EP2655801B1 - Machine à piston rotatif remplissant la fonction d'une pompe, d'un compresseur ou d'un moteur - Google Patents

Machine à piston rotatif remplissant la fonction d'une pompe, d'un compresseur ou d'un moteur Download PDF

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Publication number
EP2655801B1
EP2655801B1 EP11768006.6A EP11768006A EP2655801B1 EP 2655801 B1 EP2655801 B1 EP 2655801B1 EP 11768006 A EP11768006 A EP 11768006A EP 2655801 B1 EP2655801 B1 EP 2655801B1
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EP
European Patent Office
Prior art keywords
rotor
counter
wall
control opening
housing
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.)
Active
Application number
EP11768006.6A
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German (de)
English (en)
Other versions
EP2655801A2 (fr
Inventor
Sando Kunath
Oliver Laforsch
Dieter Amesoeder
Marian Kacmar
Evgenij Skrynski
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP2655801A2 publication Critical patent/EP2655801A2/fr
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Publication of EP2655801B1 publication Critical patent/EP2655801B1/fr
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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
    • F01C1/086—Carter
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to a rotary piston machine which works as a pump, compressor or motor, with a rotor and a counter rotor.
  • a rotary piston machine that works as a pump, compressor or motor.
  • combs of teeth of a rotating drive part to delimit working spaces run on a cycloid surface of a likewise toothed output part and in the process drive this output part.
  • the working spaces mentioned are formed between the teeth of the drive part and the driven part and are enlarged or reduced for their work during the rotation of the parts in order to generate the conveying effect on a gaseous or liquid medium.
  • Such drive and output parts run in a common housing, the interior of which is spherical.
  • the housing is divided in such a way that the parting plane contains the center point of the spherical interior, so that a first housing part with a hemispherical interior with a first center and a second housing part with a hemispherical interior and a second center result.
  • special attention must be paid to the design of the separating surfaces of the two housing parts in such a way that, in the assembled state, the first and second center points of the spherical interior spaces of the housing parts coincide. Since the two center points coincide by chance for manufacturing reasons, the gap resulting between the drive part or output part and the housing is adapted to the manufacturing technology and correspondingly generously dimensioned.
  • a rotary piston machine that works as a pump, compressor or motor has a rotor and a counter-rotor, the counter-rotor being arranged opposite the rotor.
  • the rotor has a first end face with a first toothing and the counter rotor has a second end face with a second toothing, the first and the second toothing each being formed from at least one tooth and one tooth gap.
  • the toothings are in engagement with one another in such a way that by meshing the teeth of the first toothing and the teeth of the second toothing, working spaces are formed, with volumes formed by the working spaces being changed by the meshing of the teeth.
  • the rotor has a first axis of rotation and the counter rotor has a second axis of rotation.
  • the first axis of rotation and the second axis of rotation enclose an angle that is not equal to 0 degrees.
  • the rotor has a first spherical inner wall and the counter rotor has a first spherical outer contour which is complementary to the first spherical inner wall of the rotor.
  • the counter-rotor has a second spherical-ring-shaped inner wall and the rotor has a second spherical-ring-shaped outer contour which is designed to be complementary to the second spherical-ring-shaped inner wall of the counter-rotor.
  • the gap now resulting between the spherical ring-shaped inner wall and the spherical ring-shaped outer contour can be made as small as possible. This largely eliminates gap losses. Due to the high-precision manufacture of the rotors, an adjustment process by means of grinding in or adjustment with respect to the rotor and counter-rotor can therefore be dispensed with. Since the first spherical inner wall now rotates and does not stand still, as is the case with the housing inner wall of the stationary housing, a gaseous or liquid medium to be compressed is exposed to less wall friction than on this housing inner wall.
  • the laminar flow that forms on this inner wall is subjected to less dynamics. This can lead to a distance between the first spherical inner wall of the rotor and an interface that separates the laminar flow from a turbulent flow being greater than in the case of a housing inner wall from a stationary housing.
