US20020068001A1 - Rotary hydraulic vane pump with improved undervane porting - Google Patents
Rotary hydraulic vane pump with improved undervane porting Download PDFInfo
- Publication number
- US20020068001A1 US20020068001A1 US09/728,348 US72834800A US2002068001A1 US 20020068001 A1 US20020068001 A1 US 20020068001A1 US 72834800 A US72834800 A US 72834800A US 2002068001 A1 US2002068001 A1 US 2002068001A1
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- United States
- Prior art keywords
- rotor
- pressure
- undervane
- fluid
- housing
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- 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.)
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Classifications
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- 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
- F01C21/0854—Vane tracking; control therefor by fluid means
- F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
Definitions
- This invention relates to hydraulic power converting machines and more particularly to a new and improved multi-vane rotor pump for industrial or power steering use featuring improved undervane hydraulic fluid pressure porting for optimizing undervane pressurization for urging the vanes into operative engagement with the cam surface of an outer cam ring for improving pump operations.
- the present invention provides a new and improved pump which has improved pumping efficiency.
- This invention incorporates straight forward and simplified vane pressurization porting in the pressure plates that can be readily manufactured by a wide range of processes and equipment including economical stamping and casting.
- a cam ring sandwiched between pressure and thrust plates hydraulically separates the pressure plate from the thrust plate to improve routing of hydraulic pressure fluid to the undervane via special openings in the pressure plate augmenting vane sealing operation.
- this invention with its improved pressure plate porting for undervane pressurization can be easily employed with a wide range of hydraulic vane pumps including those currently embodied in automotive application as well as transverse compact pumps and hydraulically balanced pump rotors such as disclosed in U.S Pat. No. 6,050,796 issued to Wong et al. on Apr. 18, 2000 for Vane Pump and hereby incorporated by reference.
- a cam ring sandwiched between pressure and thrust plates blocks flow from the discharge ports in the pressure plate to the discharge ports in the thrust plate (and thereby to the pump discharge) to improve pressure routing to the undervane via special inner openings in the pressure plate.
- hydraulic discharge from the pressure plate is primarily through a radial outer port to a sealed undervane pressure chamber at the outboard side of the rotor assembly. Pressure fluid is fed from this side chamber to a pair of interior rotor balancing chambers on opposite sides of the rotor which are hydraulically connected by the undervane passages. With the balancing chambers and the undervane pressurized, the radially extending vanes will be biased by the undervane pressure fluid into operative fluid sealing engagement with the cam surface of the surrounding cam ring.
- this invention provides improved volumetric efficiency through better sealing between thrust and pressure plates and the rotor sandwiched therebetween.
- FIG. 1 is a cross -sectional view of a power steering pump
- FIG. 2 is a pictorial view of the internal vaned pump assembly of FIG. 1;
- FIG. 3 is a side view taken generally along the sight lines 3 - 3 of FIG. 1;
- FIG. 4 is a pictorial view of the rotor of FIGS. 1 and 2;
- FIG. 5 is a pictorial fragmented view of a portion of the pressure plate, the rotor and associated vane of FIGS. 1 - 4 ;
- FIGS. 6 and 7 are interior side views of the pressure and thrust plates respectively taken generally along sight line 6 - 6 and 7 - 7 respectively of FIG. 1;
- FIG. 8 is a side view of another hydraulic balanced rotor for this invention.
- FIG. 1 a power steering pump 10 for an automotive vehicle having a housing 12 defining a substantially cylindrical inner space 14 closed by an end cap 16 .
- the inner space 14 is sized to accommodate a generally cylindrical vaned pump assembly or rotating group 17 and is supplied with hydraulic fluid through an inlet 19 .
- the pump assembly 17 comprises a thrust plate 18 , a cam ring 20 , a pressure plate 22 and a multi-vaned pump rotor 26 mounted within the cam ring 20 and sandwiched between the disc-like thrust and pressure plates.
