EP0897458A1 - Rotary piston internal combustion engine - Google Patents

Rotary piston internal combustion engine

Info

Publication number
EP0897458A1
EP0897458A1 EP97917929A EP97917929A EP0897458A1 EP 0897458 A1 EP0897458 A1 EP 0897458A1 EP 97917929 A EP97917929 A EP 97917929A EP 97917929 A EP97917929 A EP 97917929A EP 0897458 A1 EP0897458 A1 EP 0897458A1
Authority
EP
European Patent Office
Prior art keywords
internal combustion
exhaust
combustion engine
rotary piston
rotary
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
EP97917929A
Other languages
German (de)
French (fr)
Other versions
EP0897458B1 (en
Inventor
Ke Jian Shang
Hua Miao
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
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0897458A1 publication Critical patent/EP0897458A1/en
Application granted granted Critical
Publication of EP0897458B1 publication Critical patent/EP0897458B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/356—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F01C1/3562—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
    • 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
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/10—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F01C20/14—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using rotating valves

Definitions

  • the present invention relates to a rotary piston internal combustion engine with internal combustion, with an essentially circular-cylindrical compression space and an essentially circular-cylindrical working space, wherein in the compression space and in the working space, rotating pistons are arranged, which together around an axis of Compression chamber and work space are rotatable, slides being provided in the compression space and in the work space, which are movably arranged in the radial direction in order to lie sealingly on the surface of the respective rotary piston, and wherein a first exhaust opening is provided on the circumference of the work space
  • Internal combustion engines according to the rotary piston principle are particularly advantageous since they have no reciprocating pistons, as a result of which smooth running and high speeds can be achieved.
  • the present invention is a rotary piston internal combustion engine, in which a partition is arranged, through which the working space is separated from the compression space, and wherein oval compression pistons are arranged in the compression space and working space, which are one to the compression space and working space Concentric axis rotate compression and drive is achieved in that a substantially radially movable slide sealingly abuts the surface of the respective rotary piston.
  • the expansion of the gas mixture means that the working space is larger than the compression space.
  • Such a rotary piston internal combustion engine is known from DE-A 43 05 669.
  • a smaller compression chamber and a larger working chamber are assigned in order to ensure the compression and combustion of the intake gas mixture and the emission of the exhaust gas. It is perfectly possible to advantageously operate such rotary piston internal combustion engines at certain speeds and under certain load conditions or under certain air / fuel conditions, but there is a problem that the volume of the working space changes after the speed has been changed and load or after the change in the air-fuel ratio cannot be changed. In particular, two disadvantageous effects occur.
  • the object of the present invention is to develop the internal combustion engine described at the outset in such a way that a new control for the volume of the work space, an improved connection control between the compression space and work space and an improved seal between the slide, roller and rotary piston is possible in order to ensure optimum operation to realize under different operating conditions.
  • this object is achieved in that further exhaust openings are provided in the work space, which can be closed by exhaust valves, which exhaust valves can be closed and opened one after the other via an adjusting device.
  • the volume of the working space is related to further exhaust openings and the exhaust valves.
  • the effective volume of the work area can be increased or decreased by closing or opening the other exhaust openings.
  • the exhaust valves are designed as rotary valves, the axes of which are essentially parallel to the axis of the working space and the compression space. In this way, actuation of the exhaust valves is possible in a particularly simple manner.
  • the adjusting device is in turn designed as a rotary slide valve, which is preferably connected to the exhaust valves via driver levers. In this way, reliable actuation of the exhaust valves is achieved.
  • an exhaust manifold is provided on the outer circumference of the work space, which connects the first exhaust opening to the further exhaust openings.
  • connection control valves are designed as rotary slide valves, which are arranged in the connection openings on the partition between the compression space and the work space, and whose axes are essentially radial to the axis of the work space and compression space, is particularly advantageous.
  • actuation of the connection control valves is possible in a particularly simple manner.
  • the driver grooves which are preferably connected to the connection control valves via drivers, are provided on the rotary pistons. In this way, a reliable actuation of the connection control valves is achieved in that the connection control valves can be rotated in two opposite directions by the rotary pistons, and are thereby opened or closed.
  • the two slides particularly preferably carry rollers at their tips, which are sealed by contact strips and leaf springs.
  • the slides are guided from both sides by the slideways set up on the partition and the support disks, which is particularly important since relatively large expansion forces of the burned gas act on one side of the slider during the working cycle. In this way the wear is minimized.
  • FIG. 1 shows a partially sectioned end view of the device according to the invention
  • FIG. 2 shows a section along line AA in FIG. 1
  • FIG. 3 shows a partially sectioned end view of the housing
  • FIG. 4 shows a partially sectioned end view 3 in enlarged scale
  • FIG. 5 shows a section of the connection opening along line EE in FIG. 4
  • FIG. 6 shows a section of the connection opening according to line FF in FIG. 4
  • FIG. 7 8 is a partially sectioned left side view of the housing
  • FIG. 8 is a partially sectioned left side view of the section of the housing along line AA in FIG. 3
  • FIG. 9 is a plan view of the housing
  • FIGS. 10 and 11 are views of the cover of the exhaust manifold
  • 12 and 13 are views of the mounting plate on an enlarged scale
  • FIGS. 14 and 15 are views of the actuating device
  • FIGS. 16 to 19 are designs of the cover of the compression chamber
  • FIG. 20 to 22 designs of the cover of the working space
  • FIGS. 23 and 24 views of the support disk
  • FIGS. 25 to 28 views of the rotary pistons
  • FIG. 30 being a Section along line AA in FIG. 29 and FIG. 31 is a section along line BB in FIG. 29, and
  • FIG. 33 shows a section along line A'-A 'in FIGS. 32 and 34 Section along line B'-B 'in FIG. 32
  • FIGS. 35 to 37 are views of the exhaust valve on an enlarged scale
  • FIG. 36 being a section along line A "-A" in FIG. 35
  • FIG. 37 is a section along line B "- B
  • the device according to the invention has an essentially cylindrical housing 1 which is divided by a partition 2 into two cylindrical spaces, namely a compression space 3 and a working space 4. On the end faces, the housing 1 is closed off on the side of the working space 4 by a cover 6 and on the side of the compression space 3 by a cover 5. Cooling fins 1 a are provided on the circumference of the housing 1.
  • a rotary piston 7 is rotatably arranged, while in the working chamber 4
  • Rotary piston 8 is rotatably arranged.
  • the rotary pistons 7 and 8 are fastened on a common shaft 11 in a rotationally fixed manner.
  • the shaft 1 1 is mounted on the covers 5 and 6 with low friction via rolling bearings 11a.
  • An opening 12 serves to receive a spark plug, not shown.
  • a slide valve housing 9 is provided in the area of the compression chamber 3.
