EP1144806B1 - Moteur a pistons oscillants - Google Patents

Moteur a pistons oscillants Download PDF

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Publication number
EP1144806B1
EP1144806B1 EP00901093A EP00901093A EP1144806B1 EP 1144806 B1 EP1144806 B1 EP 1144806B1 EP 00901093 A EP00901093 A EP 00901093A EP 00901093 A EP00901093 A EP 00901093A EP 1144806 B1 EP1144806 B1 EP 1144806B1
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EP
European Patent Office
Prior art keywords
pistons
oscillating
piston engine
housing
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP00901093A
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German (de)
English (en)
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EP1144806A1 (fr
Inventor
Herbert Hüttlin
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Individual
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    • 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
    • F01C1/40—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 having a hinged member
    • F01C1/44—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 having a hinged member with vanes hinged to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18048—Rotary to reciprocating and intermittent rotary
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18272—Planetary gearing and slide

Definitions

  • the invention relates to a swing piston machine, with a Housing in which several pistons designed as two-armed levers by one parallel to a central housing axis Swivel axis arranged pivotably and together in one Circulation direction are movable, with the pistons on their one Have side treads facing away from the inner wall of the housing when rotating the pistons in the housing along at least one Control curve of a central curve piece fixed to the housing are to the pivotal movements of the pistons when rotating control, the curve piece being designed as a control curve Has outer contour, along which the running surfaces of the pistons are supported towards the housing axis.
  • Such a swing piston machine is from WO 98/13583 known, the disclosure of which is hereby expressly included in the present Registration is involved.
  • Swing piston machines belong to a genus of internal combustion engines, in which the individual work cycles of admission, Compressing, igniting (expanding) and expelling the combustion mixture by rocker-like swivel movements of the individual pistons between two end positions.
  • the known oscillating piston machine has a center in the housing a curve piece fixed to the housing, one as a control curve has trained outer contour.
  • the pistons point to hers facing away from the inner wall of the housing, i.e. the central curve piece facing sides on treads when rotating the pistons in the housing along the outer contour of the curve piece below constant contact with the same.
  • the Swiveling movements of the pistons are thereby rotating Piston in the housing by guiding the tread of the Interaction of pistons along the outer contour of the curve piece controlled by a rolling engagement of adjacent pistons.
  • DE-OS-15 51 101 is a centrifugal piston internal combustion engine known, the six spaced pistons of approximately triangular shape that so on a circular drive wheel are pivotally mounted that they when circulating in the housing of the engine by the occurring Centrifugal forces are pressed against the inner wall of the housing.
  • the control of the pivoting movement of the individual pistons is thereby due to a special trochoidal design of the inner wall of the housing causes.
  • In the housing are also two fixed Guide cams with an outer contour arranged at low Engine speeds at which the centrifugal forces are low are to ensure that the pistons against the inner wall of the housing to be pressed to the functionality of the engine maintain at low speeds.
  • This Centrifugal piston engine is, however, already required because of the special non-circular contouring of the housing inner wall disadvantageous.
  • an internal combustion engine is also with revolving piston, forming a closed chain.
  • the pistons form together with the non-round, approximately oval cylinder jacket closed rotating working chambers variable Volume.
  • the polygon formed by the pistons is a pentagon or polygon, with a regular pentagon being the most advantageous is seen.
  • two secondary rotors are provided, consisting of five segments exist, these segments articulated by means of bolts are. Rollers are mounted on the bolts, which over the Control the movement of the rotors while rolling, and by means of further bolts also the movement of the pistons.
  • This configuration a swing piston machine is comparatively complex. Further disadvantages of this configuration are the non-circular configuration the housing inner wall and the articulated connection of the segments forming the two secondary rotors for controlling the Swiveling movement of the pistons.
