DE2337554A1 - VOLUMETRIC MACHINE WITH CONNECTING ROD AND AXIAL PISTON - Google Patents

Description

PA α. JTANWALT WOLFGANG SCHONHER3 SS TRIE * - HAWSTBASSE 2 *

TEL. 06 51 - 3 48 β

Trier, July 23, 1973

Maurice glasses Nanterre - France

Volumetric machine with connecting rod and axial piston

The invention relates to a mechanism for reshaping the on Motors or compressors with axial pistons or connecting rods applicable to movement.

Such engines or compressors have cylinders with parallel Axes that are equidistant from one another and around a central axis. The cylinder axes run parallel to the central axis or run slightly towards it.

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In these motors or compressors, the reciprocating rectilinear movement of the pistons must be in a circular motion the central axis or vice versa.

This conversion is particularly difficult with good efficiency to reach. Numerous solutions have also been proposed.

Certain solutions provide an inclined disc which is attached to a central axis and rotates with it. This results in great friction because the peripheral speed of the disk is high.

The solutions with drivers also lead to a considerable Friction.

Other known solutions have a rotatable ring gear in connection with a Z-shaped shaft that serves as a crankshaft. In this case the relative speeds are lower, but strong forces occur. On the other hand, it is difficult to control the movement of the ring gear when the shaft is symmetrical and the rotation is fictional. Eventually becomes the pivot point, though

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it actually exists, from a large diameter sphere or formed by a gimbal that replaces it: in the first case, significant friction occurs, and in both cases it is difficult to avoid jamming at certain points in the cycle.

The main object of the invention is to create a conversion device with a rotatable ring gear, in which the effects on the Kurbdbrm of the engine or consumer, those of a classic Piston engine with connecting rod and crankshaft correspond while the friction of the actual rotation is zero and any requirement for wedging is suppressed.

A volumetric machine according to the invention for compressors or motors of the type mentioned has an inclined, rotatable ring gear and is characterized in that the rotatable ring gear with a crank arm of a shaft of an engine or a consumer is in engagement and the rotational movement of the ring gear by rotating without sliding a truncated cone with two fixed with the ring gear connected outer surfaces on a second truncated cone comes about, which is angled with two with the frame of the Machine firmly connected lateral surfaces is connected, the two truncated cones with the two lateral surfaces as a surface line

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have the bisector of the obtuse angle between the axis of the machine and the axis of the ring gear.

According to a further feature, the invention is characterized in that four truncated cones are connected to two and two and each can be dismantled in a conical gear train for a rotary movement with the cone under consideration as the base cone and a truncated cone supported thereon and determining the position of the apex, whereby the angle at the apex is smaller than that of the cone in question and the surface of the truncated cone supported by each side protrudes beyond the truncated cone in question,

According to another characteristic of the invention, the two elements are fixed in rotation and are coaxial and immovable are arranged in the housing of the machine, each a gear for rotary movement and a truncated cone for trimming on the smooth Surface and with an acute angle at the top.

On the one hand, these two fixed elements can be adjusted to one another during the rotary movement in such a way that

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that the play of the gear is canceled and a certain preload is generated during rotation, on the other hand, that one thing Gear is moved in relation to the other to eliminate the game when trimming on the smooth cones, which can be used to generate a certain preload when trimming can. Finally, the arrangement of the two coaxial elements, which are stationary during the rotary movement, can be displaced and in their The position can be adjusted in relation to the stationary housing of the machine, which makes it possible to determine the degree of compression of each piston in to vary its cylinder, while the movement of the pistons is determined by the angle of inclination of the rotating ring gear, remains the same.

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The invention is illustrated by way of example in the drawings. Show it:

Fig. 1 is a diagram of the kinematic principle of a volumetric machine according to the invention,

Fig. 2 shows the arrangement of the cones which rotate without one sliding on the other,

3 is an axial section showing the principle of a practical embodiment of the machine,

4 shows an axial section of the machine according to IV-IV of FIG. 5, FIG. 5 shows a cross section according to VV of FIG. 4, FIG. 6 shows a cross section according to VI-VI of FIG. 4,

7 shows a longitudinal section through the arrangement of pistons, connecting rods, Connecting rod connection, ring gear and pivot pin when the piston is at its top dead center,

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FIG. 8 shows the projection onto a transverse plane of the path of FIG Middle of the connecting rod plate connection,

FIG. 9 is a longitudinal section corresponding to FIG. 7 when the piston is in its «bottom dead center.

In Fig * 1, the kinematic principle of the rotary motion is a axial machine according to the invention.

Two axes xx 'and yy * intersect at a point S and form an angle & between them. The bisector ASB of the angles xSy and x'Sy ", which are in the plane of the two straight lines" which gives the same angles as follows: xSA = ASy = X ¹ SB = BSy ¹ = 180 ° - OO = 90 ° - _O_

2 2

If, as indicated in FIG. 2, the straight line AB about the axis xx ¹

is rotated, a cone with two outer surfaces ASA * is created

DC 2nd

and BSB * with a half angle at the apex of 90 ° - QC

In the same way, another cone with two lateral surfaces ASA * 'and BSB * "is created when the straight line is ^{rotated around the axis yy 1} , with the same half-angle at the tip as before.

