[go: up one dir, main page]

EP1035310A2 - Moteur à pistons à combustion continue - Google Patents

Moteur à pistons à combustion continue Download PDF

Info

Publication number
EP1035310A2
EP1035310A2 EP00102242A EP00102242A EP1035310A2 EP 1035310 A2 EP1035310 A2 EP 1035310A2 EP 00102242 A EP00102242 A EP 00102242A EP 00102242 A EP00102242 A EP 00102242A EP 1035310 A2 EP1035310 A2 EP 1035310A2
Authority
EP
European Patent Office
Prior art keywords
piston engine
engine according
combustion chamber
cylinder
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP00102242A
Other languages
German (de)
English (en)
Other versions
EP1035310A3 (fr
EP1035310B1 (fr
Inventor
Ulrich Dr.-Ing. Rohs
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP1035310A2 publication Critical patent/EP1035310A2/fr
Publication of EP1035310A3 publication Critical patent/EP1035310A3/fr
Application granted granted Critical
Publication of EP1035310B1 publication Critical patent/EP1035310B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/26—Engines with cylinder axes coaxial with, or parallel or inclined to, main-shaft axis; Engines with cylinder axes arranged substantially tangentially to a circle centred on main-shaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F01B3/0005—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G3/00—Combustion-product positive-displacement engine plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two

