WO1995012754A1

WO1995012754A1 - Piston engine

Info

Publication number: WO1995012754A1
Application number: PCT/EP1994/003587
Authority: WO
Inventors: Max Liebich
Original assignee: Max Liebich
Priority date: 1993-11-04
Filing date: 1994-10-31
Publication date: 1995-05-11
Also published as: EP0727014A1; DE4337668C1

Abstract

In a piston engine with at least one cylinder rotating about a first shaft and a piston reciprocating in a straight line therein which is connected to a crank drive which has a drive component rotating about a second shaft, in which the first and second shafts have axes running mutually parallel but staggered, the piston (3; 130) is connected to a piston rod (42; 141) extending outside the cylinder (4; 120) in the direction of movement of the piston (3; 130) which is connected via a restricted guidance means (44, 45; 144, 145) to a component (42; 142) rotating about the output shaft (43; 143) of the crank drive (4). The restricted guidance means (44, 45; 144, 145) permit solely a relative movement between the component (42; 142) and the piston rod (41; 143) transversely to their longitudinal axes and thus a parallel movement to a plane (E) running through the axis (B) of the output shaft (43; 143) of the crank drive (4) and intersecting the direction of movement of the restricted guidance means at right-angles.

Description

Piston machine

The invention relates to a piston machine of the type mentioned in the preamble of claim 1.

Such piston machines with rotating cylinders, in particular in the form of internal combustion engines, have been known for a long time (DE-PS 194 107). In piston engines of this type, the cylinder, which may comprise, for example, one or more combustion chambers, rotates around a first axis, while the piston or pistons arranged in the cylinder rotate around a second axis which runs parallel to the first axis, but to a certain extent with respect to the latter Amount is offset. A problem with such piston machines is obviously to be seen in the fact that the power transmission from the pistons to the crank mechanism does not lead to a uniform angular velocity of this crank mechanism and / or the rotating pistons. For this reason, attempts have already been made to remedy this by a type of differential gear, but this is very complex and cannot completely prevent lateral forces acting on the piston or pistons. Another problem with such piston machines with rotating cylinders is, on the one hand, the valve control used here and the supply and discharge of the combustion mixture and the exhaust gases. It can thus be stated that although the basic idea of the offset shafts for a piston machine with a rotating cylinder is known, no solution has been found to develop such a piston machine into a functional internal combustion engine. So far unresolved design features are in particular:

- the uneven piston movements / piston speeds caused by the shaft offset and thus no vibration-free, smooth running, especially at high speeds, the supply of the combustion mixture into the rotary cylinder,

- the discharge of the exhaust gases from the rotary cylinder.

The present invention has for its object to provide a piston machine of the type mentioned, which allows a sensible application of the principle of the rotating cylinder, which is expedient in terms of unbalanced mass forces, with a simple structure.

This object is achieved by the features specified in claim 1.

Advantageous refinements and developments of the invention result from the subclaims.

The configuration of the piston machine according to the invention results in a simple configuration of the crank mechanism without lateral forces being exerted on the piston or pistons.

Because cylinders and pistons describe an exact circular movement, without any unbalanced mass forces occurring, much higher speeds are possible than is the case with known piston machines. This enables high performance to be achieved with a small cubic capacity.

According to a preferred embodiment of the invention, the shaft around which the cylinder rotates is at least partially designed as a hollow shaft connected to the cylinder, in which the inlet and outlet lines of the cylinder run and which, together with a stationary casing tube, form a rotary slide valve arrangement. The inlet and outlet lines have corresponding radial sections in the hollow shaft which open on the outer circumference of the hollow shaft and come into alignment with openings in the casing tube during rotation at predetermined times of the work cycle. This results in a further control possibility for the inlet and outlet times, so that these are not only controlled by the piston movement, but also by a combination of the piston movement and the rotation of the rotary slide valve arrangement, which can be correspondingly adapted to one another.

In this way, it is possible to select the control so that at the beginning of the release of the exhaust gas outlet opening of the cylinder by the piston, the outlet opening in the rotary slide valve arrangement is already fully open, so that the exhaust gas can escape unhindered. When the outlet opening in the cylinder begins to close, that is to say at the start of the new compression stroke, the outlet opening in the rotary slide valve arrangement is already completely closed.

