JPS5821082B2 - Rotating engines and pumps with gearless rotor guides - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to improvements in rotating mechanisms of the type operating as engines or compressors.

Of the numerous rotating engines that have been proposed, only one has currently achieved substantial commercial success.

That is, for example, U.S. Patent No. 2,988,06
5. Application filed June 13, 1961, applicant En Nis.
Motorlenberge a Ketobankergem.
Be Bar, and also Book 11 The Wankel Engine! 1, author Jean P. Norby, published by Kelton Book Company, 1971, Library of Congress card number 73-161624, known as the 11 Wankel + 1 rotating engine.

The most common form of Wankel engine consists of one or more trilobal triangular rotors, each mounted for orbital movement within a bilobal epitrochoidal section chamber within the engine casing.

The rotor is freely rotated by a bearing interposed on an eccentric portion of the main output shaft, which eccentric is mounted in such a way that the rotor can impart the necessary torque to the main shaft.

Other leaf type combinations could theoretically be used, but the one described here appears to have been commonly used.

Due to the mounting of this eccentric, the rotor undergoes a movement within the chamber that is usually described as an orbital movement, which can be considered as a combined movement of circular and oscillating movements of the rotor.

The rotation of the rotor on the bearing must be accurately phased with its movement within the chamber so as to provide a plurality of working chambers whose volumes vary in the desired manner with the relative rotation of the rotor and chamber.

In Wankel-type engines, such as those described in the Wankel specification, also referred to herein, the required phasing is currently achieved by an internally geared ring gear rigidly mounted on the rotor meshing with a pinion reaction gear rigidly mounted on the casing. You can make a difference.

In the commonly adopted leaf shape mentioned above, if the ring gear has 72 teeth, the reaction gear has 48 teeth,
There must be a 3:2 ratio between both gears.

Among the problems in Wankel engines is the problem of rotor cooling, and the solution to this problem has often been to provide heat transfer to an external radiator through regulated pressure circulation of oil through the rotor.

The cooling oil circulation device inside the rotor is based on U.S. Patent No. 3.1.
No. 02,683, filed September 3, 1963, as described and claimed in Applicants Ennis et Motorlenberge A.G. and Wancker G.M.B.A. .

In this device, oil is supplied to a chamber inside the rotor in order to perform the desired cooling effect in this chamber.

Oil is distributed around the internal surfaces of this chamber in the form of an oil film by centrifugal force, and while the oil is removed from the chamber, this oil film thickness is maintained at a constant value by the installation of a stationary disk extending into the chamber. be made to be done.

The shape of the circumference of the disc corresponds to the shape in which the oil pan, which is adapted to maintain the oil film thickness, is swept by the rotor internal chamber, and the disc has a radially extending channel with holes, which The hole intercepts the oil and directs it through the hole into the flow path and into other parts of the engine (e.g.

casing and/or cooler).

Another problem in rotating engines of the type described and discussed in the aforementioned U.S. Pat. The angle between the epitrochoidal body surface it contacts must be less than 40° or there is a risk of the seal becoming trapped between the rotor and the surface.

According to Norby's book, the preferred value is 30°.

The novel guide mechanism of the present invention is the only means to achieve the new objectives.

This objective has never been considered in the prior art and cannot be achieved by existing gear guide mechanisms or other devices.

This new purpose is realized when the triangular rotor can act as a cycloidal pendulum in a state of natural harmony requiring minimal forces in the guidance control.

The necessary relationship is that the effective stroke Se is equal to the exact amplitude of the swing trajectory of the turning radius.

The ratio Se/amplitude is given by 3/(K-2)=1, from which (K-2)=3 and therefore=5.

Here, K=2r1/r2 is defined as usual.

In the prior art, it is usual to use a gear guide mechanism, the minimum K is 6, and the ratio Se/amplitude is 3/4, which satisfies the requirements for harmonic motion mentioned above as the new objective. do not.

A smooth cam with a K of 5 meets the specifications exactly.

It is an object of the present invention to provide a new rotation mechanism of the type that includes a trilobal rotor of triangular cross section operating in a bilobal chamber of epitrochoidal cross section.

A more specific object is to provide a new rotating mechanism of the type specified above which includes a new device for holding the rotor in the chamber in a correctly phased compound motion.

