JPS63259101A - Three dimensional volume changing rotary mechanism - Google Patents

Abstract

PURPOSE:To obtain a rotary mechanism of high working efficiency taking advantage of three dimensional volume change by providing both a rotor having a roughly conical surface whose bottom face is partially spherical and a member having a curvature composed of a plane produced by the apex locus of the rotor resulting from its precession. CONSTITUTION:A rotary mechanism is composed of a rotor 2 with a part of its spherical face forming a bottom face and with a roughly conical body whose spherical center being an apex, a casing plate 3 partitioning a working room together with the side face of the rotor 2, and a casing 1 of a hollow spherical shape enclosing the rotor and the casing plate. On the top of the casing 1, a bore 22 to allow a bearing shaft 33 rotatably bearing a drive shaft 4 to go therethrough is provided, and the bearing shaft 33 is fixed into the bore 22. Additionally, an appropriate gear ratio between the external gear 14 of the bearing shaft 33 and the internal gear 15 of the rotor 2 is set so as to permit precession at a given ratio of rotational speed. The casing plate 3 is formed on a curvature composed of a plane that an a pex locus will produce from the precession of the rotor 2.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a rotary mechanism, and particularly to a rotary mechanism that changes volume in three dimensions.

(Prior Art) Various rotary mechanisms have been known in the past, and a typical example is the Pankel rotary engine.

The rotary mechanism of a Wankel-type rotary engine is such that a roughly triangular mouth whose outer shape is the internal line of the peritrochoid curve eccentrically rotates inside a cocoon-shaped rotor casing whose inner peripheral surface is a two-node peritrochoid curve. This method utilizes the change in volume of the working chamber that occurs at that time. This working chamber is formed by giving a thickness to a planar gap (area) formed by the housing and the rotor. Almost all rotary mechanisms in practical use are based on similar principles.

(Problem to be solved by the invention) In other words, the volume change of the conventional rotary mechanism is based on a change in a two-dimensional plane, and its side surfaces do not participate in the volume change, but only serve to secure the space volume and form a seal for the space. Therefore, in that sense, the volume change is essentially two-dimensional. Therefore, there are inherent limitations in engines that utilize two-dimensional volume changes.

The present invention generally takes advantage of various excellent characteristics of rotary mechanisms while freeing the mechanism from two-dimensional constraints.
Furthermore, it is an object of the present invention to provide a novel rotary mechanism that enables three-dimensional volume changes.

(Means for Solving Problems According to the Invention) The present invention provides a rotary mechanism that changes volume three-dimensionally, particularly a spherical offset rotary mechanism.

That is, the present invention provides a rotor having a substantially conical surface having a partially spherical bottom surface and an apex extending substantially radially, and a member having a curved surface formed by a surface formed by the locus of the apex due to the two-differential motion of the rotor. , a three-dimensional volume changing rotary mechanism characterized in that a space defined within a spherical space (inside the casing) and whose volume changes due to relative two-differential motion between the curved surface member and the rotor is used as an operating space. .

The principle of the present invention will be explained in detail below.

The rotor of the present invention typically consists of a substantially conical body having a base that is a part of a spherical surface and an apex that is the center of the sphere.

(Although the conical surface is generally positive (convex), it may also be negative (concave).) Typically, this rotor constantly moves two differentials within the spherical space of the casing like a top. At this time, one point of the rotor cone moves in a wave-like manner within the spherical surface, but by forming an apex that extends radially in the cone, the curved surface formed by the locus of the apex corresponds to the rotor cone. It can be a curved surface of the casing member. An operating space is formed between this curved surface of the casing member and the surface of the rotor cone (particularly the cone surface between adjacent apexes), and the two-dimensional movement of the rotor (rotating around the rotor's own axis while rotating around the rotor's own axis) revolves around a principal axis that is oblique to the axis of rotation), thereby producing an effective three-dimensional volume change.

The rotation of this rotor is transmitted to the rotation of the main shaft (transmission shaft) via a two-differential transmission mechanism. The main shaft forms the output shaft or the input shaft.The main shaft and the rotor's rotation axis form a constant angle of 0. When the rotor rotates, the rotor's rotation axis itself revolves around the main shaft at J(. At this time, the +A mark at one point A on the apex of the rotor is generated on one spherical surface.When there is a predetermined relationship between the revolution speed of the rotor's rotation axis and the rotation speed of the rotor, the one point on the apex The locus of A forms a spherical trochoid curve defined by a spherical polar coordinate system.

When discussing 'HL motion on a spherical surface, it is convenient to use a spherical polar coordinate system, and a spherical trochoidal curve in a spherical polar coordinate system corresponds to a trochoidal curve in a two-dimensional coordinate system on a plane. Furthermore, motion on a spherical surface can be expressed more simply by using vectors.

(Embodiment Modes and Effects) Hereinafter, the present invention will be further explained in detail based on preferred embodiments.

Practically speaking, it is preferable to arrange a rotor support mechanism made of a small sphere at the top of the conical part of the rotor (the center of the sphere), in which case the shape of the top of the conical part of the rotor is cut by this small sphere (or spherical nucleus). It becomes a three-dimensional shape.

