EP3527781A1 - Drehkolbenmotor und verfahren zum betreiben eines drehkolbenmotors - Google Patents

Drehkolbenmotor und verfahren zum betreiben eines drehkolbenmotors Download PDF

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Publication number
EP3527781A1
EP3527781A1 EP18156764.5A EP18156764A EP3527781A1 EP 3527781 A1 EP3527781 A1 EP 3527781A1 EP 18156764 A EP18156764 A EP 18156764A EP 3527781 A1 EP3527781 A1 EP 3527781A1
Authority
EP
European Patent Office
Prior art keywords
rotary piston
rotary
deformation body
engine according
piston engine
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.)
Pending
Application number
EP18156764.5A
Other languages
German (de)
English (en)
French (fr)
Inventor
Dirk Hoffmann
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.)
Fuelsave GmbH
Original Assignee
Fuelsave GmbH
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 Fuelsave GmbH filed Critical Fuelsave GmbH
Priority to EP18156764.5A priority Critical patent/EP3527781A1/de
Priority to CN201980021312.1A priority patent/CN111954749B/zh
Priority to US16/969,634 priority patent/US11098587B2/en
Priority to PCT/EP2019/053215 priority patent/WO2019158449A1/de
Priority to JP2020543796A priority patent/JP2021513628A/ja
Publication of EP3527781A1 publication Critical patent/EP3527781A1/de
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/123—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with tooth-like elements, extending generally radially from the rotor body cooperating with recesses in the other rotor, e.g. one tooth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/02—Radially-movable sealings for working fluids
    • F01C19/025—Radial sealing elements specially adapted for intermeshing engagement type machines or engines, e.g. gear machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/02—Radially-movable sealings for working fluids
    • F01C19/06—Radially-movable sealings for working fluids of resilient material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0015—Radial sealings for working fluid of resilient material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/123—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially or approximately radially from the rotor body extending tooth-like elements, co-operating with recesses in the other rotor, e.g. one tooth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/084—Toothed wheels

Definitions

  • the present invention relates in a first aspect to a rotary engine according to the preamble of claim 1.
  • the invention relates to a method for operating a rotary piston engine according to the preamble of claim 13.
  • Rotary piston engines are widely used for energy conversion, in particular to convert pressure or kinetic energy of a flowing fluid into rotational energy of one or more rotary pistons.
  • a generic rotary piston engine comprises a housing, which forms an interior, and at least two rotary pistons, which are arranged in the interior. At the interior, an inlet and an outlet for passing a fluid through the interior are formed. Hiebei the fluid flows along the rotary piston, so that in particular the rotary piston can be driven by flowing fluid.
  • the fluid can in principle be arbitrary, for example any liquid, any gas or a mixture thereof, which may also contain solid particles. Used fluids differ in particular depending on the field of application of the rotary piston engine.
  • the fluid may be exhaust gas of an internal combustion engine or another internal combustion engine. It can also be a fluid in a cyclic process, with the waste heat is used. This may be desired in power plants, manufacturing plants, heating systems and a variety of other facilities.
  • each rotary piston comprises on its outer circumference at least two sealing strips, which be pushed outwards via a suspension. As a result, the sealing strips sealing contact the housing inner wall, which limits the interior.
  • Such rotary engines are known, for example from DE 102007019958 A1 . GB 576603 A . GB 2486787 A and WO 2010081469 A2 , Other rotary piston engines with advantageously low friction are described by the applicant in EP 3144494 A1 . EP 3184758 A1 and EP 3144471 A1 ,
  • a fluid is introduced through an inlet to a housing.
  • the housing forms an interior in which at least two rotary pistons are arranged. As it flows through the interior to an outlet, the fluid drives the rotary pistons.
  • Each rotary piston comprises at its outer periphery at least two sealing strips, which are pressed by a respective suspension to the outside.
  • an object of the invention can be considered to provide a rotary piston engine and a method for operating a rotary piston engine, which allows a particularly high efficiency with the highest possible service life of the engine.
  • each rotary piston comprises at least two cavities in each of which an elastic elongated or cylindrical deformation body is arranged.
  • the sealing strips protrude into the cavities and against the elastic deformation body accommodated in the respective cavity, as a result of which the sealing strips are pressed radially outward.
  • An elastic elongated deformation body may in particular be a hose, in particular made of silicone or another elastic, metal-free material.
