SK6803Y1 - Workspace with rotary moving piston - Google Patents

Abstract

Workspace with rotary moving the piston has the advantages of easier seal of two-side piston ( 4 ) , which executes pendulous motion between dead centre positions is carried out while rotating around one of the sealing lines and slid by its cylindrical surface (51 ) to the cylindrical surfaces of adjacent chambers ( 21a , 22b ) with the same radius R. Workspace has the form of regular tricuspid stars ( 1 ) . Two adjacent chambers ( 3N , 3N +1 ) always have a common center ( S ) of the opposite cylindrical surfaces ( 2Na , 2N +1 b ) with radius R. Connecting line of adjacent chambers ( 31 , 32 ) is the intersection of cylindrical surfaces ( 21b , 22a ) corresponding to a common center ( S ) of the opposite cylindrical surfaces ( 21a , 22b ) . Piston ( 4 ) executes an pendulous , rotary movement with gradually changing the axis of rotation. Its motion is transmitted on the output shaft ( 7 ) . Workspace can be part of an internal combustion engine or pump , blower , compressor or the like. Transmission mechanism ( 6 ) may be in the form of internal gear ( 10 ) with pinion ( 9 ) in the middle of the star ( 1 ) or form shaft with joints or the like.

Description

The invention relates to a new working space and a mechanical assembly of a compression machine, for example an internal combustion engine, a compressor, a pump or a blower with a rotating moving piston, which slides and rotates simultaneously into one of the three interconnected working chambers.

BACKGROUND OF THE INVENTION

Widespread internal combustion engines or reciprocating compressors have been known for more than a century, during which all of its components have been optimized, but the low-efficiency crank gearing itself has been retained as a remnant of the steam engine. The crank mechanism with connecting rods is space-intensive and has problems with balancing higher harmonics.

Attempts at rotary engines are also known, working on the principle of rotating parts, which by their movement create a continuous and cyclic enlargement and reduction of the working space between the cylinder and the piston (e.g., patent publication GB 2242706, AT 510278, WO 2011034451, FR 2778945). The advantages of rotary motors are more balanced operation and more compact dimensions. In addition to the Wankel engine, another type of combustion chamber with a rotating moving piston has not succeeded in practice. The main disadvantage is the problems with sealing the working space, the piston sealing ring has a low service life and causes higher oil consumption. Lubrication of edges, tips and consequently emissions produced during combustion is problematic. Several engines work only with the addition of oil to the prepared fuel mixture.

Individual chambers with different operating states are separated only at the tip, ie the edge of the rotating piston, which places high demands on the seal. The known rotary moving pistons have a triangular shape that divides the interior of the combustion chamber into three changing chambers. Thanks to this geometric relationship, the division into separate chambers is determined by the edges at the tips, at the tops of the rotating piston. Filling of the combustion chamber is in one place, usually without valves, and the filling control, and thus the change in engine power, is different from the investigated methods of filling a conventional internal combustion piston engine.

The essence of the technical solution

The aforementioned drawbacks are substantially eliminated by the working space within the stator block with the rotating moving piston, which is sealed against the front and rear faces, where the front and rear faces define the working space in the direction of the working space axis according to the present invention. the workspace has an internal main shape with a cross-section of a regular three-pointed star, where the star arms with their cylindrical faces with the same radii R enclose three shape and volume identical chambers, and has a double-sided piston formed by two cylindrical faces with the same radius R. represent the dead center of each chamber, and also has three inwardly directed inner edges. These edges are formed by connecting the cylindrical surfaces of adjacent chambers.

Two adjacent chambers each have a common center of opposing cylindrical surfaces with a radius R. The adjoining adjacent cylindrical surfaces of adjacent chambers correspond to a common center of opposed cylindrical surfaces with a radius R.

Inside the three-pointed star is a rotating moving two-sided piston, which has an outer cross-section in the form of a merging of two cylindrical surfaces with radius R, the piston in extreme position, fills one chamber at the head. chambers. The piston extends in the transverse direction along the main axis of the working space, so that it is located just between the front and rear faces.