  • the invention is therefore based on the object of a swing piston machine of the type mentioned at the outset, that the disadvantages mentioned above are avoided.
  • the swing piston machine is said to have wear properties and functional reliability further improved become.
  • this object is achieved with a swing piston machine of the type mentioned in that the Curve section another control curve designed as an inner contour has, along which the piston over the treads are guided supported on the centrifugal force.
  • the swing piston machine according to the invention therefore continues assume that the pivoting movements of the individual pistons controlled when circulating through a central curve piece fixed to the housing be what is in the known swing piston machine compared to the known centrifugal piston internal combustion engine has proven to be advantageous.
  • the oscillating piston machine is in the form of an inner contour trained control curve, along which the running surfaces of the pistons are taken a measure to the centrifugal forces the piston halves or lever arms of the pistons.
  • Pistons advantageously both along an "outer guide” the known outer contour and an additional one “Inner guidance” along the inner contour of the curve section.
  • a such a combination of internal and external guidance enables one Kinematically exact and at the same time dynamically favorable control the pivoting movements of the pistons when rotating in the housing, the significant advantage being achieved that the the outer contour guided treads in the 9 o'clock position and 3 o'clock in contrast to the well-known swing piston machine are relieved of pressure.
  • Another advantage of the combination of Inner and outer guidance is that in a rolling engagement each adjacent piston this essentially none Control function more, but that the rolling engagement only has the function of a seal. This opens up the possibility of the rolling engagement instead of in the form of a toothing to design in the form of a smooth rolling surface, or even to forego a rolling engagement, as in one preferred embodiment is provided.
  • the outer contour runs and the inner contour parallel to each other.
  • the inner contour and the outer contour curves that are essentially complementary to one another on. Each piston is therefore both centrifugal and centripetal as if guided on a rail.
  • the curve parallel to the outer contour Execution of the inner contour has the advantage that it is possible with simple means known from WO 98/13583 and proven swing piston machine according to the present Modify registration. For example, the Piston geometry and the geometry of the outer contour of the curve piece are taken over essentially unchanged, whereby then only on the curve piece an inner guide surface for the Piston must be provided.
  • the inner contour is trained continuously in the circumferential direction.
  • each piston has a full cycle centrifugal force side, i.e. is supported centrifugally so that centrifugal forces are absorbed in every rotary position and this reduces pressure loads in every rotational position.
  • the inner contour in the circumferential direction only over one or more peripheral sections extends.
  • the inner contour at least in the area of top dead center and the bottom dead center extends, for example from 10 a.m. to 2 a.m. And from 4 a.m. to 8 a.m.
  • the curve piece has the outer contour and the at least one inner contour in one-piece training.
  • the curve piece can be made in one piece are manufactured, whereby the manufacturing effort and reduced the number of parts entering the design can be.
  • the inner contour provided according to the invention be molded during the manufacture of the curve piece. Another advantage of a one-piece design of Outer contour and inner contour is that a fixed Orientation of the two during operation of the swing piston machine is guaranteed in the long run.
  • the curve piece is formed in several parts, at least a first Part of the control curve designed as an outer contour and at least a second part the at least one designed as an inner contour Control curve and the parts firmly together are connected.
  • the inner contour can be on one Ring flange be formed, which on the rest of the curve piece, that has the outer contour after inserting the pistons is flanged.
  • the inner contour is on the inside of pocket-like flanges of the curve piece educated.
  • the Flange or the flanges can be integral with the rest, the part of the curve piece having the outer contour be, or as separate ring flanges, which then with the rest Part of the curve piece, which has the outer contour, positively connected, for example mortised.