  • an elastic elongated or cylindrical deformation body causes a substantially uniform pressure on the sealing strip over its entire length.
  • the length here is the dimension in the axial direction of the rotary piston.
  • a stable and durable design is provided by the shape and design of a cylindrical deformation body, which still performs their function to sufficiently exert pressure on the sealing strips, even when cracks in the deformation body still largely performs. There are no significant dangers of damage to the motor in case of damage to the deformation body, which is an important advantage especially against metallic suspensions.
  • the prior art usually metallic springs are used to bias the sealing strips to the outside.
  • metallic springs In the event of damage or breakage of metallic springs, there is a risk that metal fragments could penetrate into other motor areas and cause considerable damage there.
  • metal springs exert a pressure only in a relatively small area, so that a sealing strip is not pressed uniformly over its length to the outside.
  • uneven pressure inevitably results in unnecessarily high pressure in some areas, thus unnecessarily increasing friction losses, while in other areas there may be too low a pressure which does not achieve sufficient sealing and thus degrades the efficiency of the engine.
  • a metallic leaf spring 17 is used, which does not reach a uniform pressure over the length of the sealing strip 4.
  • a breakage of the metallic leaf spring can cause serious damage to the motor.
  • Spiral springs 19 are used, which also do not exert uniform pressure and are probably made of metal.
  • a spring 52 and in WO 2010081469 A2 spirally illustrated springs used. Especially due to vibrations here is a serious risk of damage to the springs with consequential damage to the engine.
  • the invention provides a more uniform and thereby lower friction seal over the sealing strips, whereby risks are reduced by material fatigue.
  • the deformation body comprises or consists of a non-metallic material, in particular rubber or silicone elastomers such as silicone or other organosilicon compounds, carbon, nylon or plastic. In this way, the entire suspension of the sealing strips can be designed without metals.
  • cylindrical deformation bodies can be exchanged particularly easily after a certain maintenance interval.
  • a fine motor positioning as with coil springs is not required.
  • the cavities in which the cylindrical deformation bodies are accommodated can likewise be cylindrical and extend in the longitudinal direction of the rotary pistons, in particular parallel to the longitudinal axis / rotation axis of the rotary pistons.
  • the cavities and the recorded deformation bodies are each radially inwardly of an associated sealing strip.
  • the hose / cylindrical deformation body can extend over the entire length of the cavity, wherein the hose is in contact with the associated sealing strip over its entire length and presses it outward.
  • the contact over the entire length of the cavity can be continuous, so gapless, which is in contrast to conventionally used coil springs or leaf springs.
  • the deformation body in a cavity can be formed integrally or in principle also be formed by a plurality of separate cylindrical deformation body units, which are arranged one behind the other in the cavity in the longitudinal direction, for example, a plurality of lined up hoses.
  • this description generally refers to a deformation body or a tube which is arranged in a cavity; this does not mean that no further, the same or differently designed deformation bodies / hoses are additionally arranged in the same cavity. This can be advantageous in order to achieve a certain decoupling with regard to possible crack formation on one of a plurality of deformation bodies in the same cavity.
  • a single deformation body per cavity may be useful to allow easy maintenance or replacement operations.
  • an "elongated" deformation body may be defined such that its length (or extent in the direction of the axis of rotation of the associated rotary piston) is at least 5 times its diameter (or dimension in a direction perpendicular to the axis of rotation of the rotary piston).
  • a design of the elastic cylindrical deformation body as a tube provides a particularly good elasticity with a large spring travel, while high stability and durability.
  • a hose is understood to mean an elongated, hollow body, but in principle the deformation body can also have a solid rod shape, as a result of which the longevity may under certain circumstances be further improved.
  • the deformation body itself is made of an elastic material, but it is also conceivable that an elastic bearing presses a non-elastic cylinder body / deformation body against the sealing strips.
  • the deformation bodies may each be circular or oval in cross-section, with a hollow ring shape being able to be used as described. But other cross-sectional shapes, such as angular, rectangular or star-shaped shapes can be used.
  • the cross-section throughout the present description is to be considered as a section perpendicular to a longitudinal or rotational axis of the rotary pistons.
  • the cylindrical shape can be understood to mean that the deformation body has an elongated shape whose extension in the axial direction of the rotary piston is at least five times as large as its cross-sectional dimension.
  • the cylindrical shape may have a similar cross-sectional shape or size throughout its length.