With this shape, a working space is obtained in which the sealing between the piston and the cylinder is not provided by two narrow sealing strips on the piston tips which slide at the peripheral speed of the piston, which caused the main problem of rotary motors. According to this technical solution, the working space seal is provided on one side by contact of two cylindrical surfaces with the same radius R of the cylindrical surface of the piston and the cylindrical surface of the chamber and also of the seal at the inner edge of the star. On the other hand, the seal is based only on the seal at the inner edge of the star, ie the seal on the connector, but this seal does not move relative to the piston when the piston rotates, because this rotates just around the connector where the center of the opposite cylindrical faces neighboring chambers. With some simplification it can be said that one cylindrical surface of the piston is sealed similarly to the widespread conventional piston engines and the other side is sealed only at the narrow edge, but at this point the original geometry achieves a substantially zero speed of movement, which substantially simplifies claims to delete the location.

SK 6803 Υ1

Inside the piston there is a gear mechanism with a protruding shaft that passes through at least one face. The protruding shaft serves to output power when the working space according to the invention is part of the internal combustion engine, or serves to input mechanical work when the working space is part of the compressor, pump, blower and the like.

During the operating cycle, the piston moves around from one chamber to the next chamber, with its one cylindrical surface sliding along the opposite cylindrical surfaces of one and the next chamber, and at the same time rotates around a common center of these surfaces. Thus, in a single working movement, the piston essentially rotates about the inner edge of the star, which is the junction of one and the subsequent chamber, with the piston sliding with a cylindrical surface over a common cylindrical surface of these chambers having the same radius as the piston side. After the end of dead center, the point around which the piston rotates changes, and the new point of rotation of the piston is again the connection of the adjacent chambers, but now the next pair of adjacent chambers. Thus, the movement of the piston is repeated around, thus the piston performs a rotational movement, but this progressively around the three centers of rotation, so that the movement of the piston is essentially swinging with three rotations around three different points. However, the rotation, in which two cylindrical surfaces of the same radius are slipping, takes advantage of the movement of the linear movement of the piston in the crank mechanisms, while at the same time the transmission of the rotation to the output shaft does not have to be a crank mechanism.

Each chamber will have means for changing the working medium. The means for changing the working medium will comprise at least two valves for each chamber. If the working space is part of the internal combustion engine, the means for changing the working medium will comprise, for example, an intake and exhaust valve. The valves can be controlled by classical mechanical distribution or by hydraulic system with electronic control.

In the basic embodiment, the piston will have a width of size R in cross-section. In a modified version, the cross-sectional width of the piston may be less than R, then the line of contiguous cylindrical surfaces will be rounded. The radius of this rounding will correspond to the difference between the R-value and the cross-sectional width of the piston. In such a geometric relationship, the piston will roll along a rounded link.

The design of the seal connector may also be of a different design. For example, a pivot sealing lip may be provided in the connector line. This will rotate, respectively. rocking around the center S of the cylindrical surfaces. The pivoting sealing strip may have a radius of sealing side with a radius R or it may have two sealing sides with a radius R. When the piston passes through dead center, the pivoting sealing strip on the opposite side (opposite dead center) is rotated.

The working space according to this utility model finds its application not only in internal combustion engines (positive ignition or compression ignition engines), but also in internal combustion engines (eg Stirling type). The working space can also be used in machines to convert the pressure energy of media (water, steam, oil, gases) into the mechanical energy of a rotating shaft or vice versa. Since one chamber is always in the unchanged position during operation, fast-running fuel combustion and fuel preparation processes can be better optimized.