  • the gap size being the shortest distance between the outer wall of the counter-rotor and the inner wall of the rotor or the shortest distance between the outer wall of the known rotor-counter-rotor arrangement and the inner wall of the housing.
  • the rotor of the rotary piston machine has a first wall area delimited by the first spherical inner wall and by a first outer wall.
  • the first outer wall is designed as a first straight circular cylinder.
  • a first housing, in which the rotor is rotatably mounted, has a first housing inner wall which, at least in a partial area of the rotor, has the shape of a second straight circular cylinder.
  • the first straight circular cylinder is at least partially enclosed by the second straight circular cylinder.
  • the housing no longer has to have a spherical interior, but can instead be made in the form of a straight circular cylinder.
  • This is a geometric shape that is easy to produce and can be manufactured with almost any diameter and within any tolerance. In the simplest case, this shape could even be made by drilling.
  • the end of the housing can be locked in a rotationally fixed manner with a cover in which the counter rotor is rotatably mounted.
  • the storage can be done, for example, by roller or plain bearings.
  • the bearings are designed in such a way that they can absorb the forces generated radially and axially by the counter rotor during operation.
  • the counter-rotor can be pre-assembled with the rotor in order to finally close the housing with the cover, or the counter-rotor can be pre-assembled with the cover in order to attach this pre-assembled combination to the front of the housing attach.
  • a medium to be compressed can be fed radially to the housing and / or removed radially from the housing.
  • the counter rotor has a second wall area delimited by the second spherical ring-shaped inner wall and a second outer wall.
  • the second outer wall is designed as a third straight circular cylinder, with a second housing, in which the counter rotor is rotatably mounted, having a second housing inner wall which, at least in a partial area of the counter rotor, has the shape of a fourth straight circular cylinder, the third straight circular cylinder from the fourth straight circular cylinder is at least partially enclosed.
  • At least one first control opening is formed in the wall area transversely to the axis of rotation of the rotary piston machine.
  • This first control opening can be formed either in the first wall area of the rotor or in the second wall area of the counter-rotor.
  • This first control opening can be designed as a bore or as an elongated hole in the wall area, wherein the elongated hole can extend either along the axis of rotation or transversely to the axis of rotation.
  • at least two first control openings are formed in the wall area in order to supply the medium to be compressed to the at least one working space and to remove the compressed medium from the at least one working space.
  • the gap resulting between the outer wall and the inner wall of the housing can be made as small as possible.
  • the housing and associated rotor or counter-rotor can be manufactured in such a way that the gap required between the rotor or counter-rotor and housing is as small as possible.
  • the second wall area of the counter-rotor is arranged in a radial bearing, the radial bearing being supported on the second inner wall of the housing.
  • This radial bearing can be designed both as a roller bearing and as a plain bearing.
  • plain bearings as well as roller bearings
  • tight manufacturing tolerances must be maintained for the bores receiving the bearings in order to achieve precise concentricity of the rotor and counter-rotor.
  • corresponding first control openings can be provided in the plain bearing in order to supply the medium to be compressed to the working spaces or to remove the compressed working medium from the working spaces.
  • an end face is formed on the second wall region of the counter rotor of the rotary piston machine on a side facing away from the second toothing.
  • the end of the second housing can be locked in a rotationally fixed manner with a cover.
  • An axial bearing is arranged between the cover and the end face.
  • the axial bearing can be designed both as a roller bearing and as a plain bearing.
  • the axial bearing absorbs the axial forces occurring on the counter rotor during operation and introduces them into the cover, the cover being connected to the housing in such a way that these forces can be absorbed by the housing.
  • the axial bearing can be connected to the cover in a rotationally fixed manner for easier assembly with the cover, particularly in the case of the plain bearing design.
  • the cover has at least one inlet opening arranged parallel to the second axis of rotation of the counter-rotor, the axial bearing at least one second inlet control opening and the end face at least a third one Entry control opening on.