  • the tube or deformation body may have an outer radius which is substantially equal to a radius of the cavity in which the deformation body is received. If the cavity has no circular shape in cross section, the smallest distance from the center of the cavity to a wall of the cavity can be considered below its radius.
  • the cavity can also comprise in cross-section one or more circular-shaped sections as well as one or more further differently shaped sections, whereby an insertion of the tubular-shaped deformation body into the cavity can be facilitated.
  • each cavity has an extension in the radial direction of the associated rotary piston and an extension perpendicular thereto, that is in the circumferential direction of the associated rotary piston.
  • the extent in the radial direction can now be smaller than the extent in the circumferential direction. This can be achieved that with the hose or deformation body inserted still a portion of the cavity is free in the circumferential direction, while the hose or deformation body in the radial direction fills the cavity or largely fills.
  • the tube can expand into the still free part of the cavity. In this way, the possible radial compression distance of the hose is increased.
  • Each sealing strip can have a widespread central region in cross section. This engages in a corresponding retaining groove in the respective rotary piston.
  • a common central region is to be understood to mean a broadening which is formed in a central region of the sealing strip along the radial direction.
  • the limitation of the freedom of movement to the outside also means that at high speeds, the sealing strips are not pressed too much by centrifugal forces to the outside.
  • a rotary piston thus has a cavity which is open radially outwardly via a slot.
  • the sealing strip is arranged in the slot.
  • the slot can be filled laterally sealingly by the sealing strip.
  • the slot is narrower than the deformation body in the cavity, so that the deformation body can not escape through the slot.
  • a wider opening is present, which is referred to as a retaining groove.
  • the sealing strip protrudes into this wider opening, so that their freedom of movement in the radial direction is limited.
  • the slot and the sealing strip can be narrowed outward (in the radial direction). The thicker interior of the sealing strip prevents so that the sealing strip slips through the slot to the outside.
  • the sealing strips may initially have a radial dimension which is slightly larger than required for a seal; Excess material is then abraded during operation until a radial length is reached at which hardly any friction on the sealing strips and thus little abrasion occurs.
  • Each sealing strip has in cross section a length or radial length which is defined in the radial direction of the associated rotary piston, and a width perpendicular thereto. It can be provided that the radial length is at least three times as large as the width.
  • the aspect ratios of the sealing strip are relevant for the deformation of the sealing strip under pressure.
  • a pressure on the sealing strip is important to deform them slightly inward. As a result, the friction between the sealing strip and trough is reduced.
  • an air film or an air lubrication can form, through which no or hardly any contact between a sealing strip and the other rotary piston is formed and thus material abrasion is minimized.
  • this desired effect can only occur if the radial deformation of the sealing strip at a pressure is sufficiently large.
  • the radial length of the sealing strip should be at least three times the width of the sealing strip. This is in contrast to for example GB 2486787 A where a wide and short sealing strip 54 can not achieve the desired deformation.
  • the bulges and the troughs are shaped so that upon engagement of one of the bulges in one of the wells a sealing contact between the sprockets is made immediately in front of the trough and a first contact between this bulge and this trough at a rear side the bulge takes place to a rear part of the trough, so that a gas inclusion and a gas compression take place in the trough.
  • the pressure increases so far that the gas escapes gradually by a gas film is formed between the rotary piston.
  • the gas film reduces friction and can also be called air lubrication. This increases the efficiency of the engine and wear, especially the sealing strips, occurs only very slowly.
  • This embodiment is particularly effective when a gas is used as a fluid, since the compression effect is stronger here than with liquids. But even with liquids, this design can be used advantageously.
  • each bulge may form a plateau region on either side of the slot.
  • a radius of rotation radius defined to the center of the rotary piston does not drop. The radius therefore drops only outside the plateau area, ie at the front and rear side of the bulge.
  • the dimensions of the two flat areas of the plateau area adjacent to the sealing strip should together be as wide as or wider than the sealing strip so that the desired contact of the curved rear side with the trough wall of the other rotary piston occurs.
  • the two flat areas should summed together have a width which is at least 80%, the width of the sealing strip.
  • the plateau region does not have to be perfectly flat, but may have a slight curvature, especially such that the plateau region has a constant outer radius measured from the center of the rotary center.
  • the formation of the convexities and the troughs ensures that a gas film / air film forms at the outer ends of the bulges and the sealing ledges which are held in the bulges, whereby friction is reduced. It may be particularly preferred to use this design together with the above-described suspension of the sealing strips by cylindrical deformation body.