As mentioned above, the relative two-difference motion between the members forming the locus curved surface of the rotor and rotor apex is typically 1IIl'! This is true as a two-difference motion of a conical rotor, but the reverse is also true,
In some cases, as will be described later, this can also be achieved by a combination of simple rotational movements of both the rotor and the casing around the oblique axes.

For convenience of explanation and configuration, the following description will be based on the case where the rotor moves in two differential motions and the members forming the locus curved surface of the rotor apex are fixed as part of the casing.

In Fig. 1, if the Z axis is the transmission axis and the Z' axis is the rotation axis, point P is the intersection of the rotation axis of the rotor with the spherical surface, and the point P°
Let ω be the angular velocity at which the rotation axis rotates around the transmission axis, which is the point of intersection with the opposite side of the spherical surface (the point of symmetry with respect to the center 0), and let ω′ be the angular velocity of the rotation of the rotor relative to the movement of the rotation axis itself. Then, the ratio of ω to ω° is 1 : [1−
(1/n)] (n is a natural number of 2 or more), one curve is closed, and the locus of A draws a spherical peritrochoid curve.

At this time, the locus drawn by the points on the rotor's apex is a spherical peritrochoid curve.

Although it is possible to draw a spherical trochoidal curve on a spherical surface, it is difficult to illustrate it on a plane. Equi-distance projection (Equi-distance projection) used for maps
One method is to use ant projection. The pole Q is the point where the principal axis Z lies on the spherical surface. In FIG. 2, concentric circles correspond to lines of latitude and are spaced equally apart up to 180° from the center.

180° means the opposite pole Q°. 90° corresponds to the equator. The straight lines in the radial direction correspond to meridians, which divide one circumference counterclockwise at equal angles from 0° to 360°.

Taken in this way, a straight line passing through the center Q in FIG. 2 represents a great circle on the spherical surface, and a line segment (great circular arc) of this straight line corresponds to the central angle at which it is viewed.

Theoretically, it is easier to consider the unit method using the arc degree method.

The closed curve T in FIG. 2 is obtained by drawing a spherical peritrochoid curve with n=3 on a spherical surface, reading the latitude and longitude from the curve drawn on the spherical surface, and plotting them by equidistant polar projection. A solid circle C near the center pole Q is the locus of the intersection P between the axis of rotation and the surface of the sphere. In FIG. 1, ZPoA, which includes the distance from the above point P to the apex A of the rotor, is defined as the generation angle R (0 is the center of the sphere). Figure 2 shows the creation angle R=9
0°, and the angle between the rotation axis and the principal axis is 0=18°, but generally R>20, and 0 can be up to 60″.

Now, the rotor whose inclination angle between the rotation axis and the main axis, that is, the eccentricity angle (or swing angle) is 0 and the generation angle R is 1: [1
-(1/n) ] When the tip A of the apex of the rotor performs a two-difference motion with an angular velocity ratio of 1/n, the tip A of the rotor forms a spherical peritrochoid curve. The mathematical expression of this curve on the spherical surface is performed using the spherical polar coordinates and the formula for the spherical triangle (see Figure 3).Since the central circle C is the locus of the point P on the spherical surface of the rotation axis, the eccentricity angle is 0. is a circle with a radius of The coordinates of point P after L seconds are (0, ωt). The coordinates (x, Φ) of point A in the case of n = 3 are determined by using the parameter φ (1) (angle between QP and QA), (1) Φ = ω is 10φ (2) cos x = cos O fist
cos R-sin θ conflict s:nR・co
s%ωt (3) sin x /sin 3'sωt = sin
R/s: nφ where angle 0. ωt, -% ωt is Euler's angle (θ, R>0. The direction of ω, ω" follows Euler, that is, the counterclockwise direction is assumed to be 10, and the same is true for φ.

``Mechanics'' (see Baer and Johnston), this equation can be used to solve problems related to rotary engines, such as the angular velocity, angular acceleration, and swing angle of the apex, as well as the volume of the housing and the volume of the working space (stroke volume). . The general formula is satisfied by replacing % of the spin angle %ωt by (n-1)/n.

The spherical peritrochoid curve defined by Figures 2 and 3 of the spherical coordinate system and equations (1) to (3) has a certain correspondence with the known veritrochoid curve on a two-dimensional plane. I understand. That is, the generation radius R1 in a two-dimensional trochoid curve, the eccentric distance r, and the generation angle R2 in a spherical trochoid curve, respectively, the eccentric angle (crossing angle) θ with the principal axis of the base circle C on the spherical surface.
appears as. That is, a straight line segment in a two-dimensional trochoid curve corresponds to an angular component of a great circular arc in a spherical coordinate system.

