DE102005062892B3 - Rotary piston engine for use as e.g. internal combustion engine, has two symmetrically arranged elliptical control teeth gears and elliptical main tooth wheels that are encased by tooth belt, toothed chain and chains - Google Patents

Abstract

The engine has working chambers formed in a ring cylinder housing, and rotary pistons connected with one another by shafts. A belt drive comprises transmission discs that are mounted on a driving shaft. The belt drive comprises has elliptical main tooth wheels (9, 10) that are encased by a tooth belt, a toothed chain and chains (13-15). Two symmetrically arranged elliptical control teeth gears (11, 12) and the main discs are encased by the tooth belt, toothed chain and chains.

Description

was standing of the technique

From the DE 10 2004 011 583 A1 is a rotary engine, which is controlled by an elliptical gear known. In this case, so-called. Elliptical coupling body are in operative connection with each other and cause the periodically varying peripheral speed of the piston. This active compound is achieved inter alia by the shape of the elliptical coupling body, by a magnetic coupling or by an endless belt.

Of the However, the main disadvantage of this frictional coupling is the fact that by a possible Displacement of the coupling body to each other the relative movement of the piston is affected, so the process disturbed or is interrupted.

at the use of elliptical gears can reach the Rotation angle adjustment can be influenced by the ellipse, in order thus an optimal ratio between piston width (length) and To be able to produce a hub however, they are elliptical gears in terms of their running culture mainly in lower rpm ranges used.

The FR 2 760 786 has a piston motor to the content, which is controlled by elliptical gears, which are coupled together by a chain or timing belt. As a result, a permanent transmission of the periodically varying relative speeds is possible even at higher speeds. However, in the FR 2 760 786 does not take into account the alternating bias of the chain, which provides for accurate transmission characteristics within one revolution.

From the DE 1536 525 is a classification magazine with a clamping mechanism for an elliptical chain transmission known. However, this mechanism is based on spring-loaded idlers, which are not suitable for permanent operation at high speeds for internal combustion engines.

The DE 4241231 A1 describes a belt transmission with periodically variable translation, which is formed by eccentric pushing and a belt.

task the invention

The The object of the present invention is the generation of the relative movement the rotary piston of a combustion or engine from the aspect, the running characteristics, the smoothness in high speed ranges and the transmission to optimize the torque. The invention is an elliptical Gear transmission based, which with an envelope drive system in the form of a toothed belt, a toothed chain or a chain is provided, wherein elliptical Timing sprocket the bias of the hull drive system during the Keep the operation constant.

Description:

1 - A longitudinal section through a first embodiment of a rotary piston machine

1a - The embodiment of a rotary piston machine with the further rotated by 45 ° Hülltriebsystemen

2 - The position of two superimposed Hülltriebsysteme the rotary piston machine at the time of the top dead center of the currently opposed rotary piston

2a - The embodiment of a rotary piston machine after 2 with the drive systems rotated by 45 °

3 - the top dead center of the opposing rotary pistons

3a - The embodiment of a rotary piston machine after 3 with the drive systems rotated by 45 °

4 - An envelope drive system in its basic position, the main toothed discs lie on parallel axes and are rotated by 90 ° to each other, and the internal arrangement of the control pinion

5 - a view analog 4 - The Hülltriebsystem in a symmetrically equal rotated position, it shows the position of the main pulleys and the control pinion to each other

6 - a view analog 4 - An Hülltriebsystem in its normal position, as well as rotated by 90 ° position of the main gear and the position of the Steuerzahnritzel to

7 - a view analog 6 - An Hülltriebsystem from its basic position to plus, or minus 45 ° twisted position of the lower main pulleys and the position of the Steuerzahnritzel to

8th - a view analog 4 - A Hülltriebsystem in its normal position and its deflection of the pitch circle in Trumm half the center distance, at the inside arranged Steuerzahnritzeln

9 - a view analog 5 - An envelope drive system in a symmetrically equal rotated Position and the wrapping line ( 16 ) as well as the resulting relationships of the center distances (A1 .... A4) with internally arranged steering pinions