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The two cones beat each other along their common surface line AB, which is always in the plane of xx ¹ - yy ^% . The outer surface ASA ^{1 of} the cone, which is formed around xx ¹ , touches the outer surface ASA ¹ 'of the cone, which is formed around yy * along the half straight line SA, and the outer surface BSB ^{1 of} the cone, which is formed around xx ^f , touches the lateral surface BSB "of the cone, which is formed around yy ' , along the half-straight line SB.

If the two conical surfaces are rotated around their axes corresponding to xx ¹ and yy ^% with the same angular velocity u> , they rotate without one sliding on the other. Their contact always takes place only along the common surface line ASB, which is fixed in the space (always in the plane xx ¹ - yy ¹ ) Due to a classic kinematic transmission at a speed tu around the axis xx ¹ , the cones ASA ¹ BSB remain ¹ fixed, the axis yy ¹ rotates around xx 'with the speed ω and describes a cone, the half-angle of which is equal to OC at the tip. Likewise, the contact surface line ASB rotates with the plane xx ¹ - yy ' by xx ¹ brei the speed cü · This causes the cone ASA ¹ ' to rotate without sliding on the fixed cone ASA ¹ , likewise that the surface BSB ^{"rotates without BSB 1} on the fixed lateral surface

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to slide. These are immaterial geometric surfaces, because the unassigned surfaces interfere,

A first feature of the invention is the use of this kinematic Arrangement in order to obtain the rotation of the ring gear without friction, and which is intended for the movement of a hydraulic one Transfer arrangement. The hydraulic arrangement is determined by cylinders, not shown, in each of the cylinders a piston slides which is connected to a ring gear 5 via a connecting rod 10 (FIG. 3).

A second feature of the invention is to increase the interference of the unassigned surfaces so that all are needed Surfaces can be embodied. For this purpose, the surfaces are beveled at the appropriate points in such a way that a A frustoconical surface is created (Fig. 3).

The fixed outer surface ASA ¹ is determined by two circular lines cc and dd corresponding to two cylinders with the axis xx ¹ . This lateral surface ASA 'thus results in a fixed term which is delimited by the inner and outer cylindrical surfaces of the ring and by the truncated cone cd-cd.

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Likewise, the second fixed lateral surface BSB ¹ is delimited by the truncated cone ef-ef, which results in a fixed term with cylindrical surfaces ee and ff of the axis xx ^1.

The truncated cone cd is made up of a crown wheel 1 and a column 2 that are fixed against rotation and immobile against displacement.

The truncated cone ef is supported by a disk 3 and a column 4 which is concentric to the column 2.

The first rotating lateral surface ASA ¹ *, which is assigned to the fixed lateral surface ASA *, is delimited by a truncated cone gh, which results in a fixed concept with cylindrical surfaces gg and hh of the axis yy ^% (FIG. 3).

Likewise, the second rotating lateral surface BSB ¹¹ , which is assigned to the fixed lateral surface BSB ', is delimited by a truncated cone jl, which results in a fixed concept with the cylindrical surfaces Jj and 11 of the axis yy ^% .

The two truncated cones gh and jl of the axis yy ^% are carried by a part or a ring gear 5 which is concentric with them

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is. The part 5 has a washer 6 which is the carrier of a bearing journal 7 which is connected to a crank arm 8 of a motor shaft 9 cooperates.

One of the two parts 5 or 6, for example 6, has a number of equal arms corresponding to the number of engine cylinders. Each arm carries a joint 0, which can be spherical and which interacts with the corresponding connecting rod 10.

Third, the invention is characterized by an arrangement by means, described below, to keep the coincidence of the tips of the two cones in S constant and to on the one hand, to prevent the two cones from sliding one on top of the other, as well as the stress and inertia involved in the System is developed, may be.

Fourth, the invention is characterized by an arrangement of means, described below, for eliminating any play of the contact surfaces and at the same time between the surfaces to get a certain initial bias.

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A fifth feature of the invention consists in the arrangement of the means described below to allow an axial displacement of the entire arrangement shown in Fig. 3, according to xx ¹ , with respect to a fixed support frame and the cylinders, not shown, whose axis is parallel or is approximately parallel to xx ¹ . This feature allows the volumetric ratio of a known hydraulic motor to be changed, be it as desired, be it automatically as a function of the load, the ambient temperature or the type of combustion.

