WO2004111455A1 - Single-vane rotary pump or motor - Google Patents
Single-vane rotary pump or motor Download PDFInfo
- Publication number
- WO2004111455A1 WO2004111455A1 PCT/IL2004/000448 IL2004000448W WO2004111455A1 WO 2004111455 A1 WO2004111455 A1 WO 2004111455A1 IL 2004000448 W IL2004000448 W IL 2004000448W WO 2004111455 A1 WO2004111455 A1 WO 2004111455A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- vane
- pump
- socket
- rotor
- motor according
- Prior art date
Links
Classifications
-
- 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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/32—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
- F04C2/332—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
-
- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0007—Radial sealings for working fluid
- F04C15/0015—Radial sealings for working fluid of resilient material
-
- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C15/0065—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
Definitions
- the present invention relates generally to vane pumps and motors and more particularly, to single-vane rotary pumps used for pumping of fluids in the chemical, medical and food industries, where the required process cleanliness necessitates frequent pump cleaning or replacement.
- GB 926,495 discloses a rotary pump where the general layout includes a housing with a cylindrical cavity and a cylindrical piston (rotor) of lesser diameter eccentrically disposed therein.
- the pump drive by means of an eccentric crank, causes the piston to orbit the cavity scrolling its inner peripheral wall.
- a pump chamber with crescent shape is thus defined between the piston and the housing.
- the piston has a radial projection (vane) accommodated in a recess of the housing, which divides the chamber into an expanding chamber and a contracting chamber.
- the pump further has an inlet port at one side of the vane, connected to the expanding chamber, and an outlet port at the other side of the vane, connected to the contracting chamber.
- the vane has a cylindrical tip, while the recess is a radial channel with parallel walls contacting the cylindrical tip and allowing the vane to slide and swivel.
- the vane and the recess have triangular shape.
- the pump has a single vane connected to the rotor and to the housing across the pump chamber.
- the vane is slidably engaged to the housing while hinged to the rotor.
- the vane is also slidably engaged to the housing - however, the vane is not joined to the rotor but is radially urged to the rotor by a spring in the sliding joint so that the vane is in sliding contact with the rotor.
- the vane is integral with the rotor, while sliding through a socket which in its turn is rotatably joined to the housing.
- the outlet port is closed by a one-way check valve to prevent backflow of fluid, or pressure loss, when the scrolling zone of the rotor passes over the vane joint, since neither the vane, nor the rotor in that position isolate the inlet port from the outlet port of the pump.
- a rotary vane pump or motor comprising a housing with cylindrical inner peripheral wall defining a cavity, and a rotor with cylindrical peripheral surface and a socket internal to said peripheral surface, eccentrically disposed in the cavity.
- the rotor is adapted to scroll the inner peripheral wall in close proximity thereto.
- the inner peripheral wall and the rotor surface define a working chamber between them.
- the housing has a vane with an end received within the socket so as to enable the vane to slide in the socket maintaining predetermined degree of fluid tightness therebetween, and to enable the rotor to orbit the cavity.
- the housing has an inlet port adjacent one side of the vane and an outlet port adjacent the other side of the vane, both ports being open to the inner peripheral wall.
- the scroll zone of close proximity between the rotor surface and the inner peripheral wall of the housing, and the vane divide the working chamber into a first expanding inlet chamber in fluid communication with the inlet port and a second contracting outlet chamber in fluid communication with the outlet port.
- the socket has parallel walls and the vane has a cylindrical tip received in the socket and providing fluid tightness together with the walls.
- the vane is rigidly attached to the housing but is thinner than its cylindrical tip, thus allowing for rocking motion within the socket.
- the socket has an opening with two rounded lips receiving the vane therebetween and providing therewith the fluid tightness.
- the socket has a wider cavity behind the lips such that the vane is able to rock in the socket.
- the vane may have parallel walls providing, at variable angles of rocking, variable fluid tightness.
- the protrusions may be elastic, or vane thickness may vary along vane length, thereby providing, at variable angles of rocking, approximately uniform fluid tightness.
- the socket has an opening formed as a swivel cylindrical joint allowing sliding of the vane, of uniform thickness, through the joint and rocking of the vane together with the joint.