Another object of the invention is to provide a new rotary engine with an internal chamber having a value of approximately 5.

Yet another object of the invention is to provide a new rotor tip seal for use in rotating engines or pumps.

According to the invention, the rotation mechanism includes a casing and a main shaft mounted by the casing for rotation about a corresponding axis, the casing forming an internal chamber being relative to the axis of the main shaft. a vertical and symmetrical internal circumferential surface of bilobed epitrochoidal cross-section; a trilobal rotor of triangular cross-section mounted indoors to rotate about an axis parallel and spaced apart from the axis of said main shaft; and an eccentric device connecting the child and the child so as to transmit rotation between them,
The rotor has three working chambers that are symmetrical about the rotor axis and whose volumes change according to relative rotation between the rotor and the chamber between the rotor outer peripheral surface and the chamber surface. and a guide device for guiding the rotor in a desired relative movement with respect to the casing; The device includes a first substantially triangular guide surface symmetrical and parallel about the rotor axis and fixed to the rotor, and a second substantially triangular guide surface symmetrical and parallel about the main shaft axis fixed to the casing. two guide surfaces, said guide surfaces being adapted to be in relative sliding engagement with each other, the second guide surfaces being cam-shaped in their desired relative movement caused by said first surface and being cam-shaped on the inner surface of the casing. A rotation mechanism is provided with the major axis and minor axis of the second guide surface parallel to the minor axis and major axis of the second guide surface, respectively.

Preferably, in a rotating engine, said internal chamber has a value of 5.

The interposed seal between each tip and the interior surface includes two axially extending contact seal members mounted in respective axially extending grooves in the tip.

The rotating engine according to the invention has the following advantages.

(1) A guide mechanism that produces a compound motion of the rotor that combines rotation and rocking requires a minimum amount of work.

(2) The ratio of the volume of the working chamber to the total volume of the internal chamber of the casing is maximum.

(3) A rotating mechanism in which the rotor operates internally in harmonic mode produces minimal wear on the cam and rotor guiding surfaces.

(4) as a result of a symmetrical control action by identical cams fixed on opposite walls of the internal chamber, the rotor moves freely compared to conventional rotors and is retained on the rotating inner surface;
Rotor wobbling is prevented.

(5) The guide device is not susceptible to excessive mechanical forces typical of gear type guide devices.

From such forces, physical damage is likely to occur at moderate rotational speeds above rated operation.

(6) The diameter of the main shaft is that of an equivalent gear-type rotating engine.

It's the same.

(7) The compression ratio increases to 13/l, which is sufficient for the function of an Otto cycle engine and is convenient for efficient internal cooling of a multi-rotor type compressor.

(8) The bearing has a low coefficient of friction since rotor wobbling is eliminated, thereby avoiding the problem of rubbing on the side walls of the internal chamber of the casing.

The sidewalls and inner circumferential surface are exposed to frictional contact only with the sides of the rotor and the apex seal.

(9) The paired apex seals cooperate to prevent gas pressure from escaping from the working chamber and from escaping from the groove in the event of failure.

If the apex seal is housed in a single groove;
There is a possibility that it will escape from the groove in the event of damage.

(10) Direct lubrication of the apex seal helps maintain gas pressure and improves lubrication of surfaces in the combustion chamber that are not supplied with lubricant contained in the intake air flow.

The rotor cooling oil is withdrawn from the end of the rotor recess through an outlet passage in the wall adjacent the end of the cam.

(12) The vibration of a rotating engine is determined by the stable swinging of the rotor.
It is minimized because it occurs in harmonic mode.

This harmonic mode is not affected by rotational speed since each turn has a closed trajectory created by two cycles of rocking.

Two cycles of rocking correspond to the number of epitrochoidal lobes.

(13) Increased mechanical efficiency by significantly reducing the drag coefficient of the machine during operation provides highly efficient rotating engines and compressors.

04) Compact power plant with low thermal energy loss
This gives the designer greater scope to exploit the thermodynamic efficiency of the equipment.

As mentioned above, the rotating mechanism described here in the figures as a particularly preferred embodiment is used as an engine or compressor, and for special uses may be equipped with certain additional equipment (such as a vaporizer, oil cooler, etc.). However, the explanation thereof will be omitted since it is not essential to the explanation and understanding of the present invention.