  • the rotary engine according to the invention can be used for principle any purposes, for example in biogas plants, combined heat and power plants with generators for power generation, for driving vehicles or ships, for waste heat recovery, especially in power plants, vehicles or ships, or in design as an internal combustion engine.
  • the deformation body / silicone tube should be protected from excessive temperatures of combustion, including, for example, a prechamber can be used for ignition, and produced during combustion gases only from the antechamber (via, for example, a slit roller) in the described interior with the rotary piston must occur.
  • the rotary engine can replace the turbine of a turbocharger, serve as a pump drive or used in tools.
  • the fluid pressure or fluid flow is used to set the rotors in rotation.
  • the engine can also be used in reverse in variants of the invention by rotating the rotary pistons to thereby convey a fluid, whereby the motor acts as a pump, compressor or compressor.
  • the properties of the invention described as additional features of the rotary engine also result in variants of the method according to the invention when used as intended.
  • the rotary engine 100 includes two rotary pistons 20, 30, which rotate together and can be driven by a fluid flowing through.
  • the axes of rotation of both rotary pistons 20, 30 extend through the respective center points of the rotary pistons 20, 30.
  • the cross-sectional views of FIGS. 1 and 2 are sectional views perpendicular to these axes of rotation.
  • the rotary piston engine 100 comprises a housing 10, for example a metal housing, which forms an interior 11 in its interior.
  • the interior 11 may be formed fluid-tight except for an inlet 13 and an outlet 15.
  • the two rotary pistons 20, 30 are arranged so that they each form a sealing contact with the wall of the inner space 11 and also touch each other sealingly, regardless of their current rotational position. If a fluid is passed through the inlet 13 into the inner space 11, it can consequently only reach the outlet 15 when it flows along the rotary pistons 20, 30 and causes them to rotate.
  • the rotational energy of the rotary pistons 20, 30 can be used in principle known per se for any purpose, for example as a mechanical drive or to generate electrical energy by means of a generator.
  • the two rotary pistons 20, 30 have the same diameter and have on their outer circumference in each case a ring gear 22, 32.
  • the two sprockets 22, 32 engage into each other. As a result, a seal between the two rotary pistons 20, 30 is achieved and a fluid passage at this point is prevented.
  • the two rotary pistons 20, 30 by the sprockets 22, 32 synchronously rotate (one clockwise, the other opposite thereto).
  • each rotary piston 20, 30 has two bulges 25, 35 which project radially outward beyond the respective toothed rim 22, 32. Except through the bulges 25, 35, the two sprockets 22, 32 are interrupted by two wells 24, 34. In the areas of the wells 24, 34, the respective rotary piston 20, 30 thus has a smaller radius.
  • the bulge 35 engages one of the rotary pistons 30 in the trough 24 of the other rotary piston 20, and vice versa.
  • Each bulge 25, 35 has a slot that can extend in the radial direction.
  • a sealing strip 21, 31 is arranged, which protrudes out of the slot to the outside.
  • the sealing strips 21, 31 can sealingly contact the wall of the interior.
  • sealing strip as well as its support and suspension are of great importance for friction and sealing properties of the engine, which significantly determines the efficiency of the engine.
  • sealing strips and their suspensions are also the components that are subject to the greatest wear, so that the design of the sealing strips and their suspensions is also for maintenance intervals and the life of the engine of great importance.
  • Each sealing strip 21, 31 is received in a slot in one of the bulges 25, 35 on the rotary piston.
  • the slots each open into a cavity 27, 37.
  • a spring such as a coil spring or leaf spring.
  • Spiral springs also act punctually.
  • breakage of such a metal spring small metal particles penetrate into other engine areas and cause serious damage.
  • this is a hose, in particular a silicone hose.
  • the sealing strip 21, 31 projects up to or into the cavity 27, 37 and against the silicone tube. This is thereby compressed and exerts a radially outward pressure on the sealing strip 21, 31.
  • In the axial direction of this cylindrical deformation body may have a same cross section, so that a uniform pressure over the axial length of time is exercised.
  • no metal parts are used, so that there is no risk of consequential damage to the motor in case of breakage of the hose / deformation body.
  • FIG. 2 is shown for illustrative purposes on the rotary piston 30, only a single sealing strip with associated hose, while the second cavity 37 and the slot adjacent thereto are shown empty.
  • a hose as suspension in the cavity 37 and a sealing strip in the slot are arranged.
