DE3900033A1 - Engine and machine with a positive displacement effect - Google Patents

Abstract

The axial-linear guidance of a reciprocating piston rod (21) in a driving mechanism is achieved by the eccentric mounting of a shaft (1) with complete balancing of the oscillating and rotating masses and controlled by a simple epicyclic gear mechanism (11). The change of working fluid is effected by the constant rotation of a rotary slide/rotary sleeve combination (4) which periodically opens inlet and outlet openings (3) in the cylinder wall and cylinder head. Large opening cross-sections and short fluid paths ensure optimum filling, complemented by axial and radial stratification, swirling and exhaust gas recirculation in the case of internal combustion engines. A multiplicity of drive systems ensure low-loss driving (5) of the fluid control system and simple control of the timing angles. Various different pistons (2) with a large connecting-rod ratio starting from 1:2, integral piston-head cooling and minimum piston and connecting rod mass provide compact driving mechanisms for very high speeds of rotation and variable compression. Further characteristic features are: sufficient space for multiple ignition, a pressure-stable cylinder head, a minimum of components for plug-in assembly, very high pressure compression for self-ignition, internal or external combustion, precision compensation of position deviations and modular construction with five basic units. <IMAGE>

Description

The invention relates to a power and working machine with a reciprocating piston engine, in particular an internal combustion engine with an internal or external combustion, according to the preamble and the features of the claim.

From the multitude of engine and work machines designed and proposed the criticism of the prior art is limited to the essential characteristics that have an economic and technical importance have attained.

The criticism mainly concerns the internal combustion engine, its functional Parts for converting a stroke movement into a rotary movement, the control of the working fluid change by means of globe valves or Flat rotary valve, the training and cooling of the pistons and the guide of the working fluid flows, taking modern requirements into account low-pollution combustion and control of the steering angle and compression.

Obvious advantages that are consequently derived from the simplification and reduction in components will not result for everyone repeated special case because the immediate consequences like

Material savings, easier manufacture and assembly, less Warehousing, easy maintenance and repair, greater operational safety, smaller transport weight, easy reflux of the Used parts for recycling and reducing the total cost

are easily recognizable.

The principle of the invention can also be applied to work machines. At a external generation of the pressure fluid or the energy supply, these can Working machines can also be used as power machines.

Because of their importance, the crank mechanism, the working fluid control through globe valves and cam mechanisms, the piston and the two-stroke process treated in detail.

Crank operation

The dimensioning of a crank mechanism requires a lot of computing effort. The exact mathematical description of the piston travel, the piston speed  and the piston acceleration as a function of the angle of rotation of the Crankshaft is usually replaced by approximation formulas, below Inclusion of the connecting rod ratio. These formulas are created by the replacement of the root expression in the exact equation for the piston travel by transforming the root expression into a McLaurin series, and the use of the first two terms.

The mass balance of the oscillating mass forces from piston and Push rod portion due to rotating mass is imperfect.

The maximum values of the inertial forces differ for the single-cylinder machine at the top and bottom dead center with increasing values of Push rod ratio. Only the component parallel to the cylinder axis from the decomposition of a radial force of a rotating balancing mass serves to balance the oscillating mass forces; the orthogonal Component is a disruptive force. The big oscillating Masses require rotating balancing masses with a large range of motion. The first order mass forces are therefore only balanced to around 50% without balancing the second order mass forces, or this balancing requires a balance shaft that is at twice the rotational frequency the drive shaft rotates. The mass forces become a higher order usually not taken into account and are therefore another source for resonance phenomena at high rotational frequencies.

In a multi-cylinder in-line machine, additional mass moments are created in increasing orders.

These negative conditions increase with a larger push rod ratio. It increases the oscillating mass force at top dead center and creates an increasingly inharmonic movement, larger ones Normal forces on the cylinder wall and the piston skirt and periodically changing reactions of the machine torque.

The deflection of the push rod also requires:

• - Increased friction losses and one-sided wear in the movement plane the push rod,
• - the lower edge of the cylinder wall or the slideway,
• - unfavorable the maximum stroke ratio,
• - additional bending moments in the push rod,
• - the changing piston system and the noise,
• - the sliding and lubricating conditions between the piston skirt and slideway,  
• - the largest push rod ratio, and the
• - maximum piston speed.

The push rod and the piston pin require high strength and therefore consist of steel materials with large oscillating masses. The fixed push rod length results in a constant stroke.

In the case of V arrangements of two push rods on one crank pin, one is Ancillary bearing required on the main push rod, the axis of which is an ellipse describes; that is another complication of the sequence of movements. Double the arrangements with fork pushrods on a crank pin the bearing pressures with the same overall width.

Cranked crankshafts require split bearings.

Multiple natural vibration patterns are created in multi-cylinder in-line arrangements and natural frequencies of the crankshaft. The excitation angular frequency the gas torque with its higher order harmonics generated at certain rotational frequencies resonance phenomena; at high-speed Crankshafts enter the excitation forces of the tangential forces of mass forces added. Let dangerous resonances of a main harmonic do not remove yourself by changing the firing order.

At critical resonance points, the installation of a vibration damper or a vibration damper is required.

The entire simple construction of a reciprocating piston engine requires for a cylinder at least 22 parts when using a simple one Piston without ring carrier, control strips, piston rings, pin bearing bushes, and other parts for piston cooling. This multi-part construction requires a high level of machining fit and assembly effort.

Crank engines are only suitable for small to medium outputs and for medium rotational frequencies.

Crosshead engines for high performance require a lot of construction work. With large heights, they have large oscillating masses and are therefore only suitable for low rotational frequencies.

Globe valves with cam mechanism

Lift valves and valve springs form an oscillatory mechanical System. High rotational frequencies lead to strong inherent torsional vibrations the camshaft, high linear accelerations of the valves and resonance vibrations of the valve spring system, with the consequence of strong noise, Torsional breaks, head angle shift and one  bad cylinder filling.

Cam gears generate bending stresses on the valve stems, and Tangential forces on ram and rocker arm.

Mechanical damage, such as tearing off a valve plate, the break the camshaft or a valve spring lead to total damage to the affected cylinder unit; the same applies to incorrect assembly of the Traction mechanism gearbox, provided there is an overlap between piston travel and valve travel is present. With toothed belt drives, skipping is sufficient of the teeth at the high acceleration of the driving wheel during the jerky Coupling of the drive shaft with a driving gear shaft.

The traction mechanism gearboxes are only suitable for rotational frequencies. Gearboxes for driving the camshaft require multi-axis Spur gears an expensive clearance compensation, due to the length expansion the housing between the drive shaft and camshaft. The disadvantages quadruple in the two-stroke process and exhaust valves in the cylinder head.

The temperature differences between the intake and exhaust valves in the Cylinder head lead to thermal stresses and zones of different Temperature. There is a high thermal load on the exhaust valve by flow around the valve plate, the stem and parts the stem guide with fuel gases during the entire valve stroke. The heat dissipation from the valve plate takes place via the small cross-sections of the stem and the valve seat.

The thermal expansion of the long valve stems changes the head angle. A lack of valve clearance leads to burns on the sealing surfaces; there combustion deposits deteriorate the sealing effect and Heat dissipation.

The gas paths in the displacement chamber correspond at least to the piston stroke. The given tip circle limits the total cross section of the valve openings absolutely on about two thirds of the tip circle area, with more as two valves per cylinder. Multi-valve controls result in increased Construction costs around 25% larger inlet cross-sections. The free valve passage is limited by stem, stem guides and valve seat, Added to this are the multiple redirections of the gas flows to the Duct bends, on the valve plate, on parts of the cylinder wall and the impact  on the counter flow of a neighboring valve or on a screen on the valve plate. The result is a sharp reduction in the flow and discharge coefficients.

The design and management of the gas channels is due to the arrangement of the Valves, the camshaft, the ignition and injection devices in the Cylinder head limited, especially with a targeted Swirl flow of the fresh gases.

Lift valves open and close slowly because of their start and end speeds is zero.

Adjacent valves promote the overlap of the Control angle of exhaust and intake valve the overflow of fresh gas into the outlet duct.

The high proportion of openings in multi-valve arrangements reduces the Strength of the cylinder head and complicates the cooling of the fuel gases exposed surfaces. All-round cooling of the valve seat results in valve gaps that are too large.

The construction work for the valve control with cam mechanism in the cylinder head results in complicated molds and a large overall height.

A lot of parts per cylinder are required; this number of parts increases with devices with forced rotation of the valves and with automatic valve clearance compensation.

The high thermal stress on the exhaust valve forces construction from different types of steel, armor of the valve seat and sodium cooling of the shaft.

The installation conditions become more difficult with an increasing number of valves for ignition devices, pre-chambers, fuel injectors or Water and cooling chambers in the cylinder head.

The globe valve control with cam gears is relatively demanding high drive power and deteriorates the mechanical efficiency the whole machine; it also requires a complex lubrication system with long return times of the lubricating fluid.

The inclination of the valves results in a double convex combustion chamber, especially with a strongly curved or frustoconical piston crown surface.

The cylinder head gasket is directly affected by the hot fuel gases claimed.  

Due to the nature of the system, rotary vane valves cannot have the required opening cross-sections have for an optimal cylinder filling.

Your seal against the interface between the cylinder head and Cylinder wall requires a multi-part ring system with sealing bodies which are exposed to the fuel gases.

piston

The flow of force from the pressurized piston crown over parts of the piston skirt and over the pin bearing, the piston pin into that upper push rod bearing is cumbersome.

There are a variety of calculations for the dimensioning of the piston crown, the piston skirt, the pin, the pin bearing and the upper one Push rod bearing required, especially with high dynamic Loads and high gas forces.

The radial anisotropic mass distribution of the piston causes one different expansion behavior in the direction of the pin axis and orthogonal to this direction, therefore an expensive shape grinding of the Piston jacket or control elements required.

The position of the piston pin with regard to the tilting movements and uniform piston jacket load remains a compromise, and it requires the width and location of the ring section.

The lubrication of the piston pin is problematic; also arise high surface pressures with oval deformations of the bolt and explosive effects in the pin bearing, deflections with edge pressures and strong Loads on the upper push rod bearing because of the total width available is distributed to the pin bearing and the push rod bearing. With light pistons, the low inertial forces at top dead center relieve pressure the pin and the pin bearing only slightly from the highest Gas power.

The axis of the piston pin must match the axis of the crank pin to be parallel; this applies particularly to pistons with long shafts. The surface pressure of the normal force on the cylinder wall - due to Hertzian pressure - only affects small areas on the piston skirt and on the cylinder wall in the plane of movement of the push rod, and caused partial increased wear.

The high thermal load on the center of the piston crown requires a safe one  Energy drain through the grooved ring section to the piston skirt. Longer routes with increasing piston diameter reduce the specific Piston area performance. The sharp reduction in strength values The light metal alloys between 150-250 ° C affect the required Rigidity of the piston crown with large gas forces.

A strong thermal expansion of the piston requires a large installation clearance, Cause of the piston tipping and running noise at the start of operation. The changing piston system creates a sickle gap between the piston skirt and the cylinder wall, with a one-sided surcharge Fuel gases in the ring section, increased lubricant passage, solid Deposits on the top land and mostly in the first ring groove. These Combustion residues cause increased wear on the piston skirt, in the first ring groove and on the piston rings.

The piston rings must be able to move radially and require play between piston ring and groove flanks; this mobility is due to the solid combustion residues impaired, which also the sealing effect reduce. There are always one axial and two radial in an annular groove Leakage paths exist. With progressive wear arises through the play between the piston rings and the annular groove Conveying effect for the lubricating film in the direction of the combustion chamber.

The high gas forces and the mass forces require great strength the ring section, especially in the first ring groove. For light metal alloys ring carriers made of steel materials are required. If the piston travel and valve travel overlap at top dead center recesses in the piston surface are necessary. This jagged Piston surface creates an unfavorable combustion chamber and increases disadvantageous the piston surface affected by the hot fuel gases.

The usual types of cooling (injection cooling, cooling coils or cooling chambers) do not ensure optimal cooling of those exposed to the combustion chamber Piston surface, especially the heavily loaded middle of the piston crown.

Multi-part, built pistons result in heavy complex components and are therefore only suitable for low rotational frequencies.

The piston skirt must transmit the normal forces to the slide, this also requires a minimum length and a for the four-stroke process  Minimum wall thickness of the piston skirt.

The large specific weight of the steel materials for the piston pin unfavorably increases the oscillating mass forces.