  • a slide housing 10 is provided in the area of the work space 4.
  • a connection 13 which is connected to the carburetor (not shown in more detail), is provided on the outer circumference of the compression space.
  • each of the slide housings 9, 10 two slides 19 are each slidably arranged, which carry rollers 20 at their front end, which roll on the rotary pistons 7, 8.
  • the contact strips with leaf springs 21 seal the rollers 20 against the slides 19.
  • Support disks 22 and 23 represent the slideways of the slide 19 opposite the partition 2, the covers 5 and 6 of the compression chamber 3 and the working chamber 4, respectively.
  • connection control valves 24 and 24 ' are provided, which are secured in their positions by a cover 25.
  • Each connection control valve 24 or 24 ' is essentially cylindrical and has two drivers 24a, which are actuated by the rotary pistons 7 and 8.
  • connection control valves can be rotated in two opposite directions and, depending on the position of the rotary pistons 8 and 7, establish or interrupt a connection between the compression chamber 3 and the working chamber 4.
  • connection control valves 24 and 24 ' are shown in detail.
  • the connection control valves 24, 24 ' are constructed in the same way, only their length is different, since for reasons of space the connection control valves 24 must be made shorter.
  • connection openings 29 are designed as bores 29b, the axis of which is parallel to the partition wall 2, connection slots 29c extending from both sides of the bore 29b, which extend on both sides of the partition wall 2 open.
  • a cut-out 29a is provided in the lower section in order to create space for the movement of the pins 24a / u
  • first exhaust opening 26 On the outer periphery of the working space 4 there is a first exhaust opening 26 which is always open and which is connected to the exhaust, not shown, via an exhaust collecting duct 28 and a connection 14 on the cover 30 of the exhaust collecting duct 28. Furthermore, seen in the direction of rotation, after the first exhaust opening 26 further exhaust openings openings 27 are provided which extend over an angular range of approximately 90 ° of the circumference of the working space 4. These further exhaust openings 27 likewise connect the working space 4 to the exhaust manifold 28. Exhaust valves 15 are arranged in the further exhaust openings 27, which have an essentially cylindrical structure and are rotatable. Depending on the rotation of the exhaust valve 15, exhaust gas may or may not pass through the exhaust openings 27 from the working space 4 into the exhaust manifold 28.
  • Each exhaust valve 15 has a driver lever 15a, which is biased to a retaining pin 15c by the action of an annular spring 15b.
  • the driver lever 15a as can be seen in FIGS. 35 to 37, is inserted into a bore 15d which is arranged in an end section 15e.
  • a recess 15f is in the form of a radially continuous slot in order to allow the exhaust gases to pass through.
  • a mounting plate 16, which leads the exhaust valves 15 into the further exhaust openings 27, is arranged on the outside of the cover 6 of the working space 4.
  • the retaining pins 15c are fixed, and an adjusting device 17 is mounted, which is rotatable about the axis of the shaft 1 1 and is in the form of a rotary valve.
  • the adjusting device 17 is actuated by the tensioned Bowden cable 18.
  • An annular spring 16e biases the adjusting device 17 against the pulling direction of the Bowden cable 18.
  • the further exhaust openings 27 are closed in succession by the rotation of the exhaust valves 15.
  • the exhaust valves 15 are opened one after the other. If all other exhaust openings 27 are closed, the effective volume of the work space is greatest. When all other exhaust openings 27 are open, the volume of the working space is smallest.
  • FIG. 7 shows a side view of the housing 1 with a view of the opened exhaust manifold 28.
  • the first exhaust opening 26 and the further exhaust openings 27 are visible.
  • FIG. 9 shows a view from above in order to clarify the cutting guides in the remaining figures.
  • the cover 30 of the exhaust duct is shown in detail, the connection 14 for the exhaust, not shown, being visible.
  • the mounting plate 16 is drawn out individually.
  • the mounting plate 16 has an opening 16d which defines the center around which the adjusting device 17, not shown in these figures, can be rotated.
  • a row of first bores 16a, which are designed to guide the exhaust valves 15, are arranged at the same distance from this opening 16d.
  • Further bores 16b serve to receive holding pins which blow for the driver lever 15a of the exhaust valves 15 represent.
  • a bracket 16c is used to fasten the Bowden cable 18.
  • the adjusting device 17 has a first web 17a in the form of an annular sector and a second web 17b arranged concentrically thereto.
  • a groove 17c is formed between these webs 17a and 17b.
  • the groove 17c is formed so that the protruding parts of the exhaust valves 15 are accommodated in it.
  • An end region of the groove 17e, 17f or the webs 17a and 17b is designed to switch over the driver levers 15a of the exhaust valves 15 when the end 17e slides over a corresponding exhaust valve 15. This causes the individual exhaust valves 15 to be switched one after the other.
  • a bracket 17d is used to fasten the Bowden cable.
  • FIGS. 20 to 22 show views of the cover 6 of the work space 4.
  • the support disc 23 and 24 show the shape of the support disc 22.
  • the support disc 23 is of the same design.
  • the support disk 22 has a bore 22a for receiving the shaft 11.
  • a slot 22b is provided for guiding the slide 19.
  • Grooves 22c arranged on the circumference serve for the exact positioning of the support disk 22 in the compression space 3.
  • the piston 7 is drawn out.
  • the piston is oval and has a bore 7a with a groove 7b for receiving the shaft 11 or a feather key (not shown in more detail), which represents an anti-rotation device with respect to the shaft 11.
  • a recess 7c and a driver groove 7d which is in communication with the outer periphery of the piston 7 and which is in engagement with the drivers 24a of the connection control valves 24, 24 '.
  • the piston 7 is essentially oval, and has a sliding section 7e at the section furthest from the bore 7a. The sliding section 7e is designed to lie sealingly on the outer circumference of the compression space 3.
  • the sealing section 7e is designed as a circular sector-shaped surface, the center of which lies in the shaft axis. A good sealing effect can be achieved in this way.
  • the rotary piston 8 is designed analogously to the rotary piston 7, but with mirror symmetry thereto and with dimensions which are adapted to the work space 4.
  • the bore 8a together with the parallel keyway 8b, the recess 8c, the driving groove 8d and the sealing section 8e correspond to the elements with the reference numerals 7a, 7b, 7c, 7d and 7e of the rotary piston 7.
  • the internal combustion engine according to the invention makes it possible that the volume of the working space can change due to the closing or opening of the further exhaust openings after the change in the speed and load or according to the air-fuel ratio of the gas mixture, that the connection between the compression space and the work space is easily controlled by the closing or opening of the connecting valves, that the seal between the slide, roller and rotary piston is controlled by the arrangements of the slide, Abrasive pieces and leaf springs is improved. This achieves high performance and favorable exhaust gas behavior with low exhaust noise in a large number of operating states.
  • the internal combustion engine of the present invention can be designed with a plurality of compression spaces or work spaces by arranging them offset in the axial direction on a common shaft. Furthermore, it is clear that the internal combustion engine according to the invention, which has been described as a gasoline engine in the exemplary embodiment shown, can also operate according to the diesel principle. In this case, the corresponding changes regarding the compression ratio would have to be carried out in a manner known to the person skilled in the art. An injection nozzle would have to be arranged instead of the spark plug.