The characteristics and specifics of such desired additional equipment will be apparent to those skilled in the art.

The mechanism consists of a casing, generally indicated by the reference numeral 10, and a peripheral portion 12 and two end plates 14 secured thereto in any suitable manner, e.g. by through ports 17.
and 16.

The casing provides an internal chamber 18, but the inner peripheral surface 2 of the internal chamber
0 is symmetrical about the central longitudinal axis 22 and is a bilobate epitrochoidal cross section perpendicular to the axis 22.

A bearing 24 provided on the end plate supports a main shaft 26 so as to rotate around an axis that coincides with the axis 22.

The main shaft is provided with an eccentric device or eccentric section 28 integrally molded therewith or fixedly attached to the main shaft, the eccentric section having a circular cross-section perpendicular to the longitudinal axis 30, the longitudinal axis being It is spaced parallel to the center 22 by a distance re (FIG. 6).

This distance re provides an effective eccentricity to the mechanism.

A trilobal rotor, generally indicated by the reference numeral 32, is mounted for free rotation on the shaft eccentric portion 28 by a bearing member 34 so that as the main shaft rotates, the rotor moves within the chamber 18 in a so-called +1 orbit 1+ or It will be possible to carry out 11 movements of 11 planets.

The rotor 32 has an outer circumferential surface constituted by three side walls 36, each tip of which is fitted with three respective tips 38 having respective apex portions, ie tip seals, indicated generally by the reference numeral 40. It has an adductor trochoidal cross-sectional shape.

These seals have been omitted from FIGS. 2 to 6 to simplify the explanation.

The outer peripheral surface of the rotor has a general equim-square cross-sectional shape that is perpendicular to and symmetrical about its axis 30; however, the side walls 36 are not straight outward in the radial direction. It is slightly arched.

Working fluid enters through the inlet 42 of the end plate 14 into the portion of the chamber 18 not occupied by the rotor and is discharged through the outlet 43 of the member 14.

The mechanism is an ignition device 44 installed in each corresponding hole 45.
Although described as including, other forms of devices or other ignition devices (eg, when the mechanism is a diesel engine) may also be used.

Such a device is of course not necessary when the mechanism is a pump.

The structure described so far is also the basic structure of an 11 Wankel 11 rotary engine.

As the rotor moves in orbit, a plurality of working chambers are formed between walls 20 and 36 that periodically change in volume.

The operation of the device, either as an engine or as a compressor, is well known and will not be described further.

In the +1 Wankel 11 engine, however, the rotor and the main shaft are each provided with an internal toothed gear and an external toothed pinion gear that mesh with each other, and the pinion gear is fixed to the end plate around the main shaft coaxially with the main shaft. and this causes the rotor to be phased or coincident with the position of the rotor with respect to the inner circumferential surface 20 as the rotor orbits.

This gear has the center of mass of the rotor in a circular path with radius re,
and twice the average angular velocity of the rotor tip),
It has the function of providing a reaction to the inertia of the rotor and thereby taking up 11 positioning 11 loads that would otherwise be applied to the tip of the rotor.

In the mechanism according to the invention, the necessary 1" guiding connection 1' between the rotor and the casing 10 is provided by a guiding device in order to ensure that the rotor is guided in the desired relative movement with respect to the casing. , namely by two continuous free relative plain bearing guide surfaces 46 and 48 provided on the casing and the rotor, respectively.

In this particular embodiment, the first guide surface 48 of the rotor is constituted by the inner circumference of a recess 50 in one side wall of the rotor, while the second guide surface 46 of the casing
is formed by the outer peripheral surface of a core guide member 52 which is fixed to the end plate 14 and projects into the recess 50.

Surfaces 46 and 48 are symmetrical about their respective axes, and one of them must be the minimum boundary shape described by the other at the desired orbital motion of the rotor within the casing.

Additionally, one of the surfaces is shaped to match a special mathematical curve that creates a bilobed elliptical shape for that surface, and two co-acting guide surfaces provide the necessary restraint and guidance between relatively moving members. The essential condition is for the system to operate in such a way as to provide the following.

The rotor internal guide surface 48 is in the shape of an equilateral triangle contained within the shape of the rotor's outer circumferential surface.