  • a medium to be transported can be fed through the inlet opening and the second inlet control opening to the third inlet control opening.
  • the medium to be transported can also be removed through the third entry control opening, the second entry control opening and the entry opening. Furthermore, it is possible to form an outlet opening in the cover parallel to the inlet opening, a second outlet control opening in the axial bearing parallel to the second inlet control opening and a third outlet control opening parallel to the third inlet control opening in the end face of the counter rotor.
  • the inlet opening, the second inlet control opening and the at least one third inlet control opening as well as the outlet opening, the second outlet opening and the at least one third outlet control opening are connected to one another in a fluid-communicating manner.
  • the inlet opening, the second inlet control opening and the third inlet control opening are separated from the outlet control opening, the second outlet control opening and the third outlet control opening in a fluid-tight manner.
  • the counter-rotor has at least one inlet control channel which is connected in a fluid-communicating manner to the third inlet control opening and at least one of the tooth gaps such that the medium can be fed to the at least one working space.
  • the opening does not necessarily have to be made in a tooth gap, but can also be formed in the area of the tooth flank.
  • the spherical ring-shaped outer contour is clasped by the spherical ring-shaped inner wall.
  • Clasp is to be understood as meaning that the spherical ring-shaped inner wall extends at least partially into a spherical ring-shaped outer contour that tapers in the direction of a shaft of the rotor or counter-rotor, the shaft being arranged on a side facing away from the respective toothing.
  • a first diameter at the entry of the spherical ring-shaped inner wall is smaller than a second largest diameter of the spherical ring-shaped outer contour.
  • the rotor and / or counter-rotor are formed from plastic, it may be possible to move the two rotors into the rotor-counter-rotor arrangement due to the high modulus of elasticity of plastics and the associated elastic deformability as well as a force acting along the axes of rotation of the rotor and counter-rotor bring. Due to this modulus of elasticity, it may also be possible to separate the rotor and counter-rotor from one another by applying force.
  • the rotor and / or counter-rotor can also be made in several parts in order to achieve this clasping effect in rotors made in particular of metal, since metal generally has a considerably lower modulus of elasticity than the aforementioned modulus of elasticity of the plastics used here.
  • a fraction of the compressed medium is used to exert a force on the face of the counter-rotor in the axial direction, which counteracts the force that is exerted on the counter-rotor by the medium to be compressed.
  • This ensures that when the teeth of the rotors are meshed, there are no gaps that go beyond a predetermined amount.
  • the start-up phase that is to say at the start of the rotation of the rotors, there is no or at least insufficient pressure of the medium on the face of the counter-rotor.
  • the counter rotor would be pushed out by the rotor through the medium to be compressed beyond the predetermined gap size of the teeth without being clasped.
  • At least one component from the group of rotor, counter-rotor and housing is formed in one piece.
  • At least one component from the group of rotor, counter rotor and housing is made of plastic.
  • At least one component from the group of rotor, counter-rotor and housing is designed as an injection-molded part.
  • Fig. 1 shows a rotary piston machine which does not fall within the scope of the claim but is useful for the description and understanding of the invention and which operates as a pump, compressor or motor with a rotor 2 and a counter rotor 4, the rotor 2 being arranged opposite the counter rotor 4.
  • the rotor 2 has on its first end face 6 a first toothing 8, which in the present case is designed as a cycloid toothing, but can also be, for example, a trochoidal toothing.
  • the first toothing 8 is formed by at least one first tooth 10 and at least one first tooth gap 12.
  • the counter rotor 4 has a second toothing 16 on its second end face 14.
  • the second toothing 16 is formed by at least one second tooth 18 and at least one second tooth gap 20 formed.