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  • 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)
  • Valve Device For Special Equipments (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

A rotary piston internal combustion engine comprises a substantially circular-cylindrical compression space (3) and a substantially circular-cylindrical working space (4), rotary pistons (7, 8) which can rotate together about an axis of the compression space (3) and the working space (4), being disposed in the compression space (3) and the working space (4) are slides (19) which are arranged so as to be movable in the radial direction in order to abut sealingly the surface of the respective rotary piston (7, 8). The periphery of the working space has a first exhaust aperture (26). The working space has further exhaust apertures (27) which can be closed by exhaust valves (15) which can be closed and opened successively by means of an adjusting arrangement (17).

Description

Drehkolben-Brennkraftmaschine mit innerer VerbrennungRotary lobe internal combustion engine
Die vorliegende Erfindung betrifft eine Drehkolben-Brennkraftmaschine mit innerer Verbren¬ nung, mit einem im wesentlichen kreiszylindrischen Verdichtungsraum und einem im wesent¬ lichen kreiszylmdπschen Arbeitsraum, wobei in dem Verdichtungsraum und in dem Arbeits¬ raum jeweils Drehkolben angeordnet sind, die gemeinsam um eine Achse von Verdichtungs¬ raum und Arbeitsraum drehbar sind, wobei in dem Verdichtungsraum und in dem Ar¬ beitsraum Schieber vorgesehen sind, die in Radialπchtung beweglich angeordnet sind, um dichtend an der Oberfläche des jeweiligen Drehkolbens anzuliegen, und wobei am Umfang des Arbeitsraumes eine erste Auspuffoffnung vorgesehen ist Brennkraftmaschinen nach dem Drehkolbenpπnzip sind besonders vorteilhaft, da diese keine hin und her gehenden Kolben aufweisen, wodurch ein ruhiger Lauf und hohe Drehzahlen erreichbar sind.The present invention relates to a rotary piston internal combustion engine with internal combustion, with an essentially circular-cylindrical compression space and an essentially circular-cylindrical working space, wherein in the compression space and in the working space, rotating pistons are arranged, which together around an axis of Compression chamber and work space are rotatable, slides being provided in the compression space and in the work space, which are movably arranged in the radial direction in order to lie sealingly on the surface of the respective rotary piston, and wherein a first exhaust opening is provided on the circumference of the work space Internal combustion engines according to the rotary piston principle are particularly advantageous since they have no reciprocating pistons, as a result of which smooth running and high speeds can be achieved.
Bei der vorhegenden Erfindung handelt es sich um eine Drehkolben-Brennkraftmaschine, in der eine Trennwand angeordnet ist, durch die der Arbeitsraum zum Verdichtungsraum abge¬ trennt wird, und wobei im Verdichtungsraum und Arbeitsraum ovale Drehkolben angeordnet sind, die sich um eine zum Verdichtungsraum und Arbeitsraum konzentπsche Achse drehen Verdichtung und Antrieb wird dadurch erreicht, daß ein im wesentlichen radial beweglicher Schieber dichtend an der Oberfläche des jeweiligen Drehkolbens anhegt. Der Arbeitsraum ist im Ausdehnungsverhaltms des Gasgemisches größer als der Verdichtungsraum.The present invention is a rotary piston internal combustion engine, in which a partition is arranged, through which the working space is separated from the compression space, and wherein oval compression pistons are arranged in the compression space and working space, which are one to the compression space and working space Concentric axis rotate compression and drive is achieved in that a substantially radially movable slide sealingly abuts the surface of the respective rotary piston. The expansion of the gas mixture means that the working space is larger than the compression space.
Aus der DE-A 43 05 669 ist eine solche Drehkolben-Brennkraftmaschine bekannt Dabei sind em kleinerer Verdichtungsraum und ein größerer Arbeitsraum zugeordnet, um die Verdich¬ tung und die Verbrennung des angesaugten Gasgemisches und den Ausstoß des Abgases zu gewährleisten. Es ist durchaus möglich, solche Drehkolben-Brennkraftmaschinen bei be¬ stimmten Drehzahlen und unter bestimmten Lastverhältnissen bzw. bei bestimmten Luft- Kraftstoff-Verhaltnissen in vorteilhafter Weise zu betreiben, ein Problem besteht jedoch dann, daß sich das Volumen des Arbeitsraumes nach der Veränderung der Drehzahlen und Last bzw nach der Änderung des Luft-Kraftstoff- Verhältnisses nicht verändern läßt Dabei treten insbesonders zwei nachteilige Effekte auf.Such a rotary piston internal combustion engine is known from DE-A 43 05 669. A smaller compression chamber and a larger working chamber are assigned in order to ensure the compression and combustion of the intake gas mixture and the emission of the exhaust gas. It is perfectly possible to advantageously operate such rotary piston internal combustion engines at certain speeds and under certain load conditions or under certain air / fuel conditions, but there is a problem that the volume of the working space changes after the speed has been changed and load or after the change in the air-fuel ratio cannot be changed. In particular, two disadvantageous effects occur.
Bei hoher Drehzahl oder großer Last, bei den mit einem fetten Luft-Kraftstoff- Verhältnis ge¬ fahren wird, kann der Ausdehnungsdruck des verbrannten Gases bis zum Öffnen der Aus¬ laßschlitze nicht vollständig ausgenützt werden, so daß Energie durch den Auspuff ungenutzt verloren geht Dadurch kommt es zu einem relativ großen Brennstoffverbrauch und einem relativ hohen Auspuffgeräusch solcher Motoren in diesem BetriebszustandAt high speed or high load, at which a rich air-fuel ratio is used, the expansion pressure of the burned gas cannot be fully utilized until the outlet slots are opened, so that energy is lost through the exhaust unused there is a relatively large fuel consumption and a relatively high exhaust noise of such engines in this operating state
Andererseits wäre es im niedπgen Drehzahl- oder Teillastbereich erwünscht, eine frühere Öffnung der Auslaßschhtze zu erreichen, um den Gaswechsel zu beschleunigen und die Ver¬ luste zu minimieren Ähnliche Motoren zeigen auch die US 2 091 120, DE-C 817 058, DE-C 822 312 und DE-A 19 31 522. Auch bei solchen Maschinen sind Einlaß- und Auslaßöffnungen nur durch den Drehkolben beeinflußt, wodurch sich ebenfalls die oben beschriebenen Nachteile ergeben.On the other hand, it would be desirable in the low speed or part-load range to achieve an earlier opening of the outlet valve in order to accelerate the gas exchange and to minimize the losses Similar engines are also shown in US 2 091 120, DE-C 817 058, DE-C 822 312 and DE-A 19 31 522. In such machines, too, inlet and outlet openings are only influenced by the rotary piston, which also affects the ones described above Disadvantages arise.
Zwei weitere Nachteile der bekannten Vorrichtungen sind, daß die Drehung der Verbindungs¬ scheibe eine größere Reibung aufweisen, so wie dies in der DE-A 43 05 669, der US-A 2 091 120, der DE-C 817 058 und der DE-C 822 312 gezeigt ist, und daß es ein Ab¬ dichtungsproblem zwischen Schieber, Rolle und Drehkolben gibt, insbesonders bei einer Lösung, wie sie in der DE-A 19 31 522 vorgesehen ist.Two further disadvantages of the known devices are that the rotation of the connecting disc has greater friction, as is the case in DE-A 43 05 669, US-A 2 091 120, DE-C 817 058 and DE- C 822 312 is shown, and that there is a sealing problem between slide, roller and rotary lobe, especially in the case of a solution such as that provided in DE-A 19 31 522.