Definitions

  • the invention relates to a piston engine with a continuous Combustion, in which gas flows out of a combustion chamber Working medium is successively supplied to at least two cylinders.
  • Such a motor is known to consist of a fixed one Housing in which a cylinder block with a circular arrangement axially parallel cylinders rotating.
  • the pistons work on a connecting rod inclined, revolving synchronously with the cylinder block Camshaft pulley, the fixed axis of which is opposite the motor shaft is inclined at an angle.
  • a single combustion chamber is common to all cylinders a fixed cylinder head and is through an intake and a Exhaust bore connected to a control surface of the cylinder head which the rotating cylinders move past. Between the rotating cylinder block and the fixed cylinder head is one Sealing provided.
  • each cylinder receives in the area of lower piston dead center fresh air, which in the course of the further rotation condensed by the piston movement until it is close to the top dead center entered into the combustion chamber and with there injected fuel is burned.
  • the piston movement follows here from the inclination of the Kurbei disc.
  • the cylinder After passing through top dead center, the cylinder picks up Combustion gases from the combustion chamber, which then expand to one common exhaust for all cylinders shortly before bottom dead center opens. Then there is a charge change using the 2-stroke process instead of.
  • the fuel is fed through a combustion chamber Injector fed continuously, so that the combustion is maintained continuously; electrical ignition occurs therefore only for starting the engine.
  • the invention proposes a piston engine with a continuous Combustion before, in which flowing out of a combustion chamber Working medium is successively fed to at least two cylinders, each Cylinder is arranged stationary with respect to the combustion chamber and one Has inlet and control means are provided which the inlet connect successively with the combustion chamber or from the combustion chamber separate.
  • the output shaft For example, have a swash plate, the connecting rods in the Cylinder working piston is connected.
  • the term describes a swashplate rotatable on a knee shaft section of the Output shaft arranged wobble body, the radially outer Has articulation points for the connecting rods of the pistons.
  • a change in Angle of the wobble, as caused by a piston movement is, the output shaft or the knee shaft section of the output shaft just follow by rotation, causing the linear piston movement in a rotary movement is implemented.
  • An output shaft can also be provided, which has a cam disk has, along which pistons running in the cylinders run.
  • a such cam arrangement has an extraordinarily high Efficiency.
  • a particularly favorable flow of force follows when the combustion chamber is coaxial is arranged to the output shaft. This is particularly true in Connection with the use of a swashplate or cam advantageous, this favorable flow of force also in other, of the Piston driven drives is advantageous. This arrangement enables in particular a single-flow output of a generic Piston engine, which gives access to the combustion chamber, for example for maintenance purposes.
  • a piston engine according to the invention runs relatively smoothly when the Cylinders are arranged symmetrically to the combustion chamber. This leaves the working medium flow coming from the combustion chamber Distribute evenly over the cylinders.
  • While generic piston engines are known as flooders, the means that the output is only on one side, allow stationary cylinder for the first time that a generic piston engine is double-flow, so that a power take-off, for example for oil, Fuel and / or distribution pump, also take place on the combustion chamber side can.
  • a power take-off for example for oil, Fuel and / or distribution pump
  • At least one inlet of a cylinder can be on the combustion chamber side at least one slide can be opened or closed. This on the one hand ensures that when the piston returns, the Working medium is conveyed from the cylinder through an outlet can be.
  • the inlet can be closed before the corresponding piston reaches its top dead center or that Working medium has completely filled the cylinder. This allows in existing energy can be better used because otherwise part of the working medium flowing in through the inlet not make a contribution to the overall work, i.e. to driving the piston can.
  • Such an arrangement is particularly advantageous if of the Combustion chamber has a firing channel to each inlet, through which otherwise flow the working medium into the cylinder at all times could. This would cause the piston to move back after expansion Prevent working medium.
  • the slider are advantageously controlled such that they synchronized to the engine revolution or to the position of the piston become. In this way, the slider can at selected times be opened and working medium get into the cylinder. On the other hand, the firing channel can be closed, so that the expanded working medium can flow freely.
  • combustion chamber To provide the combustion chamber floor, which has at least one firing channel, the combustion chamber floor with the firing channel being displaced in such a way that the firing channel is directed successively to one inlet at a time. This is also a targeted distribution of the hot working medium possible on the individual cylinders.
  • the combustion chamber floor only to rotate synchronously with the motor speed.
  • the slide can be cylindrical to one in the Cylinder arranged piston include sleeve provided with a has the corresponding opening, the opening with the engine revolution synchronized with the intake becomes.
  • this sleeve In order to ensure a smooth movement of this sleeve, it can be suitably lubricated.
  • the sleeve can be synchronized to the extremely simple Engine revolution to coincide with the intake when the Sleeve rotates around the cylinder axis. This can on the one hand be a rotation. On the other hand, a pendulum or Vibration movement possible.
  • Such a sleeve movement also ensures distribution of the previously mentioned lubricant. If the sleeve is also a Axial movement passes axially to the cylinder, that is, an axial stroke has, can also distribute the lubricant parallel to Cylinder axis can be guaranteed.
  • Such an axial stroke can already be caused, for example, by piston friction be ensured if the piston is directly on the sleeve inside is present. If this piston friction is not sufficient, the axial stroke can but can also be done by constraining forces. This is one hand possible by levers or gears, but it can also be, for example gas-controlled axial stroke, which is caused by a pressure difference, to be available.
  • a Burt-McCullumn slider for example, can be used as a sleeve.
  • the sleeve can also undergo a periodic movement, whose period is a fraction of the engine speed. This is for example possible if the sleeve has several identical openings. A such measure enables a lower material load and lower lubrication requirements.
  • the sleeve half as fast as the engine.
  • this sleeve can be in a liner be stored, through which the sleeve, especially if it is immediate comes into contact with the corresponding piston, is stabilized.
  • a lubricant such as oil, is placed between the sleeve and the sleeve. intended. Now the sleeve or the liner becomes excessive heated, this can lead to the destruction of the lubricant film.
  • the combustion chamber and a heat shield can be provided for each cylinder.
  • a such a heat shield each between the combustion chamber and an assembly of the cylinder provided arrangement, which in a way of the Combustion chamber and the cylinder assembly is thermally separated.
  • This Separation can be, for example, an air gap, a material transfer or include another thermal obstacle.
  • the heat shield can advantageously be brought in front of the inlet, so that the Heat shield also a slider or a sleeve that this inlet closes, can cover. In this way, the temperature of the Slider or the sleeve are kept sufficiently low so that for example, a lubricant film necessary for these assemblies or oil film is not destroyed.
  • the arrangement provided in this way thus ensures that on the one hand a lubricant film is preserved and on the other hand in the Lubricant residues in the cylinder are burned virtually free of pollutants become.
  • a piston engine with such an arrangement thus enables one Separation of functions. While the heat shield is attacking immediately Temperature, the slider or sleeve provides one sufficiently tight closure of the cylinder, both inside as well as outside. Such separation of duties or provision a heat shield between an assembly of the cylinder and the The combustion chamber is also independent of the other characteristics of the Piston engine with continuous combustion advantageous.
  • the sleeve or the slide and the heat shield at the moment the inlet is released and at the moment closing the inlet is essentially rectified Carry out movement.
