EP2841695B1 - Machine à piston rotatif qui fonctionne comme pompe, compresseur ou moteur pour un fluide - Google Patents

Machine à piston rotatif qui fonctionne comme pompe, compresseur ou moteur pour un fluide Download PDF

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Publication number
EP2841695B1
EP2841695B1 EP13709334.0A EP13709334A EP2841695B1 EP 2841695 B1 EP2841695 B1 EP 2841695B1 EP 13709334 A EP13709334 A EP 13709334A EP 2841695 B1 EP2841695 B1 EP 2841695B1
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EP
European Patent Office
Prior art keywords
centre axis
gearwheel
gear
rotary piston
angle
Prior art date
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Active
Application number
EP13709334.0A
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German (de)
English (en)
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EP2841695A1 (fr
Inventor
Dieter Amesoeder
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F01C3/00—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
    • F01C3/06—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
    • F01C3/08—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/084—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/088—Elements in the toothed wheels or the carter for relieving the pressure of fluid imprisoned in the zones of engagement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
    • F04C3/06—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees
    • F04C3/08—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing

Definitions

  • the DE 42 41 320 A1 to arrange between the driven part and the drive part, a control part such that between the control part and the drive part first working spaces and between the driven part and the control part second working spaces are formed, which are opposite to each other.
  • the DE 10 2008 013991 A1 that also under WO 2008/110155 A1 is published, proposes to provide a rotor and a stator in a housing, wherein between a drive shaft and the rotor an inclined sliding plane is arranged.
  • This inclined sliding plane leads to a rotation of the shaft to a tumbling of the rotor or a tumbling of the rotor to a rotation of the shaft.
  • the rotor opposite the stator is not co-rotating and thus stationary in a housing receiving the rotor and the stator.
  • a rotary piston machine which operates as a pump, compressor or motor for liquid or gaseous medium.
  • the rotary piston machine has a first gear with a first center axis, a second gear arranged opposite the first gear with a second center axis and a drive shaft with a third center axis and a fixedly connected to the drive shaft slip plane.
  • the first center axis and the second center axis enclose an angle that is not equal to 180 °.
  • the third central axis and at least one central axis of the first central axis and the second central axis enclose an angle which is not equal to 0 ° or 90 °.
  • the first sliding plane and the central axis are perpendicular to each other.
  • the first gear has a first end face with a first toothing with at least one first tooth and the second toothed wheel has a second end face with a second toothing with at least one second tooth, wherein a first number of first teeth and a second number of second teeth differ from one another are.
  • the first tooth and the second tooth engage with each other in such a way that at least one working space is formed by combing the teeth.
  • a volume formed by the at least one working space is changed by the meshing of the teeth.
  • the at least one working space is formed by a spherical inner wall of a Limited housing. The at least one working space is connectable to an inflow and an outflow for the medium.
  • a component of the group of first gear and second gear is coupled to the housing such that the component wobbles exclusively by a rotation of the drive shaft.
  • the respective other component from the group of first gear and second gear is coupled to the first sliding plane such that rotates by a rotation of the drive shaft, the respective other component and staggers.
  • the area to which the inflows and outflows can be arranged increases.
  • the tumbling motion makes it possible to arrange more than one inflow and one outflow for the medium.
  • the first number may comprise only a first tooth and the second number two or more second teeth, and vice versa.
  • the number of inflows can be equal to the number of outflows.
  • the inflows and outflows can here be circumferentially distributed uniformly distributed.
  • the second gear can be encompassed by the spherical, in particular hemispherical, inner wall of the housing and thereby supported on the inner wall of the housing.
  • the first gear for rotating and / or tumbling can be excited. Due to the wobbling motion of the first gear, the second gear is excited to a tumbling motion.
  • the second gear may be connected to the housing or the inner wall such that a relative rotation of the second gear relative to the housing, or the first gear, is prevented.
  • the first gear and the second gear each have a number of teeth which differ from one another by at least one tooth.
  • a radial delimitation of the work spaces inwardly can be done by spherical parts, which are arranged on the gears.