  • the two toothings 8, 16 are in engagement with one another in such a way that working spaces 24 are formed by meshing the teeth 10, 18. Furthermore, the rotor 2 has a first axis of rotation I and the counter-rotor 4 has a second axis of rotation II. The first axis of rotation I and the second axis of rotation II enclose an angle ⁇ that is not equal to 0 °. By combing the teeth 10, 18, volumes formed by the first working spaces 24 are changed.
  • the rotor 2 has a first spherical ring-shaped inner wall 26.
  • the counter rotor 4 has a first spherical ring-shaped outer contour 28.
  • the first spherical ring-shaped outer contour 28 is complementary to the first spherical ring-shaped inner wall 26 of the rotor 2.
  • the rotor 2 is driven by a motor, of which only its drive shaft 30 is shown.
  • the drive shaft 30 engages in a bore 31 formed on the rotor 2.
  • the rotor 2 and the counter rotor 4 are jointly surrounded by a first housing 32.
  • the first housing 32 is closed in a fluid-tight manner at the end by a first cover 36.
  • the rotor 2 has a first wall area 40 delimited by the first spherical inner wall 26 and by a first outer wall 38.
  • the first outer wall 38 is designed as a first straight circular cylinder 44.
  • the first housing 32 has a first housing inner wall 42, which is shaped as a second straight circular cylinder 46 in the area of the rotor 2.
  • the first straight circular cylinder 44 is enclosed by the second straight circular cylinder 46.
  • a rotor shaft 54 extending in a direction facing away from the first toothing 8 is integrally formed on the rotor 2, the rotor shaft 54 being received by a roller bearing 34 which is supported on the first housing 32.
  • the rotor 2 is thus rotatably supported with respect to the first housing 32.
  • the counter-rotor 4 can be rotated in that the cover 36 is provided with a bearing receptacle 48 which has the shape of a fifth straight circular cylinder 50.
  • a counter-rotor shaft 52 extending in a direction facing away from the second toothing 16 is integrally formed on the counter-rotor 4 and is received by at least one further roller bearing 34, in the present case by two roller bearings 34.
  • the two roller bearings 34 are supported in the bearing receptacle 48 of the cover 36, the cover 36 being non-rotatably connected to the housing 32.
  • a first gap 55 which forms between the first outer wall 38 of the rotor 2 and the first inner wall 42 of the housing 32 is so small that liquid or gaseous medium can be fed to the at least one working space 24 via a feed channel 56 integrated in the housing 32 without the supplied medium mixes with the compressed medium to be discharged, which is removed from the working space 24 by means of a discharge channel 58 formed in the housing 32.
  • the working space 24 is delimited on the one hand by the first 10 and second tooth 18 and the first 12 and second tooth gap 20 a support surface 61 arranged on the rotor 2 symmetrically to its axis of rotation I and shaped complementary to the spherical cap 59, as well as through the first spherical inner wall 26 of the rotor 2.
  • the support surface 61 is in the counter rotor 4 and the spherical cap 59 in the rotor 2, as shown in Figure 3 is shown.
  • a fluid to be compressed is supplied to the opening working spaces 24 via the supply channel 56 and is compressed by means of closing working spaces 24.
  • the compressed fluid is removed from the working spaces 24 by means of the discharge channel 58 and fed to a consumer, not shown here.
  • Fig. 2 shows the off Fig. 1 known rotor 2 and counter rotor 4 in a 3D view.
  • the first outer wall 38 shaped as a second straight circular cylinder 44, is clearly visible.
  • At least one first control opening 60 is formed in the first wall region 40 transversely to the first axis of rotation I.
  • this first control opening 60 is designed as a bore perpendicular to the first axis of rotation I.
  • This at least one first control opening 60 can also be designed as an elongated hole which runs either along or transversely to the first axis of rotation I.
  • the fluid supplied via the supply channel 56 passes through this at least one first control opening 60 into the at least one first working chamber 24 in order to be removed from this at least one working chamber 24 via the at least one first control opening 60 by means of the discharge channel 58 after the compression process.
  • Fig. 3 shows an embodiment of the rotary piston machine in longitudinal section.