  • the Heat shield moved in opposite directions to the sleeves around the combustion chamber. This rectified movement can ensure that the The heat shield sufficiently covers the edge of the opening or the edge of the slide. It it goes without saying that the movement of the heat shield and Slider or sleeve need not be coordinated, so that for example the sleeve vibrates and the heat shield one Can perform rotary motion.
  • the combustion chamber floor the heat shield can also be shifted or rotated become.
  • the heat shield can also be stationary around the inlet be arranged around. Likewise, slight relocation movements are the follow the combustion chamber floor rotation only during the moment, in which the shot channel reaches a corresponding inlet, conceivable.
  • the heat shield also has a lower speed than the engine speed can revolve.
  • Means may be available to optimize engine performance a dead center position of the pistons with respect to a position of the control means or to move the slide, the sleeve or the heat shield.
  • At least one of the cylinders may include an exhaust valve.
  • an exhaust valve hereby can largely be avoided that when expressing the relaxed Working medium as exhaust gas due to the presence of lubricants or oils unnecessarily unburned carbons get into the exhaust gas. Any otherwise existing lubricants are due to the high temperature of the entering working medium has been reliably burned.
  • valves to control the outlet of the Working medium is also independent of all other characteristics of the piston engine with continuous combustion advantageous to a Avoid leakage of lubricant or oil and the expelled Minimize pollutants. So can also with the known Piston engines with continuous combustion regulations Slider or by cylinder displacement are applied, the one Force sealing on which lubricant with escaping relaxed working medium comes into contact. This can also be done with these piston engines with continuous combustion through a Avoid exhaust valve.
  • valve describes each Shut-off device in which a sealing surface is lifted from a seat becomes.
  • sealants or lubricants can be used can be dispensed with, which causes the advantages according to the invention.
  • the use of valves requires a complete change to the hitherto known for piston engines with continuous combustion applied sealing mechanisms.
  • solutions of this type can then also be used in particular Find application if other measures contact the Exhaust gas with unburned lubricants can be prevented or a subsequent disposal of these sheep substances takes place.
  • valve drives can be used as valve drives Find.
  • the valves can be hydraulically driven become.
  • a hydraulic pump for example via a Controlled cam arrangement is used. It is the same possible to control the valves electrically or magnetically. With these Both options are control of the valves depending on the load or Engine speed relatively easy to implement.
  • it is also conceivable to measure the valve lift for example by a Pressure measurement or by an electrical coil. The result of this Valve lift measurement can also be used to control the valves.
  • the valve drive can also be a cam plate, a swash plate or comprise a cam disk. Such a disc can be separate output can be moved synchronously with the other motor. On the other hand, it is also conceivable for the cam arrangement or the like to drive directly through the slide or the sleeve.
  • plate and ball valves come as valves, too ceramic, under consideration.
  • valve drives possible. It is understood that this too Valve drives according to the load or the engine speed Dead centers of movement of the corresponding compressors are shifted can, if this is advantageous for increasing the engine power.
  • a compressor may include an intake valve that Compressor-side seated valve cover by a spring is pulled against a valve seat.
  • Such an arrangement guarantees in a relatively simple way that the Inlet valve can be opened by compressor-side vacuum, so that a medium to be compressed flows in while the valve is sealing, as soon as this inflow ceases.
  • the inlet valve by the pressure occurring here against the Valve seat pressed so that the sealing effect is enhanced.
  • the compressor can comprise a ball valve as an outlet valve. There relatively small volumes are moved on the outlet side the outlet valve is a relatively short distance. This enables a Ball valve as a check valve an adequate seal and a sufficiently high flow rate of the compressed medium. Because of the little ones Suspension is not absolutely necessary.
  • the piston engine with continuous combustion can Have suction chamber with at least one compressor operatively connected and at one end pointing away from the combustion chamber the engine is arranged.
  • the inlet valves described above can open directly into this suction chamber.
  • Such Arrangement ensures a simple despite the fixed cylinder Construction of the engine and a controllable supply to the compressor the medium to be compressed. In particular, one can in this way common access to all compressors is created so that the medium, for example air, easily a common one Pretreatment, such as filtering, can be subjected.
  • Pretreatment such as filtering
  • the invention also proposes to include a separate compressor cylinder to provide a compressor piston that with a connecting rod a connecting rod of a cylinder piston running in a cylinder is.
  • the invention thus beats all previously known Piston engines with continuous use before, compressor cylinders and separate working cylinders. Such an arrangement has the advantage that the respective cylinders specialize according to their tasks can be trained. In this way, the Increase overall efficiency.
  • Working connecting rods and compressor connecting rods can be rigidly connected to one another be, so that work performed by the connecting rod directly into one Compression can be implemented. This will increase efficiency increased during compaction.
  • work and compression connecting rods as common connecting rod be formed so that from the working piston applied forces directly and straight to the compressor to get redirected.
  • the connecting rod can make installation easier are formed in two parts, these two parts during assembly be rigidly connected.
  • the connecting rod can have two rollers, one cam grasp an output shaft.
  • Such an arrangement from a rectilinear connecting rod, the working pistons and compressor pistons with connects each other, and a cam through the connecting rod is also independent of the other features for one Piston engine with continuous combustion advantageous.
  • Such Arrangement is characterized by an extremely high efficiency out.
  • cam for a piston engine with continuous Combustion can also be advantageous if such continuous connecting rod is not available.
  • a such cam also for arrangements in which working cylinders and compression cylinders are not arranged linearly to one another, use Find.
  • the connecting rods can be connected to one in a relatively simple manner Rotational movement around its own longitudinal axis can be prevented if at least one of the rollers a shoulder and / or one Has guide disc which rests radially on the outside of the cam disc.
  • a piston engine can be used continuous combustion free from translational forces caused by the piston movement are caused to be operated. Be about it.
  • Such multi-phase piston engines with continuous combustion can thus almost be done without further ado be operated vibration-free.
  • the invention proposes using a piston engine continuous combustion, which is operated single-phase, the Balancing through the between the working piston and the output shaft provided transmission links.
  • a piston engine continuous combustion which is operated single-phase, the Balancing through the between the working piston and the output shaft provided transmission links.
  • the invention proposes a piston engine with a continuous Combustion before, the transmission links between piston and Output shaft are effective to design such that their balancing forces are compensated for by the balancing forces of the pistons.
  • these transmission elements have masses or material thicknesses that exceed the Masses or material thicknesses go beyond that for stability reasons Operation of the piston engine are necessary.
  • a cam should be designed so wide that Balancing forces through the balancing forces of the piston arrangement be compensated. The smoothness gained by the latter arrangement is at the expense of a longer overall length of the entire piston engine realized.
  • the present invention also claims piston engines continuous combustion between piston and output shaft provided transmission links, their strength or mass, the Stability reasons including given tolerances necessary strength or mass and their balancing forces exceed the balancing forces of the Essentially compensate for the piston arrangement. Smaller residual unbalances can by additional weights on the transmission links, as on a Cam or even on the output shaft, can be compensated.