10 - a view analog 5 - An Hülltriebsystem in a symmetrically equal rotated position and its deflection of the pitch circle in Trumm at half the center distance with internal arrangement of the control pinion

11 - a view analog 8th - An Hülltriebsystem in its normal position and its deflection of the pitch circle in Trumm at half the center distance, with externally arranged Steuerzahnritzeln

12 - a view analog 5 - An envelope drive system in a symmetrically equal rotated position and the envelope line ( 16 ) and the consequent correlations of the center distances (A1 .... A4) with externally arranged timing sprockets

The 1 . 1a . 2 . 2a ; 3 and 3a explain the structure of a rotary piston machine with diametrically opposed rotary pistons, which are provided by two correspondingly coupled envelope drive systems (US Pat. 8th ) are moved cyclically rotationally.

The Operating principle of this rotary piston machine is known and will not closer here explained.

The Special feature of the envelope drive with the same elliptical transmission disks is that the free drive belt length, i. the drive belt length, the between the transfer discs is not engaged, depending on the installation angle of the transmission discs to each other changed periodically. This change in length comes through the ever-changing Angle of the rolling ellipse between driving and driven pulley it is repeated periodically.

The to be reached running properties are u.a. depending on the ellipticity of the disc pairs and from an always equal bias of the transmission elements used while a rotation period.

There but the free drive belt length do not change periodically This may be due to a circumferential change in the system of elliptical transmission disks be compensated. That is, to secure the required bias, either an axle box must constantly move in rhythm or an adaptive to the rhythm tension roller the length in the shoot keep constant.

This is used in all known classical envelopes over the hiring of tension rollers, slide rails etc. achieved in Trumm.

At the envelope drive without perforated belt would the transmission discs after a few turns change their position relative to each other, i. of the Effect of angular rotation of the transfer discs is undefined and therefore nonsensical.

Out these considerations proves to be a transmission element with meshing as an advantage, because its teeth equal to the control of the system to change the scope be used, at the same time transfer they are accurate to the angle or with corresponding angular rotation of the input pulse.

In the 4 If the basic structure of the invention is explained, an envelope drive ( 8th ) for an elliptical toothed disk pair ( 9 . 10 ), which in addition to the change in Drehwin angle between the driving (A2) and driven axle (A1) and the resulting periodically alternating load directions in the drive withstand and at the same time a constant bias of timing belt, chain, chain ( 13 - 15 ) within one revolution.

The condition is that the elliptical main pulleys ( 9 . 10 ) with 90 ° axis rotation and connected via a toothed belt, tooth chain, chain ( 13 - 15 ) turn in the same direction.

In this envelope ( 8th ) with elliptical disks, as in 5 shown, changes the free, that is not in engagement wrapping line ( 16 ) after about a ¼ revolution between the maximum and minimum circumferential values. Within one revolution, this repeats 4 times periodically, provided that the main elliptic discs ( 9 . 10 ) have a constant center distance (A1, A2), have a ratio of 1: 1, and rotate the disks by 90 ° angularly rotated about the axes (A1, A2).

At each periodic revolution of the main elliptical pulleys ( 9 . 10 ) with the condition of a constant center distance of A1 and A2 takes place in this envelope drive according to the invention ( 8th ) a length compensation by periodically - variable timing sprockets ( 11 . 12 ).

The control of the Steuerzahnritzel is synchronous to the rotational movement of the elliptical main gear ( 9 . 10 ) by tooth engagement in the teeth of the toothed belt, a toothed chain or a chain ( 13 - 15 ).

Like in the 5 All elliptical rotation bodies are exactly mirrored each other. The free envelope circumference between the axes (A1, A2) and the main toothed discs ( 9 . 10 ) shorter so that it periodically by the deflection of the toothed belt; the tooth chain or chain ( 13 - 15 ) by means of periodically variable control pinion ( 11 . 12 ) is corrected.

The envelope drive ( 8th ) to 2 consists of two toothed discs, the main toothed discs ( 9 . 10 ) and two control sprockets, the control sprockets ( 11 . 12 ).

The arrangement of the control pinions ( 11 . 12 ) takes place symmetrically to the main toothed discs ( 9 . 10 ).

