EP0071890A1 - Moteur à piston alternatif ou rotatif à chambre de compression à volume variable - Google Patents

Moteur à piston alternatif ou rotatif à chambre de compression à volume variable Download PDF

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Publication number
EP0071890A1
EP0071890A1 EP82106852A EP82106852A EP0071890A1 EP 0071890 A1 EP0071890 A1 EP 0071890A1 EP 82106852 A EP82106852 A EP 82106852A EP 82106852 A EP82106852 A EP 82106852A EP 0071890 A1 EP0071890 A1 EP 0071890A1
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EP
European Patent Office
Prior art keywords
piston
machine according
compression space
sealing
actuator
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.)
Withdrawn
Application number
EP82106852A
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German (de)
English (en)
Inventor
Felix Dr. H.C. Wankel
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 EP0071890A1 publication Critical patent/EP0071890A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/16—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by adjusting the capacity of dead spaces of working chambers
    • 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
    • F01C20/18—Control of, monitoring of, or safety arrangements for, machines or engines characterised by varying the volume of the working chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F02D15/04—Varying compression ratio by alteration of volume of compression space without changing piston stroke

Definitions

  • the invention relates to a reciprocating or rotary piston machine with a final compression chamber that is variable in size in the idle or operating state, the size of which is changed by a part that can be moved into and out of it.
  • DE-OS 1 925 473 and DE-OS 2 632 440 Another design principle for changing the size of the final compression space without having to change the shape of the room wall is, for example, by DE-OS 1 925 473 and DE-OS 2 632 440 known. According to this principle, the piston of the reciprocating engine is telescopically resizable by hydraulic means.
  • DE-OS 2 404 231 it is even proposed to shift the entire cylinder block relative to the crankshaft bearing carrier during operation in order to avoid changes to the cylinder head.
  • this part consists of a circular-cylindrical piston.
  • the circular cross-sectional shape of the piston has the disadvantage that the bottom of the working piston opposite wall of the compression end space can only be used to a small extent taking into account the arrangement of the valve cross sections for the additional arrangement of this piston, without the shape of the end compression space being adversely changed by adjoining spaces.
  • the object of the present invention is to avoid this disadvantage and to design a reciprocating or rotary piston machine with a size-adjustable end compression space in such a way that this size change does not result in a substantially disadvantageous change in the shape of the compression space.
  • This object is achieved in that there is at least one such movable part for changing the size of the end compression space, which has a cross-section deviating from the circular shape.
  • Deviating from the circular cross-sectional shape has the advantage that the cross-section or the end face size of the movable part can be enlarged and designed more freely.
  • the possible substantial enlargement of the cross-section has the advantage that the change in size of the end compression space can be achieved by a relatively small lifting movement of the movable part and, accordingly, an insignificant change in the shape of the end compression space occurs when the part is maximally moved out of the end compression space.
  • the sealing of the movable part to change the size of the final compression space with respect to its conversions takes place by means of a sealing limit formed from sealing strips and butt joint closures.
  • the movable part can also have an angular cross-section transversely to its direction of movement, it being possible to design the end wall of the movable part in accordance with an optimal shape of the end compression space for operational reasons.
  • the optimal shape in each adjustment position of the movable part can also be achieved by a plurality of movable parts of the same or different shape.
  • the shape of the end compression space can be influenced further by the path length, which is dependent on its cross section. When using several moving parts, the movement points or path lengths can also be selected differently.
  • a preferred special form of the direction of movement of different moving parts corresponds to the movement in the same plane, wherein the movement of two parts can take place like a pair of pliers.
  • the movement of the at least one movable part can be steplessly controlled by an actuator between two limit positions take place, preferably the drive transmission against the force due to the pressure in the compression chamber is self-locking.
  • An advantageous application of the invention is possible, for example, on the rotor of a rotary piston machine or a rotary piston machine, the adjustment movement also being able to be transmitted to the rotary piston or the rotary piston in a mechanical manner.