  • gear members designed in this way are also independent of the other features of a piston engine with continuous Combustion advantageously serve to keep the engine running smoothly.
  • Continuous combustion can be provided, which means internal Strains of the pistons with each other and with the output shaft connecting gear links reduced.
  • an oil supply channel can be arranged coaxially to the same, which at corresponding points radially outward oil distributor includes. Due to the centrifugal forces that occur during engine operation the oil from the oil distributors, which are formed as fine bores can be conveyed radially outwards.
  • the oil distributors positioned at suitable positions so that the oil or lubricant to the desired locations in the engine.
  • the Oil supply channel at least one radially arranged oil supply, the for example from a pressurized ring channel with oil is acted upon.
  • the lubricant under pressure is thus in the radial oil supply is pressed and thus reaches the coaxial to the output shaft arranged oil supply channel.
  • the lubricant pressure overcomes centrifugal forces in the ring channel.
  • the necessary pressure can be achieved by everyone known measures, such as an oil pump, maintained become.
  • Such an oil supply or lubricant supply is regardless of the other features of the invention Piston engine with continuous combustion advantageous because it works on structurally extremely simple way a precisely metered lubricant distribution guaranteed.
  • the dosage is made in particular by a suitable choice the oil distributor or its diameter.
  • the piston engine with continuous combustion can one Have cooling fluid flow that directly with a guide on one Cylinder comes into contact.
  • the cooling fluid flow can also a guide for a slide of a firing channel come into contact.
  • it is particularly sufficient
  • such sliders such as explained in detail above, exposed to high temperature loads. These loads tend to destroy a film of lubricant. Such a disturbance can be countered very effectively if the corresponding slide guide directly with the cooling fluid flow in Touch.
  • This relates in particular to a liner for a cylindrical order a piston provided sleeve which acts as a slide for closing or Serves to open a firing channel.
  • a liner can be brought into direct contact with the cooling fluid flow.
  • a cooling fluid flow through small Bores arranged in the immediate vicinity of the firing channel are conducted at a high flow rate.
  • the Bore diameter and the flow rate selected such that the pressures occurring here can be controlled.
  • Such Measure can also be used with other piston engines with continuous Combustion can be provided in the vicinity of a firing channel.
  • Such small holes can also be found in other locations immediate vicinity of the combustion chamber to be provided in the Combustion chamber temperatures that exceed 2,400 ° C can dominate.
  • each cylinder In contrast to the known piston engines with continuous Combustion where each cylinder is at an exhaust outlet is guided past, with a piston engine according to the invention continuous combustion where the cylinders are stationary, each cylinder have an outlet with an exhaust manifold is connected, which has a common exhaust connection.
  • the common exhaust port allows the exhaust can be supplied to a heat exchanger, the energy of the exhaust gas or the fluid leaving a respective outlet to that of Combustion chamber supplied fluid transfers.
  • a heat exchanger between the compressor and the combustion chamber is provided.
  • Such an arrangement is also advantageous for piston engines with continuous combustion, at which working cylinder and compressor by an identical assembly are formed.
  • a heat exchanger can also known piston engines with continuous combustion advantageous Find application.
  • a Bernard heat exchanger for example, is conceivable as a heat exchanger.
  • the A filler can be arranged as a displacer on the compressed air side.
  • the stability of the ceramic lining can be increased in that this is at least in the operating state under a voltage that such is chosen that no tensile forces can occur.
  • the ceramic lining even before commissioning under one Preload.
  • a preload in the axial direction Direction, d. H. exist along the flame chamber wall. This can be realized for example by a steel clamp.
  • the ceramic lining can also radially inwards the flame chamber is under a prestress.
  • This can for example by inward-facing supports such as stamps or a suitably cut thread.
  • the radial supports or the thread can also be used as a channel for a coolant or for a Serve fluid.
  • the ceramic lining can also have cooling fins that adhere to one another support a corresponding wall on the outside and in this way a ensure suitable preload.
  • the distance also serves between the ceramic lining and the rest of the housing Flame chamber of a thermal insulation. For this reason, they are Spacers chosen to be relatively small, so that thermal bridges be minimized.
  • Such a ceramic lining is also independent of the other features of the engine described above for a piston engine advantageous with continuous combustion.
  • the combustion chamber can have a flame chamber with holes have in a flame chamber wall, through which a fluid in the Flame chamber can be directed.
  • a fluid in the Flame chamber can be directed.
  • the fluid can be excellent, especially for smaller ones Combustion chambers isolate the combustion chamber from the outside enable.
  • the fluid can, for example, come from the compressor come.
  • the fluid supplied in this way can during the Flow through the flame chamber also participate in the combustion, especially when it has finished its backflow and back in Flame direction is accelerated.
  • the combustion chamber can be used to regulate the flame in a suitable manner via an injection pump, which is controlled by a ⁇ probe, fuel be fed.
  • a control loop can be used Piston engine with continuous combustion extremely reliable too operate independently of its other features.
  • the ⁇ probe is provided on the outlet side behind at least one cylinder.
  • the ⁇ probe can also be in an exhaust manifold or Exhaust gas connection must be arranged.
  • the control takes place via the ⁇ probe advantageous in a certain load range, especially at full load.
  • ⁇ is regulated to values ⁇ 1. That means the exhaust no lack of air or an excess of air or an excess of contains medium provided by the compressor, the injected So fuel can be burned sufficiently.
  • the injection pump via a temperature measurement to regulate.
  • the temperature measurement required for this can also be done on the exhaust side, behind a cylinder.
  • a Spark plug is only required to start the engine.
  • the control circuit of the injection pump advantageously comprises both one ⁇ probe as well as a temperature meter, taking the temperature measurement at idle and the ⁇ probe can be used at full load.
  • the regulation is carried out via a corresponding functional Linking both measured values.
  • the piston engine shown schematically in Figures 1 and 2 includes a combustion chamber 1 from which a working medium starts Shot channels 11 (exemplarily numbered) in cylinder 20 (exemplarily numbered). There the working medium expands and drives it Piston 21 on.
  • the pistons 21 are connected to connecting rods 4, which in turn are connected with Compressor cylinder 30 (numbered as an example) running back and forth Compressor pistons 31 (numbered as an example) are connected.
  • the connecting rods 4 encompass a common curved path 5 which is connected to an output shaft 51 via a spacer 50.
  • the cylinders 20 are symmetrical arranged a central motor axis. Furthermore two move opposite connecting rods 4 each rectified so that this engine runs essentially vibration-free.
  • this piston engine shows how also the motors of the other exemplary embodiments, control means that open or close the shot channels 11 according to the engine speed.
  • the piston engine shown in Figure 3 corresponds to that previously described piston engine essentially, but meet this the cylinders 20 'with their pistons 21' both the work function as well the compression function. It is also used as a transmission between the Piston and the drive shaft 51 not a cam track but one Swash plate 5 'provided. With this swash plate 5 'are over corresponding articulated connections the pistons 21 'by means of connecting rods 4' connected. The swash plate 5 'itself is on a knee shaft 51' Output shaft 51 mounted. An expansion of working medium in one the cylinder 20 'leads to a change in the inclination angle of the Swashplate 5 ', which the knee shaft 51' only by a movement of the Output shaft 51 can follow.
  • Control means ensures that the working medium in each case desired cylinder 20 'arrives.
  • the control means include one Sleeve 6 (numbered as an example), which has a gear arrangement 61 is moved synchronously with the engine revolution. As can be seen immediately we both the sleeve parallel to its longitudinal axis and around it Longitudinal axis moved around. This serves to evenly distribute Lubricant between the sleeve 6 and a sleeve bearing the Liner 62 (numbered as an example).