For sealing between the hollow shaft and the tubular casing, sealing rings in the manner of piston rings are preferably provided in corresponding grooves in the hollow pipe at an angle to the longitudinal axis of the hollow pipe. Due to the inclined position of the sealing rings, they slide overlapping over the entire inner surface of the fixed casing tube and at the same time separate the opening that opens out on the outer circumference of the hollow shaft in a well-sealed manner.

With this construction, it is possible to carry out the supply and discharge of the combustion mixture or the exhaust gases in a simple manner without the need for complicated valve arrangements and / or associated actuating mechanisms.

According to a preferred embodiment of the invention, the cylinder is divided into three rooms, of which the two outer work spaces form, while the middle space forms a load space. In this respect, this construction represents a doubling of the internal combustion engine working with a stationary cylinder according to the principles as described in DE-Al-43 37 670 by the same applicant from the same filing date. The description of these further patent applications This reference is hereby incorporated in full. Since the supercharger piston has a larger diameter, it can be connected to the crank mechanism via an eccentrically arranged additional piston rod which extends with its ends out of the cylinder.

According to a further simplified embodiment of the invention, the cylinder forms a single work space in which a piston which is closed at both ends is arranged and which divides the work space into a combustion space and an intake and pre-compression space.

This results in a very simple internal combustion engine that can run at high speed due to the lack of unbalanced mass forces and has a high workload compared to its space requirement.

In this case, but also in the case of the use of two working pistons and a supercharging piston, the cylinder can have a slot which extends through its jacket wall and is covered by this in any position of the piston or one of the pistons, and extends through this slot a piston pin which is connected to a piston rod arranged outside the cylinder, the ends of which are connected to the crank mechanism.

Embodiments of the invention are explained in more detail below with reference to the drawings.

The drawing shows:

1 is a schematic sectional view through a first embodiment of the piston engine in the form of an internal combustion engine,

2 shows a section along the line II-II of FIG. 1, 3 shows a first exemplary embodiment of the sliding connection between the piston rod and the flywheel of the crank mechanism,

4 shows a further embodiment of a sliding connection between the piston rod and the flywheel of the crank mechanism,

Fig. 5 shows a second embodiment of the piston engine in the form of an internal combustion engine with a single cylinder.

1 and 5 show a first and a second embodiment of the piston machine with a rotating cylinder, the embodiment according to FIG. 5 being a simplified embodiment with regard to the piston

Represents cylinder arrangement and shows another embodiment of the output from the piston to the crank mechanism, which can also be used in the embodiment of FIG. 1.

In the embodiment according to FIG. 1, the cylinder designated overall by 2 is subdivided into first and second working spaces 21 and 22 and a loading space 23 arranged between them, in which first and second working pistons 31 and 32 and a loading piston 33 are arranged displaceably are connected to each other via a common piston rod 34. The loader space 23 and thus the loader piston are arranged eccentrically to the work spaces 21, 22 and the work pistons 31, 32 and have larger dimensions such that a further piston rod 41, which is connected to the loader piston 33, is located outside the cylinder 2 in Area of the work spaces 21, 22 can extend. The piston rod 34, like the piston rod 41, is slidably guided into the individual spaces of the cylinder, walls 24, 25 which separate from one another, with sealing, the ends of the further piston rod 41 extending outside the loading space 23 being able to be guided in a sleeve which improves the sealing, such as this can be seen from the embodiment according to FIG. 5. In the embodiment shown in FIG. 1, the ends of the further piston rod 41 are connected via a bracket 46 extending in the axial direction of the engine to a positive guidance of the crank mechanism 4, which in the embodiment shown in FIGS. 1 and 3 5 consists of a dovetail groove 45 in an output element 42 and a dovetail wedge 44, which is attached to the ends of the bracket 46. In this way, the further piston rod 41 can close relative to the output element 42 when the cylinder arrangement rotates

10 shift both sides of a plane E (Fig. 3), which runs through the axis B of the crank mechanism and extends perpendicular to these positive guides 44, 45. In this way, an absolute parallel guidance of the further piston rod 41 becomes parallel to this plane and together with the output element

15 42 of the crank mechanism reached.

This output element 42 can be formed by a flywheel and is mounted about the axis B with the aid of an output shaft 43 in a stationary housing 1, 20 which is only shown in the form of a stator in FIG. 1, but can form a completely closed housing .