A sixth feature of the invention resides in the limitation of the shaft 9 and the crank arm 8 of the engine crankshaft. In particular any mean elongation according to xx * which penetrates the mechanism characterized above is excluded. A lateral shaft 56 is used to drive the compensating control wheel and to control the distribution of the motor over four cycles used, which runs parallel to xx * and preferably runs at half the speed of shaft 9. The shaft 56 receives its movement by a spur gear on the shaft 9, which is preferably located between the two bearings 22 and 23. She goes through the arms of the star and between the cylinders (Fig, 4). The shaft 56 opens at the top of the motor housing and carries cams 58, the

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to ensure the distribution of the engine over four cycles are necessary, regardless of whether the number of cylinders is even or odd (if the distribution through the central axis requires an odd number of cylinders) is.

The shaft 56 also carries the necessary interventions to control a central short shaft 61 which carries a compensating control wheel 63 which rotates with the engine speed and which is at the same time the axis of a wheel 66 of a mixer or compressor.

The machine shown in FIG. 4 more fully embodies the diagram of FIG. 3.

The frustoconical surface gh (Fig. 3) is replaced by a bevel gear 11 of the same point S and by a smooth truncated cone 12 of the point S ¹ on the yy ' axis and passes on each side of the fictitious surface of the truncated cone gh.

The smooth truncated cone 12 (whose angle differs from that of the toothed Truncated cone 11) is preferably arranged within the conical gear mechanism 11, but it can also to be outside. These two parts are carried by ring gears 5 and held in place by parts not shown.

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Likewise, the frustoconical surface cd (Fig. 3) is replaced by a conical gear train 13 of the same point S and by a smooth truncated cone 14 of the point S "on xx 'and passes on each side of the notional surface of the truncated cone cd. These two parts are carried by the column 2 and are fixed against rotation by means of a wedge 15. The two conical gear drives Π and 13 mesh with each other and have the same number of teeth. The smooth truncated cones 12 and 14 always have a common surface line according to S ¹ S " and since their half-angle deviates by d at the apex, they have the same diameter at the level of their corresponding points of intersection with the truncated cones gh and cd.

Likewise, the frustoconical surface jl is replaced by a conical gear mechanism 16 of the same point S and by a smooth truncated cone 17 of the point S ^IIf on yy 'and passes on each side of the fictitious surface of the cone jl. According to Fig. 4, the gear mechanism 16 is arranged outside the truncated cone 17, but the reverse position would be the same with regard to the invention.

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The two parts are carried by the ring gear 5 on the outer cylinder surrounding the above system and are through means not shown attached.

Likewise, the frustoconical surface ef of FIG. 3 is replaced by a conical gear train 18 of the same point S and by a smooth truncated cone 19 of the point S "" on xx ¹ and goes past the fictitious surface of the truncated cone ef on each side. The two elements are carried concentrically to the column 2 by the disk 3 and by the column 4. They are attached to the disc 3 by means not shown. The two conical gears 16 and 18 mesh with one another and have the same number of teeth. The smooth truncated cones 17 and 19 always have a common surface line after S ¹ "S" ** and, since the half-angles at the apex differ by dL, they have the same diameter at the level of their corresponding points of intersection with the truncated cones jl and ef.

The cylindrical part of the ring gear 5 is formed by the disk 6 which carries the bearing journal 7. The journal carries a Bearing 20 which is axially fixed by a nut 21. The bearing 20 is fitted in the crank arm 8, which revolves around the engine

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shaft 9 rotates through metal rings or roller bearings or needle roller bearings 22 and 23 are carried in such a way that they can be displaced in the longitudinal direction according to xx *.

The bearing 20 is shown with articulated rollers. It can be replaced by a bearing with two rows of balls in oblique contact, which are arranged in a spherical ring, or by two conical opposite bearings, which are in a spherical sleeve are arranged. The position of the center D of the bearing on the bearing journal 7 can be determined by washers 24.

At this point in the description and assuming that the bearing 20 is articulated on rollers, it should be noted that the arrangement of the ring gear 5 does not rotate to the right in the plane of the figure about point D because the smooth truncated cone 12 of the ring gear is rotating 5 according to S ¹ S * on the smooth truncated cone 14 which is attached to the column 2, and this without wedging in order to obtain the important angle between S ¹ S * 'and the imaginary orbit of the truncated cone 12. It should also be noted that the ring gear cannot turn to the left about point D, since the smooth truncated cone 17 of the ring gear is ^positioned on the fixed truncated cone 19 ^{according to S 111} S lftl without

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Supports wedging to get the important angle between S ¹¹¹ S ¹¹¹¹ and the imaginary orbit of the truncated cone 17 to the left. These two smooth pairs of cones, which are the subject of the invention, prevent a relative displacement of the fictitious truncated cones gh and jl of the ring gear 5 along the surface line AB with respect to the fictitious truncated cones cd and ef of the fixed arrangement. In this way they ensure the permanent coincidence of the tips of the two cones in S. In the same way, it should be noted that the conical pairs Π - 13 and 16-18 define two common points of the surface line AB and a rotation without sliding of the two cones on each other through their gear drive to back up.