Accordingly, the respective corresponding second elliptical guide surface 46 of the core guide member 46 of the casing abductor trochoidal surface 1
having a canine axis and a minor axis parallel to the minor and major axes of 2, respectively, and as explained in more detail below,
Functions as a cam.

Side seals (not shown) are provided which cooperate with the tip seals to seal the variable volume working chambers from each other and from the remainder of the chamber 18.

The construction of such side seals will be known to those skilled in the art.

A recess 51 similar to recess 50 is provided in the other rotor side wall for balancing purposes, but instead of or in addition to this a guiding coupling surface may also be provided.

2 and 5 show the different relative positions occupied by the rotor within the chamber 18 (one of the leaves is shown in dotted lines, so that its motion will be easily understood) and the rotor. Guide surface 4
8 and the corresponding relative positions occupied by the core guiding surfaces 46 engaged in FIG.

In this scaled representation, it is difficult to explain the exact relative relationship of the guide surfaces 46 and 48 in the visible image, since the spacing available in the figure is very small.

To facilitate explanation of the actual sequence of events occurring, surface 4
While the term 1' indexing +1 is used to indicate that three points on 8 are in contact with the surface 46, the term ``guiding 11'' is used to denote the case where there are only two such points of contact. Use.

The small circle shown on the rotor surface is an indicator of the contact point position.

Thus, in the relative positions described in Figures 2 and 5 there are three contact points and the rotor is adjusted by "indexing", while in all other positions there are two contact points. 11 and the rotor is adjusted in its dynamic movement by 11 guiding 11.

Both modes of adjustment provide rotor stability.

Since the shape of the continuous surface 46 is caused by the movement of the continuous surface 48 in the desired motion, the rotor is constrained to follow that movement only, and between the two engaged surfaces, the engine or compressor Produces a relative upward movement in an orderly manner such that no upward movement or some retraction may occur during operation.

One of the substantial parameters considered for a rotating mechanism of the type to which the invention applies is the factor 2r, where 2r is the maximum radius of the rotor or stator, and re is the rotor or stator radius. The eccentricity of the stator is expressed as the ratio 2r1/re.

While previously proposed rotary engines have operated with chamber values greater than 6, usually around 7, in the present invention a value of 5 is preferred which has substantial features in the design. It is something.

Point seals 40 are required to provide the necessary sealing under the extremely harsh conditions encountered in rotating engines, and the development of such seals is critical to the production of commercially acceptable engines. there were.

The problem of designing an engine with an acceptable point seal angle was mentioned above, and since it was particularly difficult to reduce the K value to less than 7, this problem became more difficult in reducing the value of the chamber. It has become urgent.

FIG. 7 shows a cross section of a particularly unique seal structure in which two axially extending seal members 54, which may be described as a boomerang cross section, have two convex surfaces in contact with each other, each outer end portion being rotatable. extending radially from the child and whose respective inner end portions engage respective axially extending longitudinal grooves 56.

A suitable gas seal 56 is provided at the innermost end of each member 54 to provide a gas transfer passageway 58 from the respective rotor face 36.
Opposing amount ゛1 is guided to the bottom of the groove.

If, for example, the rotor were to rotate clockwise as shown in FIG. 2, surface 36a would be 11 leading + 1 with respect to the seal attached thereto.

The pressurized gas in each working chamber flows through a respective passageway 58a into the connected groove 56a and reduces or at least predetermines the "tilt" angle (i.e., the angle of inclination of the seal relative to the stator wall). The seal member 54a is forced radially outward within its groove in a direction to maintain the same value.

Assuming that the gas at surface 36a becomes an expanding ignition gas as the seal passes the tip of the casing epitrochoid inner wall, the gas is exhausted from passage 58a by engine exhaust; while pressurized gas is exhausted from the seal. It is sent through passage 56b so as to reverse the direction of gas action above.

As mentioned above, in U.S. Pat. There is.

For a rotary engine with a chamber having a K value of 5, a single vertical seal has a maximum inclination angle of about 37°, and the seal according to the invention can operate at angles greater than or equal to 22°.

The seal is automatically lubricated by a spherical valve 60 operating within a radial bore 62 and by communicating a gap 64 between the contacting seal member surfaces with an internal gap 66 of the rotor.