Weitere Motoren ähnlicher Bauart sind beispielsweise in der DE-C 387 287, in der DE- C 404 080, in der DE-A 14 76 672, in der FR-A 2 083 703 oder in der GB-A 1 469 295 offenbart.Other motors of a similar design are disclosed, for example, in DE-C 387 287, in DE-C 404 080, in DE-A 14 76 672, in FR-A 2 083 703 or in GB-A 1 469 295.
Aufgabe der vorliegenden Erfindung ist es, die eingangs beschriebene Brennkraftmaschine so weiterzubilden, daß eine neue Steuerung für das Volumen des Arbeitsraumes, eine verbesserte Verbindungssteuerung zwischen Verdichtungsraum und Arbeitsraum und eine verbesserte Abdichtung zwischen Schieber, Rolle und Drehkolben möglich ist, um einen optimalen Be¬ trieb unter verschiedenen Betriebsbedingungen zu realisieren.The object of the present invention is to develop the internal combustion engine described at the outset in such a way that a new control for the volume of the work space, an improved connection control between the compression space and work space and an improved seal between the slide, roller and rotary piston is possible in order to ensure optimum operation to realize under different operating conditions.
Erfindungsgemäß wird diese Aufgabe dadurch gelöst, daß weitere Auspufföffhungen im Ar¬ beitsraum vorgesehen sind, die durch Auspuffventile verschließbar sind, welche Auspuffven¬ tile über eine Verstelleinrichtung nacheinander verschließbar und zu öffnen sind.According to the invention, this object is achieved in that further exhaust openings are provided in the work space, which can be closed by exhaust valves, which exhaust valves can be closed and opened one after the other via an adjusting device.
Wesentlich an der Erfindung ist, daß das Volumen des Arbeitsraumes mit weiteren Auspuff- Öffnungen und der Auspuffventile zusammenhängt. Je nach Stellung der Auspuffventile kann dabei das wirksame Volumen des Arbeitsraumes durch das Schließen oder das Öffnen der weiteren Auspufföffhungen vergrößert oder verkleinert werden.It is essential to the invention that the volume of the working space is related to further exhaust openings and the exhaust valves. Depending on the position of the exhaust valves, the effective volume of the work area can be increased or decreased by closing or opening the other exhaust openings.
Besonders vorteilhaft ist es, wenn die Auspuffventile als Drehschieber ausgebildet sind, deren Achsen im wesentlichen parallel zu der Achse von Arbeitsraum und Verdichtungsraum sind. Auf diese Weise ist eine Betätigung der Auspuffventile in besonders einfacher Weise mög¬ lich. Insbesonders ist es günstig, wenn die Versteileinrichtung ihrerseits als Drehschieber aus¬ gebildet ist, die vorzugsweise über Mitnehmerhebel mit den Auspuffventilen in Verbindung steht. Auf diese Weise wird eine zuverlässige Betätigung der Auspuffventile erreicht. In einer bevorzugten Ausführungsvariante der vorliegenden Erfindung ist vorgesehen, daß am äußeren Umfang des Arbeitsraumes ein Auspuffsammeikanal vorgesehen ist, der die erste Auspufföff¬ nung mit den weiteren Auspufföffnungen verbindet.It is particularly advantageous if the exhaust valves are designed as rotary valves, the axes of which are essentially parallel to the axis of the working space and the compression space. In this way, actuation of the exhaust valves is possible in a particularly simple manner. In particular, it is advantageous if the adjusting device is in turn designed as a rotary slide valve, which is preferably connected to the exhaust valves via driver levers. In this way, reliable actuation of the exhaust valves is achieved. In a preferred embodiment variant of the present invention, it is provided that an exhaust manifold is provided on the outer circumference of the work space, which connects the first exhaust opening to the further exhaust openings.
Besonders vorteilhaft ist es, wenn die Verbindungssteuerventile als Drehschieber ausgebildet sind, die in den Verbindungsöffnungen auf der Trennwand zwischen dem Verdichtungsraum und dem Arbeitsraum angeordnet sind, und deren Achsen im wesentlichen radial zu der Achse von Arbeitsraum und Verdichtungsraum sind. Auf diese Weise ist eine Betätigung der Ver¬ bindungssteuerventile in besonders leichter Weise möglich. Insbesonders ist es günstig, wenn die Mitnehmernuten, die vorzugsweise über Mitnehmer mit den Verbindungssteuerventilen in Verbindung stehen, auf den Drehkolben vorgesehen sind. Auf diese Weise wird eine zuverläs¬ sige Betätigung der Verbindungssteuerventile erreicht, daß die Verbindungssteuerventile durch die Drehkolben nach zwei entgegengesetzte Richtungen drehbar sind, und dadurch geöffnet oder geschlossen werden.It when the connection control valves are designed as rotary slide valves, which are arranged in the connection openings on the partition between the compression space and the work space, and whose axes are essentially radial to the axis of the work space and compression space, is particularly advantageous. In this way, actuation of the connection control valves is possible in a particularly simple manner. In particular, it is beneficial if the driver grooves, which are preferably connected to the connection control valves via drivers, are provided on the rotary pistons. In this way, a reliable actuation of the connection control valves is achieved in that the connection control valves can be rotated in two opposite directions by the rotary pistons, and are thereby opened or closed.
Besonders vorzugsweise tragen die beiden Schieber an ihrer Spitze Rollen, die über Schleifstücke und Blattfedern abgedichtet sind. Auf diese Weise kann die Abdichtung zwi¬ schen Schieber, Rolle und Drehkolben verbessert werden. Die Schieber werden durch die auf der Trennwand und der Stützscheiben eingerichteten Gleitbahnen von beiden Seiten geführt, was insbesonders wichtig ist, da während des Arbeitstaktes relativ große Ausdehnungskräfte des verbrannten Gases einseitig auf den Schieber einwirken. Auf diese Weise wird der Ver¬ schleiß minimiert.The two slides particularly preferably carry rollers at their tips, which are sealed by contact strips and leaf springs. In this way, the seal between slide, roller and rotary piston can be improved. The slides are guided from both sides by the slideways set up on the partition and the support disks, which is particularly important since relatively large expansion forces of the burned gas act on one side of the slider during the working cycle. In this way the wear is minimized.