  • the sleeve 6 serves as a slide which has an inlet 23 of each cylinder 20 'opens or closes synchronously with the motor revolution.
  • each liner 62 is directly cooled by water (exemplified by number 24).
  • the heat shield 7 is connected via a shaft 70 to the Drive shaft 51 connected and thus rotates synchronously with the same.
  • the heat shield has openings (not numbered) that are arranged in such a way that they have the firing channel 11 at the right time release in the desired manner so that the working medium without further notice through the inlet 23 opened at the same time in the corresponding cylinder 20 'arrives.
  • combustion chamber 1 is also water-cooled via channels 12, the areas outside the water cooling of the Combustion chamber 1 also serve as a heat shield.
  • the piston engine shown in FIG. 4 essentially corresponds to that shown in Figures 1 and 2, but also has features of the in Figure 3 shown piston engine. Components with the same effect are also denoted in this figure with identical reference numbers.
  • cooling water circuits in the piston engine shown in FIG contrary to the illustration in FIG. 1 by reference numerals 12, 24 and 36 exemplarily numbered.
  • the cooling water flows along the one hand Combustion chamber 1 through coolant channels 12, through cylinder block 2 through coolant channels 24 and in the compressor block 3 Cooling fluid channels 36.
  • the respective channels 12, 24 and 32 are in series switched. In this way, temperature compensation via the entire engine block.
  • the piston engine shown in FIG. 4 has one on each cylinder 20 Outlet 25, which opens into an exhaust manifold 8. Behind the Exhaust collector 8, a heat exchanger 80 is provided, through which the Feed line 32 for the compressed fluid. That way the compressed fluid preheated and the efficiency of the engine increase.
  • the exhaust gas leaves the engine through an exhaust gas cutoff 81.
  • Both the outlet 25 and the inlet 23 are via the sleeve 6 controlled, as can be seen directly from Figure 4.
  • the Gear arrangement 61 is designed such that the sleeves are half as fast, like the output shaft 51, rotate.
  • the sleeve 6 with a slight axial play in their bushing 62, so that they a little can follow the stroke movement of the piston 21. This will create a ensures sufficient axial displacement of the sleeve 6, whereby Sufficient lubricant between sleeve 6 and liner 62 is distributed.
  • the piston engine shown in Figure 4 has a annular suction space 37 on which the combustion chamber 1st opposite end of the piston engine is arranged.
  • This suction room 37 is connected to the inlets 34 of the compressor 30 and enables an even distribution of the supply air.
  • Compressor outlets 38 are provided, which are designed in an annular channel Guide pressure chamber 33.
  • Inlets 34 and outlets 38 are each through valves 52, 53 can be opened or closed.
  • the valves 52, 53 via tappets and a lever assembly 54 from one seated on the output shaft 51 Controlled cam arrangement.
  • FIG. 6 shows in detail, serves here, as in the rest of the In the embodiment shown in Figure 4, a compressor head 58 as Valve seat.
  • the inlet valve 56 includes a seated on the compressor side Valve cover 56 ', which is supported by a spring 56' 'against the valve seat 58 is pulled.
  • the spring 56 '' by a holder 56 '' ' kept under suitable bias.
  • the valve opening in the valve seat 58 each includes a stop 58 ' (see individual illustration of the compressor head 58 in FIG. 6), against which the spring 56 ′′ strikes when the valve 56 opens.
  • a stop 58 ' see individual illustration of the compressor head 58 in FIG. 6
  • the compressor-side seating of the Valve cover 56 ' against that when compressing the valve cover 56' the valve seat 58 is pressed and thus sealing is ensured.
  • the outlet valve 57 comprises a ceramic ball 57 'through which in the Pressure chamber 33 prevailing pressure against the valve seat 58 becomes. In this way, the outlet valve 57 is closed as long as as long as the pressure in the compressor 30 is below the pressure in the pressure chamber 33 lies. The pressure in the compressor 30 rises above the pressure in the Pressure chamber 33, the ceramic ball 57 'opens and strikes one Set screw 57 ''. As a result, the path into the pressure chamber 33 opened and the cylinder 31 can compressed air into the pressure chamber convict.
  • FIG. 5 also gives way on the cylinder head side a little bit from the embodiment shown in Figure 4.
  • the outlets 25 instead of the Sleeve 6 controlled by additional exhaust valves 26.
  • a rotating sleeve however, always leaves one on the edge Lubricant film that can be carried away by the exhaust gas flow.
  • FIGS. 7 and 8 show an alternative to this Ceramic balls 26 'serve as valves that run the respective outlets close.
  • the balls are by means of a sleeve 6 co-rotating cam assembly 29 via slide 29 ', which in Slide openings 29 '' can slide back and forth, moved. This too Arrangement ensures that no grease or lubricant from the Exhaust gases can be entrained at the outlet 25.
  • the combustion chamber 1 of the piston engine shown in FIG. 5 is essentially in three parts. It includes a combustion chamber supply 13, a fuel supply chamber 14 and a flame chamber 15.
  • the Combustion chamber supply 13 has a nozzle 13 ′′, via which compressed Fluid from the compressors 30, in particular thus air, through the Fuel supply chamber 14 into the flame chamber 15 with high pressure is broadcast.
  • the nozzle 13 ′′ comprises a central nozzle body 13 '' ', which is axially adjustable via a thread, so that a nozzle gap can be adjusted. Behind the nozzle gap is a Venturi nozzle 14 ' arranged, which leads into the flame chamber 15. The through the Venturi nozzle 14 ' flowing air tears a fuel-air mixture out of the fuel supply chamber 14 with in the flame chamber 15, whereby there is a continuous Flame is formed.
  • a compensation opening 14' 'at the Top of the flame chamber 15 is provided, which back in the Fuel supply chamber 14 leads. This compensation opening ensures a uniform flame and a complete burning of the supplied Fuel.
  • a spark plug 14 '' ' projects into the fuel supply chamber 14, which is only needed to start this engine.
  • a ceramic tube 15 ' is coaxial to the motor axis in the flame space 15 clamped both in the axial direction and in the radial direction.
  • This Ceramic tube is supported radially via cooling fins 15 ′′ ′′ shown in FIG. 9 on the outside of the combustion chamber wall and can in its cylinder side
  • Through an upper feed line 32 ' can be compressed from the feed line 32 Medium get to the outside of the ceramic tube 15 '. This flows along the ribs to the openings 15 ′′ and passes through them Openings 15 ′′ into the flame space 15.
  • the combustion chamber 1 further comprises, as already above described, a water cooling 12 via cooling channels 12 ' immediate vicinity of the firing channels 11 and the combustion chamber floor 16 cools.
  • cooling bores 24 ' are provided, which by the Cylinder cooling 24 are fed. These cooling bores 24 ' are located in the immediate vicinity of the weft channels 11. Die Bores 12 'and 24' require an extraordinarily high one Flow rate to the high occurring at these points To be able to meet temperatures.
  • the piston engine shown in FIG. 5 has in its output shaft 51 a coaxial bore as an oil supply channel 71. From this oil supply channel 71 are radial bores as oil distributors 72 (numbered as an example). Due to the centrifugal force, oil from the oil distributors 72 is caused by the engine rotation distributed in the engine at the desired height.
  • holes 73 are provided that also for a targeted transport of the oil to care.
  • Oil supply channel 71 From the oil supply channel 71 is also a radial bore Oil supply 74 out. This opens into an annular channel 75, which is not one Oil pump shown is loaded with oil. The one created by this Pressure overcomes the centrifugal forces and in this way enables the Apply sufficient oil to oil supply channel 71.
  • the Connecting rods 4 are rigid to a continuous during assembly Connecting rod 4 connected.
  • the width of the cam 5 in its area between the rollers 40 is chosen such that the by Cam 5 caused imbalance to the balancing forces of the piston-connecting rod arrangement corresponds. This way, this too single-phase motor can be realized that this is almost vibration-free running. Fine balancing of the entire motor is known per se and weights not shown in this figure, which on the Spacers 50 are attached made.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Transmission Devices (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP00102242A 1999-03-05 2000-02-14 Moteur à pistons à combustion continue Expired - Lifetime EP1035310B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19909689A DE19909689B4 (de) 1999-03-05 1999-03-05 Kolbenmotor mit kontinuierlicher Verbrennung
DE19909689 1999-03-05