- the socket has parallel walls and the end of vane received in the socket matches the clearance between the parallel walls, but the vane is not rigidly attached to the housing.
- the vane may be attached to said housing by a hinge, or may be made flexible, so as to bend when the rotor orbits within the housing.
- the parallel walls conjoin the peripheral surface along a smooth curve allowing the vane to bend smoothly.
- the inventive design affords two major advantages.
- the first is the ability to position the pump/motor inlet and outlet in closer proximity to each other, and thus reduce the rotational angle at which the rotor and cylinder are not in scrolling contact.
- the second advantage is that the rotor is balanced when exposed to fluid pressure, as the sealing between the vane and the rotor occurs at the rotor periphery.
- the fluid pressure applies a force directed through the rotor center, resulting in negligible force between the vane and the rotor socket, as opposed to prior art rotors, where the protruding vane is exposed to pressure, which urges the vane against its socket, creating friction.
- An additional advantage of the vane extending inwards from the housing is the structural compactness obtained with pumps that employ long vanes.
- the rotary vane pump or motor comprises a sealing barrier disposed between the rotor periphery and the inner peripheral wall, preferably adjacent to the inlet port or to the outlet port.
- the barrier is adapted to prevent fluid communication between the inlet port and the outlet port when the scroll zone is over the inlet port or the outlet port or between them.
- a second sealing barrier is disposed adjacent to the other port.
- the sealing barrier may be made of compliant material and attached to the inner peripheral wall or to the rotor periphery. Alternatively, it may be formed as cooperating teeth on the inner peripheral wall and on the rotor peripheral surface.
- the sealing barrier may be formed as an integral detail with the lips at the socket opening.
- the rotary vane pump is used in a pumping apparatus, coupled to a drive unit with an eccentric drive member adapted to drive the rotor.
- the pump is attachable to and detachable from the drive unit, the two units being constructed so that attaching the pump to the drive unit results in engagement of the rotor to the eccentric drive member.
- the pumping apparatus includes attachment means allowing simple manipulation without tools.
- the rotor has a concentric socket
- the eccentric drive member comprises an eccentric crank adapted to fit rotatably, by a bearing, into the concentric socket when the pump is attached to the drive unit
- the housing has a sealed opening allowing the crank to enter the concentric socket.
- the crank has a tapered head with such diameter and eccentricity that it can enter the concentric socket irrespective of the alignment between the socket and the crank before the attaching.
- the rotary vane pump is preferably made of materials suitable for its usage as a disposable unit, such as plastic.
- a pumping apparatus constructed of two main components is provided: a permanent drive unit, which contains all the costly components, and a low-cost disposable pump unit, which comes in contact with the pumped media, and is easily and quickly replaceable.
- the disposable pump unit contains all the pump parts which are subjected to high rate of wear or contamination, such that its replacement results in a complete pumping apparatus which is as good as new with respect to wear and cleanliness.
- the rotary vane pump of the present invention may further comprise a bypass channel, preferably integral with the housing, with an inlet in communication with the inlet port, an outlet in communication with the outlet port, and a one-way valve disposed between the inlet and the outlet so as to allow fluid flow bypassing said pump chamber, thereby improving flow uniformity, while the rotary vane pump is pulsating when pumping.
- the pump may further comprise a pulsation damper with an air chamber, connected to the outlet, adapted for damping the pressure ripple present at the rotary vane pump outlet.
- FIG. 1 is a schematic cross sectional view of a single vane pump in accordance with a preferred embodiment of the present invention, coupled with a pulsation damper and a by-pass valve;
- Fig. 2 is a schematic cross sectional view of the single vane pump of Fig. 1, with the rotor in registration with the vicinity of the fluid inlet and outlet ports.
- Fig. 3 is a cross sectional view of the single vane pump of Fig. I 5 showing the attachment and coupling of the pump to the drive unit and the eccentric drive member;
- Fig. 4 is a cross sectional view of the single vane pump of Fig. 3, showing the disassembly and decoupling of the pump from the drive unit and the eccentric drive member;
- Figs. 5 and 6 are cross sectional views of the single-vane pump in accordance with alternative embodiments of the present invention.