They can be arranged both inside and outside the envelope drive. In 8th - 10 is the interior arrangement and in the 11 and 12 the external arrangement of the control pinions ( 11 . 12 ).

When using a simple toothed belt or a toothed chain as a drive element, only the internal arrangement of the control pinion is possible Fig. ( 4 - 10 ).

When using a double-sided toothed belt or when using a chain as an enveloping drive ( 8th ), the timing sprockets ( 11 . 12 ) are arranged both in the inner and in the outer region of the Trumms.

The outer contour of the control pinion ( 11 . 12 ) corresponds to that of an ellipse, both control sprockets are the same in the outer contours.

A control pinion ( 11 respectively. 12 ) has half the number of teeth compared to the main toothed discs ( 9 . 10 ).

The ellipse of the control pinion ( 11 . 12 ) depends in addition to the parameters of the elliptical main gear ( 9 . 10 ), such as ellipse ratio or center distance (A1, A2), also from the arrangement of Steuerzahnritzel ( 11 . 12 ) in the system of the belt used as well as the wrap angle between the drive and driven side.

In the 8th and 10 as well as the 11 and 12 is the length of the envelope line ( 16 ) the sum of F and G as large as the distance in the 8th respectively. 11 , which results from the number of teeth (n) of the wrapping element of a page in the run times of the division (T). T × n = F + G

The design of the control pinion ( 11 . 12 ) is in the smallest curve of its ellipse to the parameters of the smallest permissible radius' of the belt element used, such as toothed belt, chain or chain ( 13 - 15 ), ie they determine the subsequent size ratios of the transmission elements.

In the design sketch of the elliptical envelope ( 8th ) is the required number of teeth ratio of 1: 2 between timing sprockets ( 11 . 12 ) and the main toothed discs ( 9 . 10 ), while the pitch circle of the transmission element used for the determination of the axial distances (A1, A2, A3, A4) plays a crucial role.

During rotation, main sprockets ( 9 . 10 ) and control pinion ( 11 . 12 ) do not collide in their head circular ellipse. This is mainly in the inner arrangement of the control pinion ( 11 ; 12 ).

The parameters for the design of the teeth or tooth gaps in the elliptical toothed discs ( 9 . 10 . 11 . 12 ) can be taken from the datasheets of the toothed belt to be used, the toothed chain or chain and corrected accordingly.

at The construction of the ellipsoidal gear is always of the pitch circle diameter (Z1, Z2) of a round toothed disc wheel or sprocket. This is exactly determined in its scope and on an ellipsoides Transfer gear equivalent. There is the ratio from D - d (or DD - dd) = the ellipse ratio at. It is approximate that of the partial circle ellipse of the ellipsoidal gear.

By interpolation, the partial circular ellipses of the ellipsoidal gears ( 9 . 10 . 11 . 12 ) are optimally divided to the number of teeth (division).

In order to determine the control pinion ellipse, the change in the length difference of the free envelope line in the runn plus the resulting additional deflection by the control toothed pinions ( 11 . 12 ) resulting from the roll-off effect during the periodic rotation phase are included in the ellipse ratio for determination.

This relationship is to be calculated exactly or determined on the basis of a sample.

From the 8th to 12 The changes or the relationship of individual changes in length within a periodic rotation phase should be illustrated.

The derivations of the resulting dimensional conditions are in certain proportions sen of the rotating Hüllteilkreisellipsen each other.

L1

– Abstand der Hauptzahnscheiben (9, 10) zueinander, Strecke von A1 zu A2

L2

– Maß zur Bestimmung der Achsabstände zwischen A3 und A4

L3

– tatsächliche Auslenkung der Umhüllungslinie (16) in symmetrisch gleicher Drehposition im kurzen Trummbereich

L4

– tatsächliche Auslenkung der Umhüllungslinie (16) in symmetrisch gleicher Drehposition im langen Trummbereich

B

– Abstand der Steuerzahnritzel (11, 12) zueinander, Strecke von A3 zu A4

C

– Übergansbereich der tatsächlichen Auslenkung der Umhüllungslinie (16) im kurzen bzw. im langen Trummbereich