  • the counter rotor 4 has a second spherical ring-shaped inner wall 62 and the rotor 2 has a second spherical ring-shaped outer contour 64.
  • the second spherical ring-shaped outer contour 64 is designed to be complementary to the second spherical ring-shaped inner wall 62.
  • the second spherical ring-shaped inner wall 62 of the counter-rotor 4 is extended by a clasping area 65. This clasping area 65 surrounds the second, second spherical outer contour 64 of the rotor 2, which tapers toward the rotor shaft 54.
  • This clasping area 65 is also designed to be complementary to the second spherical inner wall 62 of the counter-rotor 4. By clasping or embracing, the rotor 2 is fitted into the counter-rotor 4 and vice versa.
  • a first diameter d forming at an inlet 67 to the second spherical ring-shaped inner wall 62 is smaller than a second largest diameter D of the spherical ring-shaped outer wall 62
  • Rotor 2 and the counter rotor 4 are mounted, the two rotors 2, 4 cannot be separated or only with an increased force that would have to be applied along the first I and second axis of rotation II due to the clasping by the clasping area 65.
  • the increased force is not achieved by the fluid compressed to a final pressure, so that the compressed fluid cannot push the rotor 2 and / or the counter rotor 4 apart to such an extent that the rotor 2 and / or the counter rotor 4 leaves the clasping area 65.
  • the rotor 2 and the counter-rotor 4 are surrounded by a second housing 66, which is closed on the end face by a second cover 74 in a rotationally fixed and fluid-tight manner.
  • the rotor 2 is mounted on its rotor shaft 54 in a first slide bearing 68, the slide bearing 68 being supported on the second housing 66.
  • the slide bearing 68 absorbs radial and axial forces acting on the rotor 2.
  • the counter rotor 4 has a second wall region 78 delimited by the second spherical ring-shaped inner wall 62 and a second outer wall 76.
  • the second outer wall 76 is designed as a third straight circular cylinder 82.
  • the second housing 66 has a second housing inner wall 80 which, at least in a partial area of the counter-rotor 4, has the shape of a fourth straight circular cylinder 84.
  • the third straight circular cylinder 82 is enclosed by the fourth straight circular cylinder 84.
  • the second wall area 78 is arranged in a radial bearing designed as a second slide bearing 70, the second slide bearing 70 being supported on the second inner wall 80 of the housing.
  • an end face 88 is formed on the second wall region 78 on a side facing away from the second toothing 16.
  • a bearing receptacle 86 is formed on an inner side of the second cover 74 and receives an axial bearing designed as a third slide bearing 72.
  • the axial forces acting on the counter rotor 4 are absorbed by the clasping of the clasping area 65. If, for example, the axial forces should rise above a predetermined amount due to a malfunction, these axial forces can be introduced into the slide bearing 72 via the end face 88 of the counter-rotor 4.
  • the rotor 2 and the counter rotor 4 are spaced apart from one another by a predetermined second gap dimension 69. This is achieved in that a portion of the compressed fluid is directed onto the end face 88 of the counter-rotor 4.
  • the force that the fluid exerts on the The rotor 2 and the counter rotor 4 are compensated by the fact that the end face 88 of the counter rotor 4 is also acted upon by a force.
  • the fluid to be compressed can thus push the counter rotor 4 away from the rotor 2 beyond the predetermined second gap dimension 69 during the compression process.
  • the clasping in the clasping area 65 prevents the fluid from pushing the counter-rotor 4 away from the rotor 2 beyond the predetermined second gap dimension during the start-up of the rotary piston machine during the compression process.
  • a stable operating state is achieved in which the compressed fluid has received its predetermined final pressure.
  • the clasp has the effect that the fluid reaches its final pressure in a shorter time than would be the case without the clasp.
  • FIG Fig. 2 The supply and discharge of the fluid can take place here as it is in FIG Fig. 2 has been described. However, in the embodiment claimed, the fluid is supplied and discharged in the axial direction along the second axis of rotation II Figures 4 and 5 are explained in more detail.