- the end cap 16 is secured in the housing by a retaining ring 28 expanding into an internal annular groove at the outer end of the cylindrical space formed in the housing.
- the thrust plate 18 , cam ring 20 and the pressure plate 22 are maintained in fixed axial and angular alignment by a pair of elongated pins or screws 30 which extend through openings 29 , 31 , 33 respectively in these components from anchorage openings in the housing 12 and the end cap 16 .
- the rotor 26 is a generally cylindrical unit that is rotatably supported within the cam ring 20 and is formed with a plurality of vane slots 34 . These vane slots extend transversely through the rotor and radiate from a circular arrangement of undervane passages 36 passages arranged in a circular pattern on the cylindrical body of the rotor.
- the undervane passages 36 also extend transversely through the rotor and are adapted to receive the hydraulic fluid that exerts an outward directed and spring-like radial force imposed on the bottom surfaces 38 of the blade-like vanes 40 that are mounted for reciprocating movement in the vane slots as is known in this art. As best shown in FIG.
- the thrust plate 18 and the pressure plate 22 cooperate with the rotor, vanes and the cam ring to define the axial extent of the fluid chambers 46 formed between adjacent vanes 40 .
- the thrust plate 18 has a pair of diametrically opposed inlet ports 50 notched from the circumference of the body of the thrust plate and a pair of diametrically opposed discharge ports 52 .
- These thrust plate discharge ports extend through the thickness of the thrust plates and are in hydraulic communication with the pump discharge chamber 53 in housing 12 as diagrammatically shown in FIG. 1.
- the thrust plate is further formed with a centralized annular opening 54 to accommodate the reduced diameter and splined end 56 of an elongated input shaft 58 extending therethrough that supports and rotationally drives the rotor.
- the pressure plate 22 (FIGS. 2 and 6) has a pair of diametrically opposed inlet ports 60 notched in the periphery thereof which are axially aligned with the inlet ports 50 of the thrust plate.
- the pressure plate further has a pair of diametrically opposed undervane discharge ports 62 which are arcuately spaced from the inlet ports 60 that align with the discharge ports 52 of the thrust plate as diagrammatically shown in FIG. 1.
- the cam ring is solid in this area so that there is no flow of pressure from the pressure plate ports 62 to the thrust plate discharge ports as in many prior constructions. As will be further explained, this solid construction augments undervane pressurization.
- the discharge ports 62 of the pressure plate hydraulically communicates with an undervane fluid pressure chamber 66 formed outboard of the pump assembly between the pressure plate and the end cap 16 .
- Such communication is through the discharging pressure communication holes 67 extending axially from the discharge ports through the pressure plate body.
- the pressure chamber 66 formed to the outboard side of the rotor assembly hydraulically connects to the undervane passages 36 through the axially extending fluid feed passages 70 extending axially through the width of the pressure plate and located radially inward of the discharge holes 67 .
- feed passages 70 are preferably simple, straight through, fixed-diameter bores drilled or otherwise formed in the pressure plate as best shown in FIGS. 1 and 6 and function to discharge fluid directly into the outboard side chamber or pocket 72 of the rotor.
- This side chamber 72 is a pressure balance chamber formed between the pressure plate and concentric inner and outer annular lands 74 , 76 formed on the outboard side of the rotor as best shown in FIGS. 3 - 5 .
- the opposite or inboard side of the rotor has the same construction as the outboard side and cooperates with the thrust plate 18 to define an annular inboard side pressure balance chamber 78 . Accordingly both sides of the rotor are substantially the same in construction and the balancing chambers are interconnected by the undervane passages 36 so that pressure balance of the rotor may be achieved.
- the pressure plate feed ports or passages 70 are designed to feed pressure fluid from the outboard system pressure chamber 66 to charge the outboard side balance chamber 72 , the undervane passages 36 and the inboard side balance chamber 78 as defined by the concentric lands such as 74 and 76 .