  • the inner wall of the housing will be hemispherical in shape. This allows easy mounting of the first gear, the second gear and the drive shaft.
  • the slip plane may also support the first gear so that when the volume of the at least one working space is reduced and thus the first and second gears are axially loaded in the opposite direction, the first gear is held in position.
  • the second gear is supported by the housing.
  • the at least one working space is bounded radially inwardly by a common contact surface which is of spherical design in the first gearwheel and in the second gearwheel.
  • the first center axis and the third center axis include a first angle.
  • the second center axis and the third center axis include a second angle.
  • the first angle and the second angle are not equal to 0 ° or 90 °.
  • the first angle may be 5 degrees and the second angle may be 20 degrees.
  • the first angle and the second angle can be equal.
  • the first center axis and the second center axis may be skewed to each other.
  • the first central axis and the third central axis span a first plane.
  • the first center axis and the second center axis may span a second level.
  • the first level and the second level may include an angle that is not 0 ° and not equal to 180 °.
  • the first level and the second level can also be congruent.
  • the first center axis and the third center axis span a first plane and the second center axis and the third center axis span a second plane.
  • the first level and the second level are perpendicular to each other.
  • first level and the second level can take any angle to each other.
  • the first center axis and the second center axis lie in a common plane.
  • a second sliding plane is fixedly connected to the drive shaft.
  • the second sliding plane and the second center axis are perpendicular to each other.
  • the first sliding plane and the first gear are rotatable relative to each other and connected to each other.
  • the second sliding plane and the second gear are rotatable relative to each other and connected to each other.
  • the reliability of the rotary piston machine can be increased, as a result, the second gear through the second sliding plane forcibly put into a tumbling motion.
  • the first gear and the second gear can be constrained in conjunction with the spherical inner wall of the housing.
  • binding when combing the gears can be avoided, which can possibly be attributed to manufacturing tolerances of the gears.
  • the first center axis, the second center axis and the third center axis intersect at a common point, the common point being the center of a diameter of the inner wall.
  • a diameter of the spherical bearing surface also cuts the third central axis in the common point. In this way it can be ensured that no translational movements take place between the individual parts, which can lead to higher wear.
  • first sliding plane and the second sliding plane intersect the common point.
  • the first sliding plane and / or the second sliding plane do not intersect the common point.
  • the second gear is non-rotatably coupled to the housing.
  • a pin is firmly connected on an outer wall of the second gear.
  • the pin is guided in a groove-shaped recess in the inner wall, wherein the recess is circular.
  • the recess may also be formed as a circular groove, so that this groove can serve as a backdrop for the pin.
  • the pin in conjunction with the circular recess can be formed as a fixation of the second gear to the housing, so that in this way a rotational movement of the second gear is prevented.
  • the circular recess in conjunction with the pin can thus ensure only the wobbling movement of the second gear.
  • the first gear is rotatably coupled to the housing.
  • a fixation of the first gear on the housing for example, by means of a protruding on the first gear in the radial direction pin in conjunction with a formed on the inner wall, respectively the housing groove formed. Although this may wobble the first gear, but not turn. In such a configuration, the second gear will usually also tumble and usually turn as well.
  • the pin extends along a fourth central axis.
  • both the pin and the inner wall of the housing can be produced inexpensively as a plastic injection molded part.
  • At least one component from the group of at least one first tooth and at least one second tooth of the rotary piston machine has a recess, so that in a predetermined rotation angle range of the at least one component, an overlap with the inflow and / or outflow takes place ,
  • the time period in which the medium is supplied to the working space or the medium is removed from the working space can be increased.
  • the recess may be formed on a tooth flank or on both tooth flanks of a tooth.
  • the recesses may be different from each other at the two tooth flanks.
  • the individual tributaries and / or outflows can be interconnected.
  • inflows may be associated with drains to increase, for example, by such a rotary engine, the pressures to be achieved.
  • the inflows and outflows can be controlled by means of valves, in particular solenoid valves.
  • At least one component from the group of first tooth, second tooth, first sliding plane, second sliding plane, inner wall and outer wall has a recess for receiving lubricant.