  • the rotary piston machine according to FIGS. 1 and 2 has a piston rotor 2 and a shut-off rotor 3, which revolve around axes 4 and 5, which are parallel to one another, in opposite directions in a housing 1.
  • the piston rotor 2 rotates twice as fast as the shut-off rotor 3, so that one of the pistons 6, 7 engages like a gearwheel into a gap 8 of the shut-off rotor 3.
  • 1 shows the piston rotor 2 in the position of maximum compression, so that the compression space 10 corresponds to the space which is enclosed between the piston 6 and the gap of the shut-off rotor.
  • One of the two spark plugs of the Kol benlaufers is indicated by dashed lines 12.
  • the compression space 10 is sealed by sealing strips 13, 14, as described in DE-OS 3 005 694 by the same applicant.
  • the sealing against the flat housing side walls is carried out by sealing strips 15, as are generally known for rotary piston machines.
  • At least part of its wall 16 provided on the shut-off rotor 3 is formed by the end face of a slide 18.
  • This end face is shaped in accordance with the kinematics of the rotary piston machine, while the side walls of the slide guided in a guide channel 20 run parallel to one another.
  • the slide side walls are sealed off from the surface of the guide channel 20 by sealing boundaries 22, as are known per se for rotary piston machines.
  • 1 and 2 show the slide 18 in two limit positions, the compression space being the smallest according to FIG. 1 and the compression space being the largest according to FIG. 2.
  • An actuating mechanism for the four slides 18 is arranged in the central part of the shut-off rotor 3.
  • Each slide 18 has rigid bolts 24, 25 connected to it, the thread pitch of the threaded bolts of the diametrically opposed slide being directed in the opposite direction.
  • the rotation of the threaded sleeves 27, 28, in which the threaded bolts 24, 25 of two slides engage from both sides causes a simultaneous movement of the slides 18 arranged opposite one another radially outwards or radially inwards.
  • a gear 30 is formed on the circumference of the threaded sleeves 27, 28, into which a toothed rack 32 engages, which is located between the two threaded sleeves.
  • the toothed rack has a square cross-section and a toothing 33 on each of its outer surfaces.
  • the toothing of the toothed rack which is not in engagement with a toothed wheel 30 in the cross-sectional illustration of FIGS. 1 and 2, serves to move similar threaded sleeves 27 and threaded bolts 24 ', 25'. which are at an axial distance and offset by 90 ° to the arrangement shown.
  • the rack 32 as well as the positioning mechanism shown rotates together with the locking runner 30 is provided an unillustrated end of the rack having a circular cross-section, to which an adjusting element can engage in sliding contact.
  • the cylindrical part of the toothed rack 5 can have a circumferential groove in which a sliding block engages or a circumferential profile which is tooth-shaped in cross section and into which a toothed wheel of an adjustment drive engages.
  • Such designs for the axial displacement of a rotating shaft are already known in various embodiments.
  • FIG. 3 and 4 show an example of the application of the invention to a reciprocating piston engine operating according to the Otto process, the actuator for the slide in particular being shown only schematically.
  • an inclined guide channel 36 is provided for a slide 37, which has the task of optimally adapting the size of the compression space 38 depending on the operating conditions.
  • the guide channel 36 and, accordingly, also the slide 37 have side walls which are parallel to one another, and the slide can be sealed off from the guide channel by sealing limits 39, as has already been mentioned, for example, according to FIG. 1.
  • the inclined arrangement of the slide 37 in the cylinder head is advantageous with regard to the sealing by the cylinder head gasket 40 and the guidance of cooling water from the cavities 41 or 42 through openings 43, 44 through the guide channel, so that the hollow slide 37 is cooled from the inside.
  • a hydraulic drive 45 with hydraulic supply and discharge lines 46, 47 is provided in the exemplary embodiment shown, which are attached to the side of the cylinder head by means of screws 48, but it goes without saying that different types of actuators can be used, such as e.g. also an electromotive drive which executes the reciprocating movement of the slide 37 via a threaded spindle.
  • actuators such as e.g. also an electromotive drive which executes the reciprocating movement of the slide 37 via a threaded spindle.
  • the use of a threaded spindle or threaded bolts as shown in FIG. 1 has the advantage that self-locking is also present in the compression space 38 against the highest pressures.
  • Securing the position of the slide against the pressures in the compression chamber 38 can, however, also be achieved, for example, by means of at least one wedge bar 50 or an inhibitor.
  • 5 shows a schematic illustration of an example of a corresponding arrangement between a slide 37 'of a wedge bar 50 and an actuator 52'.
  • the actuator corresponds, for example, to the piston rod 52 of the actuator 45 according to FIG. 3.
  • Springs 54 arranged between the actuator 52 'and the wedge bar 50 press the wedge bar 50 against the wedge surface 55 of the slide 37', so that the outer surface 56 is also pressed against Wedge ledge against the side surface 57 of the guide channel, in which the slide 37 'is arranged.