- Pressure in the undervane passages 36 provides the radial spring force that urges the vanes 40 radially outwardly against the interior cam surface of the cam ring.
- the rotor 26 is rotatably driven about its rotational axis 80 by the elongated input shaft 58 that extends into the housing 12 and through the thrust plate and has it's inner end splined to drivingly fit the internal splined hub 82 of the rotor 26 .
- the rotor is axially retained on the input shaft by a snap ring 84 fitted in an end groove at the terminal end of the shaft 58 .
- the end cap 16 with the help of system pressure (when pump is operating) holds the pressure plate 22 , cam ring 20 and thrust plate 18 in the operative abutting relationship shown in FIG. 1.
- the inner and outer lands 74 , 76 on the sides of rotor act as sliding face seals cooperating with the flat internal faces of the pressure and thrust plates to form the opposing side face and pressure balancing chambers 72 , 78 with improved internal fluid sealing between these pump components.
- the chambers 46 between the adjacent vanes 40 will expand as they take in fluid from chamber 14 through the axially aligned inlet ports 60 , 50 of the pressure and thrust plates.
- the vane chambers 46 contract when discharging fluid into the axially aligned discharge ports 52 and 62 of the pressure and thrust plates.
- the pump effectively pumps hydraulic fluid into the discharge chamber 53 and to the power steering gear 83 or other accessory through a pressure regulating valve 81 operatively mounted in chamber 85 .
- the varying fluid volumes under the reciprocating vanes will be exchanged in accordance with vane position during pump operation so that the undervane passages remain full of pressure oil during pump operation.
- FIG. 8 illustrates another preferred hydraulically balanced rotor 110 which can be used in place of rotor 26 .
- the rotor 100 has inner annular land 102 and an outer land 104 generally serpentined in plan view. These lands define a side pressure balancing pocket 106 which connects to the undervane 108 at the end of each vane slot 110 .
- the reverse side of the rotor is the same as that shown so that equal balancing pockets are formed on opposite sides of the rotor which are connected to the undervane.
- This invention accordingly provides for improved undervane routing and pressurization without the complexities of the prior art arrangement of undervane slots and passages and their interconnection along with the requirement for making pressure and thrust plate pump components from powder metal and associated forming tools.
- the pump components of this invention such as the thrust and pressure plates can be made from more economical casting and stamping equipment.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
Description
- This invention relates to hydraulic power converting machines and more particularly to a new and improved multi-vane rotor pump for industrial or power steering use featuring improved undervane hydraulic fluid pressure porting for optimizing undervane pressurization for urging the vanes into operative engagement with the cam surface of an outer cam ring for improving pump operations.
- Prior to the present invention various rotary hydraulic vane pumps have been devised with minute and complex hydraulic systems of interconnected pockets, passages and orifices in pump components including the thrust and pressure plates thereof to provide discrete flow paths for coupling the undervane passages with a pump discharge chamber. The hydraulic fluid in the undervane passages is pressurized on pump operation so that the pressurized undervane acts as a hydraulic spring for pump priming and pump operational purposes. More particularly the pressurized undervane fluid acts as a spring to exert a yieldable radial force on the vanes, mounted for reciprocal movement in associated vane slots, to maintain the fluid sealing contact of the tips of the vanes with the associated cam surface during pumping operation.
- Examples of such undervane constructions are illustrated and described in U.S. Pat. No. 3,207,077 issued Sep. 21, 1965 to P. B. Zeigler et al for Pump and Pat No. 4,386,891 issued Jun. 7, 1983 to R. P. Riefel et al for Rotary Hydraulic Vane Pump With Undervane Passages For Priming.