- Fig. 7 is a close-up of an embodiment where lips of the socket and a sealing barrier are integrated in one detail
- Fig. 8 is an embodiment of the present invention with a hinged vane
- Fig. 9 is an embodiment of the present invention with a flexible vane.
- the pumping apparatus 10 comprises a single vane pump 12 and a drive unit 14 detachably attached to each other.
- the pump 12 includes a housing 16 with a cylindrical cavity, and a cylindrical rotor 20 disposed eccentrically in the cavity of the housing so as to define a working chamber 18.
- the housing 16 has an inlet port 24 and an outlet port 26 communicating with the working chamber 18, and a radial vane 22 disposed between the ports 24 and 26. Ports 24 and 26 are opened at the inner peripheral wall 28 of the working chamber.
- the housing 16 includes a bypass channel 29 with an inlet 30 in communication with the inlet port 24, an outlet 32 in communication with the outlet port 26, and a one-way valve 34 between the inlet and the outlet.
- Two sealing barriers 35 are disposed at the peripheral wall 28, adjacent the inlet port 24, and the outlet port 26, respectively.
- the housing 16 has a central opening 36 at its wall 37 and a cover 38 closing the working chamber 18.
- the rotor 20 is disposed in the housing cavity in sliding contact with the cover 38 and the wall 37, sealing the opening 36 by means of a ring seal 40.
- the rotor 20 has a radial socket 41 with two rounded lips 42 at its opening engaging the vane 22 so that it can slide within radial socket 41. Lips 42 are at all times in contact with both sides of vane 22, in a sealing fit.
- Vane 22 has varying thickness, for maintaining contact with both lips 42, yet allowing for free movement of rotor 20. Vane 22 and the socket 41 thus constitute a joint providing both sliding and rocking.
- Rotor 20 further has a central socket 44 facing the opening 36.
- Drive unit 14 has a rotary shaft 50 with an eccentric crank 52 equipped with a bearing 54.
- crank 52 is received by central socket 44 and shaft 50 is coaxial with the cylindrical cavity of the housing 16.
- the radial geometrical relationship between drive unit 14, eccentric crank 52, rotor 20 and diameter of the cylinder pump chamber 18 is such that rotation of rotary shaft 50, via the crank 52, causes rotor 20 to scroll the inner peripheral wall 28, maintaining contact or near-contact with the wall at scroll zone 56. Due to the vane-and-socket joint of rotor 20 to the housing 16, where rotor 20 is confined to vane 22 by means of vane socket 41, the rotor performs simultaneously a reciprocating motion parallel to the vane socket, and a transverse rocking motion (an orbital motion).
- rotor 20 and housing 16 define two separate and variable volumes: an expanding inlet chamber 58 and a contracting outlet chamber 60.
- Expanding chamber 58 is defined between the inlet side of the vane 22, a portion of the peripheral wall 28 between the inlet port 24 and the scroll zone 56, and an adjacent portion of the rotor's periphery.
- Contracting chamber 60 is defined between outlet side of the vane 22, the remaining portion of the peripheral wall 28 between the outlet port 26 and the scroll zone 56, and the remaining portion of the rotor's periphery.
- scroll zone 56 When the eccentric crank 52 rotates counterclockwise (see Fig. 1), scroll zone 56 also travels counterclockwise, and expanding chamber 58 expands, thereby drawing or suctioning fluid from inlet 30, through inlet port 24. At the same time, contracting chamber 60 contracts, discharging the fluid through outlet port 26 to outlet 32.
- scroll zone 56 In the position shown in Fig. 2, scroll zone 56 is in registration with vane 22 so that contracting chamber 60 has vanished while expanding chamber 58 has attained its maximal volume, after which it starts contracting and becomes the contracting chamber, while at the same time a "new" expanding chamber is born.
- rotor 20 In the position of Fig. 2, rotor 20 is in contact with the sealing barriers 35, thereby sealing off possible communication between inlet port 24 and outlet port 26 around rotor 20.
- Barriers 35 are made of elastic material, such as rubber, such that they are deflected by rotor 20 as it scrolls by them.