  • the pocket-like Flanges form an approximately inverted L-shaped Overlap of those treads that are used for guidance on the inner contour are provided.
  • the curve piece has axially in the area of both axial ends of the pistons limits the inner contour.
  • each piston is accordingly with its guided on both sides of the centrifugal force.
  • the axially central Area of each piston if this is provided, have the treads that radially on the outer contour supported inside.
  • each piston has at least two treads, of which at least one is guided on the inner contour, while the at least one more Tread is guided on the outer contour.
  • This configuration advantageously opens up the possibility of to realize the treads by rollers, whereby then the at least one roller guided along the inner contour roll freely on this and the at least one on the outer contour Unroll the guided roller on this as well can.
  • the treads are Surfaces of rollers rotatably attached to the pistons.
  • Rollers have the advantage that they are much smaller Friction along the inner contour or along the outer contour of the curve piece can be performed.
  • the requirements on the lubrication of the treads can differ to piston-resistant sliding shoes can be significantly reduced.
  • the pistons are each in pairs with each other.
  • the pistons are each in pairs over a toothless curved rolling surface with each other.
  • the forces in the area of Rolling engagement of adjacent pistons by the invention Guiding the pistons along the inner contour and even more the additional guidance of the pistons along the outer contour reduced, so that the rolling engagement is mainly still a sealing Function. Accordingly, the rolling engagement can also through a manufacturing technology easier than a toothing smooth rolling surface to be produced are shown.
  • the pistons are seen in the circumferential direction spaced in pairs by a separating element are, the separators together with the pistons circulate in the housing.
  • This configuration is particularly advantageous possible because the pivoting movement of the individual pistons both via the inner outer guide as well as on the outer inner guide of the curve section is completed.
  • the individual pistons are then complete due to the no longer existing rolling engagement independently of each other, with the advantage that on the system between piston and separating element in a structurally simple Ways conventional seals can be used.
  • each separating element has two Has sliding surfaces on which piston fist surfaces of the two respective corresponding to the respective separating element Slide the piston back and forth as it swivels.
  • the separating elements are therefore preferred in terms of Swiveling movement of the pistons stationary, and only run with it the piston in the housing in the circumferential direction.
  • the dividers can move with the pistons between two Annular bodies at the respective end of the swing piston machine be firmly clamped.
  • piston fist surfaces the piston and the sliding surfaces of the separating elements are complementary curved are trained to each other.
  • the piston fist surfaces of the pistons can be convex, for example and the sliding surfaces of the separating elements are concave, or the other way around.
  • Such a curved shape of the sliding Piston fist surfaces and sliding surfaces are optimal to the reciprocating pivoting movement of the individual pistons customized.
  • the complementary shape of the piston fist surfaces and the sliding surfaces continue to allow over the entire Swing stroke of the pistons for an optimal sealing of the working chambers against the oil space of the oscillating piston machine if the Separating elements in the axial direction over the length of the interior extend the housing of the oscillating piston machine.
  • each sliding surface Separating elements to arrange at least one seal.
  • Such seals can be provided in the form of sealing lips be located in the same place where the corresponding Sealing lips in the end ring surfaces of the piston cage the longitudinal center axis of the oscillating piston machine on next are arranged.
  • seals in the separators are however not mandatory, the seals can also be used instead of in the separators in the piston fist faces of the pistons his.
  • each sliding surface the separating elements a fire seal closer to the inner wall of the housing and an oil seal closer to the cam piece.
  • the fire seal seals the work chambers in which the combustion process takes place, gas-tight, while the central Oil chamber arranged in the oscillating piston machine via the oil seal is additionally sealed against the working chambers.