The cylinder arrangement, designated as a whole by 2, is in turn rotatable about an axis A with the aid of a shaft 21, which 5 is at least partially formed in the area of a valve arrangement 5 as a hollow shaft 51, which is rotatable in a casing tube 52, which is connected to the housing 1 in a stationary manner . Combustion mixture and exhaust gas passages run in the hollow shaft 51 and, depending on the rotational position of the cylinder arrangement 0 2, can be connected to the corresponding connecting piece 57, 58, 59 of the casing tube 52, as can be seen in particular from FIG. 2. The intake ports 57 can be connected to corresponding mixture preparation devices, while the ports 58, 59 are connected to an exhaust duct. 5

Between the individual openings in the peripheral surface of the hollow cylinder 51, which can be aligned with the connecting pieces 57, 58, 59, there are preferably sealing rings 60 in the manner of piston rings The longitudinal axis of the hollow cylinder 51 is arranged obliquely, although with a correspondingly close fit of the hollow tube 51 and the jacket tube 52 in the manner of a slide bearing, these sealing rings can possibly be omitted and the jacket tube 52 can serve directly for mounting the cylinder arrangement 2 via the hollow tube 51.

Due to the inclined position of the sealing rings 60, they slide overlap over the entire inner surface of the fixed casing tube 52 and separate the openings in the circumferential surface of the hollow cylinder 51 in a well-sealed manner.

In the corresponding rotational positions of the cylinder arrangement, the inlet connections 57 are connected to an inlet line 53 which, according to FIG. 1, has an inlet slot 26 in the region of the

Load space 23 is connected. This inlet slot 26 is only released in the respective end positions of the loader piston 33 towards the loader chamber 23, so that, for example in the downward movement of the loader piston starting from FIG. 1, a negative pressure is generated above this loader piston which, when the inlet slot 26 is released, becomes one abrupt inflow of the combustion mixture into this part of the cargo space 23 leads. During the subsequent upward movement of the supercharger piston 33, the combustion mixture located above this supercharger piston is compressed and flows into the working chamber 22 through its working piston 32 after the overflow channel of the working chamber 22 has been released.

During this upward movement of the pistons 31, 32, 33 continue to be at a certain time

Air inlet openings L in the cylinder arrangement are opened by the respective pistons 31, 32, so that air can flow into the section of the working space 21, 22 located adjacent to the loading space 23, which subsequently follows when the pistons 31, 32 move in the direction of the loading space Sealing of these openings L is compressed and when the respective lower (adjacent to the loading space 23) position of the working pistons is reached via overflow channels 29 in FIG Combustion chamber can flow over. Simultaneously with the release of this overflow channel 29, the exhaust gas outlet slot is also released, which leads to the respective exhaust pipe 54 or 55, so that first a flushing of the combustion chamber with the air previously compressed below the respective working piston and only then the overflow in the Load chamber pre-compressed combustion mixture takes place in this combustion chamber. This is described in more detail in DE-Al-43 37 670 by the same applicant from the same filing date, to which express reference is made.

As can be seen from FIG. 2, the exhaust pipes 54, 55 initially run approximately in the longitudinal direction of the cylinder arrangement 2 to the hollow shaft 51 and then axially to this hollow shaft, whereupon they have a correspondingly radially directed section which leads to openings in the peripheral surface of the hollow cylinder that can be aligned with the sockets 57, 58, 59.

In the described internal combustion engine, the inlet and outlet openings in the cylinder wall are closed and opened by the piston. Channels lead from these openings into the rotary slide valve and are closed and opened again there.

This double function ensures an optimal seal in the intake and exhaust area.

In normal two-stroke engines, the exhaust and intake openings are released by the piston before bottom dead center. The exhaust gas leaves the combustion chamber while the fresh mixture flows in. This means that part of the unburned mixture is also expelled, which leads to poor exhaust gas values.

The previously described disadvantage is eliminated by the described embodiment, for example, in that the discharge opening for the exhaust gases in the rotary slide valve is placed in such a way that it closes when the piston has reached its lowest point and the opening for the fresh mixture is released. The in the Exhaust pipe between cylinder and rotary valve prevents the remaining column of exhaust gas that the fresh mixture can penetrate into the exhaust pipe. In addition, there is fresh air purging, which is pressed into the combustion chamber between the exhaust gases and the fresh mixture and thus acts as a 'partition'.