- pressurized fluid from outlet port 26 could flow around rotor 20 back to inlet port 24. This undesirable reverse flow is traditionally prevented by use of a one-way valve at the outlet port. Sealing barriers 35 perform an equivalent function, preventing fluid back flow from the outlet port 26 to the inlet port 24, without the negative effects, which valves introduce.
- fluid backflow may be prevented also by a single sealing barrier 35.
- the single barrier should provide the sealing of a slightly wider gap. For example, if the left barrier in Fig. 2 is removed, the remaining right barrier 35 must keep the gap between the rotor 20 and the inner wall 28 sealed until the scroll zone 56 reaches a point to the left of the inlet port 24.
- any barrier suitably disposed between the rotor 20 and the inner peripheral wall 28, may perform the function of blocking off the backflow path from outlet port 26 to inlet port 24.
- the barriers may be disposed on the rotor periphery opposite ports 24 and 26, as shown in Fig. 5.
- a labyrinth barrier 43 shown in the close-up of Fig. 2, may be formed as cooperating teeth on the inner peripheral wall and on the rotor peripheral surface.
- the bypass one-way valve 34 is optional. It is made of resilient material, such as rubber, which may deflect under pressure differential applied thereto, permitting fluid to flow from inlet 30 to outlet 32. Thus, continuous flow of fluid may be maintained also at the time when expanding chamber 58 and contracting chamber 60 are not displacing fluid.
- the single vane pump 10 is shown assembled with an additional pulsation damper 64 which in this embodiment is a trapped air reservoir with fluid outlet 66.
- Damper 64 absorbs and dampens pressure ripple or fluctuations resultant from the cyclic nature of the fluid displacement in the single vane pump 10.
- Trapped air 68 expands and contracts in response to pressure fluctuations of the fluid at outlet 32, enhancing, together with by-pass valve 34, stable and uniform flow and pressure of the pumped fluid at outlet 66.
- Fig. 3 illustrates pump 12 of the pumping apparatus 10, attached to the drive unit 14, with the rotor 20 coupled to eccentric crank 52, via bearing 54.
- the pump is retained in place by wing nuts 70, which are manually screwed and tightened on threaded studs 72 anchored in drive unit 14.
- Drive unit 14 has a protrusion 74 mated to recess 76 in housing 16 such that pump 12 is keyed in proper relation to drive unit 14.
- Fig. 4 illustrates pump 12 detached from drive unit 14, with wing nuts 70 removed from threaded studs 72.
- Cover 38 may be an integral part of pump 12 permanently attached to housing 16, or it may be separate from housing 16.
- Eccentric crank 52 has a tapered head 78 facilitating the insertion of the crank 52 into the socket 44 of rotor 20.
- the diameter of tapered head 78 and eccentricity of the crank 52 are selected so that tapered head 78 can enter into crank socket 44 while the pump is being attached to the drive unit, irrespective of the alignment of the socket 44 and crank 52.
- the crank eccentricity is preferably less than one-fourth of the crank head diameter (the latter is presumed equal to the socket 44 diameter).
- the rotary vane pump of the present invention can be easily adapted for disposable use in the chemical, medical and food industries, where the required process cleanliness necessitates frequent pump cleaning or replacement.
- the pump is made of low-cost materials suitable for its usage as a disposable unit, such as plastic.
- the described structure of the vane-and-socket connection allows simple pump fabrication from molded components.
- the pump parts which come in contact with the pumped media are cheap and easily and quickly replaceable by a simple manipulation, without using any tools.
- the disposable pump unit advantageously contains all the pump parts that are subject to high rate of wear and contamination, while the permanent drive unit, including the eccentric crank with the bearing, contains all costly components.
- the replacement of the disposable pump unit results in a complete pumping apparatus which is as good as new with respect to wear and cleanliness.
- the vane-and-socket joint in the pump or motor of the present invention may be designed in a number of various ways, as shown in Figs. 5 and 6.
- the vane 22 is made flat, while socket 41 is equipped with swivel jaws 82 forming a swivel joint at the opening of the socket.
