WO2010094510A1

WO2010094510A1 - Synchronization gearbox for a multi-axle rotating piston machine

Info

Publication number: WO2010094510A1
Application number: PCT/EP2010/001137
Authority: WO
Inventors: Gangolf Jobb
Original assignee: Gangolf Jobb
Priority date: 2009-02-23
Filing date: 2010-02-23
Publication date: 2010-08-26
Also published as: DE102009010163A1; EP2399044A1

Abstract

The invention relates to a gearbox a) for synchronizing a plurality of rotatably mounted shafts (1) that are arranged in parallel to each other, a1) wherein the number and the arrangement of the shafts (1) is such that each shaft axis runs through a corner of at least one imaginary square, the corners of which are defined by a total of four shaft axes, which hereinafter are referred to as a quad, perpendicular to the square, a2) such that a2a) at a total of four shafts one quad is present, a2b) at a total of six shafts two quads are present, a2c) at a total of eight shafts three quads are present, a2d) and so forth; b) the gearbox has a first gearbox plane and a second gearbox plane that is axially spaced from the first plane; c) the gearbox comprises the following components in each gearbox plane: c1) one eccentric disk (2) per shaft (1), which is connected to said shaft in a rotatably fixed manner, c2) four thrust disks (3) per quad, c3) and one support disk (4) per quad, c4) wherein the four thrust disks (3) are forced between the support disk (4) and four eccentric disks (2) per quad such that the thrust disks (3) can roll both on the eccentric disks (2) and on the support disk (4); d) all eccentric disks (2) having the same dimensions; e) all thrust disks (3) having the same dimensions; f) all support disks (4) having the same dimensions; g) and wherein the eccentric disks of the first gearbox plane are arranged on the respective shafts (1) phase-shifted by 180° with respect to the eccentric disks of the second gearbox plane.

Description

SYNCHRONIZING TRIANGLE FOR A MULTI-HANDED TURNING PISTON MACHINE

The object of this invention is generally an improved multi-axis rotary engine e.g. according to US2410341, FR1199521, DE19738132 and DE102006018183. Despite their constructive simplicity, their high power density and their great smoothness, these rotary lobe array machines have not been able to prevail so far because, inter alia, the coupling of the rotor shafts has not yet been technically achieved satisfactorily. Promising applications would be in the use of renewable energy.

The aim of this invention is specifically the cost-effective, backlash-free and low-friction rotary synchronization of a shaft array, ie of regularly arranged, axis-parallel waves of a rotary piston machine.

To date, three ways of coupling the shafts have been proposed: the first are gears, the second a crank mechanism, the third an electronic gear.

Gears such as in US2410341 are not only expensive to manufacture, but can cause sealing problems due to their backlash in the rotary engines. Another disadvantage is their wear, their friction, their

Noise. Of advantage are their small footprint and the non-existing imbalance.

The coupling with cranks and a connecting rod plate as in FR1199521 is basically free of play, and there is also here because of the special number and arrangement of the cranks also no dead center, as known from a connecting rod between only two cranks ago. However, the connecting rod plate generates a considerable imbalance even at moderate speed with the known disadvantages such as vibration, increased wear and large Forces that bend and tug on the waves, causing seal problems as well. Even balancing the imbalance with counterweights would definitely put a heavy strain on the bearings of the plate.

In the electronic transmission as in DE19738132 each shaft is connected to an electric motor and electronically controlled in its rotational movement. Basically, such a system consumes energy, which corresponds to high friction. The effort is enormous and the engine power is limited. In case of failure and shutdown of the control, the rotary pistons rotate uncontrollably and can damage each other.

The present invention avoids the aforementioned disadvantages of the prior art and advantageously continues to form the latter.

The invention is a so-called push-pulley transmission, as shown in Figures 1 and 2. It roughly corresponds to the above-mentioned crank mechanism with connecting rod, but the cranks are inventively replaced by eccentric discs, and the connecting rod plate by a special arrangement of rolling bodies, which are constrained between the eccentric discs.

The power transmission between the eccentric discs is purely sliding over the constrained rolling elements. FIG. 3 shows the lines of force in a first gear plane, along which the forces act. For the indispensable transmission also pulling forces a similar, second transmission plane is required according to the invention, which is rotated relative to the first 180 ° and coupled via the common waves with this, so that the pushing forces of the second level are equivalent to apparent pulling forces of the first , The lines of force in particular have components in the direction of each connecting line between the center axes of adjacent eccentric discs, so that one can replace the constrained rolling elements in thought by push rods that exist between each two adjacent eccentric discs, or just by a connecting rod. It can be deduced from this that the eccentric discs are coupled completely and without dead points in their rotational movement, and consequently also the rotatably connected with the eccentric shafts.

