EP2655801A2 - 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

Info

Publication number
EP2655801A2
EP2655801A2 EP11768006.6A EP11768006A EP2655801A2 EP 2655801 A2 EP2655801 A2 EP 2655801A2 EP 11768006 A EP11768006 A EP 11768006A EP 2655801 A2 EP2655801 A2 EP 2655801A2
Authority
EP
European Patent Office
Prior art keywords
rotor
counter
wall
toothing
rotary 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.)
Granted
Application number
EP11768006.6A
Other languages
German (de)
English (en)
Other versions
EP2655801B1 (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
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2655801A2 publication Critical patent/EP2655801A2/fr
Application granted granted Critical
Publication of EP2655801B1 publication Critical patent/EP2655801B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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 operates as a pump, compressor or motor, with a rotor and a counter rotor.
  • a rotary piston machine which operates as a pump, compressor or motor.
  • combs of teeth of a rotating drive member for limiting work spaces on a cycloid surface of a likewise toothed output member and thereby drive this output member.
  • the said work spaces are formed, which are increased or reduced during the rotation of the parts for their work or to produce the conveying effect on a gaseous or liquid medium.
  • Such drive and driven parts run in a common housing, whose interior is spherical.
  • the housing is divided such that the separation plane contains the center 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 is formed.
  • special attention is to be paid to the design of the parting surfaces of the two housing parts in such a way that in the assembled state the first and the second center of the spherical interior spaces of the housing parts coincide. Since a coincidence of the two centers is rather coincidental due to manufacturing reasons, the resulting between the drive part or driven part and the housing gap is adapted to the manufacturing technology and dimensioned generous accordingly.
  • a rotary piston engine operating as a pump, compressor or motor has a rotor and a counter rotor, the counter rotor being located 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, wherein the first and the second toothing are each formed from at least one tooth and one tooth gap.
  • the teeth are engaged with each other such that by combing the teeth of the first toothing and the teeth of the second toothing workrooms are formed, wherein formed by the work spaces volumes are 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 include an angle other than 0 degrees.
  • the rotor has a first annular wall-shaped inner wall and the counter rotor has a first spherical ring-shaped outer contour, which is complementary to the first
  • the counter rotor has a second annular wall-shaped inner wall and the rotor has a second spherical ring-shaped outer contour, which is complementary to the second spherical ring-shaped inner wall of the counter-rotor.
  • Inner wall and the rotor has a second spherical ring-shaped outer contour.
  • annular annular inner wall and the spherical ring-shaped outer contour resulting gap are formed as small as possible. This gap losses are largely eliminated. Due to the high-precision manufacture of the rotors, an adjustment process by means of Einschieifen or adjusting with respect to the rotor and counter rotor can therefore be omitted. Since now the first spherical ring
  • Inner wall rotates and does not stand still, as is the case inside the housing of the fixed housing, the case to be compressed gaseous or liquid medium is exposed to a lower wall friction than on just this Gescouseinnenwandung. Due to the rotation of the first annular wall-shaped inner wall, which forms on this inner wall laminar
  • the rotor of the rotary piston engine has a first wall region delimited by the first annular ring-shaped inner wall and by a first outer wall.
  • the first outer wall is formed as a first straight circular cylinder.
  • a first housing, in which the rotor is rotatably mounted, has a first
  • Housing inner wall which has a shape of a second right circular cylinder, at least in a portion of the rotor.
  • Circular cylinder is at least partially enclosed by the second straight circular cylinder.
  • the housing no longer needs to have a spherical interior, but instead can be made in the shape of a right circular cylinder. This is an easy to produce geometric shape, with almost any
  • the housing is the front side with a lid rotatably closed, in which the counter rotor is rotatably mounted.
  • the storage can be done for example by rolling or plain bearings.
  • the bearings will be designed so that during operation they can absorb the forces generated radially and axially by the counter rotor.
  • the counter rotor can be preassembled with the rotor to finally close the housing with the cover, or the counter rotor can be preassembled with the cover to connect this preassembled combination to the front of the housing fasten.
  • a medium to be compressed is radially supplied to the housing and / or can be removed radially from the housing.
  • the counter rotor has one of the second spherical ring-shaped inner wall and a second
  • Outer wall is formed as a third straight circular cylinder, wherein a second housing in which the counter rotor is rotatably mounted, a second Genosuseinnenwandung having at least in a portion of the counter rotor in the form of a fourth right circular cylinder, the third straight circular cylinder of the fourth straight circular cylinder is at least partially enclosed.
  • This first control opening can be formed either in the first wall region of the rotor or in the second wall region of the counter rotor.
  • This first control opening may be designed as a bore or as a slot in the wall area, wherein the slot may extend either along the axis of rotation or transversely to the axis of rotation.
  • at least two first control openings will be formed in the wall region 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. To avoid leakage between the medium-feeding and medium-discharging
  • the resulting between the outer wall and the Gezzauseinnenwandung gap can be made as low as possible.
  • the housing and associated rotor or counter rotor can be made such that the necessary between rotor and counter rotor and housing gap is formed as small as possible.
  • the second wall portion of the counter-rotor is arranged in a radial bearing, wherein the radial bearing is supported on the second Gescouseinnenwandung.