The arrangement of the two columns 2 and 4 is ^{centered according to xx 1} by cylindrical support surfaces 25 and 26, which serve as a support against bending pressure. The two columns are wedged against rotation one against the other by pegs 27 of pillar 4, pegs 28 of pillar 2, screws 29 and their lock nuts 30.

The different wedging increases the backlash between the two pairs of gears 11 - 13, 16 - 18 and at the same time possibly gives ^ 4ine safe initial tension with play on the elasticity of the Tension of the two pillars.

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The general wedging against rotation of the arrangement of the two columns with respect to the fixed housing is provided by two pins 31 on the column 4, pin 32 on a frame 33, screws 34 and their counter nuts 35 held. The frame 33 thus absorbs the reaction torque that is transmitted through the toothed gears.

The two columns 2 and 4 are axially wedged together by two screws 36, the half means of which are not shown. The tightening of the screws 36 determines a raising of the column 2 to xx 'and a lowering of the column 4 to x'x. The smooth truncated cone pairs 12 τ 14 and 17-19 reduce the angle d, which the bearing 20 and the crank arm δ do not allow. The result of the tightening is that at the same time the clearances of the smooth truncated cones 12-14 and 17-19 and the clearances of the bearings 20, 22 and 23 are canceled and at the same time all surfaces of the bearing are given a certain initial preload by reducing the elasticity of the Stretching, compressing, bending and twisting all parts of the chain play. The axial position after xx * the arrangement of the two columns is obtained as follows:

Column 4 (the arrangement of the two columns is as described above) is trimmed on a: middle spring 37, which through here a layer of Belleville washers are shown. This can-

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te be a strong spring, which is arranged around the axis xx ¹ , the section of which is circular, square or rectangular. It could also be a plurality of spring springs with a smaller diameter, which are arranged in the form of a ring between the column 4 and the frame 33 at a distance.

The advantage of the Belleville washers lies in the setting

in that it is easy to vary the flexibility of the spring 37.

The advantage in functionality is evident.

The spring 37 is supported on a ring 38, which is threaded through 39 is screwed into the frame 33. The ring 38 can be rotated by a concentric gear transmission 40, a pinion 41, a Shaft 42 and a control member 43 with marking members 44 are driven. The control and marking can be arranged at a distance, so that the shaft 42 by a flexibility in the Rotation is controlled.

In the rest position, the spring 37 supports itself upward of the movable one Arrangement against a stop 45 which is carried by a cover 46 which is connected to the frame 33. The angular wedging of the arrangement of the movable machine part is through the

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Screws 34 determined, which give an easy game, the one small axial displacement of this arrangement in the course of the activity under the influence of the equilibrium of forces allowed. In In series production, the wedging by the screws 34 can be replaced by a sliding key connection or by keyways.

In the arrangement, which is formed by the frame 33, the cover 46 and the disc 3, Dl is filled through a nozzle 67 under moderate pressure, which comes from a lubricating pump. This oil cannot escape through the play of the cylindrical centering and through the calibrated injection nozzles 68, since a non-return valve (not shown) is arranged between the nozzle 67 and the lubrication pump.

For recording or for calling up the alternative movement of the Piston, the ring gear 5 has a certain number of arms 47 equal to the number of pistons. This number can be anything.

It can be within the scope of the invention a four-stroke or two-stroke internal combustion engine, an ignition-controlled engine or an engine with ignition by compression, a steam engine or a hot air machine (Sterling cycle)

^act · 309886/0952

A four-stroke engine with five cylinders is described here as an example.

The pivot point 0 of the connecting rod 10 on the arms 47 of the ring gear 5 is, with all arms at the same distance from S, selected in such a way that it lies in the axis of the engine cylinder. It could be placed in the plane zz ¹ perpendicular to the axis yy ' in S in order to obtain the left trajectory of the projection in symmetrical figure eight with a small displacement amplitude of 0 with respect to the axis of the cylinders (Fig. 3). It can be advantageous, as indicated in Fig. 4, ^{to choose 0 a little below the plane zz 1} in order to reduce the upper hump of the figure eight more and to almost completely reduce the lateral displacement of 0 at the moment of the angular movement of the connecting rods 10, to prevent, in which the pressure in the cylinders is maximum. This is done to the detriment of the inner hump of the eight, which enlarges (but no longer has any pressure).

There can of course be swivel joints in 0, as indicated in FIG. 3 are to be used with ball head rods. The relative sliding in a joint of this type is a little higher than what it is developed in one axis of a classic piston. The invention

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also suggests a type of swivel joint as a variant, which is practical without friction and which is more homogeneous with the pivot that has been described.

The proposed swivel joint for the variants is shown in detail in 7, 8 and 9, where the pivot pin already shown in Fig.4 is given, is given under a more developed form.