During the movement of the rotor section, centrifugal force effectively forces the oil into the passage 62.
through an open spherical valve to gap 64 and between seal members 54 .

During movement of the other parts, the forces are reversed and the spherical valve closes to prevent oil from draining out of the gap 64.

In order to establish a valid basis for comparing the guide device according to the invention with existing devices, it is necessary to consider the mathematical basis supporting each.

Misunderstandings that arise when using different factors to design the guide device and size the rotor can be avoided.

It is not at all uncommon to analyze that conclusion by using simplified conditions that assume the same application of factors.

The geometry of the epitrochoid was improved in the Norby book, and Norby's statement that the required ratio of annular ring gear to reaction pinion gear was 3:2 was discussed above.

According to this shape structure, the radius of the ring gear is rl,
And if the radius of the reaction gear is rl-re, then
These necessary relative relationships are expressed in the following equation.

In other words, in a trilobal rotor based on 2r to 3(rl-re) re2r1/3 equal m = square, the length of the longest radius must always be twice the length of the shortest radius r1. Since z, and 22 r 1 /re, the above result becomes 2 = 6.

The requirements that are likely to be encountered in practice are shown in Figures 8 and 9.
Explained in the figure.

Figures 8 and 9 show the rotation that intersects the midpoint of one side of the rotor triangle for two different ratios of a and b, where a is the dog axis and b is the minor axis. At the point of the minor radius of the child triangle, we indicate the medial-abduction trochoidal path it describes.

In conventional gear indexing systems, the reversal of motion shown in FIG. 7 would not have occurred because it would have engaged the ring gear and meant a "retraction of the pinion," and the reversal of motion shown in FIG. even occurred.

The motion shown in Figure 8 therefore becomes the limit condition for the I+Wankel 11 type engine, and using the value of re=rl/3 again as mentioned above, we can satisfy this ring gear and pinion design. Correlation is obtained.

The epitrochoidal path of points occurring on the periphery of the annular annulus was illustrated in Figure 8, where simple ends occur at each end of the minor axis and show an angular change in motion, but a backward motion. is not shown.

The mathematical solution is thus confirmed by the physical impossibility of such a retraction occurring at the engagement point of the gear teeth.

Once the actual factors are obtained for conventional guiding devices, answers can be found for all proposed design applications.

For example, while some rotating engines today typically operate with a factor of about 7 for an epitrochoid body, the guide mechanism can be effectively reduced in size to a factor of 6.

This problem is due to the sliding engagement surface of the guide member which allows a certain amount of backward movement as shown by the curve in FIG.
G) which does not occur with the guide mechanism according to the present invention.

It is therefore possible to construct the arrangement according to the invention with values smaller than 6, which themselves have substantial design features.

If we analyze the rotary engines currently available commercially, all of them have an abducent trochoid chamber with a factor of greater than 6, and the numbers we have obtained to date are that the value of the factor is approximately 6. .73 to about 7.14.

What we can now believe is that an arguable reason for this is that the value of the factor is 6, as shown in FIG. The fact is that the generally used trilobal rotor and bilobal stator exhibit unique values involving nearly the relative movement of the stator between the stator and the stator.

This theoretical consideration correlates with the practical observation that as the K-factor decreases toward a value of 6, the rotor tends to exhibit highly unstable ``oscillations'' or 11 pulsations during its motion. There is.

When the K value is 6, the period of stable or nearly stable motion is 1
Can be expanded to angles greater than 0 degrees.

The practical consequences of instability due to this singular 11 oscillation 1' or 11 pulsation +1 are, besides unpleasant noises, vibrations and possible damage to the bearing, the destruction of the lubricating oil film or the stator surface and thus cracking. and cause serious damage.

In the example of Figure 8, although there are two backward motions for each rotation, this does not imply an unstable unique position in between, but instead occurs smoothly and gradually. .

As mentioned above, the gear-type guides hitherto used cannot operate at values other than 6, and therefore in such engines it is necessary to go beyond this extremely high unstable value to a more stable value of 5. I could never do that.

The mechanism shown in FIGS. 2 through 5 has a value of 5 relative to the stator, and as previously mentioned, the small circle indicates the contact position of the guide surface at this value.