  • Fig. 4 shows the components of the Fig. 3 shown as a 3D exploded view.
  • Fig. 5 shows these components in longitudinal section.
  • a fluid to be compressed is fed to the working spaces 24 via an inlet opening 90 arranged in the second cover 74 parallel to the second axis of rotation II.
  • the fluid flows through a second inlet control opening 92 integrated in the third slide bearing 72 and subsequently formed in the end face 88 third inlet control openings 94 which are connected in a fluid-communicating manner to at least one inlet control channel (not shown here), the inlet control channel with at least one in a second tooth flank 22 of the second toothing 16 formed opening 104 is connected in fluid communication.
  • This opening 104 can also be formed in the second tooth gap 20 of the second toothing 16.
  • the medium to be compressed enters the opening working spaces 24 through these openings 104. After the fluid has been compressed, this is via at least one further opening 104, which is connected to at least one third outlet control opening 96 by means of an outlet control channel (not visible here), is discharged from the rotary piston engine via a second outlet control opening 98 formed in the third slide bearing 72 and an outlet opening 102 formed parallel to the inlet opening 90 in the second cover 74. So that the fluid can be compressed in the rotary piston machine, the supplied fluid has essentially no connection to the discharged fluid within the rotary piston machine.
  • the second inlet control opening 92 is therefore separated from the second outlet control opening 98 by means of webs 100 which are integrated in the third slide bearing 72.

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

Claims (1)

  1. Pompe à piston rotatif fonctionnant en tant que pompe, compresseur ou moteur,
    - comprenant un rotor (2) et un contre-rotor (4), le contre-rotor (4) étant disposé à l'opposé du rotor (2),
    - le rotor (2) présentant une première surface frontale (6) avec une première denture (8), le contre-rotor (4) présentant une deuxième surface frontale (14) avec une deuxième denture (16) et la première (8) et la deuxième (16) denture étant chacune formées d'au moins une dent (10, 18) et d'un espace entre-dents (12, 20),
    - les dentures (8, 16) étant en prise l'une avec l'autre de telle sorte que par engrènement des dents (10) de la première denture (8) et des dents (18) de la deuxième denture (16), des espaces de travail (24) soient réalisés, des volumes formés par les espaces de travail (24) étant modifiés par l'engrènement des dents (10 18),
    - le rotor (2) présentant un premier axe de rotation (I), le contre-rotor (4) présentant un deuxième axe de rotation (II), le premier axe de rotation (I) et le deuxième axe de rotation (II) formant un angle (ϕ) qui est différent de 0°,
    - le contre-rotor (4) présentant une première paroi intérieure en forme de bague sphérique (62) et le rotor (2) présentant un premier contour extérieur en forme de bague sphérique (64), qui est réalisé de manière complémentaire à la première paroi intérieure en forme de bague sphérique (62) du contre-rotor (4),
    - le contre-rotor (4) présentant une région de paroi (78) limitée par la première paroi intérieure en forme de bague sphérique (62) et une paroi extérieure (76), la paroi extérieure (76) étant réalisée sous forme de cylindre circulaire droit (82), un boîtier (66), dans lequel est supporté à rotation le contre-rotor (4), présentant une paroi intérieure de boîtier (80) qui, au moins dans une région partielle du contre-rotor (4), présente la forme d'un cylindre circulaire droit (84), le cylindre circulaire droit (82) étant entouré au moins en partie par le cylindre circulaire droit (84), caractérisée en ce que
    - la région de paroi (78) est disposée dans un palier radial (70), le palier radial (70) s'appuyant contre la paroi intérieure de boîtier (80),