  • the first toothing and the second toothing are selected from the group of helical toothing, involute toothing, cycloidal toothing and helical toothing.
  • a bearing element between the sliding plane and the associated gear as lubricated, hydraulically or pneumatically supported slide bearing be configured.
  • the bearing element can be designed as a roller bearing, for example as a roller bearing or other bearing according to the prior art.
  • the rotary piston machine described above can be used as a transmission.
  • FIG. 1 shows a rotary piston machine 2, which operates as a pump, compressor or motor for liquid or gaseous medium.
  • the rotary piston machine 2 has a first gear 4 with a first center axis I, a second gear 6 arranged opposite the first gear 4 with a second center axis II and a drive shaft 8 with a third center axis III.
  • the drive shaft 8 has a disk element 11 which has a first sliding plane 10 on the side facing the first gear 4. Concentric with the third center axis III, the drive shaft 8 has an axle section 13 on the disk element 11. At the axle section 13, a second slip plane 12 is formed on the side facing the second gear 6.
  • the disc member 11 may be formed such that the axle portion 13 can be dispensed with.
  • the first gear 4 has a first sliding surface 15, which is in communication with the first sliding plane 10 of the drive shaft 8. Opposite the first sliding surface 15, the first gearwheel 4 has a first end face 14, on which a first toothing 16 with at least one first tooth 18 is formed. Furthermore, the first gear 4 along the first central axis I has an opening 19 into which the axle section 13 protrudes.
  • the second sliding surface 21 is opposite to the second gear 6, a second end face 20 is formed on which a second toothing 22 with at least one tooth 24 is formed is. From the second toothing 22, a stub axle 25 extends along the second central axis II towards the axle section 13 and is bounded by the second sliding surface 21.
  • the axle portion 13 may be formed such that it is also possible to dispense with the axle stub 25.
  • a working space 26 is formed, wherein the combing of the teeth 18, 24, a volume formed by the working space 26 is changed.
  • the first gear 4 and the second gear 6 are enclosed by a housing 28 with a spherical, here hemispherical-shaped, inner wall 30. This spherical inner wall 30 seals the working space 26 to the outside.
  • the first gear 4 has a spherical first outer wall 36, which corresponds to the spherical inner wall 30 and sealingly abuts against this inner wall 30.
  • the second gear 6 has a spherical second outer wall 38, wherein the second outer wall 38 also corresponds to the spherical inner wall 30. Furthermore, in the first gear 4, a spherical first bearing surface 32 is formed, which bears sealingly against a corresponding formed on the second gear 6 hollow spherical second bearing surface 34. Thus, the working space 26 is limited by the two teeth 16, 22, by the spherical inner wall 30, and the spherical first bearing surface 32 in conjunction with the hollow spherical second bearing surface 34. Furthermore, a pin 48 is formed on the second outer wall 38, which engages in a formed on the spherical inner wall 30 of the housing 28 circular recess 50.
  • the circular recess 50 may also be formed as a circular ring.
  • the second center axis II of the second gear 6 intersects the third center axis
  • the spherical inner wall 30 extends along a diameter D, which also intersects the third center axis III in the common point S.
  • the first center axis I and the third center axis III include a first angle ⁇ 1 which extends counterclockwise starting from the third center axis III. In the present exemplary embodiment, the first angle ⁇ 1 is 5 °.
  • the third center axis III and the second center axis II include a second angle ⁇ 2.
  • the angle extends from the third central axis III clockwise and is in the present embodiment 10 °.
  • the two angles ⁇ 1 and ⁇ 2 may also have other values, in particular taking values which are between 5 ° and about 25 °.
  • the first center axis I and the second center axis II include a third angle ⁇ 3, which is not equal to 180 °.
  • the first I, the second II and the third III center axis span a common plane E.
  • the torques generated by the first gear 4 during operation of the rotary piston machine 2 are by the second gear 6 reduces moments generated.
  • the materials of the first gear 4 and the second gear 6 and by a corresponding selection of the two angles ⁇ 1, ⁇ 2 that cancel each other and thus the housing 28 is free of torque.
  • the third center axis III and the first center axis I could span a first plane and the third center axis III and the second center axis II a second plane, the two planes can be at an arbitrary angle to each other.
  • the second toothing 22 of the second toothed wheel 6 is designed such that the second end face 20 and the spherical second outer wall 38 of the second toothed wheel 6 coincide.
  • the first sliding plane 10 does not intersect the third center axis III in the common point S.