The transmission mechanism may consist of a pinion having an axis in the center of the three-pointed star, i.e. an axis in the main axis of the workspace. In this case, an internal toothing in the elliptically shaped piston cavity adjoins the pinion, the pinion being connected to a shaft extending from the stator block. To avoid tooth interference near the dead center between the pinion and the internal toothing of the piston, the toothing will need to have helical teeth. Depending on the toothing module chosen, the angle may be relatively large, exceeding the angles of commonly used gears. Such a toothing will generate high axial forces, in which case it will be convenient if the toothing is an arrowhead, thereby eliminating the axial reactions of the toothing within the toothing force.

In another embodiment, the transmission mechanism may consist of a hydraulic pump. In such a case, the internal combustion engine may be used to generate oil pressure, for example, for hydrostatic engines in the wheels of a working machine. Such a connection will increase the overall efficiency of the hitherto used engines of the internal combustion engine + gear oil pump or piston oil pump type. Many hitherto known aggregates used a conventional internal combustion engine with reciprocating pistons, where the pressure energy from the flue gas first changed to rotational energy through the crank mechanism and subsequently the rotary energy to oil pressure was changed via the connected hydraulic pump. At the same time, such an oil pump often had a piston form again, where mechanical losses occurred in a crank or similar mechanism.

In another embodiment, the transmission mechanism may take the form of a fixed, engageable connection of the projecting shaft to the rotary piston. In such a case, the protruding shaft is not mounted within the stator block in a fixed-axis bearing, but the face has an opening larger than the shaft cross-section or has an opening shaped according to the travel path of the shaft. At the same time, at least one face can also be provided with a pinion which guides the piston from the inside of the piston along a respective path of movement. The protruding shaft may subsequently be connected via joints, for example, via two cross or homokinetic joints, to a gearbox or other aggregate where the joints eliminate the sliding component of the shaft movement.

There may also be applications where the sliding component in the shaft path does not present a disadvantage, for example, the protruding shaft may be rigidly connected to a disc on the periphery of which the sliding components are relatively

EN 6803 Υ1 less than in rotary motion. Such a roll could be, for example, an alternator or dynamo rotor, where the wound coils would not be placed around the outer periphery of the roll, but would be located opposite the surface of the roll. The spool arrangement would preferably correspond to the edge path of the disc.

In another arrangement, the joint or joints eliminating the translational movement component of the rotary piston could be located directly inside the piston. The protruding shaft would extend through one face of the stator block and would then be connected via a joint to the center of the rotating piston, preferably at the opposite end of the piston as the shaft passes through the face of the stator block. The longer (in the direction of the main axis of the working space) the piston, the smaller the angular displacements will be processed by the joint. On the other hand, the face can have a guide pinion, a guide wheel which, without toothing and thus without the risk of tooth interference, can define the path of movement of the rotary piston. The piston will have an elliptical guide track formed in the respective zone, along which the guide wheel will roll.

The new workspace solution also provides additional detail solutions, based on the new shape of the workspace and the rotating piston. This foundation, which is based on the basic design, can be followed by new solutions of various machines that need a variable volume of working chambers.

If the working space is part of the internal combustion engine, a rotary flywheel will also be attached to the projecting shaft and the main shape of the working space may be complemented by a cavity-shaped compression space. The cavity will be in the piston or cylindrical face of the chamber.

The compression chamber may have an opening cavity on one cylindrical surface of the star arm and a second cavity on the opposite cylindrical surface of the star arm, which may be connected by a channel passing through the line of the star arm tip.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention is explained in more detail with the help of Figures 1 to 10. The particular details of the aggregates as well as their sizes are merely illustrative and are not to be construed as restricting the scope of protection.

Figure 1 shows the geometric context of the main shape of the workspace without an inserted piston, which is shown separately at the bottom of the figure. A solution is shown where the cross-sectional width of the piston coincides with the radius of curvature of the cylindrical surfaces.

Fig. 2 shows a working space with a plurality of plunger moving from the first dead center to the second chamber. Only the main workspace shape without stator block and other details is shown.

Figure 3 shows the piston at dead center where a pinion and stator block can be seen.