    - un côté frontal (88) étant réalisé au niveau de la région de paroi (78) sur un côté opposé à la deuxième denture (16), le deuxième boîtier (66) pouvant être fermé du côté frontal de manière solidaire en rotation avec un couvercle (74), un palier axial (72) étant disposé entre le couvercle (74) et le côté frontal (88),
    - le couvercle (74) présentant au moins une ouverture d'entrée (90) disposée parallèlement au deuxième axe de rotation (II) du contre-rotor (4), le palier axial (72) présentant au moins une ouverture de commande d'entrée (92) et la surface frontale (88) présentant au moins une ouverture de commande d'entrée (94), un milieu à transporter pouvant être acheminé à travers l'ouverture d'entrée (90), l'ouverture de commande d'entrée (92) et l'ouverture de commande d'entrée (94),
    - le couvercle (74) présentant parallèlement à l'ouverture d'entrée (90) une ouverture de sortie (102), le palier axial (72) présentant parallèlement à l'ouverture de commande d'entrée (92) une ouverture de commande de sortie (98) et la surface frontale (88) du contre-rotor (4) présentant parallèlement à l'ouverture de commande d'entrée (94) au moins une ouverture de commande de sortie (96), un milieu à transporter pouvant être évacué à travers l'au moins une ouverture de commande de sortie (96), l'ouverture de commande de sortie (98) et l'ouverture de sortie (102),
    - l'ouverture de commande d'entrée (92) étant séparée de l'ouverture de commande de sortie (98) au moyen de nervures (100) qui sont intégrées dans le palier axial (72).
EP11768006.6A 2010-12-20 2011-10-12 Machine à piston rotatif remplissant la fonction d'une pompe, d'un compresseur ou d'un moteur Active EP2655801B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010063522A DE102010063522A1 (de) 2010-12-20 2010-12-20 Pumpe, Verdichter oder Motor
PCT/EP2011/067783 WO2012084289A2 (fr) 2010-12-20 2011-10-12 Pompe, compresseur ou moteur

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EP2655801A2 EP2655801A2 (fr) 2013-10-30
EP2655801B1 true EP2655801B1 (fr) 2020-12-30

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EP11768006.6A Active EP2655801B1 (fr) 2010-12-20 2011-10-12 Machine à piston rotatif remplissant la fonction d'une pompe, d'un compresseur ou d'un moteur

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EP (1) EP2655801B1 (fr)
DE (1) DE102010063522A1 (fr)
WO (1) WO2012084289A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE102020124825A1 (de) 2020-09-23 2022-03-24 Kolektor Group D.O.O. Motor-Pumpe-Einheit
DE102021103306A1 (de) 2021-02-12 2022-08-18 Kolektor Group D.O.O. Handgeführtes Druckflüssigkeitsgerät

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US758214A (en) * 1902-04-09 1904-04-26 Jens Nielsen Rotary motor.
FR374153A (fr) * 1907-02-02 1907-06-06 Albert Keller Dorian Pompe rotative pouvant servir également de compresseur ou de moteur rotatif, soit pour les liquides, soit pour les fluides
DE1551081A1 (de) * 1967-06-06 1970-04-16 Walter Bietzig Drehkugelmaschine
DE3221994A1 (de) * 1982-06-11 1983-12-15 Rudi 2000 Hamburg Werner Rotationskolbenmaschine
US5513969A (en) 1991-12-09 1996-05-07 Arnold; Felix Rotary piston machine having engaging cycloidal gears
US5755196A (en) * 1995-03-09 1998-05-26 Outland Design Technologies, Inc. Rotary positive displacement engine
US6497564B2 (en) * 2000-01-07 2002-12-24 James B. Klassen Balanced rotors positive displacement engine and pump method and apparatus
US20100104462A1 (en) * 2007-03-13 2010-04-29 Cor Pumps + Compressors Ag Pump or motor

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Title
None *

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Publication number Publication date
WO2012084289A3 (fr) 2013-05-10
WO2012084289A2 (fr) 2012-06-28
EP2655801A2 (fr) 2013-10-30
DE102010063522A1 (de) 2012-06-21

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