As explained above, rotor stability is ensured throughout the entire cycle of each revolution, although only the rotor is indexed in two positions where motion retraction occurs and guided in all other positions. Ru.

If the K value is 6 or greater, the rotor is indexed at all rotor positions.

In general, the mechanism according to the invention preferably takes any value of the factor in the infinite range of values in which K equals 5, preferably avoiding the only clearly unstable value 6.

As a practical matter, the effective force is concentrated in a limited range where K is no greater than 8.

Also, in practice the maintenance of a stable pattern or movement must be supported.

Referring to FIGS. 2 and 5, it can be seen that there are at most three points of contact between the rotating and stationary surfaces.

In this position of the rotor, the extreme point of the fixed guide surface as well as a point on its minor axis are simultaneously in contact with a surface on the rotor.

It can be easily deduced that this condition provides an accurate indexing effect to the guiding system, which must maintain stability.

The limit value of K for the arrangement according to the invention is obtained by solving the general equation for the core guiding surface with the rotor in the position of FIG. 2 or FIG.

According to the known relationship, when ψ is double, if X is the abscissa, then
The value of is X=O.

The equation is X-=((K-4)+2cos 2ψ)(rl
CO5ψ) (1/, and since 0 = -4-1, it becomes =5.

In this way, within specified limits, stability is maintained also for all other positions in terms of the properties of the general equation.

That is, (1) the curve is a continuous function between the ends of its major axis, (2) it has no singularities or inflection points between these limits, and (3) the curve is a continuous function around its major axis. It becomes symmetrical.

The rotor moves in a very uniform circular motion under continuous monitoring of the two mating surfaces, which the path of the rotor's center of gravity guides with mathematical precision, so that dynamic and mechanical stability are correlated. The relationships become balanced.

The effect of reducing this possible factor is shown in FIGS. 10 to 16.

In these figures, calculation diagrams for a four-stroke internal combustion engine with K factors of values from 5 to 7 are shown.

In each case, the following limits were used to allow direct comparison.

That is, a) The compression ratio is 10 and constant.

b) The rotor is a rectangular shape with sides 2 R = 2 J7.

C) The rotor minor axis is r.

d) The rotor semi-major axis is 2r1.

e) The eccentric radius re including K is 2r,/.

f) The width of the rotor is at the designer's discretion, but in these examples its special value is 3re-6r1/.

g) The displacement volume is VDto.

h) The volume of the chamber 18 has an absolute volume VT.

1) The equation for VT is Vr=24πr13(K2+
3) 3 out of 7.

j) The equation for VDIO is VDto2sob・
2 in r13/.

FIG. 10 shows that as K decreases, the rotor surface area and working stroke length increase as a function of K, while FIG. 11 shows an increase in the total available volume in the epitrochoid chamber 18. shows an increase in the displacement volume VD1o of the rotor (equal to the piston displacement in a piston engine) corresponding to .

FIG. 12 is a combination of the results of FIGS. 10 and 11, and shows that three rotors with K=5 have the same output as four rotors with K=7.

Figures 13 to 16 show the expected performance of engines of the same size, but with different factors.

FIG. 13 illustrates the value of vT, which is constant in this example, the value of the friction-inducing load factor (which was found to correspond to VDlo) and the value of the relative radius of the rotating parts.

FIG. 15 shows the total power factor, and since the compression ratio is constant, the value of ■D1o is a divisor of this.

FIG. 15 shows the frictional power loss calculated using the factors in FIG. 11 and the net power factor N, which is the result of subtracting the frictional power loss from the total power.

As can be easily seen, when K=7, N has a relative value of 1.0.
On the other hand, at K-5, N is 1.6, so based on this, two rotors with K = 5 should have the net output of three rotors with = 7. .

The efficiency factor of an engine is expressed by the power output obtained from a unit amount of fuel, and this is expressed by the relationship N/vD1o.

This factor is shown in FIG. An increase in this factor indicates that as K decreases from 7 to 5, the power available per unit size of the engine increases.

At this time it was not thought to consider the issue of appropriate performance rating formulas that would serve as a standard of comparison between different rotating mechanisms.

This problem is different from the subject of the comparison of rotary mechanisms to piston-type mechanisms, which has already been dealt with in detail.