  • This radial bearing can be designed both as a rolling bearing and as a sliding bearing. Both with the use of plain bearings and bearings are to be observed for the bearing receiving holes tight manufacturing tolerances in order to achieve a precise concentricity of the rotor and counter rotor. Just a design that all the components used, such as bearings, this bearing receiving Gereheatinnenwandung and the
  • corresponding first control openings may be provided in the sliding bearing to supply the medium to be compressed to the workrooms or to dissipate the compressed working fluid from the work spaces.
  • Wall region of the counter-rotor of the rotary piston machine on a side facing away from the second toothing side formed an end face.
  • the second housing is the front side with a lid rotatably closed. Between the lid and the end face a thrust bearing is arranged.
  • the thrust bearing can be designed both as a rolling bearing and as a plain bearing.
  • the thrust bearing absorbs the axial forces occurring during operation on the counter rotor and introduces them into the cover, wherein the cover is connected to the housing such that these forces can be absorbed by the housing.
  • the thrust bearing can be rotatably connected to the lid for ease of assembly with the lid, especially in the slide bearing design.
  • the cover has at least one parallel to the second axis of rotation of the counter-rotor
  • the thrust bearing at least a second
  • Ingress control opening and the end face at least a third Entry control opening on.
  • Entry tax can be accom panyed.
  • the medium to be transported can also be through the third
  • Ingress control opening, the second inlet control opening and the inlet opening are removed. Furthermore, it is possible to form in the cover parallel to the inlet opening an outlet opening, in the axial bearing parallel to the second inlet control opening a second outlet control opening and parallel to the third inlet control opening in the end face of the counter rotor, a third outlet control opening.
  • the inlet opening, the second inlet control opening and the at least one third inlet control opening and the outlet opening, the second outlet opening and the at least one third outlet control opening are connected to each other in a fluid-communicating manner.
  • Outlet control port and the third outlet control port fluid-tight.
  • the counter rotor has at least one entrance control channel, which is connected to the third
  • Ingress control opening and at least one of the tooth gaps is connected fluidkommunizingd, such that the medium is the at least one working space can be fed.
  • the opening need not necessarily be introduced into a tooth gap, but it can also be formed in the region of the tooth flank.
  • the spherical ring-shaped outer contour is clasped by the spherical ring-shaped inner wall.
  • Umklamm ceremonies is to be understood that the ball-shaped
  • Inner wall extends at least partially into a tapered in the direction of a shaft of the rotor or counter-rotor spherical-ring-shaped outer contour, wherein the shaft is disposed on a side remote from the respective toothing side.
  • a first diameter at the entrance 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 can also be designed in several parts in order to realize this clasping effect in particular made of metal rotors, since metal usually has a significantly lower modulus of elasticity than the above-mentioned
  • a fraction of the compressed medium is used to exert on the end face of the counter-rotor in the axial direction of a force which
  • At least one component from the group rotor, counter rotor and housing is integrally formed.
  • At least one component from the group rotor, counter rotor and housing is made of plastic.
  • At least one component from the group rotor, counter rotor and housing as a
  • FIG. 1 shows a rotary piston machine in longitudinal section
  • FIG. 2 shows a 3D view of the rotor and counter rotor of FIG. 1 in FIG
  • FIG. 4 shows an exploded view of the components of FIG. 3, and FIG. 5 shows a cross section of the components shown in FIG. 4.
  • Fig. 1 shows a rotary piston machine which operates as a pump, compressor or motor with a rotor 2 and a counter rotor 4, wherein the rotor 2 is arranged opposite to the counter rotor 4.
  • the rotor 2 has at its first end face 6, a first toothing 8, which is formed in the present case as a cycloidal toothing, but may also be, for example, a Trochoidenvertechnikung.
  • the first toothing 8 is formed by at least one first tooth 10, as well as at least one first tooth gap 12.
  • the counter rotor 4 has at its second end face 14 a second one
  • the second toothing 16 is formed by at least one second tooth 18 and at least one second tooth gap 20.
  • the two gears 8, 16 are engaged with each other such that by combing the teeth 10, 18 working spaces 24 are formed.
  • 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 ⁇ which 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 annular inner wall 26.
  • the counter rotor 4 has a first spherical ring-shaped outer contour 28.
  • Outer contour 28 complementary to the first annular annular inner wall 26 of the rotor 2 is formed.
  • the rotor 2 is present in the present
  • Embodiment driven by a motor of which only the 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 at the end by a first cover 36 fluid-tight.
  • the rotor 2 has a first wall region 40 delimited by the first annular ring-shaped 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 Genzouseinnenwandung 42, which is formed in the region of the rotor 2 as a second straight circular cylinder 46.
  • the first straight circular cylinder 44 is enclosed by the second straight circular cylinder 46.
  • a rotor shaft 54 extending in a direction away from the first toothing 8 is formed on the rotor 2, wherein the rotor shaft 54 is received by a roller bearing 34, which is supported on the first housing 32.
  • the rotor 2 is rotatably supported relative to the first housing 32.
  • a rotatability of the counter rotor 4 is achieved in that the cover 36 is provided with a bearing receptacle 48, which has the shape of a fifth straight circular cylinder 50.
  • On the counter rotor 4 is formed in a direction away from the second toothing 16 opposite direction extending rotor shaft 52 which is received by at least one further rolling bearing 34, in the present case by two bearings 34.
  • the two rolling bearings 34 are supported in the bearing receptacle 48 of the lid 36, wherein the cover 36 is rotatably connected to the housing 32.