Shape and position of the rolling bodies are inventively chosen so that they can not move relative to each other, not even under the action of force. Between the synchronously rotating eccentric discs is a formunveränderlicher gap, in the four corners are so-called thrust washers. A so-called support plate in the middle of the gap prevents the thrust washers from leaving their corners. The thrust washers are rollingly supported on the eccentric discs, and the support discs are rollingly supported on the thrust washers. Each thrust washer is stably supported at three points in cross section, and each thrust washer at four. The space between the eccentric discs is thus stably supported by thrust and support discs and can not be further reduced.

Eccentric discs can only rotate about their shaft axes. Turning into a supported space is not possible. But unscrewing is also not possible, because this would have to turn the coupled, complementary eccentric discs of the other gear plane in a local space inside. Since eccentric discs can neither turn towards a gap nor away from one, the shape of a gap is fixed, the thrust and support discs are stably compressed in cross-section, and it is no rotation of the eccentric except a synchronous possible.

In the axial direction, a position stabilization constrained rolling body according to the invention is achieved in that the rolling surfaces of both the eccentric and the support disks are provided with circumferential grooves, and the rolling surfaces of the thrust washers with mating, circumferential bulges. The rolling elements are thus positively interlocked in the axial direction and can not leave their respective gear plane. Their tilting is prevented by a sufficient width of the rolling surfaces.

The transmission is stable only in cooperation with its rotatably mounted shafts. The positive joining of the rolling elements must therefore take place before their position is determined by the waves. To facilitate assembly, therefore, the components of a transmission level are first assembled according to the invention in the correct position on a table top and fixed in a special holder. With this bracket they are then all at the same time plugged onto the already stored waves, and finally the bracket is removed again.

The waves are expediently designed as profile shafts, preferably as square shafts, and the eccentric discs are provided with matching holes. According to the eccentric discs and other elements are placed on the waves and positioned there with screw wedges and spacers exactly.

With the present invention, the following advantages are achieved.

In contrast to the crank mechanism with connecting rod plate, the pushing disk gear is virtually unbalance-free. The imbalances of the complementary transmission planes are almost exactly the same, if their axial distance is small. Instead of a heavy connecting rod plate with strong bearings, there are only small rings between eccentric discs, which are lighter overall than any known connecting rod, and also roll on relatively large radii, so with less friction than the best ball bearings. Since all the thrust forces are purely parallel to the transmission plane, and not about bending stressed, laterally projecting crank pin, the thrust washer can transmit a lot of power with little material. Due to its lightness, its stability and its balanced mass distribution, the thrust-plate transmission can achieve significantly higher speeds than any crank mechanism.

In contrast to the gear mechanism requires a thrust washer gear no play, so that one must not admit such synonymous in the interpretation of about rotary piston, which would affect their tightness, of course. On the contrary, it would even be possible to manufacture the rolling elements elastically with a negative clearance and to assemble them under tension, so that they rebound, for example, when the waves move apart due to the heat. The thrust washer gear no teeth hit each other, which would thereby generate noise and vibration, tiny bending vibrations on shafts and rotary pistons, which one might have to consider in the latter by further play addition. There is hardly any wear.

A lubrication of the rolling surfaces is, if necessary, very simple: applied a small drop of lubricant at one point of a rolling surface spreads evenly after a few turns on all rolling surfaces of a transmission plane.

The push-pulley transmission is extremely cost-effective. The production of his few components succeeds with less technical equipment. It is enough lathe and drill, and a Räumveresse for the square holes. The production can therefore be carried out especially in smaller companies.

The drawings are explained in more detail below.

Figures 1 and 2 show perspective views of the Schubscheibengetriebes, the latter in section. The illustrated embodiment comprises rotatably mounted shafts (1) with square profile, placed thereon eccentric discs (2), thrust washers (3), support discs (4), also ball bearing (5) and screw wedges (6). There are two gear levels, which are rotated by 180 ° from each other. Highlighted on average are the circumferential grooves on the eccentric discs and support discs, as well as the matching bulge on the thrust washers, which stabilize the transmission in the axial direction.

FIG. 3 shows the plan view of a first transmission plane with lines of force. The sketch includes shafts (1), eccentric discs (2), thrust washers (3), carrier discs (4). The straight lines symbolize forces acting between the central axes of the rolling elements.