In the present invention, the locus of the outer edge A of the apex of the rotor forms a spherical peritrochoid curve, but since the locus of any point A'' on the apex (Fig. 7) also forms a similar curve, the curved surface traced by the apex The shape of is defined as a ``spherical veritrochoid cone''. That is, by connecting the spherical peritrochoid curve, which is the locus of the outer edge A of the apex, to the center of the sphere (the apex of the conical part of the rotor or the virtual apex), a single wavy curved surface whose outer edge is on the spherical surface is formed. (provided that the apex is a straight line from point A toward the center of the sphere), but this wavy curved surface is the casing curved surface (casing plate curved surface) corresponding to the two-difference motion of the rotor apex. Typically, the apexes (or their extensions) intersect each other at the top of the aperture.

Optimally, the outer edge of the curved surface of the substantially conical portion of the rotor consists of the inner envelope of the spherical peritrochoid curves. The locus of the radius (during precessional movement of the rotor) connecting one point on this inner envelope line and the apex of the conical part (the center of the sphere) is the trajectory between this radius line segment and the inner circumferential surface of the curved surface of the casing plate. The relative spacing therefore varies periodically according to the two-difference motion of the rotor. As a result, three-dimensional volume changes occur periodically, which can be used as an operating space.

Figure 4 shows the equidistant projection of the peritrochoid curve defined in the spherical polar coordinate system (see Figure 2) ↓ In the projection onto the two-dimensional plane, the rotor is shown and its rotation is shown (I) -(IV). According to the equidistant projection method, an expression similar to that of a two-dimensional volume-changing rotary engine is expressed using polar coordinates.In addition, in the equidistant projection method, the outline of the rotor rotates while deforming as it rotates.

It is best to make the curved surface of the substantially perplexing part of the rotor that passes through the rotor as an inner road surface that includes the radius of the apex part mentioned above, but the part excluding the apex part should be a little further inward of the rotor part than the above inner road surface. A receding curved surface is also possible.

Note that retraction of the rotor sliding surface from the theoretical curved surface to allow sliding is generally required in rotary engines having sliding surfaces, and is also applied to the present invention.

The radial shape of the apex of the rotor (the cross-sectional shape that includes the rotor's rotational axis) typically forms a straight line, but the point is that the rotor's rotational axis (typically the center of the sphere) and the outer edge of the apex (on the spherical surface) (the outer edge that appears in). This radius (the shape of the apex) can also be a curve, although the configuration is a little more complicated. However, in that case, the casing plate also has a curved surface configuration that corresponds to the interlocking of the shape of the apex.

The three-dimensional volume change (or spherical two-difference) rotary mechanism of the present invention utilizes the volume change of the working space (chamber) accompanying the relative two-difference movement between the rotor and the corresponding member, and can be used as an expansion or pressure 1i1 engine. It is useful, for example, as a power engine (e.g. internal combustion engine, steam engine, pneumatic or hydraulic motor) or for powering and working engines (e.g. pressurization or suction pumps, compressors, etc.), fluid- It can also be used as an energy exchange device between fluids. In this case, fluid inlets and outlets are arranged at predetermined positions. The design of the entrance and exit can be easily done visually using the equidistant projection method (
(See Figure 4 (I) Example of pump, (TI) Example of four-stroke engine).

Examples of the present invention will be described below.

(Embodiment) An embodiment of the spherical offset rotary mechanism of the present invention as a pump will be described based on the drawings.

In Fig. 5, the angle between the transmission shaft 2 and the rotation axis Z° is 0,
Let R be the creation angle.

Now, for convenience of explanation, if we use the unit method, there is a unit. Now, the rotor rotates around the rotation axis Z° at an angular velocity ω' with a ratio of ω; ω' = 1: [1-(1/n)], and
When the rotation axis 2' revolves around the transmission axis Z at an angular velocity ω, the tip A of the apex of the rotor forms a spherical veritrochoid curve ST with an eccentric angle of 0 and a generation angle R (Fig. 6, n
-3).

The shape of an object that can rotate within the width of the spherical velitrochoid curve ST is limited within the peritrochoid internal envelope 1aIE. Gears in transmission mechanism, i.e. outer f&& wheel and inner 1
If the south number ratio of 4 + gear is 2 = 3, the peritrochoid will be bilobed (cocoon-shaped), and the rotor 2 will be 3 m (spherical triangular).
In FIG. 6, the rotor is the inner envelope IE of the veritrochoid curve defined by the eccentric angle θ and the generation angle R. The approximately triangular rotor 2 in Figure 6 is a converted diagram (projection diagram of the bottom) of a two-difference rotor.If the size is reduced in Figure 6, θ and R are angles, so the size of one sphere is It remains unchanged regardless of

The shape of ADB also remains unchanged regardless of the size of the sphere.

The shape of the rotor side ml is formed by the inner envelope of a group of curves created by the trochoidal curve (casing plate) on the (virtual) spherical surface of the rotor as the rotor rotates. In other words, the side of the first mouth is O (forming a spherical cone).

The other two sides can be made in the same way.

As mentioned above, along with the two-difference motion of the rotor, the outer edge A of the rotor draws a spherical veritrochoid curve ST (spherical conical surface), and the curve 1 (ST) shown in FIG. This is a veritrochoid curve displayed in a projection method.