Figure 4 shows the movement of the piston as the gas expands in the respective combustion chamber.

Figure 5 shows a solution with swinging sealing strips.

The graphs of Figures 6 and 7 show the pressure and torque characteristics. The graph in Figure 6 is for a conventional piston engine with a crank gear and the bottom graph of Figure 7 corresponds to the solution of the invention. The dotted line indicates the gas pressure in the expansion chamber, the solid line indicates the torque. Values of values during one working time are displayed.

Figure 8 shows a side cross-sectional view of the stator block and the piston, where the piston is connected to the dynamo disc by a shaft extending through the rear face of the stator block.

Figure 9 is a side cross-sectional view of the stator block and the piston, where the transmission mechanism comprises two cross-joints.

Figure 10 shows the geometric context of the main shape of the workspace without an inserted piston, which is separately shown at the bottom of the figure in an arrangement where the width of the piston in cross-section is less than the radius R.

EXAMPLES

Example 1

In this example of Figures 1, 2, 3, 4, 7, the working space is located in an internal combustion engine. The working space is formed inside the stator block, which is closed on both sides by the front face 81 and the rear face 82. These faces 81, 82 define the working space in the direction of the axis of the working space. It has a cross-sectional shape of a regular three-pointed star 1, wherein each arm 2 of the star 1 with its two cylindrical surfaces 21a, 21b. 22a, 22b, 23a, 23b delimits three chambers 31, 32, 33 of equal shape and volume. All cylindrical surfaces 21a. 21b, 22a. 22b, 23a, 23 have the same radius R which coincides along the entire axis of the main space.

The pair of adjacent chambers 31, 32 has a common rounding center S of opposite cylindrical surfaces 21a, 22b. The junction of adjacent chambers 31, 32 is formed at the intersection of adjacent cylindrical surfaces 21b, 22a. these

SK 6803 Υ1 relations apply to all pairs, since star 1 is regular and symmetrical.

Inside the three-pointed star 1 there is a rotationally moving two-sided piston 4 whose length in the direction of the main axis of the working space is the same as the length of the cavity in the stator block and thus the piston 4 fills the inside of the stator block chamber 3 from the front face 81 to the rear 82. The piston 4 has an outer cross-section in the form of a merging of two cylindrical surfaces 51, 52 with a radius R. This is the same radius R as the rounded cylindrical surfaces 21a. 21b, 22a, 22b, 23a, 23b. The piston 4 in the extreme position, at the dead center of Figure 3, fills one chamber 33. The head of the piston 4 at the dead center extends from the tip of the chamber 33 to the junction of the two other chambers 31, 32. In this example, the cross-sectional width of the piston 4 is equal to the radius The length of one cylindrical surface 51, 52 is 2nR / 3. The length of each cylindrical surface 21a, 21b. 22a, 22b, 23a, 23b is xR / 3.

Inside the piston 4 is a gear mechanism 6 with a pinion 9, which is connected to a protruding shaft 7. This extends through the rear face 82 out of the stator block. The toothing of the pinion 9 and the internal toothing 10 is oblique. To avoid tooth interference, the toothing has high-pitched arrow teeth where the axial forces are eliminated by the interaction within the toothing.

In Figure 3, the piston 4 is at the dead center where it has compressed the fuel mixture into the cavity space. Each chamber 31, 32, 33 has a cavity 11 in which a spark plug (not shown) is also located. After igniting the fuel mixture, the piston 4 moves as shown in Figure 4 so that its second tip enters the chamber 32. By expanding the gases in the chamber 33, work is carried out which is transmitted to the pinion by means of internal toothing 10.

9. In the duty cycle, the piston 4 moves from one chamber 3 to the next chamber 3 (e.g., from 33 to 31), with its one cylindrical surface 52 sliding along the common cylindrical surface 23b, 22a of the chambers and 32, rotates around the common center S of the cylindrical surfaces 23b, 22a of the respective chambers 33 and 32.