  • the resulting frictional force between the surfaces 56 and 57 prevents the wedge strip from moving, and the frictional force increases in accordance with the force acting on the slide 37 'in the direction of the arrow 58.
  • the slide When the slide is pulled back by the actuator 52 ', it first engages the wedge bar 50, pulls it out of the wedge gap, and only then does the wedge bar transmit the movement to the slide 37'.
  • Grooves 59, 61 are provided in the slide and the wedge bar, into which extensions 60, 62 of the wedge bar and the actuator 52 'engage.
  • the end face 63 of the actuator presses against the rear side 64 of the slide 37 '.
  • the wedge angle of the wedge strip is to be selected taking into account the friction values between the wedge surfaces so that the actuator 52 'can pull the wedge strip out of the wedge gap without a considerable effort being required.
  • FIG. 4 in connection with FIG. 3 shows particularly clearly that, despite the limited space in the cylinder head, the slide 37 enables the compression space 38 to be significantly reduced.
  • a recess 66 on the position of the slide facing the spark plug 67 enables a maximum stroke movement, which is limited by its approach to the piston surface 68 and the inlet valve 70.
  • the piston crown is provided with a raised portion 74 which is nose-shaped in cross section and fills this space in the upper piston position, so that the combustion or compression chamber has the space shown in FIG. 3 has a visible cross-sectional shape and is laterally offset relative to the cylinder axis.
  • FIGS. 6 to 10 An exemplary embodiment is described below with reference to FIGS. 6 to 10, in which the influence not only of the size but also of the shape of the final compression space becomes particularly clear on the basis of the present invention.
  • This exemplary embodiment also shows that by changing the size of the end compression space, the present invention can maintain a special shape of the end compression space, as is desired, for example, in order to achieve favorable flow processes or an improved combustion process.
  • this special shape are out 6 and 7, the valve plates 76, 77 are arranged at different distances from the piston crown surface 78, so that an end compression chamber 80 is formed in the area below a valve plate 77 in a partial area of the cylinder head, ie laterally offset.
  • this end compression space 80 has concavely curved side surfaces 82, 84, which due to the present invention are at least partially formed by the curved end surfaces 85, 86 of displaceable combustion chamber modifiers 87, 88.
  • This arrangement and shape of the final compression chamber without its changeability is known per se, for example from DE-OS 2 913 763.
  • the various adjustment positions of the combustion chamber changers 87, 88 shown in FIGS. 8 to 10 make it clear that, despite the size change, the shape of the end compression chamber, which is round in cross section, and thus the desired swirl flow can be maintained. Starting from the position shown in FIG.
  • the various adjustment positions correspond, for example, to changes in the compression ratio from 12: 1 to 14.5: 1, 16: 1 to 18: 1.
  • the same level in Combustion chamber changers 87, 88 moving in relation to one another can also be provided a plurality of combustion chamber changers movable in the direction of the final compression chamber and that the direction of movement of different combustion chamber changers can also be different.
  • the changers 87, 88 of the exemplary embodiment shown have a rectangular cross section, as shown in the illustration in FIG. 6, and are each displaceable in a rectilinear guide channel with the same cross section.
  • the changers could, however, also be displaceable on a circular path if they, like the guide channel, are correspondingly curved are designed.
  • An arch shape may be desirable for reasons of practical arrangement, or in order to carry out the displacement movement as a rotary movement.
  • FIGS. 12 to 15 show sections from different corner areas of a sealing boundary, as are suitable for sealing the changers 87, 88 of the final compression space. 6, the sealing limit is indicated schematically by broken lines 90.
  • the sealing border 90 consists of sealing strips 91, 92 and, for example, cylindrical butt joint closures 93.
  • FIGS. 12 and 13 show the arrangement of butt joint closures 93 in the straight region of a sealing strip, while according to FIGS.
  • the sealing strips are arranged with play in correspondingly shaped recesses in the slide 37 or changer 87, 88 or also in their guide channel, so that they can press the pressure of the gas to be sealed laterally against a groove side wall and the sealing counter surface.
  • the mode of operation of such sealing limits is known per se and is described, for example, in “rotary piston internal combustion engines” by Bensinger, Springer-Verlag, 1973, or in DE-PS 1 148 824.
  • the particular advantage of sealing limits is that the sealing surface moves Part can adjust so that thermal expansion is not disadvantageous affect the seal.
