EP2669471A1 - Dispositif rotatif à chambre extensible - Google Patents

Dispositif rotatif à chambre extensible Download PDF

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Publication number
EP2669471A1
EP2669471A1 EP13003983.7A EP13003983A EP2669471A1 EP 2669471 A1 EP2669471 A1 EP 2669471A1 EP 13003983 A EP13003983 A EP 13003983A EP 2669471 A1 EP2669471 A1 EP 2669471A1
Authority
EP
European Patent Office
Prior art keywords
housing
guiding surface
rotor
track
axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP13003983.7A
Other languages
German (de)
English (en)
Inventor
Amro Al-Qutub
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.)
RPM Group Ltd
Original Assignee
RPM Group Ltd
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 RPM Group Ltd filed Critical RPM Group Ltd
Priority to EP13003983.7A priority Critical patent/EP2669471A1/fr
Publication of EP2669471A1 publication Critical patent/EP2669471A1/fr
Withdrawn legal-status Critical Current

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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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/40—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and having a hinged member
    • F01C1/44—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and having a hinged member with vanes hinged to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0836—Vane tracking; control therefor by mechanical means comprising guiding means, e.g. cams, rollers
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance

Definitions

  • the invention relates to a rotary expansible chamber device and in particular to a compressor or an expander.
  • An expander can be used as an electrical energy generating device in which a pressurized gas expands for driving a rotor.
  • a compressor is a mechanical device that increases the pressure of gas by consuming energy for driving a rotor and thereby reducing volume of said gas.
  • US 5,709,188 comprising a housing having an interior surface and defining an inlet and an outlet.
  • the compressor according to figure 2 of US 5,709,188 has a circular rotor mounted eccentrically with respect to a center of a fixed housing such that a compressor chamber is defined between an interior surface of the housing and an exterior surface of the circular rotor.
  • a radial gap between said interior surface of the housing and said rotor decreases along said compressor chamber from a maximum at an inlet to a minimum at an outlet of the housing.
  • Said rotor supports a plurality of sealing vanes to move radially to and from a retracted condition and an extended condition.
  • Said sealing vanes dynamically seal said radial gap when gliding along said interior surface of the housing from the inlet to the outlet of the housing along the compressor chamber so that gas within the compressor chamber will be compressed.
  • the compressor chamber is open to the inlet and the outlet of said housing.
  • a mechanical vane position control mechanism is necessary in order to retract and extend the sealing vane depending on the circumferential position of the vane with respect to the interior surface of the housing.
  • Said mechanical sealing vane position control mechanism comprises a guide bearing means which is supported on an arm-structure of the sealing vane. Additionally, the mechanical sealing vane position control mechanism comprises a fixed track means formed by the interior surface of the housing.
  • Said guide bearing means of the sealing vane and said track means of the housing cooperate with each other in a caming way such that in each respective circumferential position of the rotor relative to the housing said sealing vane is moved into necessarily retracted and extended position in contact with the interior surface of the housing.
  • the track means are realized by a guiding surface running substantially circumferentially around an axis of rotation of the rotor.
  • the interior surface of the housing forms a radially inwardly orientated bump according to which the guiding surface of said track means forms a corresponding bump.
  • said track means forms both an inner guiding surface running at least partly circumferentially around the axis of rotation of the rotor and pointing to said axis of rotation, and an outer guiding surface running at least partly circumferentially around said axis of rotation and pointing away from said axis of rotation.
  • said guide bearing means cooperates with the inner and outer guiding surface, alternatively.
  • the guide bearing means of the vane loses contact of one of the guiding surface, it gets in engagement with the other guiding surface in order to maintain control over the movement of the vane with respect to the interior surface of the housing such that the seal tip of the sealing vane essentially remains in a predetermined controlled position with respect to the interior surface of the housing, preferably in contact with the interior surface of the housing, if desired.
  • said guide bearing means is constituted by at least one outer track bearing member cooperating with said inner guiding surface, and by at least one inner track bearing member cooperating with said outer guiding surface of the track means.