In der Folge wird die Erfindung anhand des in den Figuren dargestellten Ausführungsbei¬ spiels näher erläutert. Es zeigen die Fig. 1 eine teilweise geschnittene Stirnansicht der erfin¬ dungsgemäßen Vorrichtung, die Fig. 2 einen Schnitt nach Linie A-A in Fig. 1, die Fig. 3 eine teilweise geschnittene Stirnansicht des Gehäuses, die Fig. 4 eine teilweise geschnittene Stirn¬ ansicht der Verbindungsöffhungen im Detail Y in Fig.3 in vergrößertem Maßstab, die Fig.5 einen Schnitt der Verbindungsöffhung nach Linie E-E in Fig. 4, die Fig. 6 einen Schnitt der Verbindungsöffhung nach Linie F-F in Fig. 4, die Fig. 7 eine teilweise geschnittene rechte Seitenansicht des Gehäuses, die Fig. 8 eine teilweise geschnittene linke Seitenansicht vom Schnitt des Gehäuses nach Linie A-A in Fig. 3, die Fig. 9 eine Draufsicht des Gehäuses, die Fig. 10 und 11 Ansichten des Deckels des Auspuffsammelkanals, die Fig. 12 und 13 Ansich¬ ten der Montageplatte in vergrößertem Maßstab, die Fig. 14 und 15 Ansichten der Stellein¬ richtung, die Fig. 16 bis 19 Ausbildungen des Deckels des Verdichtungsraums, die Fig. 20 bis 22 Ausbildungen des Deckels des Arbeitsraums, die Fig. 23 und 24 Ansichten der Stütz¬ scheibe, die Fig. 25 bis 28 Ansichten der Drehkolben, die Fig. 29 bis 34 Darstellungen der Verbindungssteuerventile in vergrößertem Maßstab, wobei die Fig. 30 ein Schnitt nach Linie A-A in Fig. 29 und die Fig. 31 ein Schnitt nach der Linie B-B in Fig. 29 ist, und wobei die Fig. 33 ein Schnitt nach der Linie A'-A' in Fig. 32 und Fig. 34 ein Schnitt nach Linie B'-B' in Fig. 32 ist, die Fig. 35 bis 37 Ansichten des Auspuffventils in vergrößertem Maßstab, wobei die Fig. 36 ein Schnitt nach Linie A"-A" in Fig. 35 und die Fig. 37 ein Schnitt nach Linie B"- B" in Fig. 35 ist.The invention is explained in more detail below on the basis of the exemplary embodiment illustrated in the figures. 1 shows a partially sectioned end view of the device according to the invention, FIG. 2 shows a section along line AA in FIG. 1, FIG. 3 shows a partially sectioned end view of the housing, and FIG. 4 shows a partially sectioned end view 3 in enlarged scale, FIG. 5 shows a section of the connection opening along line EE in FIG. 4, FIG. 6 shows a section of the connection opening according to line FF in FIG. 4, FIG. 7 8 is a partially sectioned left side view of the housing, FIG. 8 is a partially sectioned left side view of the section of the housing along line AA in FIG. 3, FIG. 9 is a plan view of the housing, FIGS. 10 and 11 are views of the cover of the exhaust manifold, 12 and 13 are views of the mounting plate on an enlarged scale, FIGS. 14 and 15 are views of the actuating device, FIGS. 16 to 19 are designs of the cover of the compression chamber, FIG. 20 to 22 designs of the cover of the working space, FIGS. 23 and 24 views of the support disk, FIGS. 25 to 28 views of the rotary pistons, FIGS. 29 to 34 representations of the connection control valves on an enlarged scale, FIG. 30 being a Section along line AA in FIG. 29 and FIG. 31 is a section along line BB in FIG. 29, and FIG. 33 shows a section along line A'-A 'in FIGS. 32 and 34 Section along line B'-B 'in FIG. 32, FIGS. 35 to 37 are views of the exhaust valve on an enlarged scale, FIG. 36 being a section along line A "-A" in FIG. 35 and FIG. 37 is a section along line B "- B" in Fig. 35.
Die erfindungsgemäße Vorrichtung besitzt ein im wesentlichen zylindrisches Gehäuse 1 , das durch eine Trennwand 2 in zwei zylindrische Räume, nämlich einen Verdichtungsraum 3 und einen Arbeitsraum 4 unterteilt ist. An den Stirnseiten ist das Gehäuse 1 auf der Seite des Ar¬ beitsraums 4 durch einen Deckel 6 und auf der Seite des Verdichtungsraums 3 durch einen Deckel 5 abgeschlossen. Am Umfang des Gehäuses 1 sind Kühlrippen la vorgesehen. Im Verdichtungsraum 3 ist ein Drehkolben 7 drehbar angeordnet, während am Arbeitsraum 4 ein Drehkolben 8 drehbar angeordnet ist Die Drehkolben 7 und 8 sind auf einer gemeinsamen Welle 1 1 verdrehfest befestigt. Die Welle 1 1 ist über Wälzlager l l a reibungsarm auf den Deckeln 5 und 6 gelagert. Eine Öffnung 12 dient zur Aufnahme einer nicht dargestellten Zündkerze. Im Bereich des Verdichtungsraums 3 ist ein Schiebergehausc 9 vorgesehen, das im wesentlichen radial nach außen vorragt. In analoger Weise ist im Bereich des Arbeitsraums 4 ein Schiebergehäuse 10 vorgesehen. Ein Anschluß 13, der mit dem nicht weiter dar¬ gestellten Vergaser in Verbindung steht, ist am äußeren Umfang des Verdichtungsraums vor¬ gesehen.The device according to the invention has an essentially cylindrical housing 1 which is divided by a partition 2 into two cylindrical spaces, namely a compression space 3 and a working space 4. On the end faces, the housing 1 is closed off on the side of the working space 4 by a cover 6 and on the side of the compression space 3 by a cover 5. Cooling fins 1 a are provided on the circumference of the housing 1. In the compression chamber 3, a rotary piston 7 is rotatably arranged, while in the working chamber 4 Rotary piston 8 is rotatably arranged. The rotary pistons 7 and 8 are fastened on a common shaft 11 in a rotationally fixed manner. The shaft 1 1 is mounted on the covers 5 and 6 with low friction via rolling bearings 11a. An opening 12 serves to receive a spark plug, not shown. In the area of the compression chamber 3, a slide valve housing 9 is provided, which projects essentially radially outwards. In a similar manner, a slide housing 10 is provided in the area of the work space 4. A connection 13, which is connected to the carburetor (not shown in more detail), is provided on the outer circumference of the compression space.
In jedem der Schiebergehäuse 9, 10 sind jeweils zwei Schieber 19 verschiebbar angeordnet, die an ihrem vorderen Ende Rollen 20 tragen, die auf den Drehkolben 7, 8 abrollen. Die Schleifstücke mit Blattfedern 21 dichten die Rollen 20 gegenüber den Schiebern 19 ab. Stütz¬ scheiben 22 und 23 stellen die Gleitbahnen der Schieber 19 gegenüber der Trennwand 2 den Deckeln 5 bzw. 6 des Verdichtungsraums 3 bzw. des Arbeitsraums 4 dar.In each of the slide housings 9, 10, two slides 19 are each slidably arranged, which carry rollers 20 at their front end, which roll on the rotary pistons 7, 8. The contact strips with leaf springs 21 seal the rollers 20 against the slides 19. Support disks 22 and 23 represent the slideways of the slide 19 opposite the partition 2, the covers 5 and 6 of the compression chamber 3 and the working chamber 4, respectively.
In die Verbindungsöffnungen 29, die in der Trennwand 2 zwischen dem Verdichtungsraum 3 und dem Arbeitsraum 4 geöffnet sind, sind Verbindungssteuerventile 24 bzw. 24' vorgesehen, die durch einen Deckel 25 in ihren Stellungen gesichert werden. Jedes Verbindungssteuer¬ ventil 24 bzw. 24' ist im wesentlichen zylindrisch aufgebaut und besitzt zwei Mitnehmer 24a, die von den Drehkolben 7 und 8 betätigt werden. Dadurch sind Verbindungssteuerventile nach zwei entgegengesetzten Richtungen drehbar und stellen je nach Stellung der Drehkolben 8 bzw. 7 eine Verbindung zwischen Verdichtungsraum 3 und Arbeitsraum 4 her bzw. unterbrechen diese.In the connection openings 29, which are open in the partition 2 between the compression space 3 and the work space 4, connection control valves 24 and 24 'are provided, which are secured in their positions by a cover 25. Each connection control valve 24 or 24 'is essentially cylindrical and has two drivers 24a, which are actuated by the rotary pistons 7 and 8. As a result, connection control valves can be rotated in two opposite directions and, depending on the position of the rotary pistons 8 and 7, establish or interrupt a connection between the compression chamber 3 and the working chamber 4.
In den Fig. 29 bis 34 sind die Verbindungssteuerventile 24 bzw. 24' detailliert dargestellt. Im Prinzip sind die Verbindungssteuerventile 24, 24' gleichartig aufgebaut, unterschiedlich ist nur ihre Länge, da aus Platzgründen die Verbindungssteuerventile 24 kürzer ausgebildet sein müssen. Die Verbindungssteuerventile 24, 24' bestehen jeweils aus einem im wesentlichen zylindrischen Körper 24b, 24b' mit einer Durchgangsöffhung 24c, 24c' und einer abgewin¬ kelten Bohrung 24d, 24d\ die durch den Mittelpunkt des Querschnitts hindurchgeht. In diese Bohrung 24d, 24d' sind zwei Mitnehmer 24a eingesetzt, die in den Fig. 1 und 2 dargestellt sind.29 to 34, the connection control valves 24 and 24 'are shown in detail. In principle, the connection control valves 24, 24 'are constructed in the same way, only their length is different, since for reasons of space the connection control valves 24 must be made shorter. The connection control valves 24, 24 'each consist of an essentially cylindrical body 24b, 24b' with a through opening 24c, 24c 'and an angled bore 24d, 24d \ which passes through the center of the cross section. In this bore 24d, 24d 'two drivers 24a are inserted, which are shown in FIGS. 1 and 2.