  • the oscillating piston machine has several chambers in the axial direction, whereby a set of pistons is arranged in each chamber, and the Sets of pistons offset from chamber to chamber in the direction of rotation are arranged to each other.
  • the smooth running of the oscillating piston machine can advantageously increases and the load on the curve piece caused by all chambers are made in one piece or in several parts can be reduced even further.
  • FIG. 1 to 3 is one with the general reference number 10 provided swing piston machine shown.
  • the swing piston machine 10 is used, for example, in a motor vehicle used as an internal combustion engine.
  • the oscillating piston machine 10 has a housing 12 around its circumference on, which seals the oscillating piston machine 10 to the outside.
  • the Housing 12 is substantially cylindrical, i.e. in cross section round, formed and extends over the axial length of the Swing piston machine 10.
  • a housing inner wall 14 is in cross section axially continuous round.
  • the housing 12 is also, as is apparent from Fig. 1, from individual Housing segments constructed, namely from cylindrical Housing segments 16 and 18 and housing front segments 20 and 22, each of which is suitably tightly connected to one another are mortised and / or screwed, for example. Due to the construction of the housing 12 in individual housing segments the assembly of the oscillating piston machine 10 is considerably simplified and enables one in the case of a multi-chamber system Modular construction.
  • the swing piston machine 10 In the axial direction, the swing piston machine 10 is in two Chambers 24 and 26 divided.
  • a set of pistons is arranged in each of the chambers 24 and 26, 2, which is a cross section through the chamber 24 which shows pistons 28a to 28d of chamber 24.
  • both chambers 24 and 26 are thus arranged in each case four pistons 28a to 28d.
  • the pistons are identical to those not shown Piston of the chamber 26 formed so that in the following only the chamber 24 with the pistons 28a to 28d arranged therein is described in more detail.
  • the pistons of the chamber 26 are identical to the pistons 28a to 28d of chamber 24, the pistons of chamber 26 are, however, about the pistons 28a to 28d of the chamber 24 ⁇ m about 45 °, seen in the circumferential direction, arranged offset.
  • the pistons 28a to 28d are each designed as two-armed levers, i.e. each of the pistons 28a to 28d has a first one Lever arm 30 and a second lever arm 32 with respect to one On pivot axis 34, which is exemplary for the piston 28a in Fig. 2 are designated. Each of the pistons 28a to 28d is thus assigned a pivot axis 34.
  • the pivot axes 34 lie on a circle and are equidistant from each other.
  • Each of the four pivot axes 34 extends in the axial direction parallel to a central housing axis 36.
  • the pistons 28a to 28d are in each case about their respective pivot axis 34 two end positions can be swung back and forth, whereby in the first End position of the respective lever arm 30 with its outside the housing inner wall 14 and in the second end position accordingly the respective lever arm 32 with its outside the housing inner wall 14 abuts.
  • each of the pistons 28a to 28d is one by one axially extending axle 38 is pivotally mounted itself is unmovable.
  • Each axle 38 forms the respective one Pivot axis 34 of the individual pistons 28a to 28d.
  • the pistons 28a to 28d are still in pairs with each other in rolling engagement.
  • the pistons 28a to 28d in each case in the circumferential direction on both ends of teeth 40 which comb each other.
  • the piston 28a stands, for example thus with both the piston 28b and the piston 28d in Rolling engagement.
  • the rolling engagement formed by the toothing 40 is tight, so that between the housing inner wall 14th and the outer sides opposite the housing inner wall 14 the pistons 28a to 28d formed by the working chambers 42 Rolling engagement are hermetically sealed.
  • the individual pistons 28a to 28d also have a convexly curved rolling surface 44 which is shown in Fig. 2 with broken lines, with each other are in rolling engagement, in which case adjacent ones of the rolling surfaces 44 sealing in each pivoting position of the pistons 28a to 28d lie against each other in order to achieve hermetic tightness to ensure the working chambers 42.
  • the pistons 28a to 28d also run together in the housing 12 in a circumferential direction 46 around the central housing axis 36 around.
  • the with rotating axis rods 38 are against the inner wall of the housing 14 sealed, using centrifugal seals 47, as described in detail in WO 98/13583, to which reference is made for a more detailed description.
  • the corresponding one Section of the housing inner wall as well as two neighboring ones Lever arms 32 and 30 ' accordingly become one of the working chambers 42 formed in the embodiment shown with four pistons 28a to 28d accordingly four working chambers 42 in the direction of rotation 46, which are sealed against one another.