Publications (3)

Publication Number Publication Date
EP1035310A2 true EP1035310A2 (fr) 2000-09-13
EP1035310A3 EP1035310A3 (fr) 2001-09-12
EP1035310B1 EP1035310B1 (fr) 2005-10-05

Family

ID=7899808

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00102242A Expired - Lifetime EP1035310B1 (fr) 1999-03-05 2000-02-14 Moteur à pistons à combustion continue

Country Status (4)

Country Link
US (1) US6412273B1 (fr)
EP (1) EP1035310B1 (fr)
JP (1) JP2000265847A (fr)
DE (2) DE19909689B4 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009062473A2 (fr) 2007-11-12 2009-05-22 Ulrich Rohs Moteur à pistons axiaux et procédé pour faire fonctionner un moteur à pistons axiaux
WO2011009451A2 (fr) 2009-07-24 2011-01-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à pistons axiaux et procédé pour réaliser un échangeur thermique d'un moteur à pistons axiaux
WO2011009450A2 (fr) 2009-07-24 2011-01-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à pistons axiaux et procédé pour réaliser un échangeur thermique d'un moteur à pistons axiaux
WO2011009453A2 (fr) 2009-07-24 2011-01-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à pistons axiaux et procédé de réalisation d'un échangeur thermique d'un moteur à pistons axiaux
WO2011009455A2 (fr) 2009-07-24 2011-01-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à piston axiaux et procédé pour réaliser un échangeur thermique d'un moteur à pistons axiaux
EP2456967A2 (fr) * 2009-07-24 2012-05-30 GETAS Gesellschaft für thermodynamische Antriebssysteme mbH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à piston axiaux et procédé pour réaliser un échangeur thermique d'un moteur à pistons axiaux
US9188000B2 (en) 2009-07-24 2015-11-17 Getas Gesellschaft Fuer Thermodynamische Antriebssysteme Mbh Axial-piston motor with continuously working combustion chamber having two combustion air inputs
DE102016119889A1 (de) 2015-10-26 2017-04-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor sowie Verfahren zum Betrieb eines Axialkolbenmotors
DE102015118239A1 (de) 2015-10-26 2017-04-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor und Verfahren zum Betrieb eines Axialkolbenmotors
DE102016100439A1 (de) 2016-01-12 2017-07-13 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Verfahren zum Betrieb eines Axialkolbenmotors sowie Axialkolbenmotor
DE102017124411A1 (de) 2016-11-07 2018-05-09 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor
WO2019149297A1 (fr) 2018-01-31 2019-08-08 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à piston axial
WO2020007418A1 (fr) 2018-07-04 2020-01-09 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux et procédé permettant de faire fonctionner un moteur à pistons axiaux