The casing plate 3 (see FIG. 7), which defines the working chamber together with the side surface of the rotor, forms a surface defined by the locus of the line segment OA (ie, the rotor apex 25) in FIG. 5. Therefore, the rotor apex 25 (line segment OA) rotates while contacting this casing plate surface 32. That is, the casing plate surface 32 facing the rotor side surface is formed of an internal envelope curved surface.
In this example, the shape of is a spherical peritrochoid curve 31
It is a curved surface (spherical veritrochoid conical surface) that connects the center 0 with It is a curved surface formed by a set of spherical peritrochoid curves.

According to the principles described above, the shapes of the substantially conical surface of the rotor and the corresponding casing plate surface are determined.

The maximum value of the inclination of the casing plate surface, that is, the angle from the driving axis, is 0+R, and the minimum value is R-0 (Figure 6).
.

Preferably, an airtight seal 23 is formed at the apex (line segment AO) of the rotor in order to ensure the sealing of the apex sliding part (especially despite temperature changes) and to prevent sliding wear. It is also preferable that this seal is movable up and down (can retreat into the rotor) and that the seal spring always presses the casing plate surface.In that case, the rotor apex always rotates while firmly contacting the casing plate surface. and maintains good airtightness.

A seal between the spherical surface of the rotor and the spherical inner surface of the casing is likewise possible. An example of a seal is shown in FIG. 24. However, depending on the properties of the fluid, the materials of the rotor and casing, and the purpose of use, there may be no need for a special seal member.

In Figure pJXJ9, the casing 1 has a hollow spherical shape,
A spherical rotor 2 and a casing plate 3 are housed therein. The casing plate 3 is fixed to the casing 1 in a predetermined position at a predetermined angle. There is a transmission shaft 4 on the top of the casing.
A hole 22 is provided for passing a support shaft 33 rotatably supported therethrough, and the support shaft 33 is fixed in this hole 22.

By setting the ratio of the number of teeth between the external gear 14 of the support shaft 33 and the internal gear 15 of the rotor to an appropriate value, it is possible to obtain two-differential motion with a rotational speed of a predetermined ratio. A spherical veritrochoid with n=3 is used, and a bevel gear is used in which the ratio of the number of teeth between the external gear 14 and the inner 1!41 wheel 15 is 2:3.

As for the support at the center of the spherical single-difference rotor 2 that rotates while being inscribed within a spherical casing and around the support shaft space 3, as shown in FIG. 8, a small sphere (spherical nucleus) is used.
can be used. The small sphere 9 aligns the top of the imaginary E of the rotor chain with the center (this center is the intersection of the rotor rotation axis and the transmission axis). As a result, the spherical 1 difference rotor 2
always precesses around the support shaft 33 with an inclination of 0. The supporting sphere 9 can be fixed to the casing plate 3, or conversely to the rotor 2, or can be rotatably interposed between the two (like a pole bearing).

The transmission mechanism between the rotation of the rotor and the transmission shaft 4 is a tilting journal 35, that is, two differential movement rotations are converted into normal shaft rotation (fixed position one
This is done by a mechanism that converts and transmits axial rotation in a plane.
This is because the transmission shaft 4 and the rotor rotation axis Z' intersect. - As an example, in FIG. 7, a tilted (eccentric) crank or an eccentric ring (bearing) is arranged between the rotor's rotation axis and the transmission shaft 4, which has an angle of inclination of 0 with respect to the rotor, for transmitting slow rotational motion. As a specific example, as shown in FIG. 12, an eccentric ring 3 is attached to the end of the transmission shaft 4 that projects into the rotor 2.
A mechanism can be used in which a rod 35c (extending from the rotor center O along the rotor axis) provided with a pole bearing centered at the eccentric position 35b is connected to the rotor center (Fig. 12). reference). In the case of outputting upward in this way, the transmission shaft 4 passes through the inside of the support shaft 33 and is rotatably supported concentrically, and the rotor 2 is supported within the casing via the spherical core 9 so as to be able to make two differential movements. Ru.

Another modification of the rotor transmission mechanism is one in which a spherical spline (9a formed parallel to the rotor axis) is provided on the surface of the spherical nucleus 9 shown in FIG. 8, and the transmission shaft 4 is extended and connected to the spherical nucleus 9. In this case, the spherical core 9 is arranged rotatably relative to the housing plate 3.

Furthermore, a tilting journal (or a tilting coupling) is formed in which the spherical nucleus 9 is integrally formed with the rotor, and engages inside the spherical nucleus 9 in the rotational direction and is engaged so as to be able to swing by an inclination angle of 0.
It is also possible to provide This tilting journal can output upwardly, or alternatively, as shown in FIG. 11, downwardly. The rotor transmission mechanism shown in FIG. 11 is an example in which a Barfield type shaft joint is used inside the bearing sphere 9. The rotor transmission mechanism shown in FIG. This type of joint transmits rotation even if the angle at which the two axes intersect freely changes, and can perform constant velocity transmission.
Further, the driving shaft 36, which has no fluctuation in rotational force, is aligned with the rotation axis of the rotor 2 and fixed to the rotor 2. Rotation of the rotor due to the two-difference movement of the rotor is controlled by the driven shaft 3 through the pawl 37.
8 will be communicated.