In the case of high-performance machines, there is a complex adjustment of pistons and Cylinder required.

Two-stroke process

The cross or reverse purge results in a symmetrical control diagram with large flushing losses. Residual gases remaining in the upper part of the displacement chamber reduce the degree of rinsing.

High outlet openings shorten the effective piston travel and cause a premature pressure drop in the fuel gases. They cause increased Flushing and performance losses.

The high specific fuel consumption is associated with an imperfect one Combustion and a high proportion of carbon-hydrogen molecules and carbon monoxide.

The overall efficiency does not reach the values of the four-stroke process. The disruptive noise emission is disadvantageous.

The internal combustion engine for the two-stroke process with auto-ignition and a very large stroke ratio (s / D <2) require crosshead engines for straight guidance of the push rod and a very long piston skirt. This construction results in a very high construction effort with a large height and very large oscillating masses. For these reasons, it is only suitable for low rotational frequencies.

The object of the invention is that described in the review To avoid disadvantages and the existing technical and thermodynamic Problems, especially with internal combustion engines, on a Minimum attributed.

It is not particularly useful, for example, to improve the Degree of filling of a cylinder through the arrangement of several inlet and Exhaust valves due to the disadvantages of a multi-part and expensive construction repeal.

The improvements concern the engine, the working fluid control, the pistons for various applications, the regulation of the head angle and compression, combustion and overall construction.  

Engine

The special tasks for the engine consist in a crucial one Simplification of the mathematical description of the movement processes which enables easy calculation of the parts and a better simulation of gas flows in the cylinder favored.

The other tasks are:

• - The complete mass balance of the oscillating masses in the Single cylinder and the multi-cylinder machine, with all switched off free mass forces and moments,
• - Simple sequential representation of movements through cinematographic Process, in particular through the digital storage of the Pixels and playback on polychrome screens,
• - Improvement of the structural strength of the drive shaft, in particular the bending and torsional rigidity of shaft sections with a high natural frequency, or alternatively
• - The decoupling of shaft sections by rotatable parts in or between the sections of the natural vibrations of the neighboring system,
• - compact design with few parts,
• - simple plug-in assembly of the shafts and bearings in undivided base bearings,
• - any stroke ratio,
• - Versatile constructions for single and multi cylinder machines in different arrangements of the cylinders,
• - low load on the toothing of the control gear and small bearing pressure in the eccentric bearing 130 ,
• - Reduction of the additional flywheel masses and improvement of the Degree of non-uniformity.

Working fluid control

The task of working fluid control is a very low power requirement for the drive. It has to consist of very few components, ensure precise compliance with the specified steering angles and must not contain any elements that limit the frequency.

The other tasks are:

• - larger free channel cross sections with better flow and discharge coefficients,
• - Multiple inlets for various fuel-air mixtures, pre-inlet  for highly flammable mixtures or of air,
• - improvement of the degree of filling,
• - Free choice of the inlet and outlet openings in terms of number and the arrangement
• - Direction of the incoming working fluids to radial and axial Stratification,
• - simple exhaust gas recirculation,
• - self-grinding, -honing, -lapping control mirror surfaces,
• - free design of the combustion chamber shape; Influencing internal surface temperatures through layers of material with selected physical Properties such as temperature conductance, heat penetration value and Heat storage value,
• - Very simple assembly of the control system.

piston

The tasks for the construction of the piston are very simple Design that allows easy calculation, and in the direct connection to the engine without a special joint in the piston for a push rod (connecting rod).

The other tasks are:

• - lowest piston mass or piston push rod mass for highest rotational frequencies,
• - Two piston designs as shaft pistons or push rod pistons, in Single or double piston design,
• direct introduction of force from the piston crown via the piston skirt 221 to the oscillation axis 100 of the engine in the case of a shaft piston, or via the push rod 250 in the case of a push rod piston,
• - no piston tilting or change of system,
• - very short design with short buckling lengths, corresponding to a connecting rod ratio from r / l = 1: 2,
• - Very short piston skirt for a push rod piston for special purposes for high-performance machines,
• - small clearance between the piston skirt and slideway,
• - increasing the relative piston speed,
• - Isotropic radial expansion of the piston crown and the piston skirt simultaneous lowering of the piston crown temperature during operation,  
• - improved piston crown cooling and simplification of the cooling fluid supply,
• - better gas sealing with recirculation effect,
• - reliable lubrication of the piston skirt, especially gas lubrication,
• - Simple and safe sealing piston ring arrangement with good Heat dissipation,
• - no jagged piston surface,
• - Easy manufacture and processing, especially the circular cylindrical Surface sliding surfaces,
• - increase of the specific piston area performance,
• - Various connection variants with the swing axis 100 of the engine, and
• - Faster heating of the lubricant to operating temperature.

Regulation of the steering angle and compression

The task of regulating the head angle is dependent from the rotational frequency of the drive shaft, the negative pressure in the Inlet channels, the degree of filling, the load or a lever position by simply moving or rotating a control shaft, the quantities of the steering angle determined by calculation or experiment to specify or continuously readjust by

• - Simple mechanical arrangements, especially lever systems, or through different
• - hydro-pneumatic actuators or drive elements, or
• - electromagnetic actuators or drive elements on the control shaft or directly on the control body.

The regulation of compression should be achieved in two ways:

• - Discrete thanks to a simple combination of components on the piston crown with different strength rotary valves, or
• - infinitely variable through a variable push rod length.

combustion

The purpose of internal combustion is to improve it the swirling of the fuel-air mixture or the fresh air and an improvement in the stratification in the axial or radial direction.  

The other tasks are:

• - inexpensive compact combustion chambers and a long expansion stroke,
• - Simultaneous operation with different fuels with different specific heat of vaporization, vaporizability or Vapor pressure,
• - Combination of regulated exhaust gas recirculation with air purge and the different stratification processes,
• - Improvement of multiple ignition by multiple ignition devices in the Cylinder head depending on control unit and number of openings,
• - Protection of the ignition devices or the injection devices from the direct action of the fuel gases through the rotary valve.

The task of external combustion is to arrange one compact, central combustion chamber directly on the cylinder head and several Heat exchangers according to the counterflow principle, which is a continuous Burning and generating thermal energy in a periodic release convert to a working medium, using a directional positive control the working medium through the heat exchanger by means of a controller 23565 00070 552 001000280000000200012000285912345400040 0002003900033 00004 23446 and low-pollutant combustion Fuels through post-oxidation of carbon-hydrogen compounds is achieved in catalysts that are integrated in the heat exchanger are.

Overall machine

The tasks of the overall machine consist of a very compact design with a small inflow area for a streamlined casing, and with a low center of gravity, for flat cylinder arrangements, for a deep installation position in land or sea vehicles.

The other tasks are:

• - better synchronization with fewer cylinders,
• - vibration-free and low-noise running of all moving parts, at better internal damping and lower noise emissions,
• - Expansion of the usable frequency range by more uniform Torque values over a wider range of rotational frequencies,
• - highest rotational frequencies for reciprocating engines for high-performance machines,
• - suitability for all processes and fuels,  
• - improvement of the room performance (kW / m³), the performance weight (kW / kg), the displacement capacity (kW / l), the ratio of construction volume to displacement (m³ / l), the quality grade, the mechanical efficiency, the mean effective piston pressure and the general operating factor, especially for fluid control,
• - reduction of specific fuel consumption,
• - Easy replacement of the wear parts exposed to the fuel gases Piston skirt and control element as a structural unit,
• - homogeneous individual parts, especially for the material reflux,
• - simple and quick assembly and disassembly of fewer parts,
• - maintenance-free and low-wear machine,
• - simple, pressure-stable cylinder heads with uniform thermal Burden,
• - Precision centering or compensation of the position dimensions for axes, shafts, Cylinder heads, bearings or similar components,
• - Performance adjustment through a modular design with five simple Base engines.

This task is solved by a power and work machine the preamble of the claim and the feature groups and features of the characteristic part.

The feature groups and individual features can be used both among themselves also in various combinations with the characteristics of the generic term form a multitude of new machine characteristics.

It should be noted that only sensible structures are the subject of the Are inventive. For example, it is useless inlet or Connect exhaust ports in the cylinder head to a rotating sleeve control, or the undivided push rod bearing of a piston with one propose one-piece swinging axle shaft washer unit, the could not be assembled at all.

The idea of the invention, the essential principles or general Features that will apply to machines and machines dealt with first. Special configurations of individual Machines are explained using the drawings. The precision centering with two eccentric rings is not on power and work machines limited, but generally applicable.  

Engine

The principle of the engine is easy to understand if the rotating movement of the kinematic points P, Q around the simultaneously rotating median axis M is considered a special case of a hypocycloid, provided that the diameter of the rolling circle is identical to the radius of the base circle. In this case the hypocycloid is a straight line.

The equations of the straight reciprocating piston engine with finite push rod are therefore simplified to the equations with infinitely long push rod (r / l = 0).

The result is a perfect harmonic movement of all oscillating parts on the two straight lines W.

However, it is a prerequisite that the oscillating masses can be reduced to one of the kinematic points P, Q by a translation on the effective line W ; the same applies to the center of gravity of the compensating masses A. The balancing of the oscillating masses is very simple. Half of the calculated or weighed mass can be distributed over the two cheeks 110 or over two wave washers 125 . If this distribution takes place at the same distance from the effective line W in parallel planes of motion, there are no free moments of mass.

The same method can be used if two isobaric oscillating masses are reduced to the kinematic points P, Q , which, however, now generate a mass moment in two planes of motion, with the specified distance from the width of the cheek and the length of the oscillating axis.

After the oscillating masses have been reduced to points P and / or Q , these masses can be treated like rotating masses around the median axis M and easily compensated for by rotating masses on the cheeks 110 .

It is of secondary importance whether the oscillation axis 100 as a pin axis 105 or as a pin axis 106 is a fixed part of the piston, or whether it is connected via a cheek 110 to an oscillation axis 100 that is moved orthogonally to it.

The eccentric circular movement of the median axis M is carried out by an eccentric shaft 120 in various designs. The associated eccentric bearings 130 rotate about the central axis Z and contain the entire balancing masses of the eccentrically rotating masses.

The dimensions of the eccentric shaft 120 are determined by the position of the epicyclic gear from a fixed ring gear 150 on the housing and from a rotating pinion 155 on the eccentric shaft.

This epicyclic gear needs only the frictional forces, and with changes in rotational frequency absorb the existing acceleration forces.

piston

Due to the straight movement of the oscillation axis 100 , the construction of the piston is very simple.

The material force acting on the piston head 210, 245 is transmitted directly to the oscillation axis 100 . In the version as a shaft piston 200 via the piston skirt 220 and in the version as a push rod piston 240 via a push rod 250 .

Both piston variants can be provided with a piston cap 270 . The thin membrane disc 275 vibrates under the influence of the mass, material and pressure forces which act on it from both sides and thereby exerts an intensifying pumping effect on the cooling fluid flow. The distance from the pressure floor 245 is adjustable.

In order to compensate for positional deviations, the piston cap 270 can be fastened in a radially displaceable or angularly displaceable manner and in this way compensate for positional deviations (distortion) which are automatically present or arise during operation; in particular as integral piston caps in connection with a push rod piston 240 without piston jacket 260 .

In the case of a stem piston, it is only suitable as a partial piston cap. The membrane disc 275 can also be replaced by a ceramic insulating disc for thermal shielding of the piston crown 245 . In the jacket of the piston cap 270 , or in the piston jacket 220, 260 , or between the partial piston cap and the piston jacket 220, 260 , a piston ring arrangement comprising the outer ring 290 , the inner ring 291 and a trapezoidal clamping ring 292 can be inserted in a wide outer ring groove 226 . The rings and the groove are dimensioned such that the trapezoidal clamping ring 292 always exerts an axial clamping force on the ring arrangement, and no radial and axial leakage paths can arise. There is constant contact between the rings, the piston skirt 220, 260 and the slideway.

The sealing function of the piston skirt can be improved by a screw groove 224 with a return effect, both of the working fluid and the lubricating film. The design depends on the rotational frequency and the direction of rotation of the control member.

The design of the piston crown 210, 245 , the push rod 250 , the piston skirt 220 , the bearing block 255 , the ribbing 247 is simple. For example, the push rod can be made very short with a large shaft cross section and can only be calculated for the greatest tensile and compressive forces. The piston skirt does not have to transmit normal forces to the slideway, so that mainly the bearing pressures of the different axes are the sizes to be determined. Several cooling systems are possible. The integral piston crown cooling is to be emphasized by the separation of the pressure plate 245 from the membrane disc 275 and the constant axial cooling fluid flow which flows radially outwards in the surface gap.