  • the sealing limit can follow any contours and ensures easy adjustability of the sealed part, i.e. of the slider or the changer and still a good seal against that at the final compression space e.g. an internal combustion engine occurring temperature and pressure loads.
  • FIG. 11 shows the shape of a sealing limit, as is suitable, for example, for sealing the changer 101 of a rotary piston 102 according to FIGS. 16-18.
  • This sealing limit 11 has two rectilinear sealing strips 96 which connect two circular sealing strips 97, 98 to one another.
  • the butt joints 99 are sealed by bolt-shaped butt joint closures 100 in which they are embedded.
  • the piston 16 to 18 relate to a Wankel rotary piston machine known per se, e.g. is described in the aforementioned "Rotary Piston Combustion Engines” textbook by Bensinger.
  • the piston has the generally known contour shown in FIG. 16, which is composed of three circular piston surfaces 103, 104 and 105 which intersect in three piston corners provided with sealing strips 106.
  • the piston 102 is mounted on the eccentric 108 of the machine main shaft 110 and is provided with an internally toothed ring gear 112 which is on a fixed, i.e. with the housing 113 connected externally toothed pinion 114 rolls.
  • the piston corners or the sealing strips 106 move on two trochoids when the shaft 110 rotates, wherein they are in constant contact with the lateral surface 116 of the machine housing, which has the shape of this trochoidal movement path.
  • the piston surfaces 103 to 105 together with the casing surface 116 delimit the working spaces of the rotary piston machine, similar to the piston crown 78 (FIG. 6) the working space of a reciprocating piston machine.
  • part of the piston surfaces 103 to 105 is designed as an end surface 118 of a changer 101 which can be displaced relative to the piston 102. In supervision, this can have the shape of the sealing limit according to FIG. 11, for example. Two such sealing limits are arranged in two circumferential grooves 120, 121 of the changer 101 arranged one behind the other in the sliding direction.
  • FIG. 17 is suitable for a machine with only one piston, so that the drive mechanism for the changer 101 can be provided on the side axially opposite the fixed pinion 114 and the internally toothed ring gear 112, while in the example according to FIG. 18 the latter Drive is provided on the same side, since a second machine unit with a second piston 102 on the shaft 110 adjacent to one another in the axial direction, ie to the right in the drawing, hardly makes the opposite side accessible.
  • a second internally toothed ring gear 124 which moves with the piston 102 but is rotatable relative to the latter is provided and rolls on a pinion 126 provided with an external toothing 125.
  • This ring gear 124 and the pinion 126 are thus comparable to the ring gear 112 and the pinion 114, with the exception of their adjustability.
  • the pinion 126 can be rotated by an actuator (not shown), so that it the ring gear 124 rotates relative to the piston on which it is mounted.
  • This rotary movement of the ring gear 124 is transmitted via a crown gear 128 formed on it to a pinion 130, with which it meshes at point 131.
  • This pinion is mounted about an axis perpendicular to aschinenwelle M 110 extending axis in the rotary piston 102 and is formed as a threaded sleeve, which encloses a fixedly connected to the threaded bolt 101 modifier 133rd Rotation of the pinion 130 or this threaded sleeve in one direction or the other causes the changer 101 to move outward or inward relative to the rotary piston or relative to its piston surface 105.
  • the ring gear 124 and the pinion 130 are shaped with their circumference in a corresponding manner Recesses of the rotary piston 102 in the 17 visible manner rotatably mounted.
  • the reference number 128 has two reference lines for the crown gear 128, since the course of the cutting line shown in FIG. 16 shows it offset radially inward in relation to a flat cutting course.
  • an externally toothed pinion 134 which is adjustable in the direction of rotation is provided and corresponds in function to the pinion 126 of the exemplary embodiment according to FIG. 17.
  • the pinion 134 is rotated through a certain angle in the circumferential direction by a drive transmission via two gear wheels 135, 136 by an actuator (not shown) acting on the shaft 137. This twisting movement is transferred to the ring gear 139 which is in engagement with the pinion with its internal toothing 138.
  • This ring gear 139 also has a crown gear part 140 which rotates the threaded sleeve 142.
  • the rotary movement of the threaded sleeve 142 moves the changer 101 outward or inward via the threaded bolt 143, as already described with reference to FIG. 17.
  • the actuator can act hydraulically or electromechanically in a manner known per se and can be regulated on the basis of signals of various types of signal transmitters. Thanks to modern electronic control technology, the signal transmitters can also achieve the optimal control of the actuator in combination.
  • detonation transmitters can also be used on internal combustion engines which indicate in good time the start of the operating state in which a knocking of the engine occurs in order to reduce the compression ratio. If at times a particularly quiet operation of the motor is desired, an acoustic transmitter can also be used.