  • the outer track bearing member and the inner track bearing member are structural different elements cooperating with respective differently positioned and formed guiding surfaces of said track means.
  • an automatically working mechanical mechanism for controlling the position of the sealing vane with respect to the interior surface of the housing is provided.
  • said inner and outer track bearing members are provided on both axial sides of the arm-structure of said sealing vane.
  • said track bearing members can each comprise a roller bearing.
  • said guide bearing means is mounted relatively to the guiding surface such that, in operation of the device, said guiding bearing means only acts on the inner or the outer guiding surface, alternately. This means that either one of the track bearing means comes into contract with the corresponding one of the inner or outer guiding surfaces while the other track bearing member loses contact to the respective other guiding surface.
  • said guide bearing means is in contact with the outer guiding surface, there is a small clearance between said bearing means and said inner guiding surface and vice versa.
  • said clearance is less than 2 mm or 1 mm.
  • said outer guiding surface is axially offset to an adjacent inner guiding surface regarding a pivot axis of the arm-structure of the vane.
  • the inner guiding surface of said track means is arranged axially closer to the arm-structure than said outer guiding surface of said track means.
  • the curved courses of the inner and outer guiding surfaces are substantially parallel to each other, consequently, the shortest radial distance between the inner and outer guiding surfaces remains substantially constant along the courses of the inner and outer guiding surfaces.
  • the guiding surfaces can be designed correspondingly.
  • said inner guiding surface of the track means may form a protruding bump which faces a corresponding depressing dint formed in said outer guiding surface, said bump in the inner guiding surface and said dint in the outer guiding surface are associated to the course of the seal tip around the interior surface of the housing, namely, in that as soon as the seal tip enters the bypass chamber and the leaves the bypass chamber, particularly just before passing the dynamic seal in the bypass chamber.
  • the compressor 1 comprises as main parts, first, a tube-shaped housing 3 defining a circular internal space confined by a circumferential shell and radial side walls (not shown) and defining a circular interior surface 5, and, second, a rotor 7 which is rotatably mounted within the housing 3.
  • the housing 3 defines an inlet 11 and an outlet 13. The gas to be compressed enters the housing 3 via the inlet 11 and leaves the housing 3 via the outlet 13.
  • the housing 3 has a basic side plate forming sides of the compressor chamber and comprising a portion 8 for fixing the compressor 1 to a further structure (not shown).
  • the housing 3 comprises a cooling channels 15 for cooling in particular the interior surface 5 of the housing 3 which will be heated by compressed air.
  • the rotor 7 forming a circular outer surface 21 is fixedly supported on a shaft 17.
  • the shaft 17 is rotatably supported on the housing 3 and defines a rotation axis R which is positioned eccentrically to a center (not shown) of the circular interior surface 5 of the housing 3.
  • a sickle-shaped compressor chamber 23 is formed defining a substantially radial gap g between the circular outer surface 21 of the rotor 7 and the interior surface 5 of the housing 3.
  • Said radial gap g increases along the compressor chamber 23 starting from the inlet 11 to a maximum at about the circumferential half of compressor chamber 23 from which maximum the radial gap g decreases along the compressor chamber vers the outlet 13.
  • the compressor chamber extends beyond the outlet 13 into a short cut passage to the inlet 13, which can be designated as a bypass chamber 26 defining a very small radial gap.
  • a dynamic end seal 25 is received in a recess formed in the interior surface 5 of the housing 3.
  • the dynamic end seal 25 comprises a sealing surface complementarily formed to the circular outer surface 21 of rotor 7.
  • the rotor 7 is formed as hollow structure.
  • the rotor 7 has shape like a wheel rim including several struts 27 defining four separated internal compartments or cavities 29. Said cavities 29 are confined by radial inner surfaces of rotor sides.
  • each sealing vane 31 comprising an L-shaped arm-structure 33 for holding a tip seal 37 which is operated to come into a sealing contact with the interior surface 5 of the housing 3 at least in the area of the compressor chamber 23.
  • a supporting L-leg of the arm-structure 33 is pivotally supported within said cavity 29 around a pivot axis P which is fixed by a bearing mounted on the rotor body which allows the vane 31 to rotate with the rotor 7 and allows free swing motion of the vane 31 relative to the rotor 7.