The special ways of feeding, distributing and returning of the cooling fluid are listed in the characterizing part. All cooling systems require a pressurized fluid. As a rule, the cooling fluid is at the same time the lubricating fluid so that sufficient cooling at large specific Piston area performances only with larger cooling fluid flows to cope with. In these cases it is useful in every cylinder unit install your own feed pump.

Regulation of the cooling fluid flow can affect the piston surface temperature to influence the combustion processes and the thermal expansions Define needs.

The thermal expansion takes place radially-isotropically due to the spatial axis symmetry of the piston elements made of mainly simple rotating bodies. Disruptive elements such as B. the journal axes 106 are in the cooler area of the engine housing.

The tasks of even pressure distribution (US 2 80 395, E 0 69 578), the separation of the sealing and guiding part of the piston (DE 27 17 692), the stability (DE 27 17 084), the deflection of the piston pin (US 5 77 562) and the reduction of the frictional forces (DE 32 35 220) are through the inventive features of the characteristic parts have become superfluous and the tasks of thermal expansion and dissipation (FR 78 27 173), the Saving the piston rings (DE 31 34 768) and the simple production (DE 32 35 220) has been solved in a much better way.

In addition to the special advantages of a very low piston mass, the small overall height, the simple connection with an oscillation axis as pin axis 105 and the simple production and cooling, there is the possibility of lubrication with fluids with low dynamic viscosity (gases), since there are no normal forces on the Act on the piston skirt. An increase in the piston speed and a practically smooth movement of the piston on the slideway are the prerequisites for the desired maximum rotational frequencies.

Working fluid control

The concrete design of the working fluid control by a control element in its designs as a rotary sleeve 400 or as a rotary slide rotary sleeve 410, 400 connects the sleeve slide controls (Knight or Burt McCollum) and the flat rotary slide controls with the constant rotary movement of proposed multiple rotary slide valves (E 1 01 431) with the desired one Increasing the channel cross-sections and stratified charge by "centrifugal force separation", or with rotary valves with secure sealing (DE 27 14 351) or cooling (E 0 16 381).

The important principle of constant rotary motion for working fluid control is particularly important for maximum rotational frequencies.

According to the equations introduced for driving the control element under feature group 5.1., The overall transmission ratio is i = 8: 1, for an internal combustion engine for the four-stroke process with four inlet radial channels. The rotational frequency of, for example, with 500 U s ^-1 (30 000 rev min ^-1) rotating drive shaft results under these conditions, a rotational frequency of the control member of U 62.5 s ^-1 (3750 rev min ^-1). The drive of the control element can therefore be controlled even at the highest rotational frequencies.

The improvement in the inlet or outlet cross sections results from the equations for the calculation of the control width by feature group 3.1.4 .; provided at the same time intake ducts in the cylinder wall and in the cylinder head are provided, put them in a uniformly moving Control element and a large control angle coefficient the theoretical Optimum.

The arrangement of the webs 302 and their secure connection to the channel walls and the cylinder wall is important for the practical configuration. The webs 302 must reliably absorb the tangential tensile stresses in the cylinder jacket at the greatest internal pressures and are therefore reinforced by inserts made of high-strength materials. The lateral channel walls are used to axially stiffen the cylinder wall. Together with an even distribution of the cylinder head bolts, they enable a low-distortion control mirror surface.

The control mirror surfaces of the cylinder, cylinder head and control element are separated by a lubricating fluid. Despite the lack of normal forces on the control element, the periodically changing material forces are partially transferred to the cylinder wall and in full to the cylinder head due to the expansion of the control element. The control mirror surfaces are therefore designed for hydrodynamic lubrication. The arrangement of the lubrication grooves, the number and size of the wedge and locking surfaces, the height of the lubrication gap for the control mirror surfaces to be treated as radial and axial plain bearings are determined in each individual case. Since the lubrication gap height changes periodically, the volume change in the gap is used to promote the lubrication film and to improve the sealing effect. The determining factors of the total length of the inlet radial channel 300 , length of the piston skirt 260 , two-stroke or four-stroke method, single or double-acting piston with closed compression space 325 are in the feature groups 3.1.3. and 2.2.4.4. described.

The direction of the fluid flows can be influenced by the outer guidance of the inlet radial ducts 300 or the inlet axial ducts 330 , since no control arrangements in the cylinder head hinder this guidance. The drive of the control element is possible in many ways.

A preferred gear arrangement consists of a toothed control shaft 510 which engages in a toothing of the rotating sleeve base 500 . This control shaft can simultaneously drive several control units in series.

With a suitable toothing, a simple controlled control angle displacement can be achieved by an axial displacement or a rotation of the control shaft 510 .

., Under the characteristic group 5. The basic transmission arrangements, control methods without control devices are described in detail, and in the drawings of Figures 8 to 16 are shown; a detailed explanation is therefore omitted.

Overall machine

The compact design is a consequence of the engine and piston characteristics in connection with the space-saving working fluid control. The total height of a cylinder block in a boxer arrangement is only that five times the stroke, therefore the dimensions of a cylinder block a 3-liter high-performance machine with 16 cylinders in this design following cuboid dimensions: width: 332 mm; Length 400 mm; Height 210 mm. That is a construction volume of around 27.8 liters and therefore the ratio from construction volume to stroke volume <10.

All other favorable values are based on this fact, in combination with the multi-channel inlets, the improved cooling and the low number of parts.

An engine unit for a cylinder requires only 7 components (Push rod piston with swinging axis, 2 eccentric shafts with pinion, 2 eccentric bearings and 2 ring gears in the base bearing); the working fluid control only 4 components (control element, sealing body, control shaft with Spur gear and drive gear), whereby most parts are easy to assemble to let. In addition, there are the diverse methods of fluid management, gas stratification, combustion, simple control of the steering angle and compression.

Further features of the invention will be explained with reference to the drawings.

Fig. 1 shows a liquid-cooled internal combustion engine for the four-stroke process in the anabatic process, with a control of the working fluid change through inlet radial channels 300 and outlet axial channels 340 and rotary sleeve 400 with rotary valve 410 . Pin 405 and sealing body 406 convey the axial contact pressure on the axial mirror surface, which is designed here as a flat cone 350 . The push rod piston 240 shows two variants of the piston cap fastening by thread 272 or by bayonet connection 273 on the radial ribs 247 . The cooling fluid is supplied centrally via a coaxial pressure pipe 280 . The principle of axial stratification is indicated by different λ values at the inlets 300 .

Fig. 2 shows an air-cooled internal combustion engine for the two-stroke method in anabatischen method. The inlet radial channels 300 and the overflow channels 320 are arranged at the bottom dead center and the outlet axial channels 340 in the cylinder head. The simple push rod piston 240 is double-acting. The compression chamber 325 is sealed against the engine housing by a cover 360 with a sealing ring bearing 363 . The length of the piston skirt 260 corresponds to the inside diameter of the overflow channels 320 . The piston is cooled by a central supply and return of the cooling fluid in the piston skirt 250 ; sealing by piston rings 290, 292, 292 in the short piston skirt 260 . The bearing of the pin contains a precision centering through two eccentric rings.

Fig. 3 shows a working machine having a shaft piston 200 and piston ring loose cladding 220 with helical grooves 224 in the Mantelgleitfläche 223rd The rotary valve 410 has a collar 402 , on the flank surface of which the material force of the pressure fluid acts in the pressure chamber 403 . The pressure chamber is connected to the collecting channel 338 via channels (not shown).

Fig. 4 is a developed view of the control mirror surface shows an internal combustion engine of the two-stroke method with overflow 320th The connection from the outlet radial channel 310 to the outlet axial channel 340 is possible via a connecting channel 339 . The relative position of the control edges 301, 331 of the rotary sleeve 400 , the rotary slide 410 and the channel openings with the corresponding piston position corresponds to the compression phase. When the control edges move to the right, the inlet radial channels 300 open and the outlet channels remain closed. Due to the even distribution of the channel openings, the direction of rotation of the control element is possible in both directions.

Fig. 5 shows in the frames af various engines for single or multi-cylinder in-line arrangements. The base bearing 140 and the ring gear 150 of the control toothing are not shown for reasons of clarity. The possible configurations of the oscillating axes 100 , the eccentric shafts 120 and their connections to cheeks 110 or with one another, in the case of single and multi-cylinder in-line arrangements, are detailed under feature group 1.3. described. Of particular note are only the external teeth 139 in FIG. 5b of the eccentric bearing 130 of the two individual engines, which allows any torque transmission to a drive shaft (not shown). The coupling part 151 with pinion 155 is mainly used to connect two shaft washers 125 . In Fig. 5d, an arrangement to compensate for the Verdrehflankenspiele between the tooth engagement surfaces on the ring gear 150 and the pinion 155 through the side pinion 156 with torsion sleeve 157, conical connection 158 and jack screw 159 is shown schematically.

Fig. 6 shows an axial arrangement of a 6-cylinder engine with a central drive shaft 9 and the axial collection channels 305th

Fig. 7 shows an 8-cylinder engine in boxer arrangement and 4 axial collection channels 305 at 4 inlet ducts per cylinder. The overall width corresponds to a 5-fold stroke s.

Fig. 17 shows an arrangement for a continuously variable compression ratio and variable group by feature 6.2. The push rod is divided into outer shaft 251 and inner shaft 252 . A control disk 600 effects a stepless change in length of the push rod 250 via the engagement surfaces on the outer shaft 251 through the movement screw connection between the outer shaft 251 and the inner shaft 252 .

Fig. 18 shows the scheme of an internal combustion engine with external combustion. The central combustion of any fuel in a combustion chamber 82 generates fuel gases which are introduced into a plurality of heat exchangers 84 via deflection surfaces 83 . The control element of a work machine forces the gaseous working medium (eg helium) through gas channels 81 to a cyclic process (circular process) with constant absorption of thermal energy, expansion of the hot gases and cooling. Part of the thermal energy is used to preheat the combustion air.

Fig. 19 shows the structure of the gas passages in the heat exchanger 84, wherein the gas passages are separated 85 for the working medium from the channels for the combustion gases 86 by partitions 87 which can store a part of the heat energy periodically.

Claims (10)

Power and work machine with displacement effect;

• - in single cylinder design;
• - in multi-cylinder design, in axial or radial arrangement; or in single-row, double-row, boxer, H, V 90 or X 90 arrangement;
• - with reciprocating piston, single or double acting; and with
• - crank mechanism and shaft, one-piece or built;
• - Air or liquid cooling of the displacement chamber;
• - Periodic control of the working fluid change through lift valves and cam gears in the cylinder head; or by
  Flat rotary valve with flat control mirror surface; or by
  Rotary valves surrounding the piston and openings in the cylinder wall and in the cylinder head for the inlet and outlet of the working fluid, or the loading and flushing of the working fluid;
• - Uncoated or coated cylinder running surface, especially in light metal alloys with coatings made of other metals, graphite, carbides or plastics;
• - plasma coating of metals with other metals or with oxide-ceramic or non-oxide-ceramic materials;
• - cast or retracted liners;
• - Reinforcements made of oxide or non-oxide ceramic mineral fibers in light metal alloys, in particular Al₂O₃ and SiC fibers;
• - circulating pressure lubrication of the rotating parts;
• - one-piece cylinder and cylinder head, cylinder and crankcase or with separation levels between these elements;
• - Multi-part, cylindrical piston and liquid cooling of the piston crown, in particular oil cooling, cylindrical push rod with fluid channel, piston rings for sealing the running clearance between the piston skirt and slideway and for stripping the lubricating film, especially in minutes, nose or L-ring version, including the ring joint fixation;
• - Storage of the axes of rotation, shafts and other rotating parts
  in hydrodynamically lubricated axial bearings,
  in hydrodynamically lubricated radial bearings with bearing bushes or bearing shells, and ring grooves, lubrication pockets, lubrication grooves and feed bores;
• - in multi-surface plain bearing design;
• - In rolling bearings in radial or axial design, especially with ceramic rolling elements and rings;
• - Screw connection with peripheral-radial slot arrangement in the screw head, for the fluid engagement of a turning tool tip for the unmistakable screwing of the detachable connection by a tool with a fixed tightening torque, in particular for expansion and fitting screws;
• - Double eccentric discs for axis shift;

in particular an internal combustion engine

• - in the two-stroke process with compound lubrication and with single pistons or with opposed pistons; and with
• - DC flushing, cross or reverse flushing;
• - in the four-stroke process with compression of the fresh gases; and with
• - Direct injection of the fuel into the combustion chamber, or indirect injection into the inlet duct or in divided combustion chambers;
• - compression ignition or spark ignition, in particular multiple and map ignition;
• - Self-priming with a matched intake-exhaust system to the number of cylinders and the cylinder arrangement;
• - Pressure charging of the working fluid by supercharger pumps, or by the underside of the piston;
• - cooling of fresh gases;
• - exhaust gas recirculation into the combustion chamber;
• - catalysts in the exhaust duct;
• - Specially designed combustion chamber in the cylinder head or in the piston crown;
• - front and swirl chamber;
• - Charge stratification in the combustion chamber and / or swirling of the fuel-air mixture;
• - Ceramic components in the outlet channels and on the piston crown;

and auxiliary units for ignition, control, lubrication, cooling, filtering, Injecting or gasifying the fuel, starting, pumping, storing, Detoxification of exhaust gases and devices for damping sound waves and vibrations; or an engine with external generation of the pressure fluid,