  • the volume of the working chambers 42 changes as it rotates the piston 28a to 28d corresponding to the reciprocating Swiveling movements of the pistons 28a to 28d to the different Work cycles of suction, compression, ignition (Expanding) and ejecting.
  • a cam piece 48 is arranged in the center of the housing 12, which extends through chamber 24 and chamber 26.
  • the curve piece 48 is different from the pistons 28a to 28d trained fixed to the housing.
  • the curve piece 48 has at least one designed as a control curve Inner contour 50 on (see. Fig. 3).
  • the pistons 28a to 28d face the inner wall of the housing 14 facing away or facing the curve piece 48 Side treads 52 on when rotating the piston 28a to 28d in the housing 12 along the control cam Inner contour 50 are guided. This will make the pistons 28a to 28d along the curve piece 48 on the centrifugal force side supported supported.
  • the inner contour 50 is on the curve piece 48 in the area of a Axial end of the pistons 28a to 28d arranged.
  • a second with respect to the course of the curve with the inner contour 50 is identical and is designed as a control curve inner contour 52 on the curve piece 48 in the area of the opposite axial End of the pistons 28a to 28d arranged. Point at this end the pistons 28a to 28d each have a further running surface 54, that along the rotation of the respective piston 28a to 28d the inner contour 52 of the curve piece 48 is guided.
  • the curve piece 48 has the inner contours 50 and 52 corresponding, also designed as control curves Inner contours 56 and 58, which serve to corresponding, treads not shown in the arranged in the chamber 26 Guide the piston supported on the centrifugal side.
  • the curve piece 48 In the area between the inner contours 50 and 52 or between the inner contours 56 and 58, the curve piece 48 also has an outer contour designed as a control curve.
  • the outer contour 62 extends axially into the area of the inner contours 50, 54, 58, 60 or ends axially in the middle between the inner contours 50 and 54 or 58 and 60.
  • the pistons 28a to 28d each have at least one further one Running surface 64, which in the rotation of the pistons 28a to 28d in the housing 12 along the outer contour 62 of the curve piece 48 are guided, whereby the pistons 28a to 28d also radially are supported inwards towards the central housing axis 36.
  • each piston 28a to 28d has three Treads 64, which are axially spaced from each other, and which together along the outer contour 62 of the curve piece 48 are led.
  • the inner contours 50, 54, 58 and 60 of the curve piece 48 are each on the inside of a flange forming a pocket 66, 68, 70 and 72, respectively.
  • the ring flanges 74 and 76 are still on their respective axial outside form-fitting with the housing end segment 22 or the housing end segment 20 connected to the housing so that the ring flanges 74 and 76 with the rest of the body of the curve piece 48 form a housing-fixed arrangement.
  • the treads 64 which are guided along the outer contour 62 are, as well as the treads 52 and 56, which along the inner contours 50 and 54 are guided, are surfaces of rollers 78 rotatably mounted on the pistons 28a to 28d or 80.
  • the rollers 78, each piston 28a to 28d two has, lie exclusively on the inner contour 50 or 54, while the rollers 80, each of which pistons 28a to 28d has three, only on the outer contour 62 issue.
  • the running surfaces 64 stand when the pistons 28a to 28d rotate with constant contact with the outer contour 62.
  • the treads 52 and 56 are below when the pistons 28a to 28d rotate constant contact with the inner contour 50 or 54.
  • the rollers 78 and 80 are preferably on a common Bolt that passes axially through the rollers 78 and 80, stored.
  • the running surfaces 54 and 52 of the rollers 78 are in constant contact with the inner contour 50 during of the pistons 28a to 28d revolving along the inner contour 50 guided, while the treads 64 of the rollers 80 while rotating the piston 28a to 28d in constant contact with the Outer contour 62 of the curve piece 48 guided along the same are.
  • the inner contour 50 extends in Full circumferential direction on the curve piece 48.
  • the curve piece 48 formed in several parts, whereby the assembly of the Swing piston machine 10, more precisely the insertion of the Pistons 28a to 28d and assembling with the curve piece 48 is facilitated.
  • the swing piston machine 10 is in one Operating position shown, in which the piston 28a, more precisely said its lever arm leading in the direction of rotation 46 30 is located at top dead center (OT).