FIG. 13 shows another example of a tilting journal.

In the spherical hollow part of the rotor, an eccentric disk 35a, which has an eccentric (and tilted) output shaft Z around a tilt axis Z' and has a spherical outer periphery and is supported in sliding contact with the rotor hollow part, rotates with respect to the rotor 2. It is arranged so that it can be tilted and tilted. A similar function can also be achieved by using a tiltable roller bearing unit.

An inlet 20, 20° and an outlet 21, 21' are provided on the upper spherical surface of the inner casing 3 of the casing corresponding to the positions v, v' and 2, vx' in FIG. The arrangement and shape of these boats can be visually designed as shown in FIG.

Moreover, it is also possible to provide a plurality of cooling holes 34 in the casing 1.

The shape of the rotor side surface (spherical conical surface) and the shape of the casing plate surface are determined by the values of the angle θ between the transmission shaft and the rotor rotation axis and the creation angle R, and it is also possible to combine θ and R in various ways. In other words, the size of θ is related to the internal volume of the working chamber and the torque, and even when the gear is disposed inside the rotor, for example, when the value of R is 90°, the value of θ is 18
Although it is possible to take up to θ, the upper limit is much larger when looking only at θ.

(Function of this embodiment) In the working chamber of a conventional rotary engine, the rotor housing forming a berytrochoid curved surface and the circular curved surface of the rotor forming its internal envelope curved surface form a width perpendicular to the plane containing the beritrochoid. to form a working chamber.

In this embodiment, the casing plate 3 forming a spherical peritrochoid curved surface is arranged rotationally symmetrically with respect to the transmission shaft 4. Also, the trajectory of the rotor apex 25 is in the same plane as the casing plate 3, so the relationship between the rotor conical surface 24 and the casing plate 3 is similar to that of the rotor and rotor housing of a conventional secondary rotary engine. Contrasted. Therefore, the volume of the working chamber in this embodiment varies from (I) to (IV
).

When a rotational force is now applied to the transmission shaft 4, the rotor 2 is caused to revolve by an internal gear 15 formed on the rotor through a tilting journal and an outer 6kl wheel 14 fixed to the casing. The rotor 2 rotates on its own axis while maintaining its center position via the support small sphere 9, and rotates around the support shaft 33 while maintaining the inclination of the rotation axis.

Rotation of the rotor causes a volume change from CI) to (IT) in Figure 4, fluid is sucked in from the inlet 20.20°, and the fluid is sucked in from the outlet 2
It is discharged from 1.21'. (See Figure 4 for entrances and exits (
(See I)) The pressure w1 (or discharge) stroke of the working chamber is as shown in steps ~■ in Figure 4 for one working chamber, and the same steps hold for each working chamber, and from ■~I. The above stroke can be used as a compression or expansion engine (such as a pump), where an expansion stroke can be achieved if the engine is traced in the opposite direction.

When used as an internal combustion engine, one cycle consists of a series of compression, one expansion, exhaust (second compression process), and intake (second expansion process).

Both the exhaust and intake steps and the compression and expansion steps are repeated by opening and closing the corresponding boats (which function as valves).

As for the arrangement and structure of the boat and ignition system, it is also possible to apply the well-known ones for the Wankel type rotary engine, and detailed explanations are omitted here.

The basic system consisting of a pair of rotor conical surfaces and casing curved surfaces (casing plate surfaces) corresponding to the I-2x locus has been described above, but the present invention is not limited to A modification example will be described below.

First, although the shape of the casing plate is different from the veritrochoid curve described above, it is also possible to rotate the casing plate with an inclination angle of 0 and correspondingly rotate the rotor in the first embodiment at a fixed position (fixed axial position). be. In this case too, a relative precession movement occurs between the rotor and the corresponding housing surface.

Next, conical surfaces can be formed on both sides of the spherical two-difference rotor, and two casing curved surfaces corresponding to the apex locus can also be formed inside the spherical space.

An example of this is shown in Figure 10, with apex 16°17 and 1
Casing plate with corresponding casing curved surface 18.
Consists of 19. In this case, the relative two-dimensional movement between the rotor and the casing curved surface is generally performed with the casing plates 18, 19 fixed. In this case, conversely, it is also possible to rotate the spherical rotor 2' at a fixed position and rotate the casing plates ia, ic+ with an inclination angle of 0. Furthermore, in FIG. 10, the angular positions of the apex of the second part and the lower part can be shifted to avoid coincidence of the top dead center and to achieve smooth operation. Also, the apex does not necessarily have to be formed in a straight line with the center of the rotor sphere as its apex; the inner edge of the apex extends toward the rotor's rotation axis (if the rotor is not rotating, the axis of the rotor, especially the center of the sphere). Being there is enough.