Die Verbindungsöffnungen 29 sind, wie dies aus den Fig. 5 und 6 ersichtlich ist, als Bohrun¬ gen 29b ausgebildet, deren Achse parallel zur Trennwand 2 ist, wobei von beiden Seiten der Bohrung 29b Verbindungsschlitze 29c ausgehen, die sich auf beide Seiten der Trennwand 2 hin öffnen. Im unteren Abschnitt ist eine Ausfräsung 29a vorgesehen, um Raum für die Be¬ wegung der Stifte 24a /u schaffen5 and 6, the connection openings 29 are designed as bores 29b, the axis of which is parallel to the partition wall 2, connection slots 29c extending from both sides of the bore 29b, which extend on both sides of the partition wall 2 open. A cut-out 29a is provided in the lower section in order to create space for the movement of the pins 24a / u
Am äußeren Umfang des Arbeitsraums 4 ist eine stets geöffnete erste Auspufföffnung 26 vor¬ gesehen, die über einen Auspuffsammeikanal 28 und einen Anschluß 14 auf dem Deckel 30 des Auspuffsammelkanals 28 mit dem nicht weiter dargestellten Auspuff in Verbindung steht. Weiters sind in Drehrichtung gesehen nach der ersten Auspufföffnung 26 weitere Auspufföff- nungen 27 vorgesehen, die sich über einen Winkelbereich von etwa 90° des Umfangs des Ar¬ beitsraums 4 erstrecken. Diese weiteren Auspufföffnungen 27 verbinden ebenso den Arbeits¬ raum 4 mit dem Auspuffsammeikanal 28. In den weiteren Auspufföffnungen 27 sind Aus¬ puffventile 15 angeordnet, die einen im wesentlichen zylindrischen Aufbau aufweisen und drehbar sind. Je nach Drehung des Auspuffventils 15 kann Abgas durch die Auspufföffnun¬ gen 27 vom Arbeitsraum 4 in den Auspuffsammelkanal 28 hindurchtreten oder nicht. Jedes Auspuffventil 15 besitzt einen Mitnehmerhebel 15a, der durch die Wirkung einer Ringfeder 15b zu einem Haltestift 15c vorgespannt ist. Der Mitnehmerhebel 15a ist, wie dies in den Fig. 35 bis 37 ersichtlich ist, in eine Bohrung 15d eingesetzt, die in einem Endabschnitt 15e ange¬ ordnet ist. Eine Ausnehmung 15f ist in der Form eines radial durchgängigen Schlitzes ausge¬ bildet, um die Auspuffgase hindurchtreten zu lassen. Eine Montageplatte 16, die die Auspuff¬ ventile 15 in die weiteren Auspufföffnungen 27 führt, wird auf der Außenseite des Deckels 6 des Arbeitsraums 4 angeordnet. Auf der Montageplatte 16 sind die Haltestifte 15c befestigt, und es ist eine VerStelleinrichtung 17 montiert, die um die Achse der Welle 1 1 drehbar und in der Form eines Drehschiebers ausgebildet ist. Ein Bowdenzug 18, der mit nicht weiter dar¬ gestellten Steuereinrichtungen in Verbindung steht, wird auch auf der Montageplatte und der Versteileinrichtung 17 befestigt. Die Verstelleinrichtung 17 wird durch den gespannten Bowdenzug 18 betätigt. Eine Ringfeder 16e spannt die VerStelleinrichtung 17 gegen die Zug¬ richtung des Bowdenzuges 18 vor. Durch die Drehung der Versteileinrichtung 17 in der Richtung gegen den Uhrzeigersinn in der Fig. 1 (Zugriff des Bowdenzuges 18) werden die weiteren Auspufföffhungen 27 durch die Drehung der Auspuffventile 15 nacheinander ge¬ schlossen. In einem entgegengesetzten Fall werden die Auspuffventile 15 nacheinander geöff¬ net. Falls alle weiteren Auspufföffnungen 27 geschlossen werden, ist das wirksame Volumen des Arbeitsraumes am größten. Wenn alle weiteren Auspufföffhungen 27 geöffnet sind, ist das Volumen des Arbeitsraumes am kleinsten.On the outer periphery of the working space 4 there is a first exhaust opening 26 which is always open and which is connected to the exhaust, not shown, via an exhaust collecting duct 28 and a connection 14 on the cover 30 of the exhaust collecting duct 28. Furthermore, seen in the direction of rotation, after the first exhaust opening 26 further exhaust openings openings 27 are provided which extend over an angular range of approximately 90 ° of the circumference of the working space 4. These further exhaust openings 27 likewise connect the working space 4 to the exhaust manifold 28. Exhaust valves 15 are arranged in the further exhaust openings 27, which have an essentially cylindrical structure and are rotatable. Depending on the rotation of the exhaust valve 15, exhaust gas may or may not pass through the exhaust openings 27 from the working space 4 into the exhaust manifold 28. Each exhaust valve 15 has a driver lever 15a, which is biased to a retaining pin 15c by the action of an annular spring 15b. The driver lever 15a, as can be seen in FIGS. 35 to 37, is inserted into a bore 15d which is arranged in an end section 15e. A recess 15f is in the form of a radially continuous slot in order to allow the exhaust gases to pass through. A mounting plate 16, which leads the exhaust valves 15 into the further exhaust openings 27, is arranged on the outside of the cover 6 of the working space 4. On the mounting plate 16, the retaining pins 15c are fixed, and an adjusting device 17 is mounted, which is rotatable about the axis of the shaft 1 1 and is in the form of a rotary valve. A Bowden cable 18, which is connected to control devices (not shown), is also fastened to the mounting plate and the adjusting device 17. The adjusting device 17 is actuated by the tensioned Bowden cable 18. An annular spring 16e biases the adjusting device 17 against the pulling direction of the Bowden cable 18. By turning the adjusting device 17 in the counterclockwise direction in FIG. 1 (access by the Bowden cable 18), the further exhaust openings 27 are closed in succession by the rotation of the exhaust valves 15. In an opposite case, the exhaust valves 15 are opened one after the other. If all other exhaust openings 27 are closed, the effective volume of the work space is greatest. When all other exhaust openings 27 are open, the volume of the working space is smallest.
Die Fig. 7 zeigt eine seitliche Ansicht des Gehäuses 1 mit einem Blick auf den geöffneten Auspuffsammelkanal 28. Dabei sind die erste Auspufföffhung 26 und die weiteren Auspuff¬ öffhungen 27 sichtbar.7 shows a side view of the housing 1 with a view of the opened exhaust manifold 28. The first exhaust opening 26 and the further exhaust openings 27 are visible.
Die Fig. 9 stellt eine Ansicht von oben dar, um die Schnittfuhrungen in den übrigen Figuren zu verdeutlichen.FIG. 9 shows a view from above in order to clarify the cutting guides in the remaining figures.
In den Fig. 10 und 1 1 ist der Deckel 30 des Auspuffkanals detailliert dargestellt, wobei der Anschluß 14 für den nicht dargestellten Auspuff ersichtlich ist.10 and 11, the cover 30 of the exhaust duct is shown in detail, the connection 14 for the exhaust, not shown, being visible.
In den Fig. 12 und 13 ist die Montageplatte 16 einzeln herausgezeichnet. Die Montageplatte 16 besitzt eine Öffnung 16d, die den Mittelpunkt definiert, um den die in diesen Figuren nicht dargestellte VerStelleinrichtung 17 drehbar ist. In gleichem Abstand zu dieser Öffnung 16d ist eine Reihe von ersten Bohrungen 16a angeordnet, die zum Führen der Auspuffventile 15 aus¬ gebildet sind. Weitere Bohrungen 16b dienen zur Aufnahme von Haltestiften, die einen An- schlag für die Mitnehmerhebel 15a der Auspuffventile 15 darstellen. Eine Halterung 16c dient zur Befestigung des Bowdenzuges 18.12 and 13, the mounting plate 16 is drawn out individually. The mounting plate 16 has an opening 16d which defines the center around which the adjusting device 17, not shown in these figures, can be rotated. A row of first bores 16a, which are designed to guide the exhaust valves 15, are arranged at the same distance from this opening 16d. Further bores 16b serve to receive holding pins which blow for the driver lever 15a of the exhaust valves 15 represent. A bracket 16c is used to fasten the Bowden cable 18.