  • a translatory movement upon rotation of the drive shaft 8 between the first sliding plane 10 of the drive shaft 8 and the first sliding surface 15 of the first gear 4 in addition to the rotational relative movement a translatory movement. Especially the translational movement can cause a groove or scoring of the first sliding plane 10 and / or the first sliding surface 15 is avoided.
  • the second slip plane 12 intersects the third center axis III at the point S. Accordingly, between the second slip plane 12 of the drive shaft 8 and the second sliding surface 21 of the second gear 6 only a rotational relative movement takes place to each other.
  • FIG. 2 shows the from the FIG. 1 known rotary engine 2 in a plan view in X-ray view.
  • the second gear 6 has five second teeth 24 and the first gear 4 has six first teeth 18.
  • the housing 28 has evenly distributed over the circumference five inflows 40 and five outlets 42.
  • the number of inflows 40, respectively the outflows 42 this corresponds to the number of second teeth 24 of the second gear 6.
  • At the spherical inner wall 36 is to each Inflow 40 an inflow control channel 41 and to each outflow 42 an outflow control channel 43rd educated.
  • the spherical recess 50 is formed eccentrically to the third central axis III.
  • the drive shaft 8 rotates clockwise in the direction of arrow 52.
  • the first gear 4 is excited by the first sliding plane 10, which is perpendicular to the first central axis I of the first gear 4, to a rotational and tumbling motion relative to the second gear 6.
  • the second gear 6 is excited to an exclusive tumbling motion about the second center axis II. Due to the forces acting through the compression of the medium in the working spaces forces and the combing of the teeth 18, 24 can be dispensed with the second sliding surface 21 in connection with the second sliding plane 12. It should be noted that the rotational speed of the first gear 4 and the rotational speed of the drive shaft 8 are different from each other.
  • the exclusive tumbling motion, that is, without additional rotational movement, of the second gear 6 is effected by the positive guidance of the pin 48 in the circular recess 50.
  • a tooth head 54 of the first tooth 18 and a tooth head 56 of the second tooth 24 face each other here in the twelve o'clock position, wherein the tooth head 54 of the first tooth 18 and the tooth head 56 of the second tooth 24 touch and In this case, adjacent work spaces 26 are sealed from each other.
  • the tooth head 54 of the first tooth 18 engages a tooth root 58 of the second tooth 24.
  • the toothing is a trochoid toothing in the adjacent working spaces 26 during a relative movement of the first toothed wheel 4 are sealed to each other to the second gear 6.
  • the teeth 18, 24 and the combing by changing volumes of the working spaces 26 medium is sucked through the inlet 40 into the working space 26, compressed and then pushed out by the inflow 40 in the direction of rotation 52 of the drive shaft 8 adjacent drain 42.
  • the work spaces 26 extending between the twelve o'clock position and the six o'clock position are connected to the inflows 40, whereas those between the six o'clock position and twelve o'clock position. Position working spaces 26 have no connection to an inlet 40.
  • FIG. 3 shows the off FIG. 1 known rotary engine 2 in a 3D view in the X-ray view.
  • the formation of the inflow control channels 41 and the outflow control channels 43 are clearly visible.
  • the inflow control channels 41 and the outflow control channels 43 are designed in such a way that the medium to be supplied fills the working space 26 as 100% as possible and through the outflow 42 the compressed medium is ejected as 100% as possible.
  • the degree of filling of the working spaces 26 influences decisively both a volume flow of the medium to be transported and a pressure to be achieved.
  • the opening 19 of the first gear 4 is in this case designed such that during the tumbling movements of the first gear 4 and the second gear 6 of the axle portion 13 of the drive shaft 8 and the stub axle 25 of the second gear 6 does not collide with the first gear 4.
  • FIG. 4 shows the drive shaft 8 of the FIG. 1 known rotary engine 2.
  • FIG. 5 shows the housing 28 of the FIG. 1 known rotary piston engine 2 with a view of the spherical inner wall 30.
  • the inflows 40 and the outflows 42 can be seen as openings through the housing 28.
  • the circular eccentrically arranged recess 50 can be seen.
  • FIG. 6 shows the first gear 4 from the of the FIG. 1 Well visible here is the shape of the first gear 16 and the spherical first bearing surface 32 with the opening 19th
  • FIG. 7 shows the second gear 6 of the FIG. 1 known rotary engine 2 in a 3D view. It can be clearly seen that the toothing 22 extends up to the spherical second outer wall 38 and thus the second end face 20 is formed by this second outer wall 38. Furthermore, the hollow spherical second bearing surface 34, which is corresponding to the spherical first bearing surface 32 of the first gear 4, clearly visible.
  • the first gear 4, the second gear 6, the drive shaft 8 and the housing 28 are each integrally formed as a plastic injection molded part.
  • the individual parts can be manufactured inexpensively in large quantities.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Rotary Pumps (AREA)