- While such prior art hydraulic pumps have generally met their objectives in providing improved pumping for power steering and other applications, more efficient and effective pumps are needed to meet higher pumping efficiency standards. Moreover, manufacture of prior art pressure and thrust plates with their special and intricately interconnected fluid pockets are difficult and costly. Even with particular attention to detail and care, such construction cannot be readily accomplished by economical manufacturing processes such as casting and stamping operations. Generally such designs require the employment of complex powder metal forming tools and precise machining. Such tooling and procedures makes thrust and pressure plates expensive to produce, particularly where limited quantities are needed
- In contrast to the prior art constructions, the present invention provides a new and improved pump which has improved pumping efficiency. This invention incorporates straight forward and simplified vane pressurization porting in the pressure plates that can be readily manufactured by a wide range of processes and equipment including economical stamping and casting. Preferably in this invention a cam ring sandwiched between pressure and thrust plates hydraulically separates the pressure plate from the thrust plate to improve routing of hydraulic pressure fluid to the undervane via special openings in the pressure plate augmenting vane sealing operation. Furthermore, this invention with its improved pressure plate porting for undervane pressurization can be easily employed with a wide range of hydraulic vane pumps including those currently embodied in automotive application as well as transverse compact pumps and hydraulically balanced pump rotors such as disclosed in U.S Pat. No. 6,050,796 issued to Wong et al. on Apr. 18, 2000 for Vane Pump and hereby incorporated by reference.
- Preferably in this invention, a cam ring sandwiched between pressure and thrust plates blocks flow from the discharge ports in the pressure plate to the discharge ports in the thrust plate (and thereby to the pump discharge) to improve pressure routing to the undervane via special inner openings in the pressure plate. More particularly, hydraulic discharge from the pressure plate is primarily through a radial outer port to a sealed undervane pressure chamber at the outboard side of the rotor assembly. Pressure fluid is fed from this side chamber to a pair of interior rotor balancing chambers on opposite sides of the rotor which are hydraulically connected by the undervane passages. With the balancing chambers and the undervane pressurized, the radially extending vanes will be biased by the undervane pressure fluid into operative fluid sealing engagement with the cam surface of the surrounding cam ring.
- It is a feature object and advantage of this invention to provide a new and improved rotary vane pump with a flattened pressure plate formed with at least one discharge port for feeding only a side chamber in the pump housing and at least one undervane feed port leading from the side chamber to opposing pressure balancing side chambers of the rotor so that all undervane passages will be pressurized to effect an outward force on the vanes therein for improved engagement of the vanes with an associated outer cam ring.
- With the present invention, mechanical noises heretofore generated by some vane pumps will be sharply reduced by the elimination of the arcuate and segmented undervane grooves or other configured undervane recesses or quadrants that may be arranged in various geometric patterns in the faces of the pressure and thrust plates adjacent to the inner ends of the vane slots formed in the pump rotor. These grooves at times formed unintended contact points for any vane tipping in its respective vane groove and projecting out of the side of the rotor. Contact with such grooves by the corner or other parts of the vane resulted in objectionable ratcheting or ticking noises.
- In addition to sharply reduced manufacturing costs and reduced noise generation this invention provides improved volumetric efficiency through better sealing between thrust and pressure plates and the rotor sandwiched therebetween.
- These and other objects and advantages of the present invention will be more apparent from the following detailed description and drawings in which:
- FIG. 1 is a cross -sectional view of a power steering pump;
- FIG. 2 is a pictorial view of the internal vaned pump assembly of FIG. 1;
- FIG. 3 is a side view taken generally along the sight lines3-3 of FIG. 1;
- FIG. 4 is a pictorial view of the rotor of FIGS. 1 and 2;
- FIG. 5 is a pictorial fragmented view of a portion of the pressure plate, the rotor and associated vane of FIGS.1-4;
- FIGS. 6 and 7 are interior side views of the pressure and thrust plates respectively taken generally along sight line6-6 and 7-7 respectively of FIG. 1; and
- FIG. 8 is a side view of another hydraulic balanced rotor for this invention.