Die VerStelleinrichtung 17 weist, wie dies in den Fig. 14 und 15 ersichtlich ist, einen kreis- ringsektorförmigen ersten Steg 17a und einen konzentrisch dazu angeordneten zweiten Steg 17b auf. Zwischen diesen Stegen 17a und 17b ist eine Nut 17c gebildet. Die Nut 17c ist so ausgebildet, daß die vorspringenden Teile der Auspuffventile 15 in ihr Aufnahme finden. Ein Endbereich der Nut 17e, 17f bzw. der Stege 17a und 17b ist dazu ausgebildet, die Mitneh¬ merhebel 15a der Auspuffventile 15 umzuschalten, wenn das Ende 17e über ein entsprechen¬ des Auspuffventil 15 gleitet. Dadurch wird bewirkt, daß die einzelnen Auspuffventile 15 nacheinander umgeschaltet werden. Eine Halterung 17d dient zur Befestigung des Bowden¬ zuges.As can be seen in FIGS. 14 and 15, the adjusting device 17 has a first web 17a in the form of an annular sector and a second web 17b arranged concentrically thereto. A groove 17c is formed between these webs 17a and 17b. The groove 17c is formed so that the protruding parts of the exhaust valves 15 are accommodated in it. An end region of the groove 17e, 17f or the webs 17a and 17b is designed to switch over the driver levers 15a of the exhaust valves 15 when the end 17e slides over a corresponding exhaust valve 15. This causes the individual exhaust valves 15 to be switched one after the other. A bracket 17d is used to fasten the Bowden cable.
Die Fig. 16 bis 19 zeigen verschiedene Ansichten des Deckels 5, des Verdichtungsraumes 3 und die Fig. 20 bis 22 zeigen Ansichten des Deckels 6 des Arbeitsraumes 4.16 to 19 show different views of the cover 5, the compression space 3 and FIGS. 20 to 22 show views of the cover 6 of the work space 4.
Die Fig. 23 und 24 zeigen die Form der Stützscheibe 22. Die Stützscheibe 23 ist gleichartig ausgebildet. Die Stützscheibe 22 besitzt eine Bohrung 22a zur Aufnahme der Welle 1 1. Ein Schlitz 22b ist zur Führung der Schieber 19 vorgesehen. Am Umfang angeordnete Nuten 22c dienen zur genauen Positionierung der Stützscheibe 22 im Verdichtungsraum 3.23 and 24 show the shape of the support disc 22. The support disc 23 is of the same design. The support disk 22 has a bore 22a for receiving the shaft 11. A slot 22b is provided for guiding the slide 19. Grooves 22c arranged on the circumference serve for the exact positioning of the support disk 22 in the compression space 3.
In den Fig. 25 und 26 ist der Pumpenkolben 7 herausgezeichnet. Der Kolben ist oval ausge¬ bildet und besitzt eine Bohrung 7a mit einer Nut 7b zur Aufnahme der Welle 1 1 bzw. einer nicht näher dargestellten Paßfeder, die eine Verdrehsicherung in Bezug auf die Welle 1 1 dar¬ stellt. In einem Hauptteil des Kolbens 7 sind eine Ausnehmung 7c und eine Mitnehmernut 7d, die mit dem äußeren Umfang des Kolbens 7 in Verbindung steht und die mit den Mitnehmern 24a der Verbindungssteuerventile 24, 24' in Eingriff steht, vorgesehen. Der Kolben 7 ist im wesentlichen oval ausgebildet, und besitzt an dem von der Bohrung 7a am weitesten entfern¬ ten Abschnitt einen Gleitabschnitt 7e. Der Gleitabschnitt 7e ist dazu ausgebildet, am äußeren Umfang des Verdichtungsraumes 3 dichtend anzuliegen. Der Dichtungsabschnitt 7e ist als kreissektorförmige Fläche ausgebildet, deren Mittelpunkt in der Wellenachse liegt. Auf diese Weise kann eine gute Dichtwirkung erzielt werden. Der Drehkolben 8 ist analog zum Dreh¬ kolben 7 ausgebildet, jedoch spiegelsymmetrisch dazu und mit Abmessungen, die an den Ar¬ beitsraum 4 angepaßt sind. Die Bohrung 8a samt Paßfedernut 8b, die Ausnehmung 8c, die Mitnehmernut 8d und der Dichtabschnitt 8e entsprechen den Elementen mit den Bezugszei¬ chen 7a, 7b, 7c, 7d bzw. 7e des Drehkolbens 7.25 and 26, the pump piston 7 is drawn out. The piston is oval and has a bore 7a with a groove 7b for receiving the shaft 11 or a feather key (not shown in more detail), which represents an anti-rotation device with respect to the shaft 11. In a main part of the piston 7, there is provided a recess 7c and a driver groove 7d which is in communication with the outer periphery of the piston 7 and which is in engagement with the drivers 24a of the connection control valves 24, 24 '. The piston 7 is essentially oval, and has a sliding section 7e at the section furthest from the bore 7a. The sliding section 7e is designed to lie sealingly on the outer circumference of the compression space 3. The sealing section 7e is designed as a circular sector-shaped surface, the center of which lies in the shaft axis. A good sealing effect can be achieved in this way. The rotary piston 8 is designed analogously to the rotary piston 7, but with mirror symmetry thereto and with dimensions which are adapted to the work space 4. The bore 8a together with the parallel keyway 8b, the recess 8c, the driving groove 8d and the sealing section 8e correspond to the elements with the reference numerals 7a, 7b, 7c, 7d and 7e of the rotary piston 7.
Die erfindungsgemäße Brennkraftmaschine ermöglicht, daß sich das Volumen des Arbeitsrau¬ mes durch die Schließung oder Öffnung der weiteren Auspufföffhungen nach der Verände¬ rung der Drehzahlen und Last bzw. nach dem Luft-Kraftstoff-Verhältnis des Gasgemisches verändern kann, daß die Verbindung zwischen dem Verdichtungsraum und dem Arbeitsraum durch die Schließung oder Öffnung der Verbindungsventile leicht gesteuert wird, daß die Ab¬ dichtung zwischen Schieber, Rolle und Drehkolben durch die Anordnungen der Schieber, Schleifstücke und Blattfedern verbessert wird. Dadurch wird eine hohe Leistung und ein gün¬ stiges Abgasverhalten mit einem niedrigen Auspuffgeräusch in einer Vielzahl von Betriebszu- ständen erreicht.The internal combustion engine according to the invention makes it possible that the volume of the working space can change due to the closing or opening of the further exhaust openings after the change in the speed and load or according to the air-fuel ratio of the gas mixture, that the connection between the compression space and the work space is easily controlled by the closing or opening of the connecting valves, that the seal between the slide, roller and rotary piston is controlled by the arrangements of the slide, Abrasive pieces and leaf springs is improved. This achieves high performance and favorable exhaust gas behavior with low exhaust noise in a large number of operating states.
Es ist für den Fachmann offensichtlich, daß die Brennkraftmaschine der vorliegenden Erfin¬ dung mit einer Mehrzahl von Verdichtungsräumen bzw. Arbeitsräumen ausgeführt werden kann, indem diese auf einer gemeinsamen Welle in Axialrichtung versetzt angeordnet werden. Weiters ist es klar, daß die erfindungsgemäße Brennkraftmaschine, die in dem dargestellten Ausfuhrungsbeispiel als Ottomotor beschrieben worden ist, ebenso nach dem Dieselprinzip arbeiten kann. In diesem Falle müßten die entsprechenden Änderungen betreffend das Ver¬ dichtungsverhältnis in einer dem Fachmann bekannten Art ausgeführt werden. Anstelle der Zündkerze wäre eine Einspritzdüse anzuordnen. It is obvious to the person skilled in the art that the internal combustion engine of the present invention can be designed with a plurality of compression spaces or work spaces by arranging them offset in the axial direction on a common shaft. Furthermore, it is clear that the internal combustion engine according to the invention, which has been described as a gasoline engine in the exemplary embodiment shown, can also operate according to the diesel principle. In this case, the corresponding changes regarding the compression ratio would have to be carried out in a manner known to the person skilled in the art. An injection nozzle would have to be arranged instead of the spark plug.