- Swivel jaws 82 form a channel of uniform width, mated to vane 22 so that the vane can slide across the swivel while rotor 20 orbits.
- vane 22 may be made with an enlarged cylindrical tip 80, while the vane socket 41 has parallel walls allowing sliding of tip 80 and rocking of rotor 20.
- vane 22 in the embodiment shown in Fig.l may be simplified to have parallel walls if a high degree of fluid tightness is not required.
- lips 42 may be made of elastic material. As shown in Fig. 7, - l i ⁇
- Figs. 8 and 9 show other possible embodiments of the present invention - vane 84 with hinge 86, and flexible vane 88 with rounded socket entrance 90. Such vanes may be made only to slide in a narrow socket 91, without rocking therein, for better fluid
Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/559,382 US20060228245A1 (en) | 2003-06-18 | 2004-05-24 | Single-vane rotary pump or motor |
JP2006516793A JP2006527818A (en) | 2003-06-18 | 2004-05-24 | Single vane rotary pump or motor |
CA002527268A CA2527268A1 (en) | 2003-06-18 | 2004-05-24 | Single-vane rotary pump or motor |
DE602004003814T DE602004003814T2 (en) | 2003-06-18 | 2004-05-24 | ROTARY PISTON OR ENGINE WITH A SINGLE WING |
EP04734594A EP1633980B1 (en) | 2003-06-18 | 2004-05-24 | Single-vane rotary pump or motor |
US11/979,162 US20080063552A1 (en) | 2003-06-18 | 2007-10-31 | Single-vane rotary pump or motor |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB0314231A GB2402975A (en) | 2003-06-18 | 2003-06-18 | Rotary single vane pump with simplified vane-and-socket joint |
GB0314231.2 | 2003-06-18 | ||
IL160096A IL160096A (en) | 2003-06-18 | 2004-01-28 | Single-vane rotary pump or motor |
IL160096 | 2004-01-28 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/979,162 Division US20080063552A1 (en) | 2003-06-18 | 2007-10-31 | Single-vane rotary pump or motor |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004111455A1 true WO2004111455A1 (en) | 2004-12-23 |
Family
ID=33554155
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/IL2004/000448 WO2004111455A1 (en) | 2003-06-18 | 2004-05-24 | Single-vane rotary pump or motor |
Country Status (9)
Country | Link |
---|---|
US (2) | US20060228245A1 (en) |
EP (1) | EP1633980B1 (en) |
JP (1) | JP2006527818A (en) |
AT (1) | ATE348957T1 (en) |
AU (1) | AU2004201396C1 (en) |
CA (1) | CA2527268A1 (en) |
DE (1) | DE602004003814T2 (en) |
ES (1) | ES2279371T3 (en) |
WO (1) | WO2004111455A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100310401A1 (en) * | 2008-02-18 | 2010-12-09 | Kim Tiow Ooi | Revolving vane compressor and method for its manufacture |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB0419848D0 (en) * | 2004-09-07 | 2004-10-13 | Carbonate Ltd | Pumps |
WO2015147744A1 (en) * | 2014-03-28 | 2015-10-01 | Nanyang Technological University | A vane-slot mechanism for a rotary vane machine |
EP3067528B1 (en) * | 2015-03-13 | 2018-04-25 | Inergy Automotive Systems Research (Société Anonyme) | Pump for a fluid |
DE102017003783A1 (en) * | 2017-04-20 | 2018-10-25 | Wabco Gmbh | Device for connecting an air compressor with a drive motor and compressed air compressor |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
BE350273A (en) * | ||||
FR656320A (en) * | 1928-06-22 | 1929-05-06 | A Marty Et E Cauvet Ets | Pump |
FR980766A (en) * | 1943-02-26 | 1951-05-17 | Oscillating Allergies Pump | |
US3081022A (en) * | 1959-02-02 | 1963-03-12 | Amanda Ann Michie | Rotary compressor |