- Referring now in greater detail to the drawings, there is shown in FIG. 1 a
power steering pump 10 for an automotive vehicle having ahousing 12 defining a substantially cylindricalinner space 14 closed by anend cap 16. Theinner space 14 is sized to accommodate a generally cylindrical vaned pump assembly or rotatinggroup 17 and is supplied with hydraulic fluid through aninlet 19. Thepump assembly 17 comprises athrust plate 18, acam ring 20, apressure plate 22 and amulti-vaned pump rotor 26 mounted within thecam ring 20 and sandwiched between the disc-like thrust and pressure plates. - The
end cap 16 is secured in the housing by aretaining ring 28 expanding into an internal annular groove at the outer end of the cylindrical space formed in the housing. Thethrust plate 18,cam ring 20 and thepressure plate 22 are maintained in fixed axial and angular alignment by a pair of elongated pins orscrews 30 which extend throughopenings housing 12 and theend cap 16. - The
rotor 26 is a generally cylindrical unit that is rotatably supported within thecam ring 20 and is formed with a plurality ofvane slots 34. These vane slots extend transversely through the rotor and radiate from a circular arrangement ofundervane passages 36 passages arranged in a circular pattern on the cylindrical body of the rotor. Theundervane passages 36 also extend transversely through the rotor and are adapted to receive the hydraulic fluid that exerts an outward directed and spring-like radial force imposed on thebottom surfaces 38 of the blade-like vanes 40 that are mounted for reciprocating movement in the vane slots as is known in this art. As best shown in FIG. 3 the outer tips of the blades sealingly engage theinner cam surface 44 of the cam ring during pump operation. This vane engagement is effected by the centrifugal forces developed during rotor rotation and by the radial force exerted on the vanes by the undervane hydraulic pressure as the pump is being driven. With the tips operatively engaging the inner surface of the cam ring an endless series offluid pumping chambers 46 is formed between adjacent vane members. - The
thrust plate 18 and thepressure plate 22 cooperate with the rotor, vanes and the cam ring to define the axial extent of thefluid chambers 46 formed betweenadjacent vanes 40. As best shown in FIGS. 2 and 7, thethrust plate 18 has a pair of diametricallyopposed inlet ports 50 notched from the circumference of the body of the thrust plate and a pair of diametrically opposeddischarge ports 52. These thrust plate discharge ports extend through the thickness of the thrust plates and are in hydraulic communication with thepump discharge chamber 53 inhousing 12 as diagrammatically shown in FIG. 1. The thrust plate is further formed with a centralizedannular opening 54 to accommodate the reduced diameter and splinedend 56 of anelongated input shaft 58 extending therethrough that supports and rotationally drives the rotor. - The pressure plate22 (FIGS. 2 and 6) has a pair of diametrically
opposed inlet ports 60 notched in the periphery thereof which are axially aligned with theinlet ports 50 of the thrust plate. The pressure plate further has a pair of diametrically opposedundervane discharge ports 62 which are arcuately spaced from theinlet ports 60 that align with thedischarge ports 52 of the thrust plate as diagrammatically shown in FIG. 1. However, the cam ring is solid in this area so that there is no flow of pressure from thepressure plate ports 62 to the thrust plate discharge ports as in many prior constructions. As will be further explained, this solid construction augments undervane pressurization. More particularly, thedischarge ports 62 of the pressure plate hydraulically communicates with an undervane fluid pressure chamber 66 formed outboard of the pump assembly between the pressure plate and theend cap 16. Such communication is through the dischargingpressure communication holes 67 extending axially from the discharge ports through the pressure plate body. Moreover the pressure chamber 66 formed to the outboard side of the rotor assembly hydraulically connects to theundervane passages 36 through the axially extendingfluid feed passages 70 extending axially through the width of the pressure plate and located radially inward of thedischarge holes 67. - These
