SE527959C2 - Piston rotor machine and internal combustion engine - Google Patents

Abstract

The rotary displacement device has a rotating piston and a rotating housing that has a fixed vane. The cylindrical rotor is eccentrically placed in relation to its cylindrical housing. The gas and air flow goes through the hollow-centered shaft via channels in the rotor. The sealing grid in the displacement space is improved to minimize the friction and thereby gain power and better efficiency.

Description

O OI IQ io n 0 I o nu 0000 Ile u 0 o I uno OI O 527 959 holding the wing approaching or tarring the contact line. This property is particularly useful in said combustion engine, where one or more compressor units and power or expander units can be connected together so that, seemingly paradoxically, compression generates pure expanding volume in the combustion chamber. This is advantageous in the effort to approach an isothermal compression. This can be accomplished by coolers between the units. It is explained in detail below. It is also easy to change the direction of rotation of a compressor before another application, such as converting a fl pressure pressure into a rotating motion, e.g. compressed air or a soldering pressure from an external combustion.

Sealing After the wing 4 is attached between the surrounding walls and against the rotor housing, it does not need a top seal or side seals as with a wankel motor. Sealing rings 16, fi g. 13 and its grooves can be constructed with a cross-sectional angle of about 45 degrees to seal properly in the seam, i.e. both against surrounding walls and as close as possible to the inner circular surface of the rotor housing 1 (contact line).

Cooling The outer rotor has cooling fins for efficient cooling during rotation. The central parts of the rotor, together with the common shaft and the end of the wing facing the rotor center, are in open contact with the surrounding air, which, through the effect of the rotatron, contributes to cooling the machine. The wing itself also has air ducts for cooling.

The gas flow is regulated by valves.

Internal combustion engine Over the years, many alternative dry combustion engines have been designed to eliminate the disadvantages of the conventional reciprocating piston engine. The gas turbine, Stirling engine and Wankel engine are some examples of alternative engines that it has and is still being researched and on which money is being invested. However, these motors have limited application areas, where their special advantages can be used. Environmental requirements are becoming increasingly important and many ideas have fallen on these requirements and other problems. The traditional piston engines are therefore still the dominant engines on the market.

As far as the application of the invention as an internal combustion engine is concerned, the aim is to have a better combustion process and make it possible to use alternative fuels, e.g. hydrogen. In addition, the aim is to significantly increase efficiency, which indirectly affects the environment through lower consumption and less toxic emissions.

Disadvantages of the standard piston engine l. Process in a single-volume engine In modern piston engines, all four roof series take place: intake, compression, combustion and exhaust in a single volume. It can be considered advantageous to divide the beats by more than one volume in order to achieve the best efficiency. 2. The crank mechanism The piston engine's crank mechanism and the associated piston movement as well as the inertial forces of the reciprocating pistons have for decades been the subject of thinkers '527,959 and researchers' thinking for better solutions. Therefore, many proposals for piston rotor motors have been made for many years. 3. The efficiency _ _ Another area that is constantly evolving is the effort to increase efficiency. According to thermodynamics, the so-called The camot process has the highest theoretical 'thermal efficiency'. Rudolph Diesel tried in his time to get his engine to work according to this process as much as possible. But it is difficult to apply to ordinary engines.

It has also long been known that the efficiency and thus the fuel consumption is to a large extent related to the compression ratio. The trend has therefore been towards manufacturing engines with an ever higher compression ratio. But the limiting factor has been the fuel properties and, in the case of diesel engines, the high compression torque that requires heavy constructions. Although the high peak pressures during combustion * YCÉS Be an important parameter for a high efficiency, it has in various ways been an effort to iron out these peak pressures to a higher average pressure. But it is difficult to implement it in the traditional piston note. 4. The compression ratio _ An internal combustion engine, and especially the otto engine, has its optimum efficiency at a given speed and load. At partial load, the efficiency decreases due to the inlet pressure decreasing due to the throttle throttling. This in turn lowers the compression pressure giving the best efficiency. Therefore, it has been considered desirable to be able to accustom the compression ratio at different loads. The proposed engine according to the invention solves this problem in a simple way.