FR1346509A (en) * | 1962-11-27 | 1963-12-20 | Mechanical device intended for the suction and delivery or compression of fluids | |
FR1478849A (en) * | 1966-05-05 | 1967-04-28 | Improvements to pumps | |
DE2262574A1 (en) * | 1972-12-21 | 1974-06-27 | Theisen Alois | SELF-PRIMING ROTARY LISTON PUMP |
US5762480A (en) * | 1996-04-16 | 1998-06-09 | Adahan; Carmeli | Reciprocating machine |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2639670A (en) * | 1948-09-18 | 1953-05-26 | Economy Faucet Company | Liquid pump |
GB926495A (en) * | 1961-12-19 | 1963-05-22 | Bernard Henry Refson | Improvements in or relating to rotary pumps |
US3116012A (en) * | 1962-04-03 | 1963-12-31 | August Pablo | Machine capable of operating as compressor and pump |
US3291059A (en) * | 1964-06-08 | 1966-12-13 | Ladish Co | Rotary pumps |
JP3622216B2 (en) * | 1993-12-24 | 2005-02-23 | ダイキン工業株式会社 | Swing type rotary compressor |
DE19857560A1 (en) * | 1997-12-23 | 1999-06-24 | Luk Fahrzeug Hydraulik | Pump unit without own bearing |
US6499964B2 (en) * | 2001-03-16 | 2002-12-31 | Visteon Global Technologies, Inc. | Integrated vane pump and motor |
-
2004
- 2004-04-05 AU AU2004201396A patent/AU2004201396C1/en not_active Ceased
- 2004-05-24 US US10/559,382 patent/US20060228245A1/en not_active Abandoned
- 2004-05-24 DE DE602004003814T patent/DE602004003814T2/en not_active Expired - Fee Related
- 2004-05-24 WO PCT/IL2004/000448 patent/WO2004111455A1/en active IP Right Grant
- 2004-05-24 AT AT04734594T patent/ATE348957T1/en not_active IP Right Cessation
- 2004-05-24 EP EP04734594A patent/EP1633980B1/en not_active Not-in-force
- 2004-05-24 JP JP2006516793A patent/JP2006527818A/en active Pending
- 2004-05-24 CA CA002527268A patent/CA2527268A1/en not_active Abandoned
- 2004-05-24 ES ES04734594T patent/ES2279371T3/en active Active
-
2007
- 2007-10-31 US US11/979,162 patent/US20080063552A1/en not_active Abandoned
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
BE350273A (en) * | ||||
FR656320A (en) * | 1928-06-22 | 1929-05-06 | A Marty Et E Cauvet Ets | Pump |
FR980766A (en) * | 1943-02-26 | 1951-05-17 | Oscillating Allergies Pump | |
US3081022A (en) * | 1959-02-02 | 1963-03-12 | Amanda Ann Michie | Rotary compressor |
FR1346509A (en) * | 1962-11-27 | 1963-12-20 | Mechanical device intended for the suction and delivery or compression of fluids | |
FR1478849A (en) * | 1966-05-05 | 1967-04-28 | Improvements to pumps | |
DE2262574A1 (en) * | 1972-12-21 | 1974-06-27 | Theisen Alois | SELF-PRIMING ROTARY LISTON PUMP |
US5762480A (en) * | 1996-04-16 | 1998-06-09 | Adahan; Carmeli | Reciprocating machine |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100310401A1 (en) * | 2008-02-18 | 2010-12-09 | Kim Tiow Ooi | Revolving vane compressor and method for its manufacture |
US8905737B2 (en) * | 2008-02-18 | 2014-12-09 | Nanyang Technological Univerity | Revolving vane compressor and method for its manufacture |
Also Published As
Publication number | Publication date |
---|---|
ATE348957T1 (en) | 2007-01-15 |
EP1633980A1 (en) | 2006-03-15 |
DE602004003814D1 (en) | 2007-02-01 |
EP1633980B1 (en) | 2006-12-20 |
DE602004003814T2 (en) | 2007-10-11 |
AU2004201396C1 (en) | 2005-04-14 |
CA2527268A1 (en) | 2004-12-23 |
US20080063552A1 (en) | 2008-03-13 |
US20060228245A1 (en) | 2006-10-12 |
JP2006527818A (en) | 2006-12-07 |
ES2279371T3 (en) | 2007-08-16 |
AU2004201396B1 (en) | 2004-08-05 |
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