feed passages 70 are preferably simple, straight through, fixed-diameter bores drilled or otherwise formed in the pressure plate as best shown in FIGS. 1 and 6 and function to discharge fluid directly into the outboard side chamber orpocket 72 of the rotor. Thisside chamber 72 is a pressure balance chamber formed between the pressure plate and concentric inner and outerannular lands thrust plate 18 to define an annular inboard sidepressure balance chamber 78. Accordingly both sides of the rotor are substantially the same in construction and the balancing chambers are interconnected by theundervane passages 36 so that pressure balance of the rotor may be achieved. - The pressure plate feed ports or
passages 70 are designed to feed pressure fluid from the outboard system pressure chamber 66 to charge the outboardside balance chamber 72, theundervane passages 36 and the inboardside balance chamber 78 as defined by the concentric lands such as 74 and 76. Pressure in theundervane passages 36 provides the radial spring force that urges thevanes 40 radially outwardly against the interior cam surface of the cam ring. - The
rotor 26 is rotatably driven about itsrotational axis 80 by theelongated input shaft 58 that extends into thehousing 12 and through the thrust plate and has it's inner end splined to drivingly fit the internal splined hub 82 of therotor 26. The rotor is axially retained on the input shaft by asnap ring 84 fitted in an end groove at the terminal end of theshaft 58. - The
end cap 16 with the help of system pressure (when pump is operating) holds thepressure plate 22,cam ring 20 and thrustplate 18 in the operative abutting relationship shown in FIG. 1. The inner andouter lands pressure balancing chambers - When the
input shaft 58 is driven by the vehicle engine through a belt or other drive, thechambers 46 between theadjacent vanes 40 will expand as they take in fluid fromchamber 14 through the axially alignedinlet ports vane chambers 46 contract when discharging fluid into the axially aligneddischarge ports discharge chamber 53 and to thepower steering gear 83 or other accessory through apressure regulating valve 81 operatively mounted in chamber 85. The varying fluid volumes under the reciprocating vanes will be exchanged in accordance with vane position during pump operation so that the undervane passages remain full of pressure oil during pump operation. - FIG. 8 illustrates another preferred hydraulically
balanced rotor 110 which can be used in place ofrotor 26. Therotor 100 has innerannular land 102 and anouter land 104 generally serpentined in plan view. These lands define a sidepressure balancing pocket 106 which connects to theundervane 108 at the end of eachvane slot 110. The reverse side of the rotor is the same as that shown so that equal balancing pockets are formed on opposite sides of the rotor which are connected to the undervane. - This invention accordingly provides for improved undervane routing and pressurization without the complexities of the prior art arrangement of undervane slots and passages and their interconnection along with the requirement for making pressure and thrust plate pump components from powder metal and associated forming tools. Moreover, the pump components of this invention such as the thrust and pressure plates can be made from more economical casting and stamping equipment.
Claims (5)
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/728,348 US6422845B1 (en) | 2000-12-01 | 2000-12-01 | Rotary hydraulic vane pump with improved undervane porting |
EP01204246A EP1211421A3 (en) | 2000-12-01 | 2001-11-06 | Rotary hydraulic vane pump with hydraulic vane actuation |
JP2001368925A JP2002202072A (en) | 2000-12-01 | 2001-12-03 | Rotary fluid pressure vane pump for improving port structure of under vane |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/728,348 US6422845B1 (en) | 2000-12-01 | 2000-12-01 | Rotary hydraulic vane pump with improved undervane porting |