  • a first gap 55 forming between the first outer wall 38 of the rotor 2 and the first housing inner wall 42 of the housing 32 is so small that liquid or gaseous medium can be supplied 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 discharged medium 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 limited on the one hand by the first 10 and second tooth 18 and the first 12 and second tooth gap 20. On the other hand, the working space 24 is limited by a symmetrical to the counter-rotor 4 to the axis of rotation II ball cap 59 which engages with one on the rotor 2
  • the support surface 61 in the counter rotor 4 and the ball cap 59 may be formed in the rotor 2, as in Figure 3 is shown.
  • a fluid to be compressed is supplied via the supply channel 56 to the opening work spaces 24 and compressed by means of closing work spaces 24.
  • the compressed fluid is by means of the Abtechnologykanals 58 the
  • Fig. 2 shows the known from Fig. 1 rotor 2 and counter rotor 4 in one
  • the first outer wall 38 which is shaped as a second, right-hand 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 port 60 is in the present
  • This at least one first control opening 60 may also be formed as a slot extending either along or transverse to the first axis of rotation I.
  • Fig. 3 shows a further 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 formed 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 clasp region 65. This clasp portion 65 engages around the second second spherical ring-shaped outer contour 64 of the rotor 2 tapering towards the rotor shaft 54.
  • This clasp region 65 engages around the second second spherical ring-shaped outer contour 64 of the rotor 2 tapering towards the rotor shaft 54.
  • Inner wall 62 forming the first diameter d smaller than a second largest diameter D of the spherical annular outer wall 62. If the Rotor 2 and the counter rotor 4 are mounted, due to the
  • the two rotors 2, 4 Clamping by the clasp portion 65, the two rotors 2, 4 not or only under an increased force, which would be applied along the first I and second axis of rotation II, to be separated.
  • the increased force is not achieved by the fluid compressed to a final pressure, so that the compressed fluid can not press the rotor 2 and / or the counter rotor 4 far enough apart that the rotor 2 and / or counter rotor 4 leaves the clasp area 65.
  • the rotor 2 and the counter rotor 4 are surrounded by a second housing 66, which is closed at the end by a second cover 74 rotatably and fluid-tight. The rotor 2 is at his
  • Rotor shaft 54 mounted in a first sliding bearing 68, wherein the sliding bearing 68 is supported on the second housing 66.
  • the sliding bearing 68 takes on the rotor 2 acting radial and axial forces.
  • 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 formed as a third, right-hand circular cylinder 82.
  • the second housing 66 has a second Gepurinnenwandung 80, which has the shape of a fourth straight circular cylinder 84 at least in a portion of the counter-rotor 4.
  • the third straight circular cylinder 82 is enclosed by the fourth straight circular cylinder 84.
  • the second wall region 78 is arranged in a radial bearing designed as a second slide bearing 70, wherein the second slide bearing 70 is supported on the second housing inner wall 80. Furthermore, an end face 88 is formed on the second wall region 78 on a side facing away from the second toothing 16. On an inner side of the second lid 74, a bearing receptacle 86 is formed, which is designed as a third sliding bearing 72
  • Axial bearing receives.
  • the axial forces acting on the counter rotor 4 are absorbed by the clasping of the clasping region 65. If, for example, due to a malfunction, an increase in the axial forces take place beyond a predetermined extent, these axial forces can be introduced into the sliding bearing 72 via the end face 88 of the counter-rotor 4.
  • the rotor 2 and the counter rotor 4 are spaced from each other to a predetermined second gap 69. This is achieved by passing a subset of the compressed fluid onto the face 88 of the counter-rotor 4.
  • the force exerted by the fluid during compression on the Rotor 2 and the counter rotor 4 compensated by the fact that the end face 88 of the counter rotor 4 is also acted upon by a force.
  • Start-up phase is still no compacted fluid available, the pressure of which could be directed to the face 88.
  • the fluid to be compressed may push the counter rotor 4 away from the rotor 2 beyond the predetermined second gap 69.
  • it takes several revolutions of the rotor 2 until a predetermined final pressure of the fluid can be achieved.
  • the clasp in the clasp area 65 prevents the fluid during the start of the rotary piston engine during the
  • Gap also presses away from the rotor 2. Thus, after only a few revolutions of the rotor 2, a stable operating state is reached at which the compressed fluid has received its predetermined final pressure. Thus, the clenching causes the fluid to reach its final pressure in a shorter time than would be the case without clasping.
  • the supply and the discharge of the fluid can in this case take place as has been described in Fig. 2.
  • the supply and removal of the fluid can also take place in the axial direction along the second axis of rotation II. This should be in the
  • Fig. 4 shows the components of Fig. 3 as a 3D exploded view.
  • Fig. 5 shows these components in longitudinal section.
  • Compressive fluid is supplied 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 third entry control openings 94 formed in the end face 88, which are connected in a fluid-communicating manner with at least one inlet control channel, not shown here, wherein the inlet control channel communicates with at least one second tooth flank 22 in FIG second toothing 16 formed opening 104 is connected fluidkommunitend.
  • This opening 104 may also be formed in the second tooth space 20 of the second toothing 16. The medium to be compressed enters through these openings 104 into the opening work spaces 24.
  • Opening 104 which is connected by means of an outlet control channel not visible here with at least one third outlet control openings 96, via a formed in the third sliding bearing 72 second outlet control opening 98 and in the second lid 74 to the inlet opening 90 in parallel
  • Outlet opening 102 removed from the rotary piston machine. So that the fluid can be compressed in the rotary piston machine, the supplied fluid within the rotary piston machine essentially has no connection to the discharged fluid. Therefore, the second entrance control port 92 is separated from the second exit control port 98 by lands 100 integrated with the third journal bearing 72.