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004061224B4 (de) * 2004-12-20 2010-09-09 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Kolben-Zylinder-Anordnung, insbesondere für einen Taumelscheibenverdichter
US20060165543A1 (en) * 2005-01-24 2006-07-27 York International Corporation Screw compressor acoustic resonance reduction
US7397049B2 (en) * 2006-03-22 2008-07-08 Varian Semiconductor Equipment Associates, Inc. Determining ion beam parallelism using refraction method
EP2245269B1 (fr) 2008-01-11 2020-01-01 McVan Aerospace, Llc Moteur à combustion alternatif
US8490380B2 (en) * 2008-01-17 2013-07-23 Advanced Propulsion Technologies, Inc. Internal continuous combustion engine system
US8986253B2 (en) 2008-01-25 2015-03-24 Tandem Diabetes Care, Inc. Two chamber pumps and related methods
US8408421B2 (en) 2008-09-16 2013-04-02 Tandem Diabetes Care, Inc. Flow regulating stopcocks and related methods
AU2009293019A1 (en) 2008-09-19 2010-03-25 Tandem Diabetes Care Inc. Solute concentration measurement device and related methods
DE102008058558B4 (de) 2008-11-20 2020-04-23 Volkswagen Ag Wärmekraftmaschine
US8156919B2 (en) 2008-12-23 2012-04-17 Darrow David S Rotary vane engines with movable rotors, and engine systems comprising same
GB2469279A (en) 2009-04-07 2010-10-13 Rikard Mikalsen Linear reciprocating free piston external combustion open cycle heat engine
EP3284494A1 (fr) 2009-07-30 2018-02-21 Tandem Diabetes Care, Inc. Système de pompe à perfusion portable
CH703399A1 (de) * 2010-07-02 2012-01-13 Suter Racing Technology Ag Taumelscheibenmotor.
DE102011018846A1 (de) * 2011-01-19 2012-07-19 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor sowie Verfahren zum Betrieb eines Axialkolbenmotors
US9003765B1 (en) * 2011-07-14 2015-04-14 Barry A. Muth Engine having a rotary combustion chamber
US9180242B2 (en) 2012-05-17 2015-11-10 Tandem Diabetes Care, Inc. Methods and devices for multiple fluid transfer
US9173998B2 (en) 2013-03-14 2015-11-03 Tandem Diabetes Care, Inc. System and method for detecting occlusions in an infusion pump
RU2679952C2 (ru) * 2013-10-22 2019-02-14 Крис Киараш МОНТЕБЕЛЛО Роторно-поршневой двигатель с внешней камерой сгорания-расширения
WO2016055923A2 (fr) * 2014-10-09 2016-04-14 Calogero Provenzano Moteur à combustion interne à piston axial
US10590845B1 (en) * 2017-04-13 2020-03-17 Roderick A. Newstrom Cam-driven radial rotary engine incorporating an HCCI apparatus
RU209106U1 (ru) * 2020-11-03 2022-02-01 Федеральное государственное казенное военное образовательное учреждение высшего образования "Военный учебно-научный центр Военно-Морского Флота "Военно-морская академия им. Адмирала Флота Советского Союза Н.Г. Кузнецова" Бинарный двигатель с теплоизолированной камерой сгорания

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE366092B (fr) * 1973-01-02 1974-04-08 T Airas
US4179879A (en) * 1976-04-21 1979-12-25 Kincaid Elmo Jr Automatic steam pressure generator
US4448154A (en) * 1979-04-30 1984-05-15 Paradox International, Incorporated Internal combustion engine
SE422346B (sv) * 1980-07-02 1982-03-01 Hedelin Lars G B Sett att reglera forloppet i en forbrenningsmotor samt forbrenningsmotor for genomforandet av settet
US5285633A (en) * 1993-03-23 1994-02-15 The United States Of America As Represented By The Secretary Of The Navy Coolant subsystem for a torpedo propulsion system
US5362154A (en) * 1993-08-16 1994-11-08 Bernard Wiesen Pivoting slipper pad bearing and crosshead mechanism
US5964087A (en) * 1994-08-08 1999-10-12 Tort-Oropeza; Alejandro External combustion engine
US5497614A (en) * 1994-11-30 1996-03-12 The United States Of America As Represented By The Secretary Of The Navy External combustion engine having an asymmetrical cam and method of operation
US6092365A (en) * 1998-02-23 2000-07-25 Leidel; James A. Heat engine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009062473A2 (fr) 2007-11-12 2009-05-22 Ulrich Rohs Moteur à pistons axiaux et procédé pour faire fonctionner un moteur à pistons axiaux
WO2009062473A3 (fr) * 2007-11-12 2009-11-26 Ulrich Rohs Moteur à pistons axiaux et procédé pour faire fonctionner un moteur à pistons axiaux
US9879635B2 (en) 2007-11-12 2018-01-30 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axial piston engine and method for operating an axial piston engine
EP2711500A2 (fr) 2007-11-12 2014-03-26 GETAS Gesellschaft für thermodynamische Antriebssysteme mbH Moteur à pistons axiaux
EP2711499A2 (fr) 2007-11-12 2014-03-26 GETAS Gesellschaft für thermodynamische Antriebssysteme mbH Moteur à pistons axiaux
CN101932792B (zh) * 2007-11-12 2013-05-08 格塔斯热力学驱动系统有限责任公司 轴向活塞发动机以及用于操作轴向活塞发动机的方法
WO2011009450A3 (fr) * 2009-07-24 2011-04-14 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à pistons axiaux et procédé pour réaliser un échangeur thermique d'un moteur à pistons axiaux
WO2011009451A2 (fr) 2009-07-24 2011-01-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à pistons axiaux et procédé pour réaliser un échangeur thermique d'un moteur à pistons axiaux
EP2456967A2 (fr) * 2009-07-24 2012-05-30 GETAS Gesellschaft für thermodynamische Antriebssysteme mbH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à piston axiaux et procédé pour réaliser un échangeur thermique d'un moteur à pistons axiaux
WO2011009455A2 (fr) 2009-07-24 2011-01-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à piston axiaux et procédé pour réaliser un échangeur thermique d'un moteur à pistons axiaux
WO2011009453A2 (fr) 2009-07-24 2011-01-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à pistons axiaux et procédé de réalisation d'un échangeur thermique d'un moteur à pistons axiaux
WO2011009450A2 (fr) 2009-07-24 2011-01-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à pistons axiaux et procédé pour réaliser un échangeur thermique d'un moteur à pistons axiaux
EP2846029A2 (fr) 2009-07-24 2015-03-11 GETAS Gesellschaft für thermodynamische Antriebssysteme mbH Moteur à pistons axiaux, procédé de fabrication d'un moteur à pistons axiaux et procédé de fabrication d'un caloporteur d'un moteur à pistons axiaux
US9188000B2 (en) 2009-07-24 2015-11-17 Getas Gesellschaft Fuer Thermodynamische Antriebssysteme Mbh Axial-piston motor with continuously working combustion chamber having two combustion air inputs
US9376913B2 (en) 2009-07-24 2016-06-28 Getas Gesellschaft Fuer Thermodynamische Antriebssysteme Mbh Axial-piston engine with a compressor stage, and with an engine-oil circuit and a pressure-oil circuit as well as method for operation of such an axial-piston engine
EP3048244A1 (fr) 2009-07-24 2016-07-27 GETAS Gesellschaft für thermodynamische Antriebssysteme mbH Moteur a pistons axiaux
US10119398B2 (en) 2009-07-24 2018-11-06 GETAS Gesellschaft fuer termodynamische Antriebssysteme mbH Axial-piston engine, method for operating an axial-piston engine, and method for producing a heat exchanger of an axial-piston engine
WO2011009453A3 (fr) * 2009-07-24 2011-04-14 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux, procédé pour faire fonctionner un moteur à pistons axiaux et procédé de réalisation d'un échangeur thermique d'un moteur à pistons axiaux
DE102015118239A1 (de) 2015-10-26 2017-04-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor und Verfahren zum Betrieb eines Axialkolbenmotors
WO2017071680A1 (fr) 2015-10-26 2017-05-04 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux, procédé de fonctionnement d'un moteur à pistons axiaux
DE102016119889A1 (de) 2015-10-26 2017-04-27 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor sowie Verfahren zum Betrieb eines Axialkolbenmotors
DE102016100439A1 (de) 2016-01-12 2017-07-13 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Verfahren zum Betrieb eines Axialkolbenmotors sowie Axialkolbenmotor
WO2017121427A1 (fr) 2016-01-12 2017-07-20 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Procédé permettant de faire fonctionner un moteur à pistons axiaux et moteur à pistons axiaux
US10450945B2 (en) 2016-01-12 2019-10-22 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Method for operating an axial piston motor, and axial piston motor
DE102017124411A1 (de) 2016-11-07 2018-05-09 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Axialkolbenmotor
WO2019149297A1 (fr) 2018-01-31 2019-08-08 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à piston axial
WO2020007418A1 (fr) 2018-07-04 2020-01-09 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux et procédé permettant de faire fonctionner un moteur à pistons axiaux
WO2020007419A1 (fr) 2018-07-04 2020-01-09 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Moteur à pistons axiaux