  • leading piston 28a acts in this position when rotating, especially at high speeds, a maximum centrifugal force. This maximum centrifugal force is however over the tread 52 and 56, respectively, on the inner contour 50 of the curve piece 48 are guided, taken up by the inner contour 50.
  • the curve piece 48 also has axially extending bores 82, 84 and 86 on that of the oil mist cooling or oil lubrication of the treads 50, 54 and 64 of the pistons 28a to 28d and the Lubricate the rollers 78, 80.
  • the Swing piston machine 10 in the axial direction as a multi-chamber system configured, more precisely in the embodiment shown said as a two-chamber system.
  • pistons arranged in the chamber 26, which in the drawing unspecified, indicate their leadership along the curve piece 48 the same design as pistons 28a to 28d of chamber 24.
  • the pistons of the chamber 26 can also be pivoted on axle rods stored, of which in Fig. 1 two axle rods 88 and 90 opposite Pistons can be seen.
  • the axle rods 88, 90 as well the other two, not visible in the drawing Axle bars are relative to the axle bars 38 on which the pistons 28a to 28d of the chamber 24 are pivoted about 45 ° staggered.
  • the axle rods 38 of the chamber 24 and the axle rods 88, 90 and the other two axis rods of the chamber 26 form together with three ring bodies 92, 94 and 96 a rigid cylindrical piston cage, which together with the pistons 28a to 28d of the chamber 24 and the piston of the chamber 26 revolves together.
  • the axle bars 38 of the chamber 24 are firmly connected to the ring bodies 92 and 94, while all axis rods 88, 90 of the chamber 26 with the Annular bodies 94 and 96 are firmly connected.
  • the first ring body 92 is rotatable and tight on the ring flange 74 of the curve piece 48 stored.
  • the third ring body is corresponding 96 rotatable and tight on the ring flange 76 of the curve piece 48 stored.
  • the middle ring body 94 is rotatable on the outer sides the flanges 68 and 70 of the curve piece 48 are mounted.
  • the third ring body 96 carries on its axially outer side a ring gear 98 which has an external toothing 100 which with a corresponding toothing of a change gear 102 meshes again with a corresponding toothing 104 of a ring gear 106 combs, the rotationally fixed with an output shaft 108 Swing piston machine 10 is connected.
  • the rotation of the third Ring body 96 around the central housing axis 36 thus causes Rotary motion of the output shaft 108, which then turns into a drive train of the motor vehicle in which the oscillating piston machine 10 is installed, transmitted via a clutch disc 110 can be.
  • the oscillating piston machine has for each chamber 24, 26 Spark plugs 112 and 114, as well as an inlet cross-section 116 and an outlet cross section for each chamber 24 and 26.
  • the four separating elements 140 to 146 extend according to FIG. 4 over the axial length of the chamber 24 ', and corresponding separating elements extend between the pistons in chamber 26 ' also over the axial length of this chamber 26 '.
  • the separating elements 140 to 146 are between the ring bodies 94 ' and 92 'or 96' and 94 'clamped and relative to them Ring bodies immobile.
  • pistons 28a 'to 28d' through the separating elements 140 to 146 are spaced apart, the pistons 28a ' to 28d 'kinematically independent of each other. It means that the reciprocating swiveling movements of the individual pistons 28a 'to 28d' solely by guiding the pistons 28a 'to 28d' are conveyed along the curve piece 48 '.
  • the separators 140 to 146 face the same as on the separator 140 is shown as an example, two sliding surfaces 148 and 150 on which piston fist faces 152 (pistons 28a ') and 154 (Piston 28b ') of the two corresponding ones on the separating element 140 adjacent pistons 28a 'and 28b' at their Slide the swivel motion back and forth.
  • the separating element 140 is enlarged in sections Scale shown.
  • seals are embedded in the separating element 140, specifically Fire seals 156 and 158, which are closer to the housing inner wall 14 ' are arranged horizontally, and two oil seals 160 and 162, which are arranged closer to the curve piece 48 '.
  • the fire seals 156 and 158 seal the working chambers 42 ' gas-tight to the longitudinal center axis of the oscillating piston machine 10 ' off while the oil seals 160 and 162 for sealing of the housing-centered oil chamber against the working chambers 42 '.
  • the seals 156 to 162 also extend over the full axial length of separators 140 to 146.
  • the sliding surfaces are 148 and 150 of the separating elements 140 to 146 are concavely curved formed, while the piston fist faces 152 and 154 of the Pistons 28a 'to 28d' complementarily curved and convex are. This causes the piston fist faces 152 and 154, respectively the piston 28a 'to 28d' in their reciprocating Swivel movement always at a minimum distance on the sliding surfaces 148 or 150 of the separating elements 140 to 146 passed.