Each chamber 31, 32, 33 has means for changing the working medium, i.e. for filling the chambers 31, 32, 33 with the fuel mixture and blowing out the flue gas. The output torque during gas expansion is substantially linearly dependent on the flue gas pressure of Figure 7.

After moving the piston 4 in this example from chamber 33 to chamber 32, the piston further moves into chamber 31, at this stage the volume of chamber 31 remains unchanged, allowing better combustion of the gases. In principle, each chamber between phase expansion and compression has one phase successively without changes in volume. Such inheritance resulting from the new geometry allows better blend preparation under relatively stable conditions and also improves control of emission processes.

Example 2

In this example of Figures 1, 2, 5, 7, a new workspace solution is used similar to Example 1 in an internal combustion engine. Swivel sealing strips 12 are mounted in the lines of the S-joints. These are rotatably inserted into the front face 81 and rear face 82, performing only a rocking movement when the piston 4 is moved. The use of the swivel sealing strips 12 increases the area on which the cylindrical surface 51 is sealed. 52nd

Example 3

In this example of Figures 1, 2, 7, 8, the working space is utilized in an external combustion engine. The chambers 31, 32, 33 are successively supplied with expanding gas, which moves the piston 4. The output of the machine is controlled by timing the valves in the chambers 31, 32, 33.

A protruding shaft 7 is interlocked in the piston 4, which in this example constitutes a gear mechanism 6. The other end of the protruding shaft 7 carries a disc that rotates between the windings of the alternator. The movement of the disc has the nature of rotation and at the same time of movement according to the displacement component of the center of the piston 4. The windings are distributed in the path of the circumference of the disc. With this arrangement, there is no need to eliminate the sliding component of the piston movement at all

4th

Example 4

In this example of Figures 1, 2, 7, 9, the working space is part of the hydraulic pump. The piston 4 is driven by a protruding shaft 7 which extends through the center of the rear face 82 and is connected to the center of the piston 4 by means of two universal joints. This connection forms the transmission mechanism 6.

Example 5

The working space of Figure 10 is part of the blower. It differs from the previous geometry in that the piston 4 has a width less than the radius R of the curvature of the cylindrical surfaces 51, 52. The transition between the chambers 31, 32, 33 is then rounded and the piston 4 rolls along this cylindrical surface. . The radius of curvature is proportional to the difference between the radius R and the width of the piston 4 in cross-section.

SK 6803 Υ1

Industrial usability

Industrial applicability is obvious. According to this technical solution, it is possible to industrially and repeatedly produce and use the working space of the machine with varying volume of working chambers, which are limited by the new shape of combustion chambers and double-sided piston. The described geometrical arrangement is the basis for further development in the areas of various machines with varying workspace volume. Therefore, the listing of different sealing methods, different transmission mechanisms or different filling options should only be considered as examples which may be subject to further development.

PATENT CLAIMS

Claims (15)