Publications (2)
Publication Number | Publication Date |
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US20020068001A1 true US20020068001A1 (en) | 2002-06-06 |
US6422845B1 US6422845B1 (en) | 2002-07-23 |
Family
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/728,348 Expired - Fee Related US6422845B1 (en) | 2000-12-01 | 2000-12-01 | Rotary hydraulic vane pump with improved undervane porting |
Country Status (3)
Country | Link |
---|---|
US (1) | US6422845B1 (en) |
EP (1) | EP1211421A3 (en) |
JP (1) | JP2002202072A (en) |
Cited By (6)
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US20110311387A1 (en) * | 2010-06-22 | 2011-12-22 | Gm Global Technoloby Operations, Inc. | High efficiency fixed displacement vane pump |
CN102619751A (en) * | 2011-09-08 | 2012-08-01 | 耐世特汽车系统(苏州)有限公司 | Oil feed channel of automobile steering pump and automobile steering pump |
US20130089456A1 (en) * | 2011-10-07 | 2013-04-11 | Steering Solutions Ip Holding Corporation | Cartridge Style Binary Vane Pump |
CN108026918A (en) * | 2015-09-11 | 2018-05-11 | Kyb株式会社 | Vane pump |
CN109611336A (en) * | 2017-10-05 | 2019-04-12 | 桂林航天工业学院 | A kind of rolling rotor compressor |
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DE10134474A1 (en) * | 2000-08-01 | 2002-02-14 | Luk Fahrzeug Hydraulik | Pump with flow regulation valve device and injector device has separate return line in induction region of rotation group inside pump |
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US6783334B2 (en) | 2002-05-31 | 2004-08-31 | Delphi Technologies, Inc. | Hydraulic pump reservoir having deaeration diffuser |
KR20040036973A (en) * | 2002-10-25 | 2004-05-04 | 엘지전자 주식회사 | Apparatus for reducing face pressor of enclossed compressor |
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US7086845B2 (en) * | 2003-01-23 | 2006-08-08 | Delphi Technologies, Inc. | Vane pump having an abradable coating on the rotor |
US6857863B1 (en) | 2003-12-18 | 2005-02-22 | Visteon Global Technologies, Inc. | Power steering pump |
US7425121B2 (en) * | 2004-03-25 | 2008-09-16 | Wood Gregory P | Rotary vane pump |
US7232139B2 (en) * | 2004-06-21 | 2007-06-19 | Cole Jeffrey E | Truck assembly for a skateboard, wheeled platform, or vehicle |
US7216876B2 (en) * | 2004-06-21 | 2007-05-15 | Cole Jeffrey E | Occupant-propelled fluid powered rotary device, truck, wheeled platform, or vehicle |
US7040638B2 (en) * | 2004-06-21 | 2006-05-09 | Jeffrey Eaton Cole | Occupant-propelled fluid powered rotary device, truck, wheeled platform, or vehicle |
US8561210B2 (en) * | 2004-11-01 | 2013-10-15 | Koninklijke Philips N.V. | Access to domain |
US7635136B2 (en) * | 2005-06-21 | 2009-12-22 | Jeffrey E. Cole | Truck assembly for a skateboard, wheeled platform, or vehicle |
US20100126023A1 (en) * | 2005-07-06 | 2010-05-27 | Mtd Products Inc. | Combination String Trimmer and Blower Tool |
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JP5395713B2 (en) * | 2010-01-05 | 2014-01-22 | 日立オートモティブシステムズ株式会社 | Vane pump |
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2000
- 2000-12-01 US US09/728,348 patent/US6422845B1/en not_active Expired - Fee Related
-
2001
- 2001-11-06 EP EP01204246A patent/EP1211421A3/en not_active Withdrawn
- 2001-12-03 JP JP2001368925A patent/JP2002202072A/en active Pending
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US20130089456A1 (en) * | 2011-10-07 | 2013-04-11 | Steering Solutions Ip Holding Corporation | Cartridge Style Binary Vane Pump |
CN108026918A (en) * | 2015-09-11 | 2018-05-11 | Kyb株式会社 | Vane pump |
CN109611336A (en) * | 2017-10-05 | 2019-04-12 | 桂林航天工业学院 | A kind of rolling rotor compressor |
CN115342015A (en) * | 2022-08-02 | 2022-11-15 | 常州市合达油泵有限公司 | Combined fuel pump |
Also Published As
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US6422845B1 (en) | 2002-07-23 |
JP2002202072A (en) | 2002-07-19 |
EP1211421A3 (en) | 2004-01-07 |
EP1211421A2 (en) | 2002-06-05 |
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