Claims (18)

  1. Moteur à pistons oscillants, comportant un carter (12 ; 12') dans lequel plusieurs pistons (28a-28d ; 28a'-28d'), se présentant sous la forme de leviers à deux bras, sont logés de façon à osciller autour d'un axe d'oscillation (34) parallèle à un axe central de carter (36) et peuvent se déplacer ensemble dans un sens de rotation (46), ces pistons (28a-28d ; 28a'-28d') présentant, sur leur côté opposé à une paroi interne de carter (14 ; 14'), des surfaces de contact (52, 56, 64) qui sont guidées, lors de la rotation des pistons (28a-28d) dans le carter (12), le long d'au moins une piste de commande d'une came centrale (48 ; 48') solidaire du carter, pour commander les oscillations des pistons (28a-28d ; 28a'-28d') lors de leur rotation, la came (48 ; 48') présentant un contour externe (62) conformé en piste de commande, le long duquel les surfaces de contact (52, 56, 64) des pistons (28a-28d ; 28a' - 28d') sont guidées de manière à prendre appui, du côté de l'axe de carter (36), caractérisé en ce que la came (48 ; 48') présente une autre piste de commande, conformée en contour interne (50, 54), le long duquel les pistons (28a-28d ; 28a'-28d') sont guidés de manière à prendre appui, côté force centrifuge, par les surfaces de contact (52, 56, 64).
  2. Moteur à pistons oscillants selon la revendication 1, caractérisé en ce que le contour externe (62) et le contour interne (50, 54, 58, 60) sont orientés l'un vers l'autre, parallèlement à la came.
  3. Moteur à pistons oscillants selon la revendication 1 ou 2, caractérisé en ce que le contour interne (50, 54) est continu, dans le sens de rotation (46).
  4. Moteur à pistons oscillants selon l'une des revendications 1 à 3, caractérisé en ce que le contour interne (50, 54), dans le sens de rotation (46), ne s'étend que sur une ou plusieurs zones de la circonférence.
  5. Moteur à pistons oscillants selon l'une des revendications 1 à 4, caractérisé en ce que la came (48 ; 48'), le contour externe (62) et le contour interne (54), au nombre minimum d'un, ne forment qu'une seule pièce.
  6. Moteur à pistons oscillants selon l'une des revendications 1 à 4, caractérisé en ce que la came (48 ; 48') est constituée de plusieurs pièces, au moins une première pièce étant constituée par le contour externe (62) et au moins une deuxième pièce étant constituée par le contour interne (50), au nombre minimum d'un, et les pièces étant reliées fixement entre elles.
  7. Moteur à pistons oscillants selon l'une des revendications 1 à 6, caractérisé en ce que le contour intérieur (50, 54) est formé sur une face intérieure d'une bride (66, 68) de la came (48) qui forme une poche.
  8. Moteur à pistons oscillants selon l'une des revendications 1 à 7, caractérisé en ce que la came (48 ; 48'), dans la zone des deux extrémités axiales des pistons (28a-28d ; 28a'-28d'), présente le contour interne (50, 54) de façon axialement délimitée.
  9. Moteur à pistons oscillants selon l'une des revendications 1 à 8, caractérisé en ce que chaque piston (28a-28d ; 28a'-28d') présente au moins deux surfaces de contact (52, 56, 64), dont au moins une est guidée sur le contour interne (50, 54), tandis que l'autre surface de contact (64), au nombre minimum d'une, est guidée sur le contour externe.
  10. Moteur à pistons oscillants selon l'une des revendications 1 à 9, caractérisé en ce que les surfaces de contact (52, 56, 64) sont les surfaces de galets de roulement (78, 80) montés tournants sur les pistons (28a-28d ; 28a'-28d').
  11. Moteur à pistons oscillants selon l'une des revendications 1 à 10, caractérisé en ce que les pistons (28a-28d) engrènent deux par deux pour rouler ensemble.
  12. Moteur à pistons oscillants selon la revendication 11, caractérisé en ce que les pistons (28a-28d) engrènent deux par deux pour rouler ensemble, par l'intermédiaire d'une surface de roulement (44) courbe non dentée.
  13. Moteur à pistons oscillants selon l'une des revendications 1 à 10, caractérisé en ce que les pistons (28a'-28d'), vus dans le sens de rotation, sont séparés, deux par deux, par un élément séparateur (140-146), les éléments séparateurs (140-146) tournant dans le carter (12') en même temps que les pistons (28a'-28d').
  14. Moteur à pistons oscillants selon la revendication 13, caractérisé en ce que chaque élément séparateur (140-146) présente deux surfaces de glissement (148, 150), sur lesquelles des surfaces de tête (152, 154) des deux pistons (28a'-28d') correspondants qui reposent contre l'élément séparateur associé (140-146) glissent selon un mouvement de va et vient, lors de leur oscillation.
  15. Moteur à pistons oscillants selon la revendication 14, caractérisé en ce que les surfaces de tête (152, 154) des pistons (28a'-28d') et les surfaces de glissement (148, 150) des éléments séparateurs (140-146) présentent une forme courbe complémentaire.
  16. Moteur à pistons oscillants selon la revendication 14 ou 15, caractérisé en ce qu'au moins un joint d'étanchéité est disposé dans chaque surface de glissement (148, 150) des éléments séparateurs (140-146).
  17. Moteur à pistons oscillants selon la revendication 16, caractérisé en ce que, sur chaque surface de glissement (148, 150), est monté un joint résistant au feu (156, 158), du côté le plus proche de la paroi intérieure du carter (14') et un joint étanche à l'huile (160, 162), du côté le plus proche de la came (48').
  18. Moteur à pistons oscillants selon l'une des revendications 1 à 17, caractérisé en ce qu'il présente, dans la direction axiale, plusieurs chambres (24, 26 ; 24', 26'), un jeu de pistons (28a-28d ; 28a'-28d') étant disposé dans chaque chambre (24, 26 ; 24', 26'), les jeux de pistons (28a-28d ; 28'-28d') étant montés en étant décalés les uns par rapport aux autres, d'une chambre (24 ; 24') à l'autre (26 ; 26'), dans le sens de rotation (46).
EP00901093A 1999-01-14 2000-01-12 Moteur a pistons oscillants Expired - Lifetime EP1144806B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19901110A DE19901110C2 (de) 1999-01-14 1999-01-14 Schwenkkolbenmaschine
DE19901110 1999-01-14
PCT/EP2000/000170 WO2000042290A1 (fr) 1999-01-14 2000-01-12 Moteur a pistons oscillants

