C and V with respect to the shaft cores O and Y in the present invention. Indicates the locus of the compression ratio of 10. It is an example of piston stroke figure of patent documents 3 compression ratio 12. The crank phase indicates the clockwise angle from a line parallel to the cylinder core axis, and the piston top surface position indicates the height from the crank journal axis. The thin line shows the minimum stroke, the thick line shows the maximum stroke, and the dotted line shows the conventional single connecting rod crank. The vertical thin line indicates the top dead center phase at the minimum stroke, and the vertical thick line indicates the top dead center phase at the maximum stroke. The horizontal line of the alternate long and short dashed line indicates the average piston top surface height at the top and bottom dead points. The average piston top surface curve is shown. This embodiment is a piston stroke diagram example of the compression ratio 12 at the time of the solid line in the left diagram of FIG. The crank phase indicates the clockwise angle from the Y 'line, and the piston top surface position indicates the height from the X axis. The thin line shows the minimum stroke, the thick line shows the maximum stroke, and the dotted line shows the conventional single connecting rod crank. The vertical line represents the top dead center phase, the one-dot chain line horizontal line represents the average piston top surface height at the top and bottom dead points, and the small curve near the horizontal line represents the average piston top surface curve at 180 ° crank. FIG. 13 is an example of a piston stroke diagram when the dotted line of FIG. FIG. 13 is a piston stroke diagram example at the time of the solid line in the right diagram of FIG. 16 and 17 indicate a sine curve. FIG. 13 is a piston stroke diagram example at the time of the dotted line on the right side of FIG.

α 最小弦長（最小ストローク）時のＢｔ、Ｖｓを結んだ線とＹ軸の交点の内角DESCRIPTION OF SYMBOLS 1 Cylinder 1-1 Cylinder gasket 2 Upper crankcase 3 Lower crankcase 4 Cam chain cover 4-1 Cam chain cover gasket 10 Crank mechanism 11 Piston 11-1 Piston pin 11-2 Circlip 12 Piston rod 12-1 Piston rod large End shaft 12-2 Plug 13 Connecting rod 13-1 Connecting rod cap 13-2 Connecting rod metal bearing 13-3 Bolt 14 Variable control arm 15 Crank shaft 15a Crank pin 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 17 Connection link 17-1 Connecting rod small end shaft 17-2 Plug 18 Connecting rod arm 18a Bridge 18-1 Connecting rod arm swinging shaft 18-2 Connecting rod arm swinging shaft 18-3 Circlip 18-4 Plug 20 Stroke volume, compression ratio variable mechanism 21U Upper driving link 21-1 Knock screw 21-2 Nut 21- 3 bolts 21L lower driving link 22U upper driven link 22L lower driven link 23U upper variable shaft 23-1-grooved shaft 23U-2 plug 23L lower variable shaft 23L-2 plug 24U upper link pin 24L lower link pin 24-1 Lug 30 Stroke volume, compression ratio control mechanism 31U Upper control motor 31Ua Drive pinion gear 31-1 Bolt 31-2 O-ring 31L Lower control motor 31La Drive pinion gear 32U Upper control motor holder 32-1 Bolt 32-2 Knock pin 32L Lower control Motor holder 33U Upper female feed screw 33Ua Driven gear part 33Ui Upper feed screw idle gear 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 37-1 Knock screw 37-2 Nut 37-3 Bolt 37L Lower variable arm 41U Limit detection upper drive link 41- 1 Knock Screw 41-2 Nut 41-3 Bolt 41L Limit Detection Lower Drive Link 42U Limit Detection Upper Drive Link 42L Limit Detection Lower Drive Link 43 Link Pin 44 Limiter Bearing 44-1 Limiter Bearing Shaft 44-2 Circlip 45 Limiter Plate 45 -1 Knock pin 45-2 Bolt 46U Upper variable shaft phase detection sensor 46-1 Bolt 46-2 O-ring 46L Lower variable shaft phase detection sensor O Crank journal axis Y Cylinder axis X Passing through axis O and perpendicular to Y axis Axis Y 'Line connecting the core O and the top dead center connecting rod small end shaft core r Crank pin radius B Piston rod large end shaft core S Connecting rod small end shaft core P Connecting rod large end shaft core (Crankpin shaft core)
L Distance between connecting link axis B and S axis C Connecting rod arm swing axis V Variable control arm swing axis t Top dead center b Bottom dead center