D

– Durchmesser der großen Achse der elliptischen Steuerzahnritzel (11, 12)

DD

– Durchmesser der großen Achse der elliptischen Hauptzahnscheiben (9, 10)

d

– Durchmesser der kleinen Achse der elliptischen Steuerzahnritzel (11, 12)

dd

– Durchmesser der kleinen Achse der elliptischen Hauptzahnscheiben (9, 10)

E

– Maß zum konstruktiven Festlegen der symmetrisch gleichen Drehposition der Hauptzahnscheiben (9, 10)

F

– tatsächliche Länge der Umhüllungslinie (16) in symmetrisch gleicher Drehposition im langen Trummbereich

G

– tatsächliche Länge der Umhüllungslinie (16) in symmetrisch gleicher Drehposition im kurzen Trummbereich

T

– Zahnteilung von Zahnriemen, Zahnkette, Kette (13–15)

n

– Zähnezahl im Trumm

Z1

– Teilkreisdurchmesser der elliptischen Hauptzahnscheiben (9, 10) bezogen auf ein rundes Zahnscheibenrad

Z2

– Teilkreisdurchmesser der elliptischen Steuerzahnscheiben (11, 12) bezogen auf ein rundes Zahnscheibenrad

In the notes to the 8th to 12 the following abbreviations are used:

L1

- distance of the main toothed discs ( 9 . 10 ) to each other, distance from A1 to A2

L2

- Measure for determining the center distances between A3 and A4

L3

- actual deflection of the envelope line ( 16 ) in symmetrically the same rotational position in the short Trummbereich

L4

- actual deflection of the envelope line ( 16 ) in symmetrically the same rotational position in the long Trummbereich

B

- Distance of the control pinions ( 11 . 12 ) to each other, distance from A3 to A4

C

- transition area of the actual deflection of the envelope ( 16 ) in the short or in the long run area

D

Diameter of the major axis of the elliptical timing sprockets ( 11 . 12 )

DD

Diameter of the major axis of the main elliptical pulleys ( 9 . 10 )

d

Diameter of the small axis of the elliptical control pinion 11 . 12 )

dd

Diameter of the minor axis of the main elliptical pulleys ( 9 . 10 )

e

Dimension for structurally determining the symmetrically same rotational position of the main toothed discs ( 9 . 10 )

F

- actual length of the envelope line ( 16 ) in symmetrically the same rotational position in the long Trummbereich

G

- actual length of the envelope line ( 16 ) in symmetrically the same rotational position in the short Trummbereich

T

- tooth pitch of timing belt, tooth chain, chain ( 13 - 15 )

n

- Number of teeth in Trumm

Z1

- pitch circle diameter of the elliptical main pulleys ( 9 . 10 ) based on a round sprocket wheel

Z2

- pitch diameter of the elliptical timing pulleys ( 11 . 12 ) based on a round sprocket wheel

For the default values of the main toothed discs ( 9 . 10 ), Sub-circle ellipse of DD and dd, the sub-circular ellipse of the timing gears is determined as follows: D = Z2 + (L3 + L4) / 4 d = Z2 - (L3 + L4) / 4

This are theoretical values that are still optimized by practical experiments should be.

By the permanent ones Paging between long and short lull during the Rotational movements of the system results from different deflections of L3 and L4 a sense of rotation of the main disks after each rotation around 90 °. This twisting results from the difference measure C, which is mediated by the calculation.

Considering this fact, an envelope drive system alone, then the Drehwinkelverstellposition would not be exactly synchronized within two periods. In the arrangement of two envelopes ( 8th ) according to claim 1 superimposed on this inaccuracy of the rotational angular position so that the errors cancel each other out.

From the 8th to 12 are the individual lengths of the envelope line ( 16 ) and the resulting relationships between the center distances (A1 to A4).

However, to be able to determine the tooth pitch of timing belt and chain, the following should be noted:
There is a direct relationship between the tooth positions of the main toothed discs, the timing sprockets and the number of teeth of toothed belt or chain.