The center S of the pivot at the intersection of the axis xx ^{1 of} the machine and the axis yy ^{1 of} the ring gear as a disk in the form of a nut, the column 2, the disk 3 and the sleeve 4 are found again. The ring gear has an upper part 5 and a lower part 6 which ends with the pivot 7. The upper part 5 of the ring gear carries the gear drive 11 and the concave smooth truncated cone 12, which are associated with the gear drive 14 and the smooth convex truncated cone 14, which are carried by the column 2 and the disc 1. The grooves 15 keep the gear mechanism 13 rotating. The lower part 6 of the ring gear carries the gear mechanism 16 and the smooth, concave truncated cone 17, which are assigned to the gear mechanism 18 and the convex smooth truncated cone 19. Their position is reversed with respect to that shown in FIG.

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One of the five arms 47 (on a machine with five cylinders), which are attached to the plate 6, carries a collar of the connecting rod of the theoretical center 0.

The axis of the corresponding cylinder tt ¹ is parallel to xx ¹ . On this axis is the pivot point of the connecting rod on the piston in P. The axis of the connecting rod is P 0.

The point 0 is selected on the crown wheel in the plane zz * perpendicular to xx * in point S. When the ring gear is moving, this point 0 describes a path in the form of a circular arc 0 0 "O ¹ , where OSO" β O ¹¹ SO ¹ s Ow with the creation of a straight line 00 ', which in I is the path nn' of the transverse plane of the machine intersects and goes through S so that 0 1 = 10 *. When projected onto the plane nn ¹ , this path describes a circle (Fig. 8) with a diameter equal to the distance of the segment I 0 "and a center point U, so that UI = U 0". If 10 "= SO ( l-cos. and SU = S 0 - U 0 "= S 0 (1 - cos, ft ), results

S 0 ( 1 + cos. Ct ). So that the axis tt 'goes through U, its 2nd

Distance to xx ^{1 have} a value of S 0 ( 1 + cos, ft ).

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Under these conditions, the PO axis of the connecting rod describes a cone around tt * with a half-angle β at the tip.

If it is assumed that the length PO is very large, then ρ is canceled.

The bisector AB goes through the center of rotation of the ring gear S, i.e. the common generatrix of the original basic cones crosses the contact section of the smooth cones 12 and 14 with a large angle and a contact portion of the cone and 17 with an equal angle, indicating the rotation of the ring gear in the plane of the figure around the pivot 7 prevented *

If a parallel KK * to AB is drawn through 0 and a parallel OV to yy \ , the same situation is obtained in 0 as in S »

A convex truncated cone 80, which on a rod 81 of the axis OV is mounted on the ring gear by the arm 47. A corresponding concave truncated cone 82 is designed as a sleeve 83 and arranged on the smooth end 84 of the connecting rod 93.

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This sleeve 83 is supported by means of an alignment wedge 92 a part 85 that is screwed onto the connecting rod and through a lock nut 86 is locked.

On the piece 85 a sleeve 87 is attached concentrically to the sleeve and the sleeve 87 carries a concave cone 88, the corresponds to a convex cone 89 seated on sleeve 90 concentric with rod 81 and in position simultaneously is fixed on the arm 47 by a nut 91.

The axis KK ¹ traverses the contact surface line of the corresponding truncated cones 88 and 89 and the contact surface line of the corresponding truncated cones 80 and at a large angle

Determine the two pairs of truncated cones that are opposite each other the point 0 and the noticeable! Stresses caused by the Loads and inertia go through the surface line mentioned above with a weak hertz pressure and turning conditions with almost no sliding.

Due to the equality of the mean diameters in each pair the connecting rod does not turn while the ring gear is moving

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on its axis and not the support column 2 of the pivot. But if there is an advantage in the rotation of the connecting rod on its axis (and there is one) is seen, it is easy to turn it by sliding it slightly and at the same time the contact portion 89 to the tip of its cone and the contact portion 80 to be moved to its tip. When moving of the two in opposite directions, the connecting rod rotates around itself in the opposite sense as described above, became.

All of this causes the angle $ to be zero. If the connecting rod is short enough, β has a wat of approximately 2. A pinion 54, which may be axially displaceable, is keyed on the shaft 9 of the motor. A toothed wheel 55 advantageously of twice the diameter engages in the pinion without it being indispensable according to the invention.

This gear is keyed on the shaft 56, the axis of which is parallel to XX ¹ and which cannot be moved axially. In order to avoid a change in the angular wedging relative between the WaLIe 9 and the shaft 56, the gear train pair is meshed with one another. The shaft 56 goes between the two arms 47 of the part

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idler wheels (Fig. 5) without hindering its movement through. It also goes through between the two corresponding cylinders. Controlled by a helical pair of pinions 57 the shaft 56 the oil pump, the combustion pump and the ignition distributor in the engine with ignition control. These three elements are not shown. The Shaft 56 controls the injection pump of an ignition engine by compression.

In the case of a group of two, the shaft 56 goes into the housing and by the cams 58, which are shown schematically, to be in classic Way to secure the distribution of the engine in four strokes. The shaft 56 has a gear 59 with the same diameter at its end like the gear 55, which cooperates with a pinion 60 of the same diameter as the pinion 54. The pinion 60 is arranged on shaft 61 coaxially with shaft 9 and rotates at the same speed in the same direction and maintains the desired wedging.