To expand the range of design improvements in rotating mechanisms, a standard rating formula is needed, which will guide the development of rotating mechanisms and serve as a yardstick for potash development.

A formula is needed to measure the efficiency with which available volume is utilized for useful work.

A notable feature of the mechanism according to the invention and with a value of 5 is that almost all of its internal volume seems to be utilized for the work cycle even if its moving parts are eliminated. .

This total internal volume is therefore called 11 absolute volume 1' and is designated as VT.

The displacement volume must take into account the compression ratio and is denoted by V D (n) (indicated by the letter n).

The number of output impulses is three per rotor revolution.

At this time, the absolute volumetric efficiency ratio is is given by

If II n==101+ is used in the above formula, the ratio is expressed as a percentage as follows.

That is, =7 K=6 K=5ε
When the factor is 5 for A near 4.0 factor 84.8 factor 98.5 factor, if a compression ratio of 8-8 is used, εA21
00, indicating that such a ratio can be theoretically obtained in an actual mechanism.

The invention can be applied to mechanisms that are engines or pumps (compressors are one form of pump).

The engine is of a known cycle such as a combined cycle or two to four cycles with or without supercharging.

More than one rotor can be mounted on a single shaft, and multiple devices can be used.

The engine may be of internal combustion or external combustion type. The guide mechanism according to the invention can be used in engines or pumps in which it is added to other mechanisms, such as the above-mentioned known gear type 11 Wankel+1 mechanism, in order to stabilize the motion of the rotor.

[Brief explanation of the drawing]

Figure 1 is an exploded view of one rotating mechanism that operates as a prime mover or pump, shown along the axis of rotation of the main shaft of the mechanism, and Figures 2 to 5 show the rotor located indoors. FIG. 6 is a sectional view taken along line 2--2 in FIG. 1 to show the relative positions of different rotors with respect to the chambers and their respective relative positions with respect to the members constituting the guide device; FIG. -6 is a cross-sectional view showing the mechanism in a combined state, and FIG. FIGS. 8 and 9 are illustrations of medial-abducer trochoidal paths to illustrate certain limitations in the shape of the paths used; FIGS.
FIG. 10 to FIG. 16 are comparison diagrams of the characteristics that occur when the present invention is used and the characteristics of a known rotating engine. DESCRIPTION OF SYMBOLS 10... Casing, 18... Internal chamber, 20... Inner peripheral surface, 22... Axis center of main shaft, 26... Main shaft , 28...Eccentric device, 30...Rotor axis center, 32...
...Trilobal rotor, 40...Seal, 54a. 54b... Seal member, 56a, 56b...
···groove.

Claims (1)

[Claims] 1'7''--a housing 10 and a main shaft 2 mounted by said casing for rotation about a corresponding axis 22;
6, the casing providing an internal chamber 18 having an internal circumferential surface 20, said internal chamber being perpendicular to and symmetrical about the axis 22 of said main shaft 26, and comprising two lobes. A trilobal rotor 3 having an epitrochoidal cross section and having a slightly triangular cross section installed in the internal chamber so as to rotate around an axis 30 parallel to the axis of the main shaft.
2 and an eccentric device 28 for associating the rotor and the main shaft and transmitting rotation therebetween, the rotor being symmetrical about its own axis 30 and having three circumferentially spaced The apex portions 40 are in sealing engagement with the inner circumferential surface 20 of the inner chamber to form three working chambers between the outer circumferential surface 36 of the rotor and the inner circumferential surface 20 of the inner chamber; The operating chamber is the internal chamber 18.
The volume changes during the rotation of the rotor 32 at , further comprising a guiding device for guiding the rotor in the required movement with respect to the casing 10, the guiding device being fixed to the rotor and a first generally triangular guiding surface 48 fixed to the casing and symmetrical about the axis 30 of the main shaft and parallel to the rotor axis; a second guiding surface 46 parallel to the axis of the main shaft, these guiding surfaces being in sliding engagement relative to each other, said second guiding surface 46 being parallel to said second guiding surface in the required relative movement. The cam has a two-lobed cam shape created by the guide surface 1, and its long axis and short axis are parallel to the short axis and long axis of the inner circumferential surface 20 of the casing, respectively. Rotating mechanism.