Claims

P A T E N T A N S P R Ü C H EP A T E N T A N S P R Ü C H E
1 Drehkolben-Brennkraftmaschine mit innerer Verbrennung, mit einem im wesentlichen kreiszylindrischen Verdichtungsraum (3) und einem im wesentlichen kreiszylindrischen Ar¬ beitsraum (4), wobei in dem Verdichtungsraum (3) und in dem Arbeitsraum (4) jeweils Dreh¬ kolben (7, 8) angeordnet sind, die gemeinsam um eine Achse von Verdichtungsraum (3) und Arbeitsraum (4) drehbar sind, wobei in dem Verdichtungsraum (3) und in dem Arbeitsraum (4) Schieber (19) vorgesehen sind, die in Radialrichtung beweglich angeordnet sind, um dichtend an der Oberfläche des jeweiligen Drehkolbens (7, 8) anzuliegen, und wobei am Umfang des Arbeitsraumes eine erste Auspufföffnung (26) vorgesehen ist, dadurch ge¬ kennzeichnet, daß weitere Auspuffόffnungen (27) im Arbeitsraum vorgesehen sind, die durch Auspuffventile (15) verschließbar sind, welche Auspuffventile (15) über eine Verstell- einnchtung (17) nacheinander verschließbar und zu öffnen sind.1 rotary piston internal combustion engine with internal combustion, with an essentially circular-cylindrical compression chamber (3) and an essentially circular-cylindrical working chamber (4), with rotary pistons (7, 7) in the compression chamber (3) and in the working chamber (4). 8) are arranged, which can be rotated together about an axis of the compression space (3) and the work space (4), slides (19) being provided in the compression space (3) and in the work space (4), which are arranged to be movable in the radial direction in order to lie sealingly on the surface of the respective rotary piston (7, 8), and wherein a first exhaust opening (26) is provided on the circumference of the work space, characterized in that additional exhaust openings (27) are provided in the work space, which are provided by exhaust valves (15) can be closed, which exhaust valves (15) can be closed and opened one after the other via an adjusting device (17).
2. Drehkolben-Brennkraftmaschine nach Anspruch 1 , dadurch gekennzeichnet, daß die2. Rotary piston internal combustion engine according to claim 1, characterized in that the
Auspuffventile (15) als Drehschieber ausgebildet sind, deren Achsen im wesentlichen parallel zu der Achse von Arbeitsraum (4) und Verdichtungsraum (3) sind.Exhaust valves (15) are designed as rotary valves, the axes of which are essentially parallel to the axis of the working chamber (4) and the compression chamber (3).
3 Drehkolben-Brennkraftmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Versteileinrichtung (17) als Drehschieber ausgebildet ist.3 rotary piston internal combustion engine according to claim 1 or 2, characterized in that the adjusting device (17) is designed as a rotary slide valve.
4. Drehkolben-Brennkraftmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die als Drehschieber ausgebildete VerStelleinrichtung (17) über Mitnehmerhebel (15a) mit den Auspuffventilen (15) in Verbindung steht.4. Rotary piston internal combustion engine according to claim 1 or 2, characterized in that the adjusting device designed as a rotary slide valve (17) is connected to the exhaust valves (15) via driver levers (15a).
5. Brennkraftmaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Versteileinrichtung (17) über einen Bowdenzug (18) betätigbar ist.5. Internal combustion engine according to one of claims 1 to 4, characterized in that the adjusting device (17) via a Bowden cable (18) can be actuated.
6. Drehkolben-Brennkraftmaschine nach einem der Ansprüche 1 bis 5, dadurch gekenn¬ zeichnet, daß am äußeren Umfang des Arbeitsraumes (4) ein Auspuffsammelkanal (28) vor¬ gesehen ist, der die erste Auspufföffnung (26) mit den weiteren Auspufföffhungen (27) verbindet.6. Rotary piston internal combustion engine according to one of claims 1 to 5, characterized gekenn¬ characterized in that on the outer periphery of the working space (4) an exhaust manifold (28) is seen vor¬, the first exhaust opening (26) with the further exhaust openings (27 ) connects.
7. Drehkolben-Brennkraftmaschine nach einem der Ansprüche 1 bis 6, dadurch gekenn¬ zeichnet, daß jeweils zwei Schieber (19) in einem Schiebergehäuse (9, 10) gleitbar gelagert sind, und daß sie an ihrer Spitze Rollen (20) tragen, die über Schleifstücke (21) und Blattfe¬ dern abgedichtet sind.7. Rotary piston internal combustion engine according to one of claims 1 to 6, characterized gekenn¬ characterized in that two sliders (19) in a slide housing (9, 10) are slidably mounted, and that they carry rollers (20) at their tip are sealed via contact strips (21) and leaf springs.
8 Drehkolben-Brennkraftmaschine nach einem der Ansprüche 1 bis 7, dadurch gekenn¬ zeichnet, daß zwischen Verdichtungsraum (3) und Arbeitsraum (4) Verbindungssteuerventile (24, 24') angeordnet sind, die durch die Drehkolben (7, 8) geöffnet und geschlossen werden.8 rotary piston internal combustion engine according to one of claims 1 to 7, characterized gekenn¬ characterized in that between the compression chamber (3) and the working chamber (4) connection control valves (24, 24 ') are arranged, which are opened and closed by the rotary pistons (7, 8) become.
9 Drehkolben-Brennkraftmaschine nach Anspruch 8, dadurch gekennzeichnet, daß die Verbindungssteuerventile (24, 24') Mitnehmer (24a) aufweisen, die in eine Mitnehmemut der Drehkolben (7d, 8d) eingreifen. 9 rotary piston internal combustion engine according to claim 8, characterized in that the connection control valves (24, 24 ') have drivers (24a) which engage in a driving groove of the rotary pistons (7d, 8d).
EP97917929A 1996-05-06 1997-04-30 Rotary piston internal combustion engine Expired - Lifetime EP0897458B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AT80596 1996-05-06
AT805/96 1996-05-06
AT80596 1996-05-06
PCT/AT1997/000085 WO1997042398A1 (en) 1996-05-06 1997-04-30 Rotary piston internal combustion engine

Publications (2)

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EP0897458A1 true EP0897458A1 (en) 1999-02-24
EP0897458B1 EP0897458B1 (en) 1999-10-27

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JP (1) JP3831414B2 (en)
CN (1) CN1095026C (en)
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JP3831414B2 (en) 2006-10-11
WO1997042398A1 (en) 1997-11-13
JP2000509459A (en) 2000-07-25
DE59700632D1 (en) 1999-12-02
ATE186100T1 (en) 1999-11-15
CN1211299A (en) 1999-03-17
ES2137783T3 (en) 1999-12-16
AU2626197A (en) 1997-11-26
EP0897458B1 (en) 1999-10-27
US6349696B1 (en) 2002-02-26
CN1095026C (en) 2002-11-27

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