The teeth of the gear train pair 59, 60 can be helical be. On the shaft 9 and on the shaft 61, two control wheels 62 and 63 with unbalances 64 and 65 are arranged offset by 180 to to compensate for the initial inertia of the couples. The wave 81

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carries a wheel 66 that controls the distribution of the carbon mixture in the Engine with ignition control ensures what a certain charge ensures in any case.

The steering wheel 62 is used to control the transmission through a clutch, not shown, despite its slight possible axial Shift.

In the description above, the kinematic function of the ring gear, its journal, its swivel joint on the connecting rods and the transmission of motion between the connecting rod and the motor shaft 9 already very obvious. The possibility of axial movement of the arrangement is also emphasized.

The following remarks complete the picture of the functionality. The arm 47 (i) in the upper position, ie when the corresponding piston is at 01, is at top dead center and 01 is in the plane of the crank arm xED. The amplification of the explosion is carried by the parallel in 01 to the axis xx ^f . The inertial force applied to the piston connecting rod mass eludes FI. The least desirable case is that of slow motion, where inertia is almost 0 and where FI

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is maximum. If the axial effect on the bearing 20 is to be zero or almost zero, the effect F2 of the crank arm is transferred to the extension of ED. The reaction F3 of the truncated cone to the truncated cone 12 should be perpendicular to the common surface line S ¹ S ' ^f at the point where it intersects the surface line ASB. It is therefore best to ^{choose the angle S 1} S "and ASB. As noted above, there is no sliding at the point of the common surface line of the truncated cones 12 and 14, nor is there any friction. On the other hand, there is little friction on the common surface line of each side from ASB. The bearing 20 works exactly like a crank pin of the crankshaft. The conical bearing 12-14 works much better than a classic bearing due to the weak Hertz pressures. The forces Fi, F2, F3 remain proportional.

The truncated cones 17 and 19 show no reaction. Rather, they have a tendency to separate, with the advantage of being preloaded. Near bottom dead center the pressure effects are cbr arms (3) and 47 (4) are very weak and can be neglected.

If the movement is fast, the inertial force must be the mass the piston of the connecting rod and the ring gear become noticeable. They are maximally in the upper position 01. If the number of cylinders

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is paired, the inertias of the two opposing pistons are equal and their resultant is zero along the axis xx *. If the number of cylinders is not equal, as is the case in the selected example, the flywheel mass, not shown, can be arranged in the cavity of the ring gear at points 69 in such a way as to obtain a resultant zero in the same way. In all these cases there is an important moment of inertia on the ring gear, which is transmitted to the frame 33 on the one hand by touching the truncated cones 17 and 19 along the contact line S " ¹ S ¹ " ¹ and on the other hand by the journal 7 and the crank arm 8. The moment of inertia is supplemented by a counteracting moment that is generated by the rotating masses 64 and 65 of the steering wheel

In a position 01 other than above, for example in position 02 (FIG. 5), the force F2 acts on the crank pin 20 (or D) _7, which causes the instantaneous torque of the motor. The response F'3 is obtained by the response F4 and F5 of the teeth of the conical gear pairs. F4 on pair 11-13 and F5 on pair 16-18 *

The values of F4 and F5 are variable according to the position of 02 and become zero when Ö2 is in the highest: position. the

Moments of force are obtained through the two pillars 4 and 2 and transferred to the frame 33 through the stops 28 and 32. The instantaneous changes in the gear train pairs are in such a way that a reduction in play, as already described, is advantageous and so is the slight bias.

In the case of a compressor, a steam engine or a hot air rotor, the axial displacement of the arrangement is not of relative advantage and it is preferred in this case to replace the spring 37 with wedges.

In contrast with an internal combustion engine with controlled ignition or with ignition by compression with two or four strokes, the axial displacement is of great importance because it changes the compression spring allowed in the course of the arbuit.

In the example chosen, the entire movable arrangement of the columns 2 and 4 by the spring 37 is in the rest position against the Stop 45 pressed, which helps that the compression at start is maximum. When the engine is working it will be the middle one Pressure in the sense of x'x very force, so that the mean pressure in the Cylinders (P.M.E.) becomes very strong. The stronger the mean pressure, the closer the spring 37 is pressed, the more the rotary

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point S is removed from the stop 45, the further the setting of the course of the koien from the plane of the housing, the larger the volume of the combustion chamber and the smaller the compression is, the more constant the run is. The stiffness of the spring 37 can be selected. For example with an engine With controlled ignition, a pressure value of 7: 1 can be achieved at full load (which reduces nitrogen oxide) and at 14: 1 at start-up (which ensures a good start) can be chosen with values which vary in such a way that they are between 14; 1 and 7: 1 for the whole values of P.M.E., continue (which at reduced load a complete combustion without non-burned Carbon oxide and a thermal efficiency as with full load ensures). If the mechanical action of the arrangement is good is, a pollution is preserved and a need for special resources is greatly reduced.