In the same way, the exhaust opening in the rotary slide valve opens earlier than the opening in the working cylinder. The remaining exhaust gas column in the exhaust pipe can escape before the new exhaust gas is expelled from the cylinder. This enables precise 'control' of the flow, which leads to good exhaust gas values, which was previously not possible with normal two-stroke engines.

As already mentioned, a dovetail guide is shown as an example of the forced guidance in FIGS. 1 and 3. A large number of possibilities are conceivable for the configuration of this forced guidance, a further embodiment being shown in FIG. 4. In this embodiment, the positive guide consists of guide rods 45A, on which sliding bushes 44A connected to the ends of the bracket 46 slide. It is not intended to be limited to these special embodiments of the positive guides.

The essence of this positive guidance and thus the basic idea of the present invention is that, although this positive guidance enables a relative displacement between the output element 42, for example a flywheel, and the piston rod 41, it only allows a parallel displacement between this piston rod and the output element parallel to that in FIG 3 and 4 plane E may be.

In this way, tilting forces between the cylinder and piston are absorbed and the bearing on the cylinder is relieved. 5 shows a further embodiment of the piston machine in the form of an internal combustion engine, in which the cylinder arrangement forms a single cylinder 120, in which a piston 1430, which is closed at its ends, is arranged. The cylinder 120 has a slot 123 in the region of its jacket wall facing the crank mechanism 4, in which a piston pin 134 is slidably guided and is connected essentially centrally to the piston 130. The piston pin 134 is guided in a sleeve extension 121 of the cylinder arrangement 121 in order to improve the seal, although the piston 130 has such a dimension that it always closes the slot 123 regardless of its working positions.

The ends of the further piston rod 141 are connected via a positive guide of the type shown in FIG. 4 to an output element 142 in the form of a flywheel 142 which can be rotated about the axis B via a shaft 143.

The piston arrangement is divided by the piston 130 into a combustion chamber denoted by an asterisk and an oppositely arranged pre-compression and intake chamber, these spaces being connected to one another via an overflow channel 129 which leads to the bottom dead center of the

Piston 130 is released by this. At the same time, an exhaust gas outlet channel 126 is released by the piston at this time, so that the burned combustion mixture can flow into the valve arrangement 5, which is similar to that in FIGS. 1 and 2.

From this valve arrangement 5 continues an intake duct 153 which opens into an inlet slot in the precompression chamber.

The arrangement of the connection between the piston and crank mechanism shown in FIG. 5 can also be used in the embodiment according to FIG. 1 with a corresponding adaptation. In particular, the embodiment according to FIG. 5 results in a very simple, space-saving design which, in view of the high speeds that are possible due to the lack of unbalanced mass forces, can have a very high power output.

A fresh air purge can also be provided in the embodiment according to FIG. 5. For this purpose, the sleeve extension 121 can be designed such that the piston rod 141 has an end sliding in a cylinder section of the sleeve extension 121, so that a type of air pump is formed which injects the outside air drawn in via an inlet slot formed in the cylinder 120, which is so is arranged that it is released when the piston is at bottom dead center.

Claims

claims

1. Piston machine with at least one cylinder rotating around a first shaft and a piston which can reciprocate in a straight line and is connected to a crank mechanism that has an operating element rotating around a second shaft, the first and second shafts running parallel to one another, however, have axially offset axes, characterized in that the piston (3; 130) is connected to a piston rod (41; 141) which extends out of the cylinder (4; 120) in the direction of movement of the piston (3; 130) and which is connected via a positive guide (44, 45 ;; 144, 145) is connected to an element (42; 142) rotating around the output shaft (43; 143) of the crank mechanism (4), and that the positive guide (44, 45, '144, 145) is only a relative displacement between the element (42; 142) and the piston rod (41; 143) in directions transverse to their longitudinal axis and thus a parallel displacement to one through the axis (B) of the output shaft (43, 143) of the crank Operating (4) extending and the direction of displacement of the positive guides intersecting at a right angle plane (E).

2. Piston machine according to claim 1, characterized in that the shaft (21), around which the cylinder (2) rotates, is at least partially designed as a hollow shaft (51) connected to the cylinder, in which the inlet and outlet line of the cylinder runs and which, together with a stationary casing tube (52), forms a rotary slide valve arrangement.