  • Each rotary piston can be constructed symmetrically, that is, the shapes of the bulges, sealing strips and troughs are independent of the direction of rotation of the rotary piston to the fluid inflow side.
  • the rotary piston engine can be operated equally in both directions of rotation. For a change of direction only the introduction of the fluid is reversed, ie through the outlet 15 into the interior 11 and through the inlet 13 addition.
  • FIG. 3 An enlarged section of the rotary piston 30 is in Fig. 3 shown.
  • the sealing strip 31 protrudes radially outward beyond the bulge 35 and projects inwardly into the cavity 37, in which a hollow tube 38B is used here as a deformation body 38.
  • the sealing strip 31 has a thickening 31A in a central area.
  • the gap or slot for the sealing strip has at a corresponding point a recess (retaining groove) into which the thickening 31A protrudes.
  • the sealing strip 31 accordingly has a cross-shaped cross-section. As a result, the sealing strip 31 is held in the slot and can not escape radially outwardly or radially inwardly out of the slot.
  • the cross-sectional dimensions of the sealing strip 31 and the position of the recess at the slot are selected so that the sealing strip 31 projects into the cavity 37 and (when the motor is stopped) compresses the tube 30B.
  • the tube 30B is thus biased and causes at standstill or when starting the engine a sealing contact of the sealing strip 31 to the inner wall of the housing.
  • the tube 38B has a circular cross section, which may be circular without bias and may have a vaulted or oval shape due to the bias against the sealing strip 31. At higher speeds of rotation of the engine, the centrifugal forces cause a pressure of the sealing strip to the outside and thus provide a sealing effect.
  • a movement space of the sealing strip 31 is limited to the outside by the thickening 31A. If, at higher centrifugal forces, the sealing strip 31 is pressed outwardly by its own weight, the silicone hose 38B is thereby relieved, which has a positive effect on the service life of the silicone hose 38B.
  • the thickening 31A on the sealing strip 31 can in principle also be formed on its inner end, ie directly on the deformation body 38.
  • a possible compression travel of the deformation body 38 is greater, however, if the contact surface with the sealing strip is not too large, so that it may be advantageous to when the thickening 31A is formed in a central area.
  • the thickening 31A also limits the possibility of movement of the sealing strip 31 inwards, whereby replacement of the deformation body 38 for maintenance purposes is easier.
  • the sealing effect of the sealing strips 21, 31 is desired for contact with the housing inner wall;
  • a seal between the two rotary pistons 20, 30 is already effected by the intermeshing sprockets 22, 32 and also in that the bulges 25, 35 engage in the troughs 24, 34. Therefore, a contact of the sealing strips 21, 31 to the wells 34, 24 is not required and may even be undesirable on the contrary, since this the sealing strips 21, 31 are sanded and would have to be replaced after a shorter time.
  • FIGS. 4A to 4C show the contact area between the two rotary pistons 20, 30, the figures differing in the instantaneous rotational positions of the rotary pistons 20, 30.
  • FIG. 4A is the bulge 25 still outside of the trough 34
  • FIG. 4B the bulge 25 just dips into the trough 34
  • FIG. 4C almost completely absorbed in the trough 34.
  • a sealing contact between the rotary pistons 20, 30 is at Fig. 4A already reached by the intermeshing sprockets 22, 32 before the bulge 25 touches a wall of the trough 34.
  • the trough 34 is thus filled by the fluid in the interior 11, wherein the sprockets 22, 32 prevent leakage of the fluid from the trough 34 in the direction of rotation of the two rotary pistons. If the bulge 25 is now screwed into the trough 34 ( Fig. 4B ), the fluid in the trough 34 is compressed. The high pressure in the trough 34 pushes the sealing strip 21 into its slot.
  • the sealing strip 21 is not or hardly in contact with the wall of the trough 34, so that hardly wear and friction on the sealing strip 21 occur.
  • 30 escapes the compressed air / the compressed fluid from the trough 34, against the direction of rotation of the piston 20, 30 (because in the direction of rotation of the piston through the sprockets, in which always at least two teeth of each piston in two grooves of the other piston engage, no fluid can escape).
  • This escape of air creates an air film or an air lubrication on the sealing strip 21 and the bulge 25, whereby the contact is reduced and thus unnecessary friction is avoided ( Fig. 4C ).
  • This advantageous effect can be well demonstrated experimentally by the noise of the air compression and distinguished from conventional structures in which although bulges engage in wells, but no adequate seal is formed, which leads to air compression and the friction-reducing air film.