Numbers 14 and 7 are shown for ease of understanding. The increase in pressure is made experimental by limiting the explosion in each power position and for each Motor type determined.

If the instantaneous pressure of the pistons on the ring gear varies periodically. and the moving equipment is not in

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"so

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If there is a vibration, the damping is provided by the oil channel of the lubrication in the space, which is provided by the piston 3 and the frame 33 is formed. The choice of the caliber of the exit bores 68 allows the value of the damping to be regulated.

When there is an axial displacement, the movable arrangement drives the crank arm 8 and the motor shaft 9, which are displaceable in the bearings 22 and 23. This shift controls in the same way the damping of the movable assembly due to the inertia of the steering wheel and the friction of the gear trains 54 and 55. In addition the displacement of a few millimeters is not uncomfortable for the transmission of power.

The displacement of the base of the support 38 of the spring 37 means an external manual control 40, 41, 42, 43 allows Ήη Modifying pressure in one sense or another. This allows. To use fuels, their octane number and liquid very much are different. In an engine with controlled ignition you can get a medium ratio of lead-free petrol, knock-proof Use fuel, methanol and lightly hydrogenated methanol. In the case of an engine with ignition by compression, various types of regulation for gas, Ul and petrol are ensured.

309886/0952

The same control 40, 41, 42, 43 can also measure instruments Use for atmospheric conditions and especially thermometers.

309886/0952

Claims (25)