• - operated in an open process,
  • with hot gas or exhaust gas, in particular from free-piston gas generators,
  • - with compressed air or other compressed gases,
  • - With incompressible media, especially pressurized fluids, which utilize a positional energy;
• - operated in a closed cycle, with external combustion of the fuel,
  • - with helium as working fluid, and recooling after the expansion phase,
  • - In the two-cylinder process with a regenerator between the cylinders and isentropic or isothermal expansion of the working fluid in the theoretical process;

or a work machine for conveying and compressing a working fluid in

• - Single or step arrangement as
  • - Pumps for conveying incompressible media or gases, or
  • - Compressors for compressing compressible media, especially heat pumps;

characterized by the following groups of characteristics and characteristics:
1. Engine for converting a linear, reciprocating movement into a rotary movement, described by the
1.1. kinematic movement of two points (P, Q) ,
1.1.1. that are rigidly connected,
1.1.2. have a fixed distance r ,
1.1.3. lie in a plane of movement,
1.1.4. and equidistant,
1.1.5. with the constant negative angular velocity - ω
1.1.6. rotate around their common median axis (M) ,
1.1.6.1 the median axis (M) is a normal of the plane of motion,
1.1.6.2. and rotates simultaneously,
1.1.6.3. with the constant positive angular velocity ω
1.1.6.4. at a distance r / 2,
1.1.6.5. about a central axis (Z) parallel and fixed to the median axis (M ) ,
1.1.7. simple and mathematically exact formalization of path, speed and acceleration as a function of the angle of rotation of the median axis (M) around the central axis (Z) ;
1.2. Kinetic realization of the kinematic system of the feature group 1.1., so that the
1.2.1. moving, real masses,
1.2.1.1. either from two identical pistons according to characteristic group 2,
1.2.1.1.1. whose external centers of gravity (outside the kinematic system) can be congruently shifted to one of the two moving points (P, Q) by a linear translation on the cylinder axis,
1.2.1.2. or from a piston according to feature group 2 and balancing weights (A) , where
1.2.1.2.1. two equalizing masses (A) ,
1.2.1.2.2. have internal focuses (within the kinematic system),
1.2.1.3. form two isobaric masses,
1.2.1.3.1. which can be reduced as mass points to the moving points (P, Q) of the kinematic movement, and
1.2.1.3.2. perform harmonic, linear oscillatory movements,
1.2.1.3.2.1. with a phase angle difference of π / 2 rad,
1.2.1.3.2.2. and an amplitude r of the mass points
1.2.1.3.2.3. at least two orthogonal straight lines (W) ,
1.2.1.3.2.3.1. which are in parallel planes of motion
1.2.1.3.2.3.2. only one of which is the main axis of a cylinder of a reciprocating piston machine, or
1.2.1.3.2.3.3. two of which are the main axes of two cylinders of a reciprocating machine,
1.2.1.3.3. and form a kinetic unit with the remaining, exclusively rotating masses of an engine;
1.3. mechanical specification of the engine dynamics of feature group 1.2. due to the structure of the following machine elements:
1.3.1. Swinging axis ( 100 ),
1.3.1.1. its geometric axis is a normal to the plane of motion and the cylinder axis, and the intersection with the plane of motion creates one of the moving kinematic points (P, Q) ,
1.3.1.2. it is a cylindrical hollow axis, optionally with
1.3.1.2.1. cylindrical recess ( 101 ), or
1.3.1.2.2. barrel-shaped recess ( 102 ) in a central bearing, or
1.3.1.2.3. semi-barrel-shaped recess ( 103 ) with a pin axis ( 106 ),
1.3.1.3. it is a rotating axis (axis of rotation)
1.3.1.3.1. for a push rod bearing, the control length of which is smaller than the piston diameter, or
1.3.1.3.2. for a shaft piston bearing, the control length of which corresponds at least to the piston diameter,
1.3.1.3.3. it is connected in one piece with two cheeks ( 110 ) or two shaft washers ( 125 ) by means of round or elliptical transitions, in the case of a divided push rod or shaft piston bearing,
1.3.1.3.4. it is constructed in several parts and can be detachably assembled with the cheeks ( 110 ) or the shaft washers ( 125 ) in the case of an undivided push rod or shaft piston bearing - in particular with double pistons in a diametrical arrangement - through
1.3.1.3.4.1. frictional cone, press, or clamping connections, or
1.3.1.3.4.2. positive polygon connection or serration; or
1.3.1.4. it is a non-rotating axis (fixed axis), rotatably mounted in a cheek or shaft disc bore,
1.3.1.4.1. as pin axis ( 105 ),
1.3.1.4.1.1. firmly connected to the undivided push rod bearing, or
1.3.1.4.1.2. integrally formed on the push rod foot by round or elliptical transitions; or
1.3.1.4.2. as pin axis ( 106 )
1.3.1.4.2.1. firmly formed on the piston skirt base of a shaft piston by means of round or elliptical transitions,
1.3.1.4.2.1.1. in one piece, from a continuous pin, or
1.3.1.4.2.1.2. two parts, from two diametrical outer pins;
1.3.1.5. it has channels and bores, or inner concentric guide tubes for guiding a cooling and lubricating fluid;
1.3.2. Cheek ( 110 ),
1.3.2.1. it rotates freely around the median axis (M) ,
1.3.2.2. and has an elliptical basic shape,
1.3.2.3. it contains the bearing bores of the non-rotating axes according to feature group 1.3.1.4., whereby it is made in one piece with an eccentric shaft according to feature group 1.3.3.2. is connected, or
1.3.2.4. it is the connecting element
1.3.2.4.1. of two rotating axes according to feature group 1.3.1.3., or
1.3.2.4.2. from an axis of rotation according to feature group 1.3.1.3. with an eccentric shaft according to feature group 1.3.3.2.,
1.3.2.5. and is the carrier of the integrally formed balancing masses (A) of the entire oscillating mass,
1.3.2.5.1. with calibration points ( 111 ) arranged symmetrically to the effective straight line (W ) for the mass calibration,
1.3.2.6. with bevels ( 112 ) to the swing axes ( 100 ) or the eccentric shafts ( 121 ) according to feature group 1.3.3.2.,
1.3.2.7. and channels for guiding a cooling and lubricating fluid;
1.3.3. Eccentric shaft ( 120 ),
1.3.3.1. its geometric axis is the median axis (M) of the kinematic system with the eccentricity e = r / 2,
1.3.3.2. it is a simple cylindrical shaft ( 121 ) without balancing mass, and has
1.3.3.2.1. in the case of simple storage in an eccentric bearing ( 130 ), an outer diameter which is at most the root diameter of the pinion toothing according to feature 1.4.1.2.2. if the pinion is between the cheek ( 110 ) and the eccentric bearing ( 130 ), or
1.3.3.2.2. an outer diameter which is at least the tip diameter of the pinion toothing according to feature 1.4.1.2.2. if the pinion is at the shaft end, or
1.3.3.2.3. in the case of double storage in a pair of eccentric bearings, it is a stepped shaft ( 122 ), the cheek-side shaft diameter being at least the tip circle diameter of the pinion toothing according to feature 1.4.1.2.2. corresponds and the diameter of the shaft shoulder is smaller than the root diameter of the toothing minus the bearing wall thickness in the eccentric bearing,
1.3.3.2.4. with cutouts according to feature group 1.3.1.2., or it is a
1.3.3.3. Wave washer ( 125 ), with a
1.3.3.3.1. Control diameter that corresponds at least to the sum of the swinging axis diameter and the radius r ,
1.3.3.3.2. with the balancing masses (A) of the entire oscillating mass within the shaft washer ( 125 ), the calibration points, the recesses ( 126 ) and the ribbing ( 127 ) around the swinging axis area,
1.3.3.3.2.1. with a connection of the swing axis according to feature group 1.3.1.3. to the wave washer ( 125 ), or
1.3.3.3.2.2. with a bearing bore ( 128 ) for non-rotating axes according to feature group 1.3.1.4 .; or she is
1.3.3.3.3. without compensating masses (A) inside the shaft washer ( 125 ) for at least two orthogonally acting pistons, and
1.3.3.3.3.1. Connection of two swing axes according to feature group 1.3.1.3.,
1.3.3.3.3.2. or the arrangement of two bearing bores according to feature group 1.3.1.4,
1.3.3.4. with channels, ring grooves and bores for guiding a cooling and lubricating fluid;
1.3.4. Eccentric bearing ( 130 ) for eccentric shafts according to feature group 1.3.3.,
1.3.4.1. its geometric axis is the central axis (Z) of the kinematic system, and
1.3.4.2. it consists of a cylindrical circular disc, the
1.3.4.2.1. Outside diameter is greater than the sum of the eccentric shaft diameter and the radius r , and the
1.3.4.2.2. is rotatably mounted on the base bearing ( 140 ) of the engine housing,
1.3.4.2.2.1. in single arrangement ( 131 ) or in
1.3.4.2.2.2. Bearing pair arrangement ( 132 ) for offset eccentric shafts according to feature 1.3.3.2.3.,
1.3.4.2.3. it contains the eccentric bearing bores of the eccentric shafts
1.3.4.2.3.1. as a single bearing ( 133 ) for the general eccentric shaft ( 120 ),
1.3.4.2.3.2. or as a double bearing ( 134 ) for two eccentric shafts in a radial arrangement, the outer diameter of which is smaller than the radius r , in particular with the radial angles 2π / 2 and 4π / 5 rad,
1.3.4.2.3.2.1. with a double bearing width ( 138 ) with rotating shaft discs ( 125 ),
1.3.4.2.4. and the balancing masses of the total reduced oscillating and the eccentrically rotating engine masses, with the
1.3.4.2.4.1. Recesses ( 136 ) and the ribs ( 137 ) around the bearing bore,
1.3.4.2.5. or it is a double bearing ( 135 ) without compensating masses, for two identical diametrical eccentric shafts according to feature 1.3.3.2.1.,
1.3.4.2.6. with several circumferential holes for the guidance of a cooling and lubricating fluid, and
1.3.4.2.7. optionally with an external toothing ( 139 ) of a part of the bearing width between the bearing surfaces of the eccentric bearing, so that the tip circle diameter of the toothing corresponds to the inside diameter of the base bearing, and the engagement with the spur gears of a main drive shaft arranged in parallel;
1.3.5. Base bearing ( 140 ),
1.3.5.1. it is arranged coaxially to the eccentric bearing,
1.3.5.2. its inside diameter corresponds to the outside diameter of the eccentric bearing ( 130 ) and
1.3.5.3. its outer diameter corresponds to the inner diameter of the engine housing bore, whereby
1.3.5.4. the width of the sliding or rolling surface of the base bearing ( 140 ) corresponds to the width of the eccentric bearing arrangement,
1.3.5.5. it's divided, or
1.3.5.6. closed, and
1.3.5.6.1. optionally integrally connected with a ring gear ( 150 ) according to feature group 1.4.1.1.,
1.3.5.7. it is axially and tangentially adjustable against the engine housing, or
1.3.5.8. it is an integral part of the engine housing,
1.3.5.9. and is provided with annular grooves, channels and bores for guiding a cooling and lubricating fluid;
1.4. Control of the rotational movement of the median axis (M) and the eccentric shaft ( 120 )
1.4.1. consisting of a planetary gear
1.4.1.1. an internally toothed ring gear ( 150 ) on the base bearing ( 140 ),
1.4.1.1.1. coaxial to the central axis (Z) of the engine,
1.4.1.1.2. the pitch circle diameter is identical to the piston stroke 2 r ,
1.4.1.1.3. it is straight or helical,
1.4.1.1.4. fixed and
1.4.1.1.5. adjustably attached to the engine housing,
1.4.1.1.6. the position in the engine depends on the type of eccentric shaft and its row arrangement,
1.4.1.1.6.1. it lies between the cheek ( 110 ) and the eccentric bearing ( 130 ) in the case of an eccentric shaft according to feature 1.3.3.2.1., or
1.4.1.1.6.2. between two eccentric bearings ( 130 ) for an eccentric shaft according to feature 1.3.3.2.3., the width of the ring gear being greater than twice the width of the pinion ( 155 ) for two independently rotating pinions ( 155 ), or
1.4.1.1.6.3. only at the shaft ends of a single-cylinder or a multi-cylinder eccentric shaft according to feature 1.3.3.2.2., and from one
1.4.1.2. revolving external toothed pinion ( 155 ),
1.4.1.2.1. coaxial to the median axis (M) of the engine,
1.4.1.2.2. the pitch circle diameter is identical to the radius r ,
1.4.1.2.3. with a toothing suitable for feature 1.4.1.1.3., and
1.4.1.2.4. firmly connected to the rotating eccentric shaft ( 120 ) in the same position as the ring gear ( 150 ), and
1.4.1.2.5. optionally insertable as a form-fitting coupling part ( 151 ) axially between two adjacent eccentric shafts ( 120 ),
1.4.1.3. or by an epicyclic gearbox according to feature group 1.4.1., the pitch circle diameter of the ring gear is larger than the piston stroke and which is coupled to the eccentric shaft ( 120 ) via a cross-plate clutch (double-loop gearbox),
1.4.2. Play compensation of the backlash between the tooth engagement surfaces on the ring gear ( 150 ) and on the pinion ( 155 ) by a
1.4.2.1. wider toothing of the ring gear ( 150 ) and a
1.4.2.2. coaxial pinion ( 156 ),
1.4.2.2.1. that is connected to a torsion sleeve ( 157 ) and
1.4.2.2.2. is centered on the eccentric shaft axis via a conical connection ( 158 ) and is releasably fastened with an expansion screw ( 159 ), and
1.4.2.2.3. is rotated by a pretension angle with respect to the pinion ( 155 ),