Another problem is the high compression temperature which rises at higher compression ratios. It increases the compression work and gives higher nitrogen oxide emissions. Therefore, experiments have been made with different systems of coolers for charge air cooling. 5. Exhaust gas energy The combustion gases in the standard piston engine, when leaving the engine, still have a high energy content. An Englishman, James Atkinson, introduced in the late 19th century a piston engine with a complicated crank mechanism, with an extended rate of expansion to utilize this energy content. It was then noted that these engines had a higher efficiency than comparable engines at that time. But after the crank mechanism became clumsy, attempts were made with the next-generation engines to approach the Atkinson cycle by controlling the compression and excision intervals with control of the valves. But this did not give as good results as in the previous Atkinson engine. 6. Sealing Blowing out the burned gases in the space between the top of the piston in the upper dead center and the top of the top is another area that has resulted in extensive efforts for improvement.

Complete purge can hardly be achieved in a traditional piston engine, as the outlet valve closes at the upper turning position of the piston and residual gases remain in the said volume. 7. The torque arm The length of the torque affects the torque. The longer the arm, the greater the torque.

The power line of the rotary motion in a normal motor is almost vertical to the center of rotation at the upper 527 959 turning position and a few degrees thereafter. This makes the torque arm very small, and then when most of the energy is generated. A lot of power is therefore lost 8. Valves _ _ Intake and exhaust require valves. Traditional piston engines have two or two valves in each cylinder. This makes the engine complex and expensive.

Solutions. l. Process in more than one volume, The present invention is very useful for alternative applications. Since the machine can work as a compressor, luñmotor or expander, it is possible to combine two or more machines for the best efficiency. This description presents only two solutions, one proposal with two machines and another with three machines. 2. The Crank Mechanism The present invention is designed as a rotary piston machine and therefore the traditional crank mechanism is not needed. The invention solves the said problem and can be built according to the so-called the bryton principle, i.e. an engine with two units where intake and compression take place in one unit and combustion, expansion and exhaust take place in another unit.

Another proposal shows, as mentioned above, three machines: two compressors and a rake unit (expander). The rotary piston principle makes it possible to avoid the inertia requirements of a crank mechanism and therefore enables a higher speed. 3. The efficiency street In the proposal with three machines, one can approach the camot process, which is a heating process with the highest efficiency. The compression is made more or less isothermal in the first compressor with connected radiator. In the second compressor (adiabatic), an isentropic compression continues until a valve is opened in the expander unit, where the compression continues to a certain level. Then the valve closes and the gas ignites. As the wing in the expander moves from the contact line and forward, the volume of this compression and combustion chamber changes from zero to a desired volume. Despite the volume increase, the compression pressure in the expanding volume can be kept constant or even stegras. This seems to be a paradox, but is due to the open connection with the compressor when the valve is open and the volume reduction in the compressor is greater than the volume increase in the expander's compression and combustion chamber. This lowers the compression heat and thus reduces nitrogen oxide emissions but increases efficiency. 4. The compression ratio The compression ratio is variable during engine operation by a device that affects the opening and closing times of the intake valve via an external influence. This is an advantage in case of partial load. - The process has no turning masses as in the regular piston engine, but is more similar to the process in a gas turbine. This means that the compression ratio can be higher than in ordinary engines and the combustion pressure can be more evened out. 527 959 5. Exhaust gas energy _ _ The present invention makes it easier to achieve advantageous parameters in that the size relationship between the units, compressor / s and expander can be freely chosen mutually depending on the desired application. For example, the expander may have a larger expansion ratio than the compression ratio in the compressor. All energy in the exhaust gases can therefore be utilized. 6. Sealing _ _ The outlet volume of the expander goes during each turn towards zero volume, when the wing moves towards the contact line. This is an advantage in gas exchange. There will be no mixture of fresh and pre-burned gases. The inlet valve has no contact with the outlet port and the construction is therefore safe against involuntary ignition. This should be an advantage when using hydrogen. 7. The torque arm _ _ The winding has no crank mechanism but a fixed wing with a torque of almost constant length which transmits force to a rotating motion without losses. 8. Valves _ Only one valve is needed, and then to regulate the inlet fl fate. The outlet duct is constantly open.

Several alternative compositions are possible within the wide scope of the invention.

As far as the internal combustion engine is concerned, for the sake of simplicity, only two alternatives are described below: alt 1; a compressor with associated cooler + an expander combined with each other with a common hollow shaft, Fig. 12 and alt 2; a compressor, called "K1" with associated radiator + another compressor, called "K2" + an expander, connected in each other in the same way, schematically shown in Fig. 16. uouo 0000 o 0 II o 00 0 o I 0 ooo I 00 'oo oooo ooo 0 oo o oo ooo ooo Description of the drawings Fig. G. 1. shows a rotary piston machine, for example a compressor, in a dry section along the line A - A in Fig. 2. "Fig. 2. shows the same machine from the inlet side.