Publications (2)

Publication Number Publication Date
EP1144806A1 EP1144806A1 (fr) 2001-10-17
EP1144806B1 true EP1144806B1 (fr) 2002-10-16

Family

ID=7894192

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00901093A Expired - Lifetime EP1144806B1 (fr) 1999-01-14 2000-01-12 Moteur a pistons oscillants

Country Status (7)

Country Link
US (1) US6431139B1 (fr)
EP (1) EP1144806B1 (fr)
JP (1) JP2002535529A (fr)
AT (1) ATE226275T1 (fr)
AU (1) AU2108000A (fr)
DE (2) DE19901110C2 (fr)
WO (1) WO2000042290A1 (fr)

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* Cited by examiner, † Cited by third party
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DE19901110C2 (de) 1999-01-14 2002-06-06 Herbert Huettlin Schwenkkolbenmaschine
US7178502B2 (en) * 2001-06-05 2007-02-20 Paul D. Okulov Balanced rotary internal combustion engine or cycling volume machine
US20030062020A1 (en) * 2001-06-05 2003-04-03 Okulov Paul D. Balanced rotary internal combustion engine or cycling volume machine
US6729296B2 (en) * 2002-02-22 2004-05-04 Matthew Brandon King Variable vane rotary engine
WO2004070169A1 (fr) * 2003-02-10 2004-08-19 Gilles Saint-Hilaire Moteur rotatif
DE10345342A1 (de) * 2003-09-19 2005-04-28 Engelhard Arzneimittel Gmbh Verfahren zur Herstellung eines lagerstabilen Extraktes aus Efeublättern, sowie ein nach diesem Verfahren hergestellter Extrakt
US20100143174A1 (en) 2004-03-09 2010-06-10 Maciej Radziwill Rotary Working Machine Provided with an Assembly of Working Chambers and Periodically Variable Volume, In Particular a Compressor
PL1574664T3 (pl) 2004-03-09 2009-09-30 Radziwill Compressors Sp Z O O Wirnikowa i oscylacyjna maszyna z wahliwymi tłokami
DE102007009707A1 (de) 2007-02-28 2008-12-11 Jung, Brigitte Schwingkolbenverbrennunsmotor
US8177536B2 (en) 2007-09-26 2012-05-15 Kemp Gregory T Rotary compressor having gate axially movable with respect to rotor
FR2925571A1 (fr) * 2007-12-19 2009-06-26 Sycomoreen Sarl Machine a pistons rotatifs a battement controle
CN101555827B (zh) * 2008-11-21 2012-02-01 靳北彪 弧形缸负荷响应发动机
FR2950926B1 (fr) * 2009-10-05 2011-12-02 Pk Enr Moteur a pistons rotatifs
DE102018123409A1 (de) 2018-09-24 2020-03-26 Manfred Max Rapp Kolbenmaschine, modulares Baukastenystem für eine Kolbenmaschine sowie Verfahren zur Herstellung einer Kolbenmaschine

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US3438358A (en) * 1967-08-25 1969-04-15 Fred W Porsch Rotary internal combustion engine
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US3614277A (en) * 1969-05-14 1971-10-19 Toyoda Chuo Kenkyusho Kk Vane-type rotary engine
DE1936273A1 (de) * 1969-07-17 1971-01-28 Fritz Ilg Drehkolbenvorrichtung,geeignet zur Herstellung von Verbrennungskraftmaschinen,Pumpen fuer Fluessigkeiten und Gase sowie Apparaten fuer Messungen von Durchflussmengen von fluessigen oder gasfoermigen Stoffen
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DE19639503C1 (de) 1996-09-26 1998-01-15 Herbert Huettlin Schwenkkolbenmaschine
DE19901110C2 (de) 1999-01-14 2002-06-06 Herbert Huettlin Schwenkkolbenmaschine

Also Published As

Publication number Publication date
DE50000646D1 (de) 2002-11-21
WO2000042290A1 (fr) 2000-07-20
AU2108000A (en) 2000-08-01
ATE226275T1 (de) 2002-11-15
DE19901110C2 (de) 2002-06-06
EP1144806A1 (fr) 2001-10-17
US20020029756A1 (en) 2002-03-14
DE19901110A1 (de) 2000-07-27
US6431139B1 (en) 2002-08-13
JP2002535529A (ja) 2002-10-22

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