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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)
EP82106852A 1981-08-04 1982-07-29 Moteur à piston alternatif ou rotatif à chambre de compression à volume variable Withdrawn EP0071890A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CH502381 1981-08-04
CH5023/81 1981-08-04
CH738381 1981-11-17
CH7383/81 1981-11-17

Publications (1)

Publication Number Publication Date
EP0071890A1 true EP0071890A1 (fr) 1983-02-16

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EP82106852A Withdrawn EP0071890A1 (fr) 1981-08-04 1982-07-29 Moteur à piston alternatif ou rotatif à chambre de compression à volume variable

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EP (1) EP0071890A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1394441A2 (fr) 2002-08-23 2004-03-03 Audi Ag Transmission toroidale
CN106121810A (zh) * 2016-09-27 2016-11-16 上海洲跃生物科技有限公司 一种变压缩比的汪克尔发动机
CN106194411A (zh) * 2016-09-25 2016-12-07 上海洲跃生物科技有限公司 一种高膨胀比高扭矩转子发动机
CN106640387A (zh) * 2016-12-06 2017-05-10 江苏大学 一种可实现转子发动机不同压缩比的执行机构

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR443692A (fr) * 1911-11-18 1912-09-30 Ettore Bugatti Moteur à combustion avec compression automatiquement variable
US2381895A (en) * 1943-08-23 1945-08-14 David F Foster Compression control device
DE963739C (de) * 1951-09-22 1957-05-09 Kurt Kuers Verbrennungs-Kraftmaschine mit Gemischverdichtung und Selbstzuendung durch die Verdichtungswaerme
US2883974A (en) * 1955-12-02 1959-04-28 Raymond A Heising Internal combustion engines

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR443692A (fr) * 1911-11-18 1912-09-30 Ettore Bugatti Moteur à combustion avec compression automatiquement variable
US2381895A (en) * 1943-08-23 1945-08-14 David F Foster Compression control device
DE963739C (de) * 1951-09-22 1957-05-09 Kurt Kuers Verbrennungs-Kraftmaschine mit Gemischverdichtung und Selbstzuendung durch die Verdichtungswaerme
US2883974A (en) * 1955-12-02 1959-04-28 Raymond A Heising Internal combustion engines

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1394441A2 (fr) 2002-08-23 2004-03-03 Audi Ag Transmission toroidale
CN106194411A (zh) * 2016-09-25 2016-12-07 上海洲跃生物科技有限公司 一种高膨胀比高扭矩转子发动机
CN106194411B (zh) * 2016-09-25 2018-10-30 上海洲跃生物科技有限公司 一种高膨胀比高扭矩转子发动机
CN106121810A (zh) * 2016-09-27 2016-11-16 上海洲跃生物科技有限公司 一种变压缩比的汪克尔发动机
CN106640387A (zh) * 2016-12-06 2017-05-10 江苏大学 一种可实现转子发动机不同压缩比的执行机构
CN106640387B (zh) * 2016-12-06 2022-11-18 江苏大学 一种可实现转子发动机不同压缩比的执行机构

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