Fig. 3. shows the same machine in perspective.

Fig. 4. shows the same machine in section along the line B-B in Fig. 5.

Fig. 5. shows the same machine in side view.

Fig. 6 shows a rotary piston machine constructed as an expander in an internal combustion engine in section along the line C-C in Fig. 7, and exposes the valve mechanism.

Fig. 7. shows the same expander in side view.

Fig. 8. shows the same machine in section along the line D-D in Fig. 9, and exposes the outlet duct and a toothed device (here a spark plug).

Fig. 9. shows the same machine in the same view as in Fig. 7.

OC I 00 0000 000 I O OO 00 0 0 c 0 0 000 in: coon 527 959 Fig. 10. shows the same machine in section along the line E-E in Figl 1, and exposes part of the valve mechanism. (12 and 13).

Fig.11. shows the same machine in side view as in Fig. 7 and Fig. 9.

Fig. 1 la. shows an expander in enlarged section along the line F-F in Fig. 1 lb.

Figl lb. shows the same machine in front view.

Pig. 12. shows an internal combustion engine with compressor, radiator and expander connected to each other.

Fig. 13. shows a rotor in perspective with the sealing device 16 and the support halves 8 of the wing exposed.

Fig.14. a) shows an expander rotor in perspective with an example of a valve arrangement. b) shows the same rotor with a split view that shows the valve mechanism more clearly.

Fig. 15. shows the valve lifter and the adjusting core 13: i a) split view, b) the cam in the upper position and c) the cam in the lower position.

Fig. 1 6. shows a schematic view of an isothermal compressor (K1) with an intercooler and an adiabatic compressor (K2) and an expander connected together.

Fig. 1 7 - 21. shows schematic views of the flow in different positions of the wing during one revolution.

Fig.22. shows a chart with volume and pressure curves. It only serves to roughly illuminate the process of the internal combustion engine and is not considered a complete analysis.

Job description of a rotary piston machine.

The machine consists of a rotor 2, which is eccentrically placed in a rotating housing 1 abutting said housing 1 (contact line 2a) and whose rotor 2 has a diameter smaller than said housing, so that a space is thereby formed between the rotor 2 outer circumference and the inner circle surface of the housing 1. Due to the eccentric location, said space has its largest cross-sectional area opposite the contact line 2a. On the inner circular surface of the house 1, a wing 4 is toasted, the purpose of which is to create variable volumes together with the surrounding surfaces. Because the wing 4 is enclosed by the rotor 2 through a recess therein, said rotor will follow the rotation. The blade also transmits power to or from the rotor housing 1, depending on the application area of the machine.

The rotor housing 1 and the rotor 2 are each stored in a frame 14. The rotor 2 is not loaded with any torque except that caused by its own friction. A transmission 9a transmits power to or from (depending on the application) a shaft 9b for extreme power receivers and sensors, respectively. The rotor 2 has inlet and outlet channels 6, which independently lead via other arislutria channels 5 to openings on the outer circular surface of the rotor 2 near and on each side of the wing 4. The rotor 2 has on each side axial recesses Sa, whose The purpose is to balance and cool the rotor. The heat is evacuated through adjacent holes 9 to the surroundings. The wing 4 is surrounded by two support halves 8, which are articulated in the rotor 2, so that during the wing, in relation to the rotor, oscillating movement is constantly sealed against the wing 4 during the rotation. The sealing device 16, fig. 13 , consists of a ring on each side of the rotor 2 fitted in grooves. The piston rings and their grooves can be constructed with a diagonal cross section of approximately 45 degrees to seal partly against adjacent ends and partly as close as possible to the inner circular surface of the rotor housing 1.

Job description of an internal combustion engine.

As an internal combustion engine, the invention can be constructed with one or two compressors and one or two expanders interconnected. In the first alternative, the description describes an engine with a compressor and an expander, fi g. 12. The inlet rate and the compression rate take place in the compressor. In the expander, the combustion and discharge rate takes place. In the second alternative, another compressor K2 is connected, schematically shown in fi g.l7-2l.

Between the units it is possible to connect a cooler 18 to reduce the compression guard.

The expander unit has the same construction as described above for the compressor, but also has an inlet valve 7 and an ignition device 10, Fig. 6 and Fig. 8, respectively. An example of a valve system is shown in ñg. 14 and Fig. 15. The valve lifter arm 11 has a needle 12 which, when rolling against the adjustable rabbit 13, transmits force via the arm 11 to the valve 7, which then opens.