Furthermore, as a modified example, the rotor shown in FIGS. 7 and 8 is
It is possible to combine the two by sandwiching the casing plates 3 above and below and using both sides of the plates. This not only saves space, but also connects the upper and lower rotors (
It is also possible to connect via a small sphere, etc.). However, in this case, it is not necessary to have a symmetrical shape, but to make it symmetrical, the angle of R needs to be smaller than 90°. A pair of upper and lower rotors is extremely preferable in terms of rotational balance of the rotary mechanism.

As another modification, it is also possible to combine two rotors of two parts with their conical side faces facing each other. That is, the casing plate in the first embodiment can also be formed as a rotor (referred to as a plate rotor), and it can be formed by combining it at an angle with the first rotor so that both rotors rotate relative to each other. Instead of rotating the Z" axis, the plate rotor is rotated to accomplish the same purpose.

As a means for transmitting the rotation of the rotor to the outside (main shaft), there is the rotor transmission mechanism described above, and such functional elements are collectively referred to as a tilting journal. In other words, it refers to a mechanism in which a shaft tilted with respect to the main shaft is rotationally connected to the main shaft.

Furthermore, the seal between the inner circumferential surface of the casing, which forms one spherical surface, and the rotor can be easily achieved by using, for example, a piston ring that is curved in a wave-like manner along the spherical surface. (See Fig. 24) In the rotary mechanism of the present invention, the outlet 21' is used as an exhaust boat and the inlet 20 is used as an intake boat.
If you place the spark plug at an appropriate position near the entrance 20,
Can be used as a rotary engine. This intake and exhaust boat is automatically opened and closed in response to the rotation of the rotor. Additionally, a synchronous on-off valve may be provided as an auxiliary device. In FIG. 4, a four-stroke engine is constructed by providing a pair of entrances and exits only in the upper or lower half of the equidistant polar projection. Figure 4 (II) shows the entrance 20. In the case where the outlet 21' is provided only in the lower half, the ignition plug is indicated by the symbol SP.

Figure 515 is a graph showing the relationship between the ratio (%) of the stroke volume to the total casing volume and the inclination angle O for generation angles of 70 to 90 degrees in the case of n=3.

16 to 20 show various embodiments of the (1 difference) transmission mechanism and the relative 2 difference interlocking, Z indicates the fixed position axis and Z' indicates the 1 difference motion axis, respectively. The term "rotor" refers to a member having an apex.

FIG. 16 shows an example in which the internal gear 15 is provided on the rotor 2 and the external gear 14 is provided on the stationary casing 1. A disc-shaped tilting journal 35 is arranged between the rotating shaft 4 and the rotor 2 in a fixed position.

The shaft 4 is supported by the casing l via a bearing 39.

FIG. 17 shows a relationship of relative two-difference motion opposite to that of FIG. 16. A circular gear 15 is provided at 2° of the rotor, and an outward gear 1
4 is provided on a casing l' which is integrally formed with a casing plate 3' and is capable of revolution. The small sphere 9° is formed integrally with the rotor 2′. The arm 35a of the tilting journal 35' engages with the center of the external gear 14, and the 0 rotation torque is supported via a bearing so as to be rotatable about the fixed rotation axis Z by a stationary object (not shown).
It can be transmitted from ゛ through the small sphere 9''.

FIG. 18 shows an example in which an internal gear 15 is provided in the casing 1, and an external I
An Am wheel 14 is provided on the rotor 2. An arm 35a of a tilting journal 35' is provided at the tip of the fixed position rotating shaft 4, and the arm 35a is located at the center (Z') of the external gear gear 14.
engage with.

In FIG. 18 it is clear that the relative rotation between rotor 2 and casing 1 can be reversed. That is, the Z° axis rotates at a fixed position, and the Z axis can be moved by two differentials. (In that case, the 2° shaft is supported on a fixed object (not shown) so as to rotate in a fixed position, and the casing l is held so as to be able to revolve.) Fig. 19 shows that the external gear 14 is fixed (or the rotating shaft is in a fixed position). It is provided in the rotor 2', and the internal gear 15 is provided in the casing 1'. The casing l' rotates around the stationary axis Z by two degrees with its axis 2 degrees, and a zero rotation torque can be transmitted via the shaft 4. A seal can be provided between the inner end 3a of the casing plate 3 and the small sphere 9''.

Fig. 20 shows a rotor 2 in which a casing plate 3'' is integrally formed with a small sphere 9'', an internal gear 15 is provided on the small sphere 9'', and an external gear 14 that meshes with the internal gear 15 is integrated with a casing 1''. The spherical casing 1'' comes into sliding contact with the outer edge 3a' of the casing plate 3''. A tilting journal 35° is provided at the tip of the shaft 4° which is supported via a bearing 39 on a stationary object.

As far as the relationship between the rotor and the casing plate 3' is concerned, this example has the same relative two-differential retardation relationship as the example of FIG. 17. A seal can be provided between the outer edge 3°a of the casing plate 3' and the inner surface of the spherical casing 1°'.

As mentioned above, n can be arbitrarily selected to be 2, 3.4, or even larger. In the example described above, n=3. The case where n=2 or 4 will be described below.