Landscapes

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

Abstract

Machine à piston rotatif qui fonctionne en tant que pompe, compresseur ou moteur et qui comporte un rotor (2) et un contre-rotor (4), le contre-rotor (4) étant situé face au rotor (2). Le rotor (2) présente une première face frontale (6) pourvue d'une première denture (8). Le contre-rotor (4) présente une seconde face frontale (14) pourvue d'une seconde denture (16). Les première (8) et seconde (16) dentures sont constituées chacun d'au moins une dent (10, 18) et un entredent (12, 20). Les dentures (8, 16) s'engrènent de manière telle que l'engrènement des dents (10) de la première denture (8) et des dents (18) de la seconde denture (16) forme des chambres de travail (24), les volumes formés par les chambres de travail (24) étant modifiés par l'engrènement des dents (10, 18). Le rotor (2) présente un premier axe de rotation (I). Le contre-rotor (4) présente un second axe de rotation (II). Le premier axe de rotation (I) et le second axe de rotation (II) forment un angle (φ) qui est différent de 0 degré. Selon l'invention, le rotor (2) comporte une première paroi interne (26) en forme d'anneau sphérique et le contre-rotor (4) présente un premier contour externe (18) en forme d'anneau sphérique qui est conçu de manière à être complémentaire à la première paroi interne (26) en forme d'anneau sphérique du rotor (2).
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

Publications (2)

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

Family

ID=44789470

Family Applications (1)

Application Number Title Priority Date Filing Date
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

Country Status (3)

Country Link
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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Publication number Priority date Publication date Assignee Title
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
DE4241320C2 (de) 1991-12-09 2002-01-17 Arnold Felix Drehkolbenmaschine
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
SI2137378T1 (en) * 2007-03-13 2018-02-28 Robert Bosch Gmbh Pump or engine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2012084289A2 *

Also Published As

Publication number Publication date
EP2655801B1 (fr) 2020-12-30
WO2012084289A3 (fr) 2013-05-10
DE102010063522A1 (de) 2012-06-21
WO2012084289A2 (fr) 2012-06-28

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