In this example of application, the compressor and expander are so connected to each other that when the wing 4 in the compressor has rotated a bit and created a volume reduction and thus a certain pressure, the valve 7 is opened by the adjustable cam 13, which can be actuated by a outer device (here illustrated by a simple handle 15). The flow continues into the combustion chambers in the expander, where ignition and combustion occur and the working phase begins.

The whole process begins with the suction of air or gas to the compressor, Fig. 12, through the channel 6 in the hollow shaft. The rotor channels 5 on each side of the wing 4 rotate in corresponding volume before and after the wing 4. From the compressor, the compressed fl is passed via a cooler 18, in the first alternative to the expander and in the second alternative to the compressor K2 for further compression into expandem.

The second alternative is described in more detail as follows.

The aim of two compressors is to approach the camot process, which is well known in the world of ternodynamics for having the best theoretical tennis efficiency. There, the first compression phase is described as isothermal, i.e. the heat generated by the compression is dissipated to the environment by cooling. The next phase is isentropic compression. The friend that is generated is now preserved as much as possible before incineration. It is not possible to carry out both compression phases in the ordinary piston engine, where all the beats take place in one and the same volume. Therefore, the present invention presents a solution with two compressors.

The first Kl, fig. 16-21, has large cooling surfaces and combined with a cooler 18 dissipates all heat generated to the environment (isothermal phase). The second compressor K2 has a smaller volume compared to K1 so that the volume ratio between the two is determined to the optimum for best efficiency. 'K2 receives the precompressed fl fate Kl (curve a in ñg.22) and in turn continues to compress into the expander to the desired level.

See Figures 17 - 22. In the compressor K1, the suction and compression rates have begun a new round. In the expander, the work phase is in progress. The nth units have reached the position in Fig. 17 and diagram fi g.22. Valve 7 in the expander is closed. (Note that the valve in the fi clock is shown as an open flap to mark an interrupted fl fate into the expander.) In the position fig. 18, the pressure, curve b, 00000: 0 p 000000 527 959 has reached the level shown in diagram ñg.22. The valve 7 has just opened (closed kla fl) in expand and the compression continues simultaneously in K2 and expands up to the position in fi g.l9, where fl fate is interrupted by the valve 7 which closes and the combustion begins. The pressure curve slopes upwards from around 180 degrees to just over 240 degrees (corresponding to 0 and 80 respectively in the expander). By following the curves for the volume change, it is easy to see that the volume decrease is greater in compressor series than the volume decrease in the expander. This explains the increase in pressure in an expanding volume.

A channel 19 is proposed in the rotor KZ, which opens when the expander valve 7 has closed and allows fl fate to pass into the inlet volume, ñg.20. In the team ll gll a new round begins. A non-return valve 17 prevents the remaining flow pressure in the radiator from flowing back to the grain presser K1 instead of to KZ. The inlet pressure in KZ increases again approximately at the position in fi g.l8.

Claims (1)

1 527 959 Patent claims A machine with a rotating piston for evacuating or compressing a medium, or alternatively for converting a rotary piston into a rotating movement, comprising a rotor housing (1) with two ends (1a) and a rotating piston (2) which is eccentrically placed in relation to said housing, thereby providing a contact line (Za) to the housing (1), characterizes! of that! a wing (4) is loaded between the ends (1a) and the housing (1) and that the rotor housing (1), the wing (4) and the ends (1a) are firmly joined to each other, thereby forming a rotating unit (1 + 1a +4) enclosing the rotor (2). Machine according to claim 1, characterized in that the shaft of the rotor (2) is hollow and forms channels (6) for input and output of the working medium. Machine according to one of the preceding claims, characterized in that the complete rotor housing (1 + 1a + 4) transmits, or alternatively receives force, via a transmission device (9a), through the fl pressure pressure which affects the wing (4), or is affected by the wing. Machine according to one of the preceding claims, characterized in that a sealing device (16) has two, parallel and annular sides which each form, in an imaginary extension towards the circle center of the sealing device (16), a cone, and has a third side which seals against the torvelets (1) gavlar (la). Machines, each according to any one of the preceding claims, one or more of which operate as a compressor and the other or referred to herein and operate as an expander, which machines cooperate to act as a combustion engine, characterized in that a medium is compressed in an expander during its operation. rotation simultaneously formed and expanding combustion chamber before combustion starts. Machines, according to claim 5, characterized in that a medium is cooled during ongoing compression and an expanding combustion chamber formed in the expander during its rotation before combustion starts. in that a valve (7) has variable opening and closing times in order to provide a variable compression ratio.