Claims (10)

  1. Machine à piston rotatif fonctionnant en tant que pompe, compresseur ou moteur pour milieux liquides ou gazeux,
    comprenant une première roue dentée (4) avec un premier axe médian (I), une deuxième roue dentée (6) disposée à l'opposé de la première roue dentée (4) avec un deuxième axe médian (II) et un arbre d'entraînement (8) avec un troisième axe médian (III), et un plan de glissement (10, 12) connecté fixement à l'arbre d'entraînement (8),
    le premier axe médian (I) et le deuxième axe médian (II) formant un angle (α3) différent de 180°,
    le troisième axe médian (III) et au moins un axe médian (I, II) du groupe du premier axe médian (I) et du deuxième axe médian (II) formant un angle (α1, α2) différent de 0° ou 90°,
    le plan de glissement (10, 12) et l'axe médian (I, II) étant perpendiculaires l'un à l'autre,
    la première roue dentée (4) présentant une première surface frontale (14) avec une première denture (16) avec au moins une première dent (18) et la deuxième roue dentée (6) présentant une deuxième surface frontale (20) avec une deuxième denture (22) avec au moins une deuxième dent (24), un premier nombre de premières dents (18) et un deuxième nombre de deuxièmes dents (24) étant différents l'un de l'autre,
    la première dent (18) et la deuxième dent (24) étant en prise l'une avec l'autre de telle sorte qu'au moins un espace de travail (26) soit réalisé par un engrènement des dents (18, 24),
    un volume formé par l'au moins un espace de travail (26) étant modifié par l'engrènement des dents (18, 24),
    l'au moins un espace de travail (26) étant limité par une paroi interne (30) d'un boîtier (28) réalisée sous forme sphérique,
    l'au moins un espace de travail (26) pouvant être connecté à une alimentation (40) et une sortie (42) pour le fluide,
    caractérisée en ce
    qu'un composant (4, 6) du groupe de la première roue dentée (4) et de la deuxième roue dentée (6) est accouplé au boîtier (28) de telle sorte que le composant (4, 6) oscille exclusivement par une rotation de l'arbre d'entraînement (8),
    l'autre composant respectif (4, 6) du groupe de la première roue dentée (4) et de la deuxième roue dentée (6) est accouplé au plan de glissement (10, 12) de telle sorte que l'autre composant respectif (4, 6) tourne et oscille sous l'effet d'une rotation de l'arbre d'entraînement (8).
  2. Machine à piston rotatif selon la revendication 1,
    caractérisée en ce que
    le premier axe médian (I) et le troisième axe médian (III) forment un premier angle (α1),
    le deuxième axe médian (II) et le troisième axe médian (III) forment un deuxième angle (α2), le premier angle (α1) et le deuxième angle (α2) étant différents de 0° ou de 90°.
  3. Machine à piston rotatif selon la revendication 2,
    caractérisée en ce que
    le premier axe médian (I) et le deuxième axe médian (II) sont situés dans un plan commun (E).
  4. Machine à piston rotatif selon la revendication 2 ou 3,
    caractérisée en ce
    qu'en commençant à partir du troisième axe médian (III), le premier angle (α1) tourne dans le sens inverse des aiguilles d'une montre et le deuxième angle (α2) tourne dans le sens des aiguilles d'une montre.
  5. Machine à piston rotatif selon l'une quelconque des revendications précédentes,
    caractérisée en ce
    qu'un deuxième plan de glissement (12) est connecté fixement à l'arbre d'entraînement (8), le deuxième plan de glissement (12) et le deuxième axe médian (II) étant perpendiculaires l'un à l'autre,
    le premier plan de glissement (10) et la première roue dentée (4) étant connectés l'un à l'autre et de manière à pouvoir tourner l'un par rapport à l'autre,
    le deuxième plan de glissement (12) et la deuxième roue dentée (6) étant connectés l'un à l'autre et de manière à pouvoir tourner l'un par rapport à l'autre.
  6. Machine à piston rotatif selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    le premier axe médian (I), le deuxième axe médian (II) et le troisième axe médian (III) se coupent en un point commun (S), le point commun (S) étant le centre d'un diamètre (D) de la paroi interne (30).
  7. Machine à piston rotatif selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    le premier plan de glissement (10) et le deuxième plan de glissement (12) passent par le point commun (S).
  8. Machine à piston rotatif selon l'une quelconque des revendications 1 à 6,
    caractérisée en ce que
    le premier plan de glissement (10) et/ou le deuxième plan de glissement (12) ne passent pas dans le point commun (S).
  9. Machine à piston rotatif selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    la deuxième roue dentée (6) est accouplée de manière solidaire en rotation au boîtier (28), un tourillon (48) étant connecté fixement à une paroi externe (38) de la deuxième roue dentée (6), le tourillon (48) étant guidé dans un renfoncement (50) dans la paroi interne (30), le renfoncement (50) étant réalisé sous forme circulaire.
  10. Machine à piston rotatif selon l'une quelconque des revendications précédentes,
    caractérisée en ce
    qu'au moins un composant (4, 6) parmi le groupe d'au moins une première dent (4) et d'au moins une deuxième dent (6) présente un évidement de telle sorte qu'une intersection avec l'alimentation (40) et/ou la sortie (42) se produise dans une région d'angle de rotation prédéterminée de l'au moins un composant (4, 6).
EP13709334.0A 2012-04-25 2013-02-20 Machine à piston rotatif qui fonctionne comme pompe, compresseur ou moteur pour un fluide Active EP2841695B1 (fr)