A working space with a rotating moving piston inside a stator block, wherein the piston is sealed against the front and rear faces of the stator block, wherein the front and rear faces delimit the working space in the direction of the main axis of the working space, characterized in that it has an internal a cross-section of a regular three-pointed star (1) wherein each star arm (2) with its two cylindrical faces (21a, 21b, 22a, 22b, 23a, 23b) with the same radii R delimits three chambers of the same shape and volume (31, 32) 33), each pair of adjacent chambers (3N, 3N + 1) has a common center (S) of opposed cylindrical surfaces (2Na, 2N + 1b) with radius R, a junction of adjacent chambers (3N, 3N + 1) at the intersection of cylindrical surfaces ( 2Nb, 2N + 1a) of adjacent chambers (3N, 3N + 1) correspond to the common center (S) of opposite cylindrical surfaces (2Na, 2N + 1b) with radius R, inside the three-pointed star (1) is a rotating moving double-sided piston (4) which has a cross section in the shape of the merging of two cylindrical surfaces (51, 52) with the radius R, wherein the piston choke (4) is equal to or less than the distance of the chamber tip (3) from the opposite connecting line; energy cycle of the working cycle, with the working cycle moving the piston (4) from one chamber (3N) to the next chamber (3N + 1), sliding on its common cylindrical surface (2Na, 22N + 1b) one and successive chambers (3N, 3N + 1) while rotating around a common center (S) of cylindrical surfaces (2Na, 22N + 1b) of one chamber (3N) and subsequent chambers (3N + 1), and each chamber ( 31, 32, 33) has means for changing the working medium, where the index N expresses the chamber number, after the number N = 3, the index N + 1 starts again cyclically from 1. Working space inside a rotary-moving piston stator block according to claim 1, characterized in that the width of the piston (4) corresponds to the radius R of the cylindrical surfaces (51, 52). Working space within a rotary moving piston stator block according to claim 1, characterized in that the width of the piston (4) is smaller than the radius R of the cylindrical surfaces (51, 52) and the link is rounded, the radius of curvature of the link corresponds to the difference between the radius size R and the width of the piston (4). Working space within a rotary moving piston stator block according to any one of claims 1 to 3, characterized in that the transmission mechanism (6) comprises a projecting shaft (7) which extends through at least one face (81, 82). Working space within a rotary moving piston stator block according to any one of claims 1 to 4, characterized in that the transmission mechanism (6) consists of a toothed pinion (9) with an axis in the main axis of the working space, adjacent to the pinion (9). an internal toothing (10) in an elliptically shaped interior of the piston (4), the pinion (9) being connected to a shaft (7) extending from the stator block. The working space inside the rotary-moving piston stator block according to claim 5, characterized in that the toothing of the pinion (9) and the internal toothing (10) is inclined, preferably arrow-shaped. Working space within a rotary-moving piston stator block according to any one of claims 1 to 3, characterized in that the transmission mechanism (6) consists of a hydraulic pump. Working space within a rotary moving piston stator block according to any one of claims 1 to 4, characterized in that the transmission mechanism (6) comprises a protruding shaft (7) in contact with the center of the piston (4), the protruding shaft (7). ) passes through an aperture in at least one face (81, 82) of the stator block and the aperture has a size at least in the form of a path of the projecting shaft (7). Working space within a rotary-moving piston stator block according to any one of claims 1 to 4, characterized in that the protruding shaft (7) is connected to the center of the piston (4) by at least one joint, the protruding shaft (7) being rotatably mounted in at least one face (81, 82) in a major axis of the working space. SK 6803 Υί A working space within a rotary moving piston stator block according to any one of claims 1 to 9, characterized in that a pivot sealing lip (12) is arranged in the line of the coupling. Working space inside a rotary moving piston stator block according to any one of claims 1 to 10, characterized in that it is part of an internal or external combustion internal combustion engine, which also includes a rotary flywheel connected to the projecting shaft (7), the main shape being The working space is supplemented by a compression space in the piston (4) and / or in each chamber (31, 32, 33). The working space within a rotary moving piston stator block according to claim 11, characterized in that the compression space is formed by a cavity (11) on at least one cylindrical surface (21a, 21b, 22a, 22b, 23a, 23b) of each arm (11). 21, 22, 23). Working space inside a rotary moving piston stator block according to any one of claims 1 to 10, characterized in that it is part of a machine for converting the mechanical energy supplied to the projecting shaft (7) into the dynamic and / or pressure energy of the medium supplied to the stator. block. Working space within a rotary-moving piston stator block according to any one of claims 1 to 13, characterized in that the means for changing the working medium are in the form of valves near the tips of the chambers (31, 32, 33), preferably the valves are operated by hydraulic and / or electrical distribution. A working space within a stator block with a rotating moving piston according to any one of claims 8, 11 to 14, characterized in that the piston (4) is connected to a rotor moving between the windings for generating electricity, the windings being mounted on the sides of the rotor. , which has the shape of a flat disc.