FIG. 21 is an equidistant polar projection diagram when n=2. To
shows the integral spherical peritrochoid curve for the case of 0=18°, R=90′, and 42 shows the corresponding rotor,
FIG. 22 is a perspective view of the casing plate 43. In this example, an inclination angle of up to 20' is possible, and the ratio of stroke volume to casing internal volume reaches as much as 45%. Regarding the relationship of relative two-dimensional motion between two members, the case where n=3 can be similarly applied. When the radius is 90°, the rotor visually shows a conical shape (FIG. 23). FIG. 24 shows an example with sealing means, including an apex seal 23 and a spherical (side) seal 46. Alternatively, if necessary, a ring seal 47 extending around the internal gear 15 is provided. The seals can be arranged in various ways, such as a combination of a ring seal 47 and a radial spherical seal 45 extending radially outward on the sphere to the outer end of the hairpex.

Figures 25 and 26 show the case where n=4.
The case is shown in which the casing plate 43'' forms a three-lobed (or three-node) spherical peritrochoid and θ is set large.
Indicates 2°.

The relative two-difference motion relationship between the rotor and the casing (or the casing plate) can be similarly applied to the case where n=3.

A seal ring 47'' extending in a wavy manner is attached to the rotor 42'.
can be fit into a groove (not shown) on the spherical surface of the tube in a biased condition to expand radially outwardly. Furthermore, a radially extending seal 45' is disposed from the seal ring 47° to the outer end of the apex. Figure 27 shows a three-lobed spherical peritrochoid T.
” (R=90', 0=18°) and the corresponding rotor 4
Although not shown, it is also possible to set n to 5 or more, in which 2' is shown by the equidistant projection method.

In the descriptions mentioned above, the symbol “2” “2”° etc. “rotor”
The term piston, which is also referred to as a piston, does not necessarily mean a rotating member, but is based on the existence of a relative differential movement between the rotor 2 and the curved surface 3 (typically a casing plate).

1; As is clear from the above description, the present invention also provides a method for designing a spherical rotary mechanism, which is characterized in that a spherical peritrochoid is theoretically created by calculation based on a formula that defines a spherical peritrochoid. do. Three-dimensional (or spherical) one-difference motion can be visually expressed in a two-dimensional planar graph using the equidistant projection method to visually understand the locus of the precessional detour of an object, line, or point.

When compared to the Wankel engine, the sliding stroke distance or speed is maximized with the apex seal, but is much reduced in the present invention. In addition, the connection between the rotor and the casing spherical surface is further facilitated by using a spherical seal in the form of a small piston ring with advanced sealing properties and wear resistance.

The provision of small spheres provides the following advantages: That is, this stabilizes the central support of the rotor. However, since the stroke volume is proportional to the cube of the radius, it is not affected greatly. It also allows for a connection between the first and second rotors arranged oppositely on both sides of the casing plate. In this case, the spherules are arranged slidably relative to the casing plate. This embodiment can omit the planetary gear train of the second rotor, which is required when not coupled. Significant space savings and smooth rotation are expected due to the well-balanced rotation of both rotors. At the same time, the smoothness of rotation is further improved by providing a phase difference of one differential motion in order to avoid the top dead centers of both rotors coinciding. It is also possible to combine the expansion stroke of the second rotor with the compression stroke of the second rotor in a four-stroke engine.

In this disclosure, the stroke volume Vs is Vs=Vmax-Vmin
is defined as Here, Vmax and Vwin are the maximum and minimum volumes of the working chamber, respectively. The shapes of the casing plate and rotor are determined by the inclination angle θ between the two axes and the generation angle H.

The magnitude of θ and the magnitude of H also determine the stroke volume and torque. When the gear is fixed to the rotor, when R is set to 90', θ can be up to about 18°. In other embodiments, even larger O's are possible. The inclination angle 0 mainly affects the torque, and the generation angle R affects the working space volume in the casing.

As already discussed, there is a marked contrast between this invention and the Wankel-type engine. Conceptually, the Wankel generation radius R of a two-dimensional trochoid curve is the generation angle R of a three-dimensional spherical coordinate system, and the Wankel eccentricity distance e is the inclination angle 0, that is, the line segment element of the trochoid curve divided by an arc line on the spherical surface. corresponds to the color component for the arc of spherical polar coordinates. The working chamber of a Wankel engine is created by giving a thickness to a two-dimensional area, but in a spherical engine, it is created by giving a radius to a spherical area. It can be more easily expressed using a vector based on Euler angles. Euler angle is precession angle 0, nutation angle φ
, rotation angle ψ, but here they are respectively spherical trochoid curves with an inclination angle of 0, a revolution angle of ω, and a rotation angle of −%ωL. For convenience, if we use the unit method and arc degree method, they are equal to the corresponding great arc components.

Using vectors, the creation point A of the two-difference rotor can be expressed as follows. As with the Wankel type, the radial vector E is the sum of the eccentric vector E and the generating vector H (see Figure 14), and the mathematical expression is as follows.