1.4.2.2.4. and with damping elements between the pinions, in particular axially acting friction linings or ring springs; or
1.4.2.3. by a bias angle between the ring gears ( 150 ) of an eccentric shaft portion;
2. Reciprocating piston, in the version as
2.1. Piston ( 200 ) consists of the following elements:
2.1.1. Piston plate ( 210 ), with control function of the upper edge of the plate
2.1.1.1. a flat or spherically convex circular disc,
2.1.1.1.1. with constant base thickness and molded radial reinforcing ribs, inside the piston crown and on the upper piston skirt, or
2.1.1.1.2. with increasing base thickness from the center of the piston crown to the edge of the piston crown,
2.1.2. Piston skirt ( 220 ) with sealing function of the surface,
2.1.2.1. a thin-walled, circular-cylindrical hollow cylinder ( 221 ),
2.1.2.1.1. the ratio of inner to outer diameter depends on the fabric pressure, the strength of the material, the type of cooling, the rotational frequency and the internal ribbing,
2.1.2.2. the total length is greater than the sum of the piston stroke and the swing axis diameter,
2.1.2.3. it acts as a push rod,
2.1.2.4. with transitions to the shaft piston bearing and reinforcing ribs between the piston skirt and the shaft piston bearing,
2.1.2.5. with recesses ( 222 ) in the piston skirt in the plane of movement on the piston base, up to the sliding area of the piston skirt,
2.1.2.6. the surface sliding surface ( 223 ) is optional
2.1.2.6.1. piston ringless
2.1.2.6.1.1. helical grooves ( 224 ) with a semicircular groove base ( 225 ) are machined into the surface sliding surface ( 223 ),
2.1.2.6.1.1.1. one or more courses, or
2.1.2.6.2. for piston rings
2.1.2.6.2.1. in a wide outer ring groove ( 226 ) for a piston ring arrangement according to feature group 2.5., limited by
2.1.2.6.2.1.1. an axis-normal top land flank ( 227 ), and
2.1.2.6.2.1.2. a flat conical counter flank ( 228 ) optionally with a
2.1.3. Shaft piston bearing ( 230 ), analogous to a pin bearing for an axis of rotation according to feature group 1.3.1.3.,
2.1.3.1. molded on the inside of the piston skirt ( 220 ) and on the base,
2.1.3.2. as a one-piece continuous bearing, or
2.1.3.3. as a two-part diametrical edge bearing, or
2.1.3.4. as a central center bearing, analogous to the bearing bracket ( 255 ) of the push rod according to feature group 2.2.3. educated,
2.1.3.5. in a closed version, or
2.1.3.6. divided straight or diagonally in the middle, and screwed several times by a releasable expansion screw connection
2.1.3.6.1. a camp chair with a bearing cap, or
2.1.3.6.2. connects two diametrical bearings of a double-bottomed piston, or with
2.1.4. Pin axes ( 106 ) according to feature group 1.3.1.4.2.,
2.1.4.1. with mounted liners ( 229 ) made of steel alloys for plain or roller bearings in light metal alloys;
2.1.5. Double-shaft piston, which consists of two piston shapes, symmetrical to the axis of the shaft piston bearing, of piston crown ( 210 ) and shaft piston jacket ( 220 );
2.2. Push rod piston ( 240 ), it consists of the elements:
2.2.1. Pressure floor ( 245 ), from one
2.2.1.1. circular disc concentric and orthogonal to the piston axis,
2.2.1.1.1. flat ( 246 ) or spherical convex, and it is
2.2.1.1.2. the pressure part for the concentration of the flat material force,
2.2.1.1.2.1. with constant base thickness for stiffening radial ribs ( 247 ),
2.2.1.1.2.2. or self-stiffening due to increasing floor thickness from the edge of the pressure floor to the center of the pressure floor, and
2.2.1.1.3. Transitions ( 248 ) between the pressure floor boundary surfaces and the inner and outer surfaces of a push rod ( 250 ),
2.2.1.1.3.1. in particular elliptical or parabolic transitions, and
2.2.1.1.4. rigid connection to a coaxial
2.2.2. Push rod ( 250 ), from one
2.2.2.1. straight and short hollow shaft,
2.2.2.1.1. with a connecting rod ratio which corresponds to a connecting rod ratio r / l from 1: 2, and
2.2.2.1.2. with circular cylindrical or elliptical cross section, and one
2.2.3. Storage chair ( 255 ),
2.2.3.1. with transitions or formations between the hollow shaft and the bearing bracket,
2.2.3.2. undivided for receiving a socket, or
2.2.3.3. divided for the accommodation of a bearing cover ( 256 ) or the bearing chair of a diametrically lying push rod,
2.2.3.3.1. for holding two bearing shells
2.2.3.3.1.1. with coaxial bearing shell back and sliding surface, for a relative movement with two degrees of freedom between the bearing shells and the oscillation axis, or
2.2.3.3.1.2. optionally equipped with a bearing shell back, which consists of a circular cylinder section, the axis of which is a normal of the shaft and the oscillation axis, the radius of the bearing shell back being larger than the outer radius of the oscillation axis, for a relative movement with four degrees of freedom between the bearing bracket and the oscillation axis with a
2.2.4. Piston jacket ( 260 ) with sealing function of the piston jacket and control function of the piston jacket edges,
2.2.4.1. its outer diameter corresponds to the slide track diameter,
2.2.4.2. it consists of a thin-walled circular cylindrical sleeve, and
2.2.4.3. is directly connected to the pressure floor ( 245 ) by means of transitions,
2.2.4.4. the jacket length depends on the mode of action of the piston,
2.2.4.4.1. it is greater than the total height of the inlet radial channels in the single-acting piston, or
2.2.4.4.2. corresponds to a quarter of the piston stroke for a double-acting piston,
2.2.4.5. it has a surface sliding surface according to feature group 2.1.2.6., and
2.2.4.6. Engagement and centering surfaces for a partial piston cap above the pressure floor according to feature group 2.3.1.4., For the versions with piston cap, or
2.2.5. Without piston skirt for an integral piston cap, the radial ribs ( 247 ) being connected to the pressure plate ( 245 ) and the push rod, and the engagement surfaces for a positive connection, centering surfaces or contact shoulders according to feature group 2.3.1.4. for a piston cap ( 270 );
2.3. Piston cap ( 270 ) as a partial piston cap or integral piston cap,
2.3.1. it consists of a circular cylindrical cap jacket ( 271 ),
2.3.1.1. whose outer diameter is identical to the piston diameter,
2.3.1.2. with a length according to characteristic 2.2.4.4. with a push rod piston without piston skirt, or
2.3.1.3. which is only a fraction of the total length of a shaft or push rod piston jacket,
2.3.1.4. it is fixed axially opposite the radial ribs on the push rod or the piston skirt
2.3.1.4.1. Internal thread ( 272 ), especially with
2.3.1.4.1.1. continuous flat, trapezoidal or sawing profile, or
2.3.1.4.1.2. as a bayonet version, or one
2.3.1.4.2. Bayonet connection ( 273 ), the
2.3.1.4.2.1. is radially displaceable, by plane normal flanks of the ring grooves, or
2.3.1.4.2.2. angularly displaceable, by concentric spherical flanks of the ring grooves, the center of the spherical shells also being the center of the spherical surface of the pressure plate ( 245 )
2.3.1.4.3. or a fitting bore with contact shoulder and groove for a snap ring, and
2.3.1.5. the surface sliding surface according to feature group 2.1.2.6. is formed, and represents the top land of a piston for an internal combustion engine; if the end face of the cap casing is the flank of the wide annular groove according to feature 2.1.2.6.2.1.1. is in a piston skirt, and
2.3.2. it is connected in one piece to a flat circular disc, or a curved disc that follows the pressure floor surface, with isotropic expansion behavior when the temperature changes,
2.3.2.1. it consists of a thin membrane disc ( 275 ), and
2.3.2.1.1. it is attached at a short distance in front of the pressure floor, the distance being determined by calibrated spacer rings ( 276 ) between the systems,
2.3.2.1.2. A circumferential annular groove ( 277 ) on the inner corner between the membrane disc ( 275 ) and the cap jacket ( 271 ) also reduces the wall thickness of the cap jacket ( 271 )
2.3.2.1.2.1. a trapezoidal, rounded cross-section,
2.3.2.1.3. it has a coaxial beam splitter ( 278 ), and
2.3.2.1.4. it consists of a heat-resistant and good heat-conducting material with coordinated thermal expansion coefficients, either of a metal or a metal alloy, or of a non-oxide ceramic, in particular SiC,
2.3.2.2. or it's an insulating washer,
2.3.2.2.1. the slice thickness is a function of the set temperature difference between the two surfaces, and
2.3.2.2.2. it touches the pressure floor ( 245 ), and
2.3.2.2.3. contains one or more combustion chamber troughs,
2.3.2.2.4. it consists of a heat-resistant and well-insulating material, in particular an oxide ceramic such as Al₂O₃-TiO₂,
2.4. Piston cooling by supplying a cooling fluid via the oscillation axis bearings of the oscillation axis ( 100 )
2.4.1. Cooling of the piston crown center through the
2.4.1.1. central supply of the cooling fluid
2.4.1.1.1. in the hollow shaft of the push rod ( 250 ) of a push rod piston,
2.4.1.1.2. or in a coaxial pressure tube ( 280 ), and
2.4.1.2. Return to the collecting room
2.4.1.2.1. through the annular surface between the pressure pipe ( 280 ) and the hollow shaft, and the drain holes on the hollow shaft foot, or
2.4.1.2.2. over the open annular gap ( 281 ) between the pressure tube and the piston crown of a shaft piston; or one
2.4.2. integral surface cooling of the piston crown at one
2.4.2.1. central supply of cooling fluid according to feature group 2.4.1.1.,
2.4.2.1.1. with a radial distribution of the cooling fluid
2.4.2.1.1.1. in the surface gap between the membrane disc ( 275 ) and the pressure plate ( 245 ), or above
2.4.2.1.1.2. semicircular, open radial grooves in the pressure floor surface, or over
2.4.2.1.1.3. Channels in the radial ribs, with mutually offset junctions at the central feed point, and the
2.4.2.1.2. Deflection of the cooling fluid flow in the annular groove ( 277 ) of the piston cap ( 270 ), and the
2.4.2.1.3. Return to the collecting room via
2.4.2.1.3.1. the cylinder surface gap between the lower edge of the pressure floor and the annular groove edge of the piston cap ( 270 ), or over
2.4.2.1.3.2. a ring of holes in the piston skirt ( 220, 260 ), or over
2.4.2.1.3.3. radial channels in the pressure plate ( 245 ) or in the radial ribs ( 247 )
2.4.2.1.3.3.1. with immediate drain into the collecting room, or
2.4.2.1.3.3.2. over the ring surface according to feature 2.4.1.2.1. derived; and
2.4.2.2. with peripheral supply of the cooling fluid via the edge bearings or the journal axes ( 106 ) of a shaft piston, via
2.4.2.2.1. Rising channels on the inside of the piston skirt ( 220 ), and
2.4.2.2.2. radial distribution of the cooling fluid in radial, star, or tangential channels on the piston crown ( 210 ), and
2.4.2.2.3. Return to the collecting room via
2.4.2.2.3.1. an open central collection opening and direct drain, or
2.4.2.2.3.2. via individual, tangentially aligned, drain holes in the cooling channels with gating on the upper piston skirt;
2.5. Piston ring arrangement, which consists of
2.5.1. the alternative sequence of sealing rings from several radially deformable, elastic rectangular rings with ring joint, in detail
2.5.1.1. sliding outer rings ( 290 ) with a wide sliding surface,
2.5.1.1.1. whose outer diameter is larger than the inner diameter of the slideway in the relaxed state, and
2.5.1.2. non-sliding inner rings ( 291 ) with a narrow contact surface,
2.5.1.2.1. whose inner diameter in the relaxed state is smaller than the outer diameter of the piston groove base, and one
2.5.1.3. non-sliding trapezoidal clamping ring ( 292 ),
2.5.1.3.1. wherein in the installed state the inner diameter is larger than the outer diameter of the piston groove base and the outer diameter is smaller than the slide track diameter under all operating conditions, and
2.5.1.3.2. Due to its inward radial prestressing force on the counter flank ( 228 ) of the outer ring groove ( 226 ), an axial wedge force effect is generated, which exerts a surface pressure on all piston rings and on the top land flank ( 227 ),
2.5.1.4. so that there are annular vortex chambers ( 295 ) between the outer and inner rings ( 290, 291 ) on the piston slideway and on the piston groove base, and
2.5.1.5. All rings are radially displaceable in the installed state and in operation, taking into account the greatest temperature and mass forces on the ring arrangement.
3. There are openings in the cylinder wall and in the cylinder head
3.1. Inlet radial channels ( 300 ), which are evenly distributed around the circumference of the cylinder wall of a displacement chamber, the cylinder axis being the intersection line of all main planes (H) of the inlet radial channels,
3.1.1. their number n (n ∈ N) depends on the cylinder arrangement, the wall thickness of the control element, the internal pressure in the cylinder, the external working fluid guide, the material properties and the cycle or combustion process,
3.1.2. the radial angle between the main planes (H) of the inlet radial channels is:

• - 2 π / n rad
  with a work machine and
  in the case of an internal combustion engine for the four-stroke process or the two-stroke process with overflow channels,
• - 2 π / nk rad
  in an internal combustion engine for the two-stroke process without overflow channels (with k ∈ N) ,

3.1.3. the total height of the internal cross-section depends on the piston skirt and the cycle method,
3.1.3.1. for a piston ( 200 ) it is
3.1.3.1.1. only limited by the stroke length of the piston, in a working machine or in an internal combustion engine for the four-stroke process, or it
3.1.3.1.2. is predetermined by the selected control angle of the drive shaft for the working fluid inlet around the bottom dead center, in an internal combustion engine for the two-stroke process, and
3.1.3.2. for a push rod piston ( 240 ) it is
3.1.3.2.1. shorter than the length of the piston skirt, or in the single-acting push rod piston of a machine or an internal combustion engine for the four-stroke process
3.1.3.2.2. equal to the length of the piston skirt, with the double-acting push rod piston and overflow channels of an internal combustion engine for the two-stroke process,
3.1.4. The standard width b _{S of} the internal cross-section in the control mirror surface is:
3.1.4.1. b _S = R _S πΦ / 2 n in a work machine or in an internal combustion engine for the two-stroke process with overflow channels,
3.1.4.2. b _{S ₄} = R _S πΦ / 4 n in an internal combustion engine for the four-stroke process,
3.1.4.3. b _{S ₂} = R _S πΦ / 2 nk in an internal combustion engine for the two-stroke process without overflow channels, so that the
Total width of all nk (k ∈ M = {2, 3, 4,...}) Inlet openings at bottom dead center is at least Σ b _{S ₂} = R _S π , where
Φ is the steering angle coefficient for the working fluid inlet, a quotient of the predetermined total control angle in radians of the drive shaft to the control angle π rad for a full stroke, and
R _{S is} the radius of the circular cylindrical control mirror surface, and the
3.1.5. Control edges ( 301 ) are the surface lines of the two parallel inner wall planes of the inlet radial channels in the control mirror surface,
3.1.6. Webs ( 302 ) divide the inlet radial channels ( 300 ) into sub-channels, starting from a predetermined ratio of the channel width to the channel height,
3.1.6.1. they are firmly attached to the canal walls,
3.1.6.2. they have round or elliptical transitions ( 303 ) to the channel wall,
3.1.6.3. the distribution of the webs on the total height of the inlet radial channel ( 300 ) is carried out in such a way that more webs are arranged at the highest fluid pressure and fewer webs at the greatest volume change due to the piston movement, and so on
3.1.6.3.1. takes into account the position of the cooling fins during air cooling of the cylinder wall, so that the webs ( 302 ) and the cooling fins are congruent outside the wall opening cross section,
3.1.6.4. the webs ( 302 ) are made of reinforcements when the cylinder wall is made of light metal alloys
3.1.6.4.1. annular high-strength steel inserts, or
3.1.6.4.2. Mineral fiber bundle made of oxide ceramic materials, e.g. B. Al₂O₃ or made of non-oxide ceramic materials, for. B. SiC,
3.1.6.5. their minimum cross-section in the channel direction is larger than the proportionate opening cross-section in the cylinder wall,
3.1.7. the position of the inlet radial channels ( 300 ) is on the cylinder wall
3.1.7.1. exactly radially in the direction of the main plane (H) , or
3.1.7.2. aligned tangentially to the displacement chamber, and
3.1.8. the surrounding upper channel walls ( 303 ) and the lower channel walls ( 304 ) including the dividing webs ( 302 ) lie in relation to the cylinder axis
3.1.8.1. orthogonal planes, or in
3.1.8.2. inclined planes, especially screw surfaces, and
3.1.9. the outer sub-channels are guided
3.1.9.1. bringing together
3.1.9.1.1. when the working fluid is supplied axially in a collecting channel ( 305 ) on the cylinder wall with a semicircular cross section which grows linearly with the connected free opening cross section in the control mirror surface, or
3.1.9.1.2. with radial supply of the working fluid in an annular channel around the cylinder wall, or it
3.1.9.2. remains separate, by connecting the inlet subchannels to associated connecting channels, especially in internal combustion engines, and
3.2. Exhaust radial channels ( 310 ), which are distributed analogously to the inlet radial channels ( 300 ) on the circumference of the cylinder wall, with the following special features:
3.2.1. their total height of the inner cross section at the upper cylinder section is optionally shorter than the total height of the inner cross section of the inlet radial channels ( 300 ), and
3.2.2. the main planes of the outlet radial channels ( 310 ) are offset from the main planes (H) of the inlet radial channels ( 300 ),
3.2.2.1. with adjacent channels

• - π / n rad
  in a work machine, the position being independent of the direction of rotation of the control member,
• - π / 2 n rad
  in the case of an internal combustion engine for the four-stroke process, the position being dependent on the direction of rotation of the control member, so that the outlet radial ducts ( 310 ) lie in front of the inlet radial ducts ( 300 ),
  with a given direction of rotation,
  and form

3.2.2.2. with channels one above the other, any radial angle from 0 to π / n rad, with an internal combustion engine for the two-stroke process, or they are optional
3.2.2.3. offset by a further radial angle ϕ _S , for the pre-discharge of the working fluid or an overlap of the control angles for the inlet / outlet at selected piston positions,
3.3. Overflow channels ( 320 ) for an internal combustion engine for the two-stroke process and a double-acting piston,
3.3.1. they connect the closed compression space ( 325 ) on the underside of the piston to the displacement space, and
3.3.2. they lie between the inlet radial channels ( 300 ),
3.3.3. their height is according to feature 3.1.3.1.2. set, and
3.3.4. the width according to feature 3.1.4.1.,
3.3.5. the channel shape in the cylinder jacket has a semicircular ring shape ( 321 ) with an oblique cylinder inlet ( 322 ), and
3.3.6. the inner diameter of the circular ring ( 321 ) corresponds to the length of the piston skirt of a push rod piston ( 240 ) according to feature 2.2.4.4.2.
3.4. Inlet axial channels ( 330 ) are even in the tip circle of the cylinder head analogous to feature group 3.1.2. distributed, their main planes coinciding with the main planes (H) of the inlet radial channels ( 300 ), or being offset from the main planes (H) by a radial angle of 0 to π / n rad,
3.4.1. their number n is identical to the number of inlet radial channels ( 300 ) in the cylinder wall,
3.4.2. the total length of the inner cross section is limited
3.4.2.1. outside by the piston or cylinder radius,
3.4.2.2. inside by the outer radius of the journal bearing ( 335 ) for a rotary slide journal ( 405 ), or a prechamber, an ignition or fuel injection device or the like,
3.4.3. the opening angle of the radial control control edges ( 331 ) in the control mirror surface is analogous to the control width of the inner cross section of the inlet radial channels ( 300 ) through the equations according to feature group 3.1.4. fixed without the factor R _S , where
3.4.3.1. Connect the radii of the control edges on the inside and transfer them to the delimiting arc of the piston or cylinder circuit on the outside
3.4.4. their surrounding channel walls are due to the general channel course according to feature group 3.4.5. given, the radial walls ( 332 ) being caused by the control edges ( 331 ), and at the same time
3.4.4.1. Stiffening ribs of the cylinder head cover are, and the
3.4.4.2. outer wall surfaces are rounded off with the cylinder head cover and the wall ( 334 ) of the journal bearing ( 335 ),
3.4.5. the total cross-section is optionally divided by thin webs, in accordance with features 3.1.6.1.2.,
3.4.6. the channeling of the inlet radial channels ( 330 ) follows their main planes
3.4.6.1. directed radially outwards
3.4.6.1.1. via a bend ( 336 ) into an annular channel ( 337 ), or
3.4.6.1.2. a suction funnel directly into the atmosphere, or
3.4.6.2. axially into one
3.4.6.2.1. collecting duct ( 338 ) coaxial to the cylinder axis, or in
3.4.6.2.2. several parallel subchannels of an outer combustion chamber,
3.4.6.3. the main planes being at an angle to the cylinder axis or being replaced by screw surfaces, and
3.4.7. they are via connecting channels ( 339 )
3.4.7.1. directly to the inlet radial channels ( 300 ), or
3.4.7.2. connected to the outlet radial ducts ( 310 ) via a Venturi tube or a throttle or blocking element,
3.5. Exhaust axial channels ( 340 ) are analogous to the inlet axial channels, distributed in the tip circle of the cylinder head, taking into account the position of the inlet radial channels ( 300 ) and the exhaust radial channels ( 310 ), whereby
3.5.1. the position of the main levels from feature 3.2.2.1. in connection with the ducting according to feature group 3.4.6. follows, and
3.5.2. the suction funnel according to feature 3.4.6.1.2. is replaced by a Laval nozzle, and
3.5.3. the connecting channels ( 339 ) to the outlet radial channels ( 310 ), or the inlet radial channels ( 300 ) or the inlet axial channels according to feature group 3.4.7. are executed
3.6. Depending on the method selected, cylinder head has feature group 7 for the change of working fluid
3.6.1. no openings for fluid change, whereby
3.6.1.1. the inner cylinder head surface according to feature group 4.2.3. is shaped or has
3.6.2. Inlet axial channels ( 330 ) and / or outlet axial channels ( 340 ) and
3.6.2.1. a control mirror surface to the displacement chamber, as
3.6.2.1.1. Flat cone ( 350 ), or as
3.6.2.1.2. Spherical cap, and the
3.6.2.1.3. forms a sealing surface on the cylinder head for the control element of the working fluid change,
3.6.3. the cylinder head is centered in the cylinder
3.6.3.1. congruent axes of the cylinder head and cylinder, above with a flat and axis-normal control mirror surface by a
3.6.3.1.1. Press fit between centering projection ( 355 ) on the cylinder head and cylinder wall, or through
3.6.3.1.2. a plastically deformable metallic trapezoidal ring between the centering insert ( 355 ) on the cylinder head and a conical expansion of the cylinder wall, or by
3.6.3.1.3. a flat tapered washer between the centering shoulder on the cylinder head and an annular rebate ( 356 ) in the cylinder wall;
3.6.3.2. non-congruent axes of the cylinder head and cylinder
3.6.3.2.1. a double eccentric arrangement according to feature group 11 between the centering projection ( 355 ) and the annular fold ( 356 ) in the cylinder;
3.7. Closure cover ( 360 ) of the compression space on the underside of the piston is a functional part of a double-acting push rod piston,
3.7.1. it consists of two half-shells ( 361 ) which are detachably connected in an undivided push rod, and
3.7.2. it has a curved, conical base ( 362 ), the inner shape of the pressure base ( 245 ) and the piston skirt ( 260, 271 ), and the outer shape of the bearing block ( 255 ) adapted, with a coaxial sealing ring bearing ( 363 ), and one
3.7.3. Centering in the control mirror surface of the cylinder with dowel pins or the like for unmistakable fastening, and
3.7.4. the connection channels ( 365 ) of the overflow channels ( 320 ),
4. Working fluid is controlled by the simultaneous stroke movement of the piston and the rotary movement of the control member, with a complete stroke of the piston rotating the control member