The tooth position of the interlocking elements must be coordinated so that the envelope drive ( 8th ) aligns in one revolution in all four periods to an exactly symmetrical positional image.

The elected number of teeth of the toothed belt or the chain must always be divisible by two be.

If one assigns to this envelope drive system ( 8th ) a second system in parallel and with 90 ° to each other twisted main toothed disks, wherein both systems are interconnected on a common output shaft ( 4 . 5 ), one obtains the doubly achievable angular rotation in the axes of each main toothed disc ( 10 ) of the drive sides.

This described arrangement of the two envelopes ( 8th ) allows the axles (A2) of the driven side and the mirror-image arranged Steuerzahnritzel (A3 or A4) of each Hülltriebes are on the same axes, the drive sides and their same axes (A2) but lie on different waves, the übereingeeschobene waves Apply torque cyclically from the rotary pistons. The control sprockets ( 11 . 12 ) rotate per hull drive system ( 8th ) not synchronous with each other. They are individually mounted in pairs per axis (A3 mirror image A4).

The Advantages of an elliptical envelope drive are that it is quieter and in the power transmission more optimal than the elliptical gear pair, because not just a tooth is engaged.

By positive locking between the elliptical main toothed discs ( 9 . 10 ) and the elliptical steering pinions ( 11 . 12 ) and their position relative to one another in the system and the toothed belt, the toothed chain or chain ( 13 - 15 ) is a power transmission with changing direction of force in Trumm possible or the direction of rotation of the Hülltriebes be changed regardless of the direction of force change.

Claims (6)

Rotary piston machine for use as an internal combustion engine or as a working machine, wherein each two diametrically arranged rotary piston periodically volume variable working chambers in a ring cylinder housing and the rotary pistons are rotationally rigidly connected via nested shafts, the waves individually via a respective envelope ( 8th ) act with elliptical transmission disks on a common output shaft and the elliptical transmission disks of both Hülltriebe ( 8th ) are mounted on the output shaft at 90 ° radially to each other and an envelope drive system ( 8th ) made of elliptical main pulleys ( 9 ; 10 ) of a toothed belt, a toothed chain or a chain ( 13 - 15 ) are enveloped, characterized in that two symmetrically arranged elliptical timing sprockets ( 11 . 12 ) and the two elliptical main sprockets ( 9 . 10 ) through the toothed belt, the toothed chain or the chain ( 13 - 15 ) and within a revolution a constant bias of the toothed belt, the toothed chain or the chain ( 13 - 15 ) guarantee. The rotary piston machine according to claim 1, characterized in that the power transmission with toothed belt, toothed chain or chain ( 13 - 15 ) with a straight pitch across the elliptical main pulleys ( 9 ; 10 ), wherein these rotate in the transmission ratio of 1: 1 on parallel axes (A1, A2) in a fixed center distance to each other and whose teeth have identical features and a divisible by four teeth. The rotary piston machine according to claim 1 and 2, characterized in that the center distance (A1, A2) of the main toothed discs ( 11 . 12 ) is dimensioned in its basic position so that it of toothed belt, chain, chain ( 13 - 15 ) and while the predetermined bias voltage without additional deflection on the Steuerzahnritzel ( 11 . 12 ) reached. The rotary piston machine according to one of claims 1 to 3, characterized in that the control sprockets ( 11 . 12 ) compared to the main toothed discs ( 9 . 10 ) at twice the speed. The rotary piston machine according to one of claims 1 to 4, characterized in that by the rotational position of the elliptical main toothed discs ( 9 . 10 ) and the elliptical timing pinion ( 11 . 12 ) and the rotational position and the symmetrical axis position (A1, A2, A3, A4) to each other, the power transmission for direction-changing torques in Trumm is achieved. The rotary piston machine according to claim 1 to 5, characterized in that the elliptical control sprockets ( 11 . 12 ) in the basic position to the elliptical main toothed discs ( 9 . 10 ) a symmetrical center distance (A3, A4) to the toothed belt, the toothed chain or the chain ( 13 - 15 ) and that this can be adjusted symmetrically by a suitable adjustment between the axes (A3, A4) when worn.