Bottom = E + IR The center of the sphere is taken at the origin of the (x, y, z) coordinates. In this case, E is lE(ε COSωt, ε
sinωt, cosOφ casR), and the composite vector R is R(pC(ωt/3), pS(ωt
/3), -5in θpcoslωtl.

Here p=slnR.

e=sin θ cosR.

C(%ωt) = cosOcasOt cos%ωt
+ sinωt sin% ωt S (%ωt) = casOsinωt cos%
ωt-C08 (1) t s:nl (1) tθ,
R and ωt are as described above (the directions are taken in the same manner). Note that by replacing %ωt with (n-1)/n, the general formula is obtained. These C and 3 functions I are Euler's transformation formulas. E is a point dropped from A perpendicular to the Z' axis, and is not on the spherical surface. This method solves exactly the same mechanical problems as those solved using the parameters described above.

(Effects) The present invention is generally useful as an energy conversion device between fluid and mechanical force, between fluid and fluid, etc. The working space is used as an expansion or compression chamber or a combination thereof. By adjusting the arrangement of the boat, it can also be used as an engine, especially as an internal combustion engine. Various design possibilities are possible by selecting the value of n, the inclination angle 0, the generation angle R, and the arrangement of ports. Therefore, the present invention will have a wide range of industrial applications based on the basic concept and embodiments disclosed herein.

That is, the present invention expresses an expansion/compression mechanism that effectively changes volume in three dimensions by using a spherical one-differential interlocking rotor, and is applicable to pumps, engines, blowers, compressors, etc. It is useful as a rotary energy conversion system and has extremely high practical effects. Numerous advantages can also be obtained, such as reduction in spatial space, simplification of shape, and pressure resistance.

A piston ring type seal can be applied to the spherical surface of the casing, and the length of the seal surface (line) is shorter than that of a Wankel rotary engine.

Sliding frictional resistance and wear are reduced, that is, one working space can be sealed with two apex seals and one spherical seal. In contrast, in the Wankel type, 2
One apex seal and two seals on both sides are required, and the seals on both sides are necessary over the entire working space.

The joint efficiency of the working space for a given engine space can also be high, i.e. the ratio of the maximum (effective) volume of one working chamber (i.e. stroke volume) to the total volume of the casing is R = 9.
0', θ=18°, it is about 26%, but in the case of a normal Wankel type rotary engine, the effective maximum volume of the working chamber (
How long is it? The ratio of fl) is approximately 22%. This maximum volume (
Since the ratio (ratio) is proportional to the torque, the present invention has good output efficiency in terms of space for one working chamber, and even higher output efficiency can be achieved when three working chambers are considered. Furthermore, as a result, it is possible to increase the compression ratio (or expansion ratio) by changing the values of R and o to obtain a larger stroke volume ratio (Fig. 15). In engines, there is a limit in terms of the compression ratio related to the trochoidal ratio (K), and there is a contradiction in that in order to increase the compression ratio, the ratio of the stroke volume to the total casing volume must be reduced.In the present invention, There are no such restrictions.

Since the rotor's motion is all rotationally linked, smooth rotation can naturally be expected when compared to a reciprocating engine, and even compared to Wankel-type eccentric rotor motion, the two-differential rotor is more stable.

Since the intake, compression, expansion, and exhaust strokes can be easily set, it has a wide range of applications as an internal combustion engine.

[Brief explanation of drawings]

FIG. 1 is a basic line diagram for explaining the present invention, FIG. 2 is an equidistant polar projection diagram of a spherical surface used in the present invention together with an example, and FIG. 3 is an equidistant polar projection diagram for explaining the present invention. FIG. 4 is a reference diagram for explaining the planar transformation of a spherical surface based on the Akebono projection method, and FIG. 6 is a reference diagram for explaining an embodiment of the present invention, FIGS. 7 and 8 are partial elevational views of an embodiment of the present invention, and FIG. 9 is a diagram showing an embodiment of the present invention. FIG. 10 is a partial elevation view of another embodiment of the present invention, FIG. 11 is a partial cross-sectional elevation view showing another embodiment of the transmission mechanism, and FIGS. 12 and 13 are A partial schematic diagram of an example of a rotor transmission mechanism is shown, respectively. Figure 2014 is a diagram showing vector representation of a spherical surface. FIG. 15 shows 0. 16 to 20 are graphs showing the relationship between R and stroke volume (n=3), and FIGS. 16 to 20 are cross-sectional views showing different embodiments (n=3). Figures 21 to 24 and Figures 25 to 27 show still another example (n = 2.4), and Figure 21.27 of the internal temperature is an equidistant polar projection diagram (n = 2.4).

Claims (1)

[Claims] A rotor having a substantially conical surface having a partially spherical bottom surface and an apex extending substantially radially; a member having a curved surface formed by a surface formed by a locus of the apex due to precession of the rotor; A three-dimensional volume-changing rotary mechanism characterized in that a space defined within a spherical space and whose volume changes due to relative precession between rotors is used as an operating space.