  • a bulge has a central straight portion 35B which transitions to the ring gear 32 via curved side portions 35A and 35C.
  • an air compression in the trough 24 occurs before the sealing strip comes into contact with the trough wall.
  • a first contact or alternatively a minimum distance between the bulge 35 and the trough 24 at a point of the bulge 35 behind (that is, behind in the direction of rotation) of the sealing strip 31 done.
  • This is either the curved portion 35C (bending portion 35C) in FIG Fig. 3 or the central plateau region 35B between the sealing strip 31 and the arched region 35C.
  • the bulge 35 must be sufficiently wide. This may in particular be the case if the plateau region between the sealing strip 31 and the curved region 35C corresponds to at least 40% of the sealing strip width.
  • this friction-reducing use of an air film is used together with the sealing strip suspension via a silicone tube or a similar cylindrical deformation body.
  • the invention provides a rotary engine with superior efficiency, while wear is low.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
EP18156764.5A 2018-02-14 2018-02-14 Drehkolbenmotor und verfahren zum betreiben eines drehkolbenmotors Pending EP3527781A1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP18156764.5A EP3527781A1 (de) 2018-02-14 2018-02-14 Drehkolbenmotor und verfahren zum betreiben eines drehkolbenmotors
CN201980021312.1A CN111954749B (zh) 2018-02-14 2019-02-08 旋转活塞发动机和用于操作旋转活塞发动机的方法
US16/969,634 US11098587B2 (en) 2018-02-14 2019-02-08 Rotary piston engine and method for operating a rotary piston engine
PCT/EP2019/053215 WO2019158449A1 (de) 2018-02-14 2019-02-08 Drehkolbenmotor und verfahren zum betreiben eines drehkolbenmotors
JP2020543796A JP2021513628A (ja) 2018-02-14 2019-02-08 ロータリピストンエンジン及びロータリピストンエンジンを動作させる方法

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EP18156764.5A EP3527781A1 (de) 2018-02-14 2018-02-14 Drehkolbenmotor und verfahren zum betreiben eines drehkolbenmotors

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JP (1) JP2021513628A (zh)
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EP3543501A1 (de) 2018-03-20 2019-09-25 Fuelsave GmbH Schiffsantriebssystem und umrüstungsverfahren für ein schiffsantriebssystem

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EP3144471A1 (de) 2015-09-21 2017-03-22 Fuelsave GmbH Drehkolbenmotor und verfahren zum betreiben eines drehkolbenmotors
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GB576603A (en) 1944-03-22 1946-04-11 Richard Rutherford Improvements in and relating to rotary machines, such as motors, compressors, pumps and the like
US4506637A (en) * 1983-12-01 1985-03-26 Rotorque Associates Rotary internal combustion engine
DE102007019958A1 (de) 2006-08-14 2008-02-21 Ralf Hettrich Vielzahndrehkolbenmotor mit extrem hohen Drehmoment bei niedrigsten als auch bei sehr hohen Drehzahlen wie in Bereichen einer Turbine, als Antrieb oder zum Einsatz der Energiegewinnung, Energieumwandlung oder Energierückgewinnung
WO2010081469A2 (de) 2009-01-19 2010-07-22 Oleg Tchebunin Drehkraftmaschine mit drei rotierenden verdrängern mit eintrittsdruckklappen und einer steuerung der einlassöffnungen in das brennrohr
GB2486787A (en) 2010-12-20 2012-06-27 Stephen Morant Harding Machine with a lobed rotor in a chamber
EP3144494A1 (de) 2015-09-21 2017-03-22 Fuelsave GmbH Abgasenergierückgewinnungssystem und verfahren zur abgasenergierückgewinnung
EP3144471A1 (de) 2015-09-21 2017-03-22 Fuelsave GmbH Drehkolbenmotor und verfahren zum betreiben eines drehkolbenmotors
EP3184758A1 (de) 2015-12-21 2017-06-28 Fuelsave GmbH Blockheizkraftwerk und verfahren zum betreiben eines blockheizkraftwerks

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WO2019158449A1 (de) 2019-08-22
US11098587B2 (en) 2021-08-24
CN111954749B (zh) 2022-04-01
JP2021513628A (ja) 2021-05-27
US20200400022A1 (en) 2020-12-24
CN111954749A (zh) 2020-11-17

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