3. Piston machine according to claim 2, characterized in that the jacket tube (52) is provided at predetermined points on its circumference with intake and outlet ports (57, 58, 59) which have openings through the wall of the jacket tube that the inlet and Exhaust pipes (53,54,55) of the cylinder in the hollow shaft (51) extend partially in the axial direction thereof and then have a radially directed section which leads to openings in the peripheral surface of the hollow shaft (51) and that the openings in the peripheral surface of the hollow shaft (51) can be aligned in the predetermined angular positions with respect to the casing tube (52) with the openings formed therein.

4. Piston machine according to claim 2 or 3, characterized in that in the peripheral surface of the hollow shaft (51) at an angle to the longitudinal axis of the oblique grooves for receiving sealing rings are formed, the openings in this peripheral surface opening the inlet and outlet lines sealed from each other separate.

5. Piston machine according to one of claims 1 to 4, characterized in that the positive guide (44, 45) between the piston rod (41) and around the shaft (43) of the crank mechanism element (42) is formed by a dovetail guide.

6. Piston machine according to one of claims 1 to 4, characterized in that the positive guidance (44, 45) between the piston rod (41) and the element (42) rotating around the shaft (43) of the crank mechanism is formed by guide rods on which Slide bushings.

7. Piston machine according to one of the preceding claims, characterized in that the cylinder (2) forms a first and a second working space (22) and a loading space (23) arranged between them, which are separated from one another by partition walls (24, 25), in which a first piston rod (34) is slidably guided under sealing, the first piston (31) displaceable in the first working space (21), a second piston (32) displaceable in the second working space (22) and a piston between them arranged supercharger piston (33) connects to each other, which is connected to a further piston rod (41), the ends of which come out of the cylinder (2) extend and which is connected to the crank mechanism (4).

8. Piston engine according to claim 7, characterized in that an inlet channel (26) of the load space (23) via an in the hollow shaft (51) arranged inlet line (53) with the rotary valve (5) is connected, and that of the axially outer ends of the cargo space (3) overflow channels (27, 28) run to the oppositely arranged work spaces (21, 22), the overflow channels (27, 28) through the pistons (31, 32) arranged in the respective work spaces (21, 22) be closed until these pistons have at least substantially reached their bottom dead center.

9. Piston machine according to claim 7 or 8, characterized in that the working spaces (21, 22) are divided by the piston (31, 32) respectively arranged therein into a combustion chamber and a compression chamber arranged adjacent to the loading space (23), that an overflow channel (29) is provided between the compression chamber and the combustion chamber, which is released substantially simultaneously with the release of the exhaust ducts by the respective working piston (31, 32), and that the compression chamber has an air inlet opening which extends outwards through the cylinder wall and which at a movement of the piston towards its bottom dead center is closed.

10. Piston machine according to one of claims 7 to 9, characterized in that the inlet and outlet positions of the rotary valve assembly are in a predetermined time relationship with the piston-controlled opening of the inlet and outlet channels of the cylinder.

11. Piston machine according to one of claims 1-6, characterized in that the cylinder (120) one of the

Crank gear facing slot (123) which is always covered by the outer wall of a piston sliding in the cylinder (130) regardless of its position, and that Piston (120) is connected to the crank mechanism (4) via a piston pin (134) which extends through the slot (123) perpendicular to the axial direction of the piston (130).

12. Piston machine according to claim 11, characterized in that the piston pin is connected to a piston rod (141) extending in the direction of movement of the piston (130), which is guided under sealing in a sleeve (121) and the ends of which are via the positive guides (144 , 145) are connected to the element (142) rotating around the shaft (143) of the crank mechanism.

13. Piston machine according to one of the preceding claims, characterized in that the cylinder (120) contains a single piston (130) which is closed at its ends and divides the cylinder (120) into a combustion space and a compression space, and in that the compression space is connected via an overflow channel (129) to the combustion chamber at the bottom dead center of the piston in relation to the combustion chamber.

14. Piston machine according to claim 13, characterized in that the piston rod connected via the positive guide to the rotating element at least partially forms a piston of a piston-cylinder arrangement, with the aid of which purge air can be pressed into the working cylinder.