Applications Claiming Priority (2)

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DE102012206797A DE102012206797A1 (de) 2012-04-25 2012-04-25 Drehkolbenmaschine, die als Pumpe, Verdichter oder Motor für ein Fluid wirkt
PCT/EP2013/053327 WO2013159946A1 (fr) 2012-04-25 2013-02-20 Machine à piston rotatif qui fonctionne comme pompe, compresseur ou moteur pour un fluide

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EP2841695A1 EP2841695A1 (fr) 2015-03-04
EP2841695B1 true EP2841695B1 (fr) 2016-10-26

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US (1) US9670778B2 (fr)
EP (1) EP2841695B1 (fr)
CN (1) CN104246130B (fr)
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WO (1) WO2013159946A1 (fr)

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WO2015139554A1 (fr) * 2014-03-18 2015-09-24 西安正安环境技术有限公司 Mécanisme anti-blocage de rotor de compresseur sphérique, mécanisme de puissance anti-blocage de compresseur sphérique, et compresseur sphérique
CN106703982A (zh) * 2015-08-10 2017-05-24 马宏丹 球形转子发动机
CN108425703B (zh) * 2018-03-12 2023-09-26 陈武 流体齿轮式汽能机

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US3236186A (en) * 1963-04-29 1966-02-22 Wildhaber Ernest Positive-displacement unit
US3895610A (en) * 1974-05-17 1975-07-22 Robert H Wahl Rotary Nutating engine
DE9218694U1 (de) 1991-12-09 1995-03-30 Arnold, Felix, 69239 Neckarsteinach Drehkolbenmaschine
SI2137378T1 (en) 2007-03-13 2018-02-28 Robert Bosch Gmbh Pump or engine
DE102008023475A1 (de) * 2008-05-14 2009-11-19 Robert Bosch Gmbh Hydromaschine
JP5576191B2 (ja) 2010-06-18 2014-08-20 トヨタ自動車株式会社 車両用内接歯車型オイルポンプ
DE102010063542A1 (de) * 2010-10-08 2012-04-12 Robert Bosch Gmbh Strömungsgetriebe

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DE102012206797A1 (de) 2013-10-31
US20150086407A1 (en) 2015-03-26
CN104246130A (zh) 2014-12-24
CN104246130B (zh) 2017-08-25
US9670778B2 (en) 2017-06-06
EP2841695A1 (fr) 2015-03-04
WO2013159946A1 (fr) 2013-10-31

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