• π / n rad
  in a work machine or an internal combustion engine for the two-stroke process, or
• π / 2 n rad
  in an internal combustion engine for the four-stroke process,

4.1. the control element is a thin-walled, circular cylindrical rotating sleeve ( 400 ),
4.1.1. the outer surface is the control mirror surface, and
4.1.2. the inner surface is the slideway for a reciprocating piston,
4.1.3. the openings in the rotary sleeve ( 400 ) are congruent with the inlet openings of the inlet radial channels ( 300 ) in the cylinder wall,
4.1.3.1. and, depending on the process, are both inlet and outlet openings,
4.1.3.2. the control edges in the rotary sleeve ( 400 ) in the upper and lower stroke section of the piston can deviate from the position of the control control edges by a radial angle ϕ _E , or the opening control edges represent a sine curve when the control mirror surface is developed,
4.1.3.3. they are aligned radially or tangentially, corresponding to the channel direction in the cylinder wall, and they
4.1.3.4. have funnel-shaped widenings ( 401 ) of the control edges towards the slideway,
4.1.2. the rotating sleeve ( 400 ) is pressed against the cylinder head by an axial force,
4.1.2.1. the axial force is a material force of a pressure fluid on the flank surface of an outer rotating sleeve collar ( 402 ), wherein
4.1.2.1.1. an annular pressure chamber ( 403 ) is or is connected to the pressure chamber in a work machine via channels
4.1.2.2. the axially acting component on the sleeve teeth of the driving force, or
4.1.2.3. the spring force of a prestressed pressure roller or a sliding block acting on the end face of the rotating sleeve base, or
4.1.2.4. the material pressure of the working fluid on an inner collar on the rotating sleeve,
4.1.3. it is sealed against the cylinder head by
4.1.3.1. floating coaxial slide rings and fixed counter ring in the cylinder head, or through
4.1.3.2. a minute grinding angle of the rotating sleeve face and fixed counter ring in the cylinder head, or by
4.1.3.3. a sliding counter ring in a U-shape with a wave ring spring,
4.1.4. it has lubrication grooves, lubrication pockets, bores and helical lubrication grooves in the control mirror surface for the distribution of a lubricating fluid, and
4.1.4.1. Accumulation fields, wedge surfaces and distribution grooves for a multi-surface plain bearing on the rotating sleeve base, in particular for gas storage with connection to the sliding gap between the piston skirt and slideway,
4.1.5. it consists of a composite material made of metal and a ceramic material, the thickness of the individual layers being based on the calculated temperature gradient between the inner surface and the outer surface of the rotating sleeve, for determining the internal temperature, the thermal expansion or the bearing play in the control surface,
4.2. the control element is a rotating sleeve according to feature group 4.1., which is firmly connected to a coaxial flat rotary valve ( 410 ),
4.2.1. the openings in the rotary valve ( 410 ) are congruent with the inlet openings of the inlet axial passages ( 330 ) in the control mirror surface of the cylinder head, and
4.2.2. the outer surface corresponds to the feature group 3.6.2.1., and
4.2.3. the inner surface of the rotary valve ( 410 ) can be freely defined between the selected axial control mirror surface and the piston surface,
4.2.3.1. it is an axial translation of the piston surface, in a working machine, or it is
4.2.3.2. a surface of revolution, with the cylinder axis as the axis of rotation, of an arbitrarily constructed generator, in particular
4.2.3.2.1. from circular arc ( 411 ) in connection with sections ( 412 ), and
4.2.3.3. with the piston surface it creates pinch zones and compact compression spaces in internal combustion engines, and it is included
4.2.4. connected to a coaxial pin ( 405 ) which
4.2.4.1. has a centering cone ( 407 ) with threaded pin ( 408 ) for receiving a sealing body ( 406 ), and in
4.2.4.2. the outer surface of the sealing body ( 406 ), grooves according to feature 2.1.2.6.1.1. Has,
4.2.5. the rotary valve rotary sleeve unit is pressed against the control mirror surface on the cylinder head by an axial force
4.2.5.1. from the adhesive work of the lubricating film between the control mirror surfaces, or
4.2.5.2. from a spring-loaded axial roller bearing at the end of the pin, or
4.2.5.3. from the lubricating fluid pressure to the base of the sealing body ( 406 ),
4.2.5.4. or from a combination with axial forces according to feature group 4.1.2. exists, and
4.2.6. the bearing of the rotary valve pin ( 405 ) in the pin bearing is a plain bearing according to feature group 4.1.4. or a roller bearing, which is optionally available with
4.2.6.1. Double eccentric rings according to feature group 11 are centered in the journal bearing,
4.2.7. the axial bearing of the rotary valve rotating sleeve unit is a hydrodynamically lubricated axial bearing between the control mirror surfaces on the cylinder head and on the rotary valve,
4.2.7.1. in particular a single-disc thrust bearing, or
4.2.7.2. a multi-surface thrust slide bearing with lubrication grooves, lubrication grooves and wedge surfaces in the control mirror surface of the rotary valve;
5. The control element is driven
5.1. mechanically via a gear arrangement, with a total transmission ratio i , corresponding to the quotient of the angular velocity of the drive shaft and the angular velocity of the control member, wherein
i = 2 n : 1 in an internal combustion engine for the four-stroke process,
i = n : 1 for an internal combustion engine for the two-stroke process or for a work machine,
is determined by the selected number n of the inlet radial channels ( 300 ), and the angular position of the opening and closing control edges ( 301, 331 ) on the control member relative to the opening and closing control edges in the cylinder wall or in the cylinder head by the position of the upper piston edge on the stroke is fixed, at which the control edges open and close, this also applies to the lower piston edge in internal combustion engines with a compression and supercharger function of the underside of the piston, in particular with
5.1.1. Gear transmission in the engine housing, with an external toothing ( 500 ) of the rotating sleeve base, and one
5.1.1.1. Control shaft ( 510 ), rotatably mounted in the engine housing
5.1.1.1.1. its axis is parallel to the axis of the drive shaft,
5.1.1.1.2. it is a hollow shaft,
5.1.1.1.3. mounted in two bearings ( 511 ) symmetrically to the engagement distance on the external toothing ( 500 ) of the rotating sleeve base, and
5.1.1.1.4. with a tip diameter of the toothing, which corresponds to the outer diameter of the hollow shaft,
5.1.1.1.5. it is driven by a spur gear pair ( 512 ), the driving wheel being attached directly to the drive shaft, and
5.1.1.1.6. it has an axial fixed bearing with position adjustment, or
5.1.1.1.7. it is axially displaceable, and
5.1.1.1.8. on the path of engagement with the control member, the control shaft has a helical gear toothing in the form of a
5.1.1.1.8.1. Helical gear teeth for partial gear ratios up to 5: 1, or one
5.1.1.1.8.2. Worm gear teeth for partial gear ratios from 5: 1, whereby it forms a roller gear with intersecting axes with the teeth of the rotary sleeve base; or one
5.1.1.2. Spur gear ( 520 )
5.1.1.2.1. its axis is parallel to the cylinder axis,
5.1.1.2.2. it is straight or helical, and
5.1.1.2.3. it is connected to the drive shaft via an intermediate shaft ( 525 ) and a helical gear, as a bevel gear pair ( 521 ) when axes intersect, or as a pair of helical gears ( 522 ) when axes intersect; or a
5.1.2. Gear transmission in the cylinder head, with an external toothing ( 530 ) of the rotating sleeve collar ( 402 ), and one
5.1.2.1. Spur gear ( 535 ) in the plane of the rotating sleeve,
5.1.2.1.1. its axis is parallel to the cylinder axis, and
5.1.2.1.2. it has an extended intermediate shaft ( 525 ) compared to the drive according to feature group 5.1.1.2., and
5.1.2.1.3. is otherwise according to feature 5.1.1.2.3. driven;
5.1.3. Gear transmission over the cylinder head, in the case of an external drive via the rotary slide pin ( 405 ), whereby
5.1.3.1. the control shaft drive according to feature group 5.1.1.1. engages in a spur gear on the rotary valve pin, the
5.1.3.1.1. via an intermediate shaft ( 525 ) and two screw gears, or
5.1.3.1.2. is moved by a positive traction mechanism from the drive shaft, or
5.2. electrically with a
5.2.1. Drive for converting electrical energy into rotational work, especially one
5.2.1.1. Stepper motor ( 540 ) per cylinder unit, where
5.2.1.1.1. the stator is fixed to the cylinder head, and
5.2.1.1.2. the rotor is firmly connected to the rotary valve pin ( 405 ),
5.2.1.2. and the relative position of the control member and the drive shaft can be read off by angle-coded disks via an electro-optical or electromagnetic sensor unit and is regulated by a control unit, or
5.2.2. with a direct coupling of the drive according to feature group 5.2.1.1. to the control shaft ( 510 ), or
5.3. hydraulic or pneumatic with one
5.3.1. Drive for converting pressure medium energy or flow energy into rotational work, in particular
5.3.1.1. Vane motors and gear motors, with one
5.3.1.2. Control of the relative position according to feature 5.2.1.2. by regulating the pressure or the flow velocity of the fluid,
5.4. Simultaneous drive of multi-cylinder in-line arrangements
5.4.1. with the same direction of rotation of the control elements
5.4.1.1. via a one-piece control shaft ( 510 ) for all control elements with a toothing on the engagement paths that increases in the same direction, or
5.4.1.2. via idler gears ( 550 )
5.4.1.2.1. on the rotating sleeve base, or
5.4.1.2.2. in the rotating sleeve plane
5.4.2. with changing direction of rotation of the control elements
5.4.2.1. via a one-piece control shaft ( 510 ) for all control elements with oppositely increasing teeth on the engagement sections,
5.4.2.2. or with direct engagement of the rotating sleeve collar teeth ( 530 ),
5.5. Regulation of the control angle as a function of the rotational frequency, the torque of the drive shaft or the intake pressure by changing the phase angle difference between the drive shaft and the control member
5.5.1. the axial displacement of the control shaft ( 510 )
5.5.1.1. mechanically
5.5.1.1.1. with manual actuation via a lever system ( 560 ) or via Bowden cables, or
5.5.1.1.2. with automatic actuation by electric or hydraulic drives of the lever systems ( 560 ), or
5.5.1.1.3. by reshaping the radial displacement of the movable rotating mass into an axial movement, the rotational frequency-dependent radial forces being compensated by restoring forces of elastic materials or springs with coordinated characteristic curves, or
5.5.1.2. electromagnetic ( 570 ) due to the action of magnetic forces
5.5.1.2.1. on linearly movable actuators on the control shaft, or
5.5.1.2.2. via servomotors to a mechanical system,
5.5.1.3. hydropneumatic ( 580 ), via a pressurized piston,
5.5.1.3.1. single-acting, with restoring force via a spring system, or
5.5.1.3.2. double acting, with pressure control of the piston position, or by
5.5.2. the angular displacement of the control shaft ( 510 ) or the intermediate shaft ( 525 )
5.5.2.1. mechanically
5.5.2.1.1. by reshaping the radial displacement according to feature 5.5.1.1.3. in a rotary motion, or
5.5.2.1.2. through a phase shifter gear ( 590 ) in front of the control shaft ( 510 ) consisting of a planetary gear as a minus gear with a stationary ratio i _o <-1, or i _o = -1 from two identical bevel gear pairs, through the regulated change of the position of the web according to feature group 5.5. 1.1., Or
5.5.3. electromagnetic, through the direct coupling of the control shaft with a stepper motor and control according to feature 5.2.1.2 .;
6. change of the compression ratio with constant stroke and constant dimensions of the displacement space,
6.1. discretely by a combination of different shapes and thicknesses of the rotary valve ( 410 ), the membrane disc ( 275 ), or of intermediate discs on the pressure plate ( 245 ), or
6.2. mechanically stepless
6.2.1. by a regulated change in the push rod length as a function of the load, the rotational frequency or the fuel ignition behavior,
6.2.2. by dividing the push rod ( 250 ) of a push rod piston in one
6.2.3. rotatable outer shaft ( 251 ) which is fixedly connected to the pressure base ( 245 ), and
6.2.3.1. has circumferential engagement surfaces that are made of
6.2.3.1.1. there are planes parallel to the push rod axis,
6.2.3.1.1.1. in a diametrical arrangement of two levels, or
6.2.3.1.1.2. in a regular arrangement of several levels, in particular
isogonal cross sections, or from
6.2.3.1.2. a profile-shaft connection, in particular a polygon profile connection, and in one
6.2.4. Inner shaft ( 252 ), which is fixedly connected to the bearing block ( 255 ) or a pin axis ( 105 ), and the
6.2.5. positive connection of the outer shaft ( 251 ) with the inner shaft ( 252 )
6.2.5.1. is caused a movement screw that
6.2.5.1.1. is single or multi-course, and
6.2.5.1.2. has a thread profile with a small flank angle, in particular a rectangular, trapezoidal or sawing profile, wherein
6.2.6. the initiation of the rotary movement on the outer shaft ( 251 )
6.2.6.1. a control disc ( 600 ) with an enclosed engagement surface, corresponding to the profile of the outer shaft ( 251 ), the
6.2.6.1.1. Basic shape corresponds to a sealing cover ( 360 ) with teeth,
6.2.6.1.2. and which is rotatably mounted on the cylinder base,
6.3. hydraulically stepless,
6.3.1. by a piston cap which is movable and sealed against the piston head and is pressurized internally by a pressure fluid;
7. Procedures for fluid management of the
7.1. Working fluid change of a working machine or an internal combustion engine for the four-stroke process
7.1.1. in the inverse process, through inlet and outlet openings that are only in the cylinder wall, with predominantly radial-tangential inflow and outflow of the working fluid, or
7.1.2. in the anabatic process, through inlet openings in the cylinder wall and outlet openings in the cylinder head, with predominantly radial-tangential inflow and axial outflow of the working fluid, or
7.1.3. in the mixed procedure according to characteristics 7.1.1. and 7.1.2., through inlet and outlet openings in the cylinder wall and in the cylinder head;
7.2. Charge change of the internal combustion engine for the two-stroke process,
7.2.1. in the inverse method according to feature 7.1.1., wherein the inlet openings are arranged around bottom dead center and the outlet openings around top dead center, or
7.2.2. in the anabatic procedure according to characteristics 7.1.2. and 7.2.1., or
7.2.3. in the overflow channel method
with the overpressure introduction of the fresh gases through overflow channels into the displacement chamber, the gas masses sucked in from the underside of the piston and compressed in the compression chamber;
8. Procedure for the stratification of fuel-air mixtures in internal combustion engines by the introduction of fuel-air mixtures with different fuel content ( λ values), in connection with fresh air or exhaust gas, via separate inlet subchannels according to feature groups 3.1. and 3.4.,
8.1. with radial stratification,
by the tangential guidance of the fresh gases in the inlet radial channels ( 300 ) and the helical guidance in the inlet axial channels ( 330 ),
8.2. with axial stratification,
8.2.1. by the radial-tangential guidance of the fresh gases in the inlet radial channels ( 300 ), or
8.2.2. by the indirect injection of the fuel into the axial collecting channels, the specific fuel distribution in front of the inlet openings being generated by the characteristic outlet jet of the injection nozzle,
8.3. with axial-radial stratification according to feature 8.1. and 8.2. optionally combined with
8.4. regulated preheating through the recirculation of exhaust gas into the displacement space according to feature group 3.4.7., and
8.5. the expulsion of the residual gases by the introduction of fresh air at the piston end positions before the introduction of the fuel-air mixture;
9. Modular construction through the arrangement of the five different modules:

• - Module with a cylinder as a mono block
• - module with two cylinders in tandem arrangement,
• - Module with two cylinders in a boxer arrangement,
• - module with two cylinders in V 90 arrangement,
• - module with four cylinders in X 90 arrangement,
  which represent individual components with a defined output, for the composition of multi-cylinder machines with a simple multiple of the module output in

9.1. axial arrangement of the modules with a cylinder, or of tandem or boxer modules, and the combination of the rotational energy via angular gear on a central main shaft, or
9.2. radial arrangement of mono blocks or tandem blocks; or
9.3. Row arrangement of
9.3.1. Mono blocks, whereby the eccentric shaft ( 121, 122 ) and the eccentric bearing ( 132, 134, 135 ) are themselves the form-fitting, coupling elements, according to the characteristics 1.3.3.2.1 .; 1.3.3.2.3. and 1.3.4.2.2.2 .; 1.3.4.2.3.2; 1.3.4.2.5., Or
9.3.2. Single cylinder in a machine block and a one-piece drive shaft
9.3.2.1. with continuous swing axes, especially 4-cylinder machines in a boxer arrangement,
9.3.2.2. with offset swing axes,
for multi-cylinder machines in V 90 or in X 90 arrangement,
9.3.2.3. with at least four coaxial gears, which are firmly connected to the drive shaft and which engage in the external toothing ( 139 ) of the eccentric bearing, provided that the eccentric bearings for each cylinder unit can be rotated independently in pairs.
10. external combustion engine,
10.1. their mechanical structure corresponds to a work machine, whereby
10.1.1. the inlet openings in the cylinder head and
10.1.2. the outlet openings are arranged in the cylinder wall, and
10.1.3. the gas exchange through a rotary valve rotating sleeve unit according to feature group 4.2. is controlled
10.2. it is operated in a closed cycle, the total internal volume of the gas channels ( 81 ) for the gaseous working medium (eg helium) outside the displacement chamber ( 80 ), which is the compression space,
10.3. it has a cylindrical combustion chamber ( 82 ) which
10.3.1. is arranged coaxially to the displacement chamber ( 80 ), with a
10.3.2. Deflection surface ( 83 ) of the fuel gases on the cylinder head by rad, and
10.3.3. a heat exchanger ( 84 ) with opposing fluid flows of the fuel gases and the working medium,
10.3.3.1. with constant absorption of the thermal energy of the fuel gases and periodic release to the working medium,
10.3.3.2. it is divided into individual chambers, corresponding to the number of inlet openings in the cylinder head, which are arranged axially around the combustion chamber ( 82 ), the
10.3.3.3. total free cross section of the gas channels for the working medium corresponds to the total free cross section of the inlet openings, and
10.3.3.4. the channel bundle has a hexagonal basic structure
10.3.3.4.1. from circular gas channels ( 85 ) for the working medium, and
10.3.3.4.2. from square gas channels ( 86 ) for the fuel gases, and
10.3.3.4.3. triangular partition walls ( 87 ) between the fluid flows, which serve as storage mass during the compression stroke,
10.3.3.5. and it consists of a good heat-conducting and heat-resistant material, in particular a non-oxide ceramic such as SiC,
10.4. Combustion chamber ( 82 ) and cylinder head, and heat exchanger ( 84 ) and cooler are separated by heat-insulating layers ( 88 ),
10.5. After expansion in the displacement space, the working medium cycles through the following stations:
1. preheater for the combustion air, 2. cooler, 3. heat exchanger ( 84 ),
10.6. the catalysts being installed in the heat exchanger ( 84 ) in the optimum temperature section for the reaction;
11. Eccentric ring pair with precisely adjustable and readable size and position of the eccentricity, the
11.1. Inner ring either
11.1.1. the bearing bore for receiving any surface of rotation of a machine part, or
11.1.2. the outer race of a rolling bearing, or
11.1.3. is the bushing of a plain bearing, and
11.2. the total width of which is specified by two end faces from axially normal planes, at a distance from the required bearing width,
11.3. the outer and inner boundary surfaces are surfaces of revolution of a common base axis, which is present when the axes of the outer and inner surfaces are congruent, in particular
11.3.1. straight circular cylindrical surfaces and / or
11.3.2. straight circular conical surfaces with a small pitch,
11.4. the outer and inner rings are against each other in the separating surface
11.4.1. rotatable about a minor axis, the
11.4.1.1. parallel to the basic axis,
11.4.1.2. is arranged at a distance E ,
11.4.1.2.1. where 2 E is the maximum size of the position deviation or position shift to be compensated for, and
11.4.1.2.2. E is preferably a decade or hectare of one µm,
11.4.2. and the rotation surfaces according to feature group 11.3. consists,
11.4.3. or from a spherical section, the center of which is equidistant from the end faces on the minor axis, and the
11.4.4. generates the pitch circle with the radius R in one or both end faces, with the following relationship: 11.5. there are marks in one or both faces,
11.5.1. the inner ring has an adjustment mark,
11.5.1.1. it lies on the connecting beam from the basic axis to the secondary axis, with the congruence of the axes according to feature group 11.3.
11.5.1.1.1. the connecting beam and its orthogonal in the center structure the pitch circle into first and second quadrants,
11.5.1.2. it is an arrow or a line that
11.5.1.2.1. is etched, scratched or printed on,
11.5.2. the outer ring has a size scale with non-linear division in the second quadrant,
11.5.2.1. the beginning of the scale 0 lies on the connecting beam according to feature 11.5.1.1., and
11.5.2.2. it has a quarter circle shape for values from 0 to E , or
11.5.2.3. it has a semicircular shape for values from 0 to 2 E ,
11.5.2.4. the scale division into radial graduation marks on the pitch circle is constructed by the transfer of the division points, the distance R divided into N equal intervals from the minor axis to the beginning of the scale, with the beginning of the scale as the fulcrum, whereby
11.5.2.4.1. the number N of intervals between the tick marks has a simple rational relationship to the numerical value of E ,
11.5.2.4.1.1. especially the ratio 1, and
11.5.2.4.1.2. the distance between the graduation marks can be read without tools,
11.5.3. the outer ring has a position scale with a non-linear division in the first quadrant,
11.5.3.1. the beginning of the scale is offset by minus π 2 rad from the beginning of the scale of the size scale,
11.5.3.2. it has an eight-circle shape for values from 0 to E , or
11.5.3.3. it has a quarter circle shape for values from 0 to 2 E ,
11.5.3.4. the graduation marks are generated by a central projection of the inner axis on the outer ring, with the basic axis as the projection center, when the inner axis rotates around the minor axis, from the points of the inner axis on the locus described which are assigned to the graduation marks on the size scale,
11.5.4. The size and location scale have a different background,
11.6. the outer ring or the inner ring has the following designation:
Information about the largest setting range in the selected unit in short form, e.g. B. 120 microns
and the smallest unit of eccentricity between two tick marks, e.g. B. <|| <5 µm
in particular data in 1 nm, or 1 µm or 1 mm, depending on the size range and the manufacturing tolerance of the eccentric rings,
11.7. The inner and outer ring are against each other after the size adjustment, and the outer ring can be fixed against the housing after the position adjustment
11.7.1. frictionally, or
11.7.2. form-fitting, by means of notches, grooves, pins or similar means.