  • the sealing vane 31 can be pivoted from an extended position in which a free ended working L-leg 35 of the arm-structure 33 extends through an opening 38 formed in the outer surface 21 of the rotor 7 vers the outside of the rotor 7 to the interior surface 5 of the housing 3.
  • the tip seal 37 is mounted in an L-shaped slit formed in a free end of the free ended L-leg 35 of the arm 33.
  • a sealing vane 31 is shown in its extended position said tip seal 37 being in contact with the interior surface 5 of the housing 3.
  • the sealing vane diametically positioned to the extended one (31) is in a completely retracted position, i.e. the vane is 31 is situated substantially completely within in the cavity 29 of the rotor 7. If a dynamic end seal 25 is provided in the bypass chamber 26, the vane 31 is retracted such that the tip seal 37 departs from the interior surface 5 of the housing 3 when travelling along the bypass chamber 26. Without the use of a dynamic end seal 25 in the bypass chamber 26, the tip seal 37 may remain in contact with the interior surface 5 of the housing 3 when travelling through the bypass chamber 26 from the outlet 13 to the inlet 11.
  • the compressor 1 comprises a mechanical vane position control mechanism for extending and retracting the vane 31 dependently on the circumferential position of the rotor 7.
  • Said mechanical sealing vane position control mechanism comprises a track means 41 which is illustrated in figures 2 , 3 , and 4 .
  • Said track means cams on a guiding bearing means and is constituted by a pair of outer track bearing members 43, 45 and a pair of inner track bearing members 49, 51.
  • Each inner and outer track bearing members 43, 45, 49, 51 are formed as a roller bearing supported on a stem 53 which is received in an arc shaped slot 55 ( figure 1 ) formed in a radial wall of the rotor 7 to be substantially radially shifted.
  • One inner and one outer track bearing members 43, 49 and 45, 51 are positioned on each axial side of the arm-structure 33 of the vane 31.
  • the roller bearings of the outer track bearing members 43, 45 and the inner track bearing members 49, 51 define a common rotation axis S. Said rotation axis S of the roller bearings travels along the arc shaped recess 55.
  • the operation movement of the vane 31 is determined by a first axis being the pivot axis P and a second axis being the rotation axis S of the roller bearing of the track bearing member 43, 45.
  • the second axis S coincides with the axis of the stem 53.
  • the second axis S is fixed with respect to the vane structure and the inner and outer tracking bearing 43, 45, 49, 51 are guided by the inner and outer guiding surfaces 61, 63, 65, 76.
  • the mechanical sealing vane position control mechanism further comprises a guide bearing means which is constituted by inner guiding surfaces 61 and 63 facing to the rotation axis R of the rotor 7 and cooperating with respective outer track bearing members 43 and 45. Further, said guide bearing means is constituted by outer guiding surfaces 65 and 67 facing away from the rotation axis R of the rotor 7 and cooperating with respective inner track bearings members 49 and 51.
  • the sealing vane 31 is positioned only by the outer track bearing members 43, 45 being in contact with respective inner guiding surfaces 61, 63 while inner track bearing members 49, 51 are distanced to respective outer guiding surfaces 65, 67.
  • All guiding surfaces 61, 63, 65, 67 of said guide bearing means are realized by correspondingly formed portions of the housing 3, particularly respective side plates 8.
  • the function of the above defined double track structure of the mechanical sealing vane position control mechanism will be described particularly in reference to figure 2 .
  • the outer track bearing members 43, 45 travels over the bump 71 whereby the outer track bearing members 43, 45 are shifted radially inwardly and the vane 31 is further retracted so that the tip seal 37 loses contact to the interior surface 5 of the housing 3.
  • the inner track bearing member will come into contact with the outer guiding surface 65 to bring back the vane 31 in the extended position and therefore the tip seal 37 into contact with the inner surface of the housing.
  • the inner and outer guiding surfaces 61, 63, 65, 67 can be designed such that the tip seal loses contact to interior surface 5 of the housing 3 as soon as the tip seal 37 travels along the entire bypass chamber 26.
  • a double track structure including inner and outer guiding surfaces 61, 63, 65, 67, it is possible to maintain a predetermined controlled distance between the tip seal 37 of the vane 31 and the interior surface 5 of the housing 3 even in the cases of abrupt profile changes.
  • Said inner track bearing members 49, 51 come immediately in contact with respective outer guiding surfaces 65, 67 of a track means 53 when the outer track bearing members 43, 45 intend to lose contact with respect to inner guiding surfaces 61, 63, and vice versa.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP13003983.7A 2008-07-08 2008-07-08 Dispositif rotatif à chambre extensible Withdrawn EP2669471A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13003983.7A EP2669471A1 (fr) 2008-07-08 2008-07-08 Dispositif rotatif à chambre extensible