α Inner angle of intersection of line connecting Bt and Vs at minimum chord length (minimum stroke) and Y axis

The stroke volume and compression ratio variable mechanism 20 is a variable control arm swinging shaft that regulates the movement of the piston rod, and the position of the swing shaft is fixed and fixed by a five-bar linkage mechanism. The core of the lower variable shaft 23L, which is the opposite of the link 21L, is disposed and the shaft is disposed in parallel with the crank journal shaft. A tool is inserted into the head quadrangular column of the knock screw 21-1, and the lower end screw portion is variable. After temporarily assembling the shaft screw hole to an appropriate axial position, the bolt 21-3 is tightened, and then the nut 21-2 is tightened to prevent the loosening of the knock screw with a square pole, thereby preventing the loosening, and the lower driving link The phase and the axial position are determined so as to be swingable together with the lower variable shaft.
On the other hand, the upper drive link 21U is assembled in the same manner as the lower drive link to the upper variable shaft 23U, which is a pair, which is rotatably inserted into the shaft hole of the upper crankcase that is opened in parallel to the crank journal axis. It can swing with the shaft. (See Figures 1-5)

Claims (8)

The connecting rod that connects the piston and the crank is divided into three parts, the piston-side connecting rod, the crank-side connecting rod, and a link that slidably connects them in the direction perpendicular to the crank journal axis. A stroke volume and compression ratio continuous variable device that two-dimensionally variably controls the swing axis position of the swing arm that fixes the swing shaft of the moving arm and strokes the piston-side connecting rod large end in an arc. The axis of the bottom dead center at the bottom end of the crank side connecting rod is arranged on a line connecting the axis of the top dead center at the small end of the crank side connecting rod and the center axis of the crank journal when viewed from the crank journal axis direction. Stroke volume, compression ratio continuously variable device. As viewed from the direction of the crank journal axis, the pivot axis of the piston-side connecting rod large end and the crank-side connecting rod small end swinging arm with respect to the line connecting the top dead center axis at the crank side connecting rod small end and the crank journal axis Is located on the same quadrant side, and on the maximum stroke side, the arc-shaped locus of the piston-side connecting rod large end is arranged opposite to the crank-side connecting rod small-end oscillating arm swing axis with respect to the arc-shaped locus of the crank-side connecting rod. The stroke volume / compression ratio continuously variable device according to claim 1. As viewed from the direction of the crank journal axis, the pivot axis of the piston-side connecting rod large end and the crank-side connecting rod small end swinging arm with respect to the line connecting the top dead center axis at the crank side connecting rod small end and the crank journal axis Are arranged in opposite quadrants, and on the maximum stroke side, the arc-shaped trajectory of the piston-side connecting rod large end is placed on the opposite side of the crank-side connecting rod small-end swinging arm swing axis with respect to the crank-side connecting rod small-end arc-shaped trajectory. The stroke volume / compression ratio continuously variable device according to claim 1 to be arranged. As viewed from the direction of the crank journal axis, the pivot axis of the piston-side connecting rod large end and the crank-side connecting rod small end swinging arm with respect to the line connecting the top dead center axis at the crank side connecting rod small end and the crank journal axis Is located on the same quadrant side, and on the maximum stroke side, the crank-side connecting rod small end swing arm swinging shaft is located at the bottom dead center position of the piston-side connecting rod large end arc-shaped locus relative to the arc-shaped locus of the crank side connecting rod small end. The stroke volume / compression ratio continuously variable device according to claim 1, which is disposed on the core side. In the crank journal axial direction, a crank side connecting rod small end swing arm and a swing shaft are provided on both outer sides of the link and crank side connecting rod small ends with bridges, and pistons are provided on the inside of the crank journal axial direction. 4. The stroke volume / compression ratio continuously variable device according to claim 1, wherein the side connecting rod swing arm and the swing shaft are arranged so that the swing shaft position can be varied. 5. The stroke volume / compression ratio continuous variable device according to claim 1, wherein the shaft length of the swing shaft of the crank-side connecting rod small end swing arm is shorter than the outer end face width of both swing shaft holes of the swing arm. . Determine the axial position and phase of the driving link and variable arm, which change the swing axis position of the piston-side connecting rod large end swing arm in a two-dimensional manner, with a knock screw against the variable shaft, and use a nut to prevent loosening. The stroke volume / compression ratio continuously variable device according to claim 1.

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