V- '^ VW.t: 3CKONHERR D 5S Γ K ' ι · ■': '' STTASSE 28 Trier, the B 632 Claims Volumetric device with connecting rod or axial piston, consisting of pistons that are tilted with a rotatable Cooperating ring gear, characterized in that the rotatable ring gear with a crank arm of a shaft of a motor or of a consumer is engaged and the rotary movement of the ring gear by rotating without sliding a truncated cone with two outer surfaces firmly connected to the crown wheel come into being on a second truncated cone, which is angled with two the frame of the machine firmly connected lateral surfaces, the two truncated cones with the two lateral surfaces as the surface line the bisector of the obtuse angle between the axis of the machine and the axis of the crown wheel. 2. Apparatus according to claim 1, characterized in that four Truncated cones are connected to two and two and each in a conical gear train for a rotary movement with the considered cone as the basic cone and one supported on it and the truncated cone determining the position of the apex can be dismantled, 3Q98S6 / Q952 - X - the angle at the apex being smaller than that of the considered Is cone and the surface of the truncated cone supported 'protrudes from both sides of the truncated cone under consideration. 3. Apparatus according to claim 2, characterized in that the two fixed, rotating elements are arranged coaxially to the housing of the machine and each has a gear for one Rotary movement and bear a pointed truncated cone for trimming, while they are adjustable in their rotation relative to one another in such a way that the play of the gear can be canceled and a certain amount Bias of the rotary movement can be generated and the gears are mutually displaceable in such a way that the game in Pressure lifted and a certain bias generated in the pressure. 4. Device according to one of the preceding claims, characterized in that the arrangement consisting of the two coaxial, fixedly attached to the housing of the machine, rotating Elements is carried by a spring, which allows a slight displacement in the axial direction, the displacement on the ring gear and the motor shaft is transmitted, a displacement caused by the mean value of the axial thrusts of the pistons 309886/0952 and is therefore caused by the mean actual pressure on the pistons and thus brings about a height shift, the volumes of the compression chambers being so much greater than the mean actual pressure increasing and the pressure conditions being weaker. 5. Apparatus according to claim 4, characterized in that the axial displacement can be damped by the lubricating oil between the housing and the piston connected to the movable device is enclosed and via an adjustment device and a one-way valve penetrates and exits via calibrated injectors to lubricate the mechanisms, the degree of Damping is adjustable through the caliber of the injectors. 6. Apparatus according to claim 4, characterized in that the The support of the support spring can be displaced in the axial direction by turning an externally actuatable nut to change the mean pressure ratio, the operation being manually actuatable to differentiate the ratio of fuels Adjust octane number or different fluid, or by a heat measuring device can be influenced in order to adapt this ratio to the atmospheric or starting conditions. 309886/0952 7. Device according to one of the preceding claims, marked t ^ urch a steering wheel with respect to a steering wheel of the motor or Consumption that rotates at the same speed and wears wet to compensate for the moment of inertia, this balance wheel being controllable via an intermediate shaft that runs parallel to the motor shaft, which rotates at any speed and with the two shafts of the two control wheels Connected via pairs of gears of the same type, the intermediate shaft engaging in the space between the two corresponding cylinders. 8. Device according to one of the preceding claims, characterized in that each piston (P) on the periphery of a ring gear (47) by a smooth truncated cone pair (82 and 88), the is arranged on a rod (93) of the piston (P) and a pair of truncated cones (80, 89) is seated on the ring gear (47), is fastened, wherein the pairs of truncated cones roll on each other and are mounted opposite one another, and at the same time an accurate setting of the theoretical pivot point 0 as well as a transfer of all load and inertia influences via a rotary movement is ensured. 30S886 / 0952 9. Apparatus according to claim 8, characterized in that the two sections of the contact surface lines of the two truncated cones pairs on both sides of the line of the same speed KK parallel to the bisector of the angle <k of the two basic truncated cones (80, 82 or 88, 89) and an angle (90 - <λ ) form with the axis of the cylinder, where dL is the Is the angle of the axis yy * of the ring gear with the axis x ^f x of the cylinder. 10. Device according to claims 8 and 9, characterized in that the truncated cones (80 and 89) are both attached to the ring gear (47), while the truncated cones (82) and (88) both on the connecting rod (93) of the piston (P) are attached. 11. Device according to one of claims 8 to 10, characterized in that the two smooth truncated cone pairs are conical Have running surface (82) which is positively connected to the rod (93) and converges in the direction of the piston (P), a have conical running surface (80) which is positively connected to the ring gear (47) and converges in the direction of the piston (P), the running surface completely inside the surface (82), with which it is constantly in contact only via a surface line, runs, have a conical running surface (88) that is frictionally connected with 309886/0952 the stage (93) is connected and diverges in the direction of the piston (P) and has a conical running surface (89) which is positively connected to the ring gear (47) and diverges in the direction of the piston (P), the running surface completely inside the surface (88), with which it is constantly in contact only via a surface line, runs. 12. The device according to one of claims 8 to 10, characterized in that the two truncated cones (80 and 89) attached to dex connecting rod (93) of the piston (P), while the truncated cones (82 and 88) both on the ring gear (47 ) are attached. 13. Device according to claims 8 and 11, characterized in that that the conical running surfaces (82 and 88) are arranged coaxially and axially displaced to one another with the surface (82), which the Piston (P) is more closely adjacent than surface (88) in order to form a gap between them in which the two conical Surfaces (80 and 89) of the ring gear (47) are arranged opposite one another. 14. Device according to claims 8 and 11, characterized in that that the annular path formed by the tread (82) 30 98 86/0952 has an outer diameter which is smaller than the diameter of the annular path which is defined by the surface (88) is formed, whereby a bushing (90) can be attached between these two tracks, which bushing is fixedly connected to the ring gear (47) is. 15. Device according to one of claims 8 to 14, characterized in that the line of equal speeds KK 'with the Contact surface line of the connected truncated cones (88 and 89) an angle over 20 and thus greater than the clamping angle of the Mechanism forms. 16. Device according to one of claims 8 to 15, characterized in that the mean diameter of the running surfaces of each pair (80, 82 and 888 89) are the same, so that the connecting rod (93) does not revolve around itself. 17. Device according to one of claims 8 to 15, characterized in that the mean diameter of the treads each Pair (80, 82 and 88, 89) are unequal, so that the connecting rod (93) rotates easily on itself. 309886/0952 18. Device according to one of the preceding claims, characterized in that the angle β (angle of the actual axis of the rod (81) with respect to the theoretical axis P 0 "of the cylinder (95)) is less than or equal to 3. 19. Device according to one of claims 8 to 18, characterized in that that each Kiben (P) is firmly attached to its coaxial connecting rod (93), the running surface of the piston, just like that of the single sealing segment (97) on the cylinder (95) is spherical, while a scraper segment (99) in one CounterlcLben (100) is arranged, which slides in the cylinder (95) and the rear part of the can be moved to and fro via a ball joint Piston (P) picks up. 20. Device according to one of claims 8 to 18, characterized in that that each piston is firmly attached to its coaxial connecting rod (93), with the running surface of the piston (P) on the cylinder is conical and that of its sealing segment (97) is spherical, while a scraper segment (99) in one Opposing piston (100) is arranged, which slides in the cylinder (95) and the rear part of the back and forth via a ball joint moveable piston (P) receives. 309886/0952 21. The device according to claim 20, characterized in that the Frustoconical running surface of the piston (P) on the cylinder (95) has a half-angle at the tip which is equal to the angle made by the axis of the connecting rod (93) and the axis tu of the cylinder (95) is formed. 22. Device according to one of the preceding claims, characterized characterized in that it is a four-stroke engine, the balancing control wheel having a wheel opposite the main steering wheel, which serves to distribute the fuel mixture and to give the gas fed to the cylinders a slight overpressure. 23. Device according to one of claims 1 to 22, characterized in that it is a kolberrgeti ^ flat compressor with connecting rod. 24. Device according to one of claims 1 to 22, characterized in that it is a steam engine with a single or double Mode of action is. 25. Device according to one of claims 1 to 22, characterized in that it is a hot air engine with double action and four cylinders is. 309886/0952