Claims

claims

1. gear for synchronizing a wave array,

that is, a plurality of rotatably mounted waves, the axes of rotation of which run along integer and contiguous Cartesian xy coordinates in the z-direction, but here each wave must belong to a group of four, each with a wave on the xy coordinates {i, j}, { i + 1, j}, {i + 1, j + 1}, and {i, j + 1}, for each of a set of integer and contiguous {i, j} pairs that determines the shape of the array,

comprising the following components, which are all rolling elements with z-parallel roll axis and each one of at least two xy-parallel transmission planes k with z coordinate z _k belong, and whose xy positions depend on a phase φ, namely

so-called eccentric disks, with a radius r _E , _k <1/2 at the height z _k , with an axis of rotation at one of the xy coordinates {i, j}, {i + l, j}, {i + l, j + l} or {i, j + l}, with a rotationally fixed connection to the shaft located there, with a roll axis which is opposite the axis of rotation about the xy vector V _k : = {e _k cos (<p + m _k ) , e _k sin (φ + m _k )} is shifted, with a mounting angle 0 ≤ m _k <360 °, and with an eccentricity parameter 0 ≤ e _k <R _{E / k} ,

so-called thrust washers, with a radius r _{S / k} <1/2 at the height z _k , with a rotation and roll axis at one of the xy coordinates {i + 1/2, j + h _k } + V _k , { i + lh _k , j + 1/2} + V _k , {i + 1/2, j + lh _k } + V _k or {i + h _k , j + l / 2} + V _k , with h _k : = ((r _{E / k} + r _s , _k ) ² -l / 4) ^1/2 , so-called support disks, with a radius

^ _L , k = l / 2-h _k -r _s , _k at the height z _k , with a rotation and

Roll axis at one of the xy coordinates {i + 1/2, j + 1/2} + V _k ,

characterized,

that all of the above components exist at all possible positions,

that all thrust washers are stably wedged between their adjacent eccentric and support disks, these touch and roll on this, and in particular can transmit shear forces,

that all support disks are stably wedged between the thrust washers adjacent to them, touch them and roll on them, and in particular can transmit thrust forces,

that eccentric discs do not touch each other,

eccentric discs and discs do not touch each other,

the totality of all mounting angles m _k divides the full angle such that no partial angle is greater than 180 °.

2. Transmission according to claim 1, wherein the number of transmission planes is 2 and the two mounting angles differ by 180 °.

3. Transmission according to claim 1 or 2, wherein all transmission levels are constructed of the same components.

4. Transmission according to one of the preceding claims, wherein the rolling surfaces of the rolling bodies are provided with complementary circumferential profiles, so that slipping of the rolling elements, in particular the thrust and support disks, in the z-direction is not possible.

5. Transmission according to one of the preceding claims, wherein the waves at least partially or in places have a non-circular cross section, which facilitates the rotationally fixed mounting of eccentric discs and other elements on the waves, provided that they are provided with a form fit to the shaft cross-section hole.

6. Transmission according to one of the preceding claims, wherein the eccentric discs and other elements are positioned and held by means of screw wedges and spacers on and along the shaft.

7. Transmission according to one of the preceding claims, wherein the rolling body for weight savings, but also to achieve a certain elasticity

Material recesses provided, or specially designed ring-shaped.

8. Transmission according to one of the preceding claims, wherein at least one of the rolling elements is exceptionally elastic, so that the transmission can absorb torque shocks, but also compensate for the deformation of a machine housing, which is caused by thermal expansion or by external forces.

9. Transmission according to one of the preceding claims, wherein at least one exceptionally elastic rolling body is installed slightly compressed, so that this at an enlargement of the shaft spacing approximately by Thermal expansion nachfedert and guaranteed in this case, the play-free coupling of the waves.

10. Transmission according to one of the preceding claims, wherein this particular synchronized the rotational movement of rotary piston of a rotary piston engine, such as a gas compressor, a gas pressure motor, a heat engine, a heat pump.

11. A method for facilitating the mounting of a transmission according to one of the preceding claims, wherein a plurality of transmission components, such as all components of a transmission plane, initially assembled in the correct position and then fixed in a holder to put them all at the same time with the support on the waves, and then the bracket is removed again.

12 variant of a transmission according to one of the preceding claims, wherein the waves are arranged differently regularly in the x-y plane, with a correspondingly different arrangement of constrained rolling elements between the eccentric discs.

13. A variant of a transmission according to the preceding claim, wherein each wave belongs to a group of three, each with three waves at the tips of an equilateral triangle in the x-y plane, and with a single, constrained thrust washer between the three eccentric discs.