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP08012339.1A EP2143879B1 (fr) 2008-07-08 2008-07-08 Dispositif rotatif à chambre extensible
EP13003983.7A EP2669471A1 (fr) 2008-07-08 2008-07-08 Dispositif rotatif à chambre extensible

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP08012339.1 Division 2008-07-08
EP08012339.1A Division-Into EP2143879B1 (fr) 2008-07-08 2008-07-08 Dispositif rotatif à chambre extensible

Publications (1)

Publication Number Publication Date
EP2669471A1 true EP2669471A1 (fr) 2013-12-04

Family

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP08012339.1A Not-in-force EP2143879B1 (fr) 2008-07-08 2008-07-08 Dispositif rotatif à chambre extensible
EP13003983.7A Withdrawn EP2669471A1 (fr) 2008-07-08 2008-07-08 Dispositif rotatif à chambre extensible

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP08012339.1A Not-in-force EP2143879B1 (fr) 2008-07-08 2008-07-08 Dispositif rotatif à chambre extensible

Country Status (1)

Country Link
EP (2) EP2143879B1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105201557A (zh) * 2015-09-21 2015-12-30 重庆大学 一种旋片机

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB263127A (en) * 1925-12-15 1927-03-31 Albert Thoreau Improvements in or relating to vane pumps or compressors
DE443963C (de) * 1923-12-14 1927-05-13 Hans Hundrieser Kraftmaschine mit umlaufenden, in der Kolbentrommel durch Rollen und Kurven gefuehrten radialen Kolben
US3787125A (en) * 1969-08-15 1974-01-22 Washington Scient Ind Inc Coupling assembly
US5709188A (en) 1993-12-09 1998-01-20 Al-Qutub; Amro Heat engine
GB2405672A (en) * 2003-09-04 2005-03-09 Curtis Liposcak Hinged-vane rotary pump with vane tip bearings

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5455804A (en) 1977-10-12 1979-05-04 Sanyo Electric Co Ltd Rotary type fluid machine and its preparation
US4410305A (en) * 1981-06-08 1983-10-18 Rovac Corporation Vane type compressor having elliptical stator with doubly-offset rotor
EP0103985A3 (fr) 1982-08-20 1985-02-20 Mack H. Williams Moteur rotatif ou compresseur
SE510647C2 (sv) * 1993-03-18 1999-06-14 Hoegdahl Innovation Ab Rotationsmaskin
CA2468169C (fr) 2002-01-09 2008-03-25 Karnes Dyno-Rev Engine, Inc. Moteur a combustion interne
CN1329627C (zh) * 2002-02-06 2007-08-01 赫伯特·许特林 摆动活塞式机械

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE443963C (de) * 1923-12-14 1927-05-13 Hans Hundrieser Kraftmaschine mit umlaufenden, in der Kolbentrommel durch Rollen und Kurven gefuehrten radialen Kolben
GB263127A (en) * 1925-12-15 1927-03-31 Albert Thoreau Improvements in or relating to vane pumps or compressors
US3787125A (en) * 1969-08-15 1974-01-22 Washington Scient Ind Inc Coupling assembly
US5709188A (en) 1993-12-09 1998-01-20 Al-Qutub; Amro Heat engine
GB2405672A (en) * 2003-09-04 2005-03-09 Curtis Liposcak Hinged-vane rotary pump with vane tip bearings

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105201557A (zh) * 2015-09-21 2015-12-30 重庆大学 一种旋片机

Also Published As

Publication number Publication date
EP2143879A1 (fr) 2010-01-13
EP2143879B1 (fr) 2015-12-02

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