Also Published As

Publication number Publication date
EP1035310A3 (fr) 2001-09-12
DE50011266D1 (de) 2006-02-16
EP1035310B1 (fr) 2005-10-05
DE19909689A1 (de) 2000-09-07
DE19909689B4 (de) 2009-07-23
JP2000265847A (ja) 2000-09-26
US6412273B1 (en) 2002-07-02

Similar Documents

Publication Publication Date Title
EP1035310B1 (fr) Moteur à pistons à combustion continue
EP2456956B1 (fr) Moteur à pistons axiaux
DE10145478B4 (de) Hubkolbenmaschine mit umlaufendem Zylinder
DE69614250T2 (de) Kühlung für eine gasturbine-zweitaktkolben-verbundmaschine
DE69619836T2 (de) Drehschieberventil für eine brennkraftmaschine
DE4022705C2 (de) Brennkraftmaschine
EP0153675B1 (fr) Moteur à combustion interne
DE19806175C2 (de) Plunger-Brennkraftmaschine
DE2613992A1 (de) Als verdichter fuer gase oder als brennkraftmaschine arbeitende maschine
DE102004034719A1 (de) Hochleistungs-Ein- und Zweitakt-Axialkolben Otto-Diesel- und Hybrid-Motorensystem
DE19819233C2 (de) Aus mehreren Maschineneinheiten zusammengesetzte Kolbenbrennkraftmaschine
DE640812C (de) Drehkolbenbrennkraftmaschine
DE102019128935B4 (de) Brennkraftmaschine und Verfahren zum Betrieb einer Brennkraftmaschine
DE19812800A1 (de) Gegenkolben-Brennkraftmaschine
DE3029934A1 (de) Brennkraftmaschine
EP0451466B1 (fr) Moteur à pistons à combustion interne
DE599340C (de) Durch eine Kurvenbahn um ihre Zylinderlaengsachse rotierende Verbrennungskraftmaschine
DD140156A1 (de) Heissgasmotor mit geschlossenem arbeitskreislauf
DE102019009258B4 (de) Brennkraftmaschine und Verfahren zum Betrieb einer Brennkraftmaschine
EP1838949B1 (fr) Procede de conversion d'energie thermique en travail mecanique et moteur a combustion interne
DE102010060814A1 (de) Kolbenkraftmaschine
DE617288C (de) Mehrzylindrige Diesel- oder Halbdieselmaschine
DE4418286A1 (de) Kraftmaschine
WO2017118542A1 (fr) Moteur à combustion interne
DE29711460U1 (de) Zweitakt-Taumelscheiben-Brennkraftmaschine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE ES FR GB IT

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

RIC1 Information provided on ipc code assigned before grant

Free format text: 7F 02B 75/02 A, 7F 02B 75/26 B, 7F 01B 3/00 B, 7F 02G 3/00 B, 7F 02G 3/02 B

17P Request for examination filed

Effective date: 20020307

AKX Designation fees paid

Free format text: AT BE CH CY DE LI

RBV Designated contracting states (corrected)

Designated state(s): DE ES FR GB IT

17Q First examination report despatched

Effective date: 20040121

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051005

Ref country code: GB

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20051005

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060116

REF Corresponds to:

Ref document number: 50011266

Country of ref document: DE

Date of ref document: 20060216

Kind code of ref document: P

GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]

Effective date: 20051005

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20060706

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061020

EN Fr: translation not filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20051005

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20160226

Year of fee payment: 17

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50011266

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170901