US20100119396A1 - Variable displacement dual vane pump - Google Patents

Variable displacement dual vane pump Download PDF

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Publication number
US20100119396A1
US20100119396A1 US12/594,277 US59427708A US2010119396A1 US 20100119396 A1 US20100119396 A1 US 20100119396A1 US 59427708 A US59427708 A US 59427708A US 2010119396 A1 US2010119396 A1 US 2010119396A1
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US
United States
Prior art keywords
vane
axis
series
vanes
pump
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.)
Abandoned
Application number
US12/594,277
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English (en)
Inventor
Chengyun Guo
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.)
SLW Automotive Inc
Original Assignee
SLW Automotive Inc
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 SLW Automotive Inc filed Critical SLW Automotive Inc
Priority to US12/594,277 priority Critical patent/US20100119396A1/en
Assigned to BORGWARNER INC. reassignment BORGWARNER INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GUO, CHENGYUN
Assigned to SLW AUTOMOTIVE INC. reassignment SLW AUTOMOTIVE INC. CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: BORGWARNER INC.
Publication of US20100119396A1 publication Critical patent/US20100119396A1/en
Abandoned legal-status Critical Current

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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
    • F04C2/34—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 the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—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 the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/348—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 the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the vanes positively engaging, with circumferential play, an outer rotatable 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis

Definitions

  • the present invention relates to sliding vane pumps; more particularly, the present invention relates to sliding vane pumps having a stacked integrated vane configuration.
  • Sliding vane pumps are commonly used to transfer fluid from an inlet port to an outlet port.
  • they have a ring which is eccentric, and an inner rotor; the inner rotor is typically fixed to and rotates with a shaft, and a series of vanes slide in and out of a set of vane slots.
  • the vanes will slide along the inner surface of the eccentric ring.
  • the eccentricity between the inner rotor and the eccentric ring can be varied to vary the amount of fluid that is displaced by the pump.
  • the present invention includes a variable displacement pump having an inner rotor rotatable about a first axis having at least two slots, with the slots substantially extending diametrically through the width of the inner rotor.
  • the present invention also includes at least two vanes, each located in a distinct one of said at least two slots.
  • the pump also has an outer rotor rotatable about a second axis and operably associated with the inner rotor.
  • the outer rotor has two or more recesses, each configured to receive one of said at least two vanes.
  • the pump also includes an expandable chamber formed by the outer rotor and the inner rotor, and an eccentric ring surrounding the outer rotor. Also included is a housing having an eccentric ring located within the housing for adjusting the relative relationship between the first axis and the second axis in order to vary the displacement of the pump.
  • FIG. 1 is a sectional side view of a sliding vane pump with the outer rotor aligned with the inner rotor, according to the present invention
  • FIG. 2 is a sectional side view of a sliding vane pump with the outer rotor offset from the inner rotor;
  • FIG. 3 is an exploded view of a sliding vane pump, according to the present invention.
  • FIG. 4 a perspective view of a vane used in a sliding vane pump, according to the present invention
  • FIG. 5 is a side view of a vane used in a sliding vane pump, according to the present invention.
  • FIG. 6 is a perspective view of a hub and inner rotor used in a sliding vane pump according to the present invention.
  • FIG. 7 is a perspective view of an alternate embodiment of a sliding vane pump with the cover and housing removed, according to the present invention.
  • FIG. 8 is a perspective view of a rotor used in an alternate embodiment of a sliding vane pump, according to the present invention.
  • FIG. 9 is an first exploded view of an alternate embodiment of a sliding vane pump, according to the present invention.
  • FIG. 10 is a second exploded view of an alternate embodiment of a sliding vane pump, according to the present invention.
  • a sliding vane pump according to the present invention is generally shown at 10 .
  • the pump 10 has an inner rotor 12 which rotates about a first axis 14 .
  • the inner rotor 12 also has a series of slots 16 for receiving a plurality of vanes 18 .
  • the vanes 18 have a first side 20 which is offset and parallel to a second side 22 .
  • the vanes 18 also have a third side 21 which is parallel to and equal in length compared to a fourth side 23 . Both the third side 21 and fourth side 23 serve as a flat engagement 24 .
  • the vane 18 also includes an extension 26 which is of a reduced width compared to the remainder of the vane 18 .
  • the pump 10 also has an outer rotor 28 which rotates about a second axis 30 , and has recesses 32 for receiving the flat engagements 24 of the vanes 18 .
  • the first side 20 being offset from the second side 22 creates an angle 27 between the flat engagements 24 and the first side 20 , as well as between the flat engagements 24 and the second side 22 .
  • the recesses 32 are in sliding contact with each of the flat engagements 24 .
  • An individual example of one of the vanes 18 is depicted in FIGS. 4 and 5 .
  • an eccentric ring 34 located within a housing 36 .
  • the housing 36 also includes an inlet port 40 for delivering fluid into the expandable chamber 38 , and an outlet port 42 for receiving fluid from the expandable chamber 38 .
  • There is also an inlet aperture 43 in fluid communication with the inlet port 40 where fluid is fed into the inlet port 40 via the inlet aperture 43 prior to being pumped by the pump 10 .
  • the eccentric ring 34 includes a flange 44 , a pivot hole 46 , and a pivot pin 47 received in the pivot hole 46 .
  • the pivot hole 46 and pivot pin 47 connect the eccentric ring 34 to the housing 36 , so as to allow the eccentric ring 34 to pivot about the pivot pin 47 .
  • the flange 44 is also connected to a bias mechanism such as a spring on one side, and a piston on the opposite side, such that force can be applied to the flange 44 , changing the eccentricity between the inner rotor 12 and the outer rotor 28 , the function of which will more clearly be described later.
  • the inner rotor 12 is affixed to, and driven by a hub 48 .
  • the inner rotor 12 turns and applies force to and drives the vanes 18 .
  • the flat engagement 24 of the first end 20 and the second end 22 then applies force to the recesses 32 of the outer rotor 28 .
  • the recesses 32 are located at an angle which is identical to the angle 27 of the vanes 18 , the recesses 32 are in flush contact with the flat engagements 24 , allowing the flat engagements 24 to apply force to the recesses 32 , and drive the outer rotor 28 .
  • the outer rotor 28 is allowed to rotate relative to the eccentric ring 34 because of a hydrodynamic journal bearing 50 located therebetween.
  • the hydrodynamic journal bearing 50 in this embodiment is a hydrodynamic film which minimizes friction between the outer rotor 28 and the eccentric ring 34 .
  • the hydrodynamic journal bearing 50 could also be a ball bearing, a type of grease, or any other device which would reduce friction between the outer rotor 28 and the eccentric ring 34 .
  • the pump 10 has the ability to vary the amount of fluid pumped from the inlet port 40 to the outlet port 42 .
  • the first axis 14 of the inner rotor 12 and the second axis 30 of the outer rotor 28 are aligned.
  • no fluid is transferred from the inlet port 40 to the outlet port 42 .
  • the eccentric ring 34 will pivot about the pivot pin 47 located in the pivot hole 46 .
  • the outer rotor 28 will move as well. The outer rotor 28 can be moved to a maximum position shown in FIG. 2 .
  • the amount of fluid in the expandable chamber 38 will reach a maximum volume, and then the expandable chamber 38 will begin to compress the fluid.
  • the expandable chamber 38 will compress the fluid between the vanes 18 even further as the inner rotor 12 and outer rotor 28 rotate, and the vanes 18 move across the outlet port 42 .
  • the contraction of the fluid between each of the vanes 18 will force the fluid through the outlet port 42 .
  • the flat engagement 24 of the vanes 18 are allowed to slide in the recesses 32 , while still transferring rotational force to the outer rotor 28 .
  • each vane 18 has an extension 26 formed as a portion of each vane 18 .
  • the width of each extension 26 is narrower than the overall width of the vane 18 .
  • Each extension 26 is also located in a different location along the width of the vane 18 . This allows the vanes 18 to “stack” together, allowing all the vanes 18 to be inserted into a corresponding slot 16 in the inner rotor 12 .
  • there are four vanes 18 : a first vane 52 , a second vane 54 , a third vane 56 , and a fourth vane 58 .
  • the extension 26 of the first vane 52 is adjacent to the extension 26 of the second vane 54
  • the extension 26 of the second vane 54 is adjacent to the extension 26 of the third vane 56
  • the extension 26 of the third vane 56 is adjacent to the extension 26 of the fourth vane 58 .
  • Each extension 26 is adjacent to one another, but will be at a different angle relative to one another because of each vane 18 being located in a corresponding slot 16 in the inner rotor 12 .
  • the present invention is not limited to having four vanes 18 , as described above.
  • the number of vanes 18 can be changed to suit any particular application requiring a sliding vane pump 10 of the present invention.
  • the width of each extension 26 is approximately 25% of the total width of each vane 18 . If more or less vanes 18 were used, the width of the extension 26 would change proportionately. For example, if six vanes were used, each extension would be 1 ⁇ 6 of the total width of the vane 18 ; if two vanes 18 were used, the width of each extension 26 would be half of the total width of the vane 18 .
  • the present invention has several advantages over other types of sliding vane pumps and articulated vane pumps.
  • the sliding vane pump 10 of the present invention has a lower number of vanes 18 , but still performs as effectively, and has higher volumetric efficiency.
  • the vanes 18 having the flat engagements 24 driving the outer rotor 28 in the manner described by the present invention reduces the amount of wear on the flat engagements 24 and the outer rotor 28 , the amount of contact stress on the vanes 18 is also reduced when compared to a conventional sliding vane pump.
  • the engagement between the flat engagements 24 of the vanes 18 and the recesses 32 also provides for the ability to prime the pump 10 at start up. This eliminates additional components such as guide rings and/or oil pressure, which are used to prime typical sliding vanes pumps.
  • the pump 10 of the present invention is also facilitates easier assembly during manufacturing, and is more packaging efficient.
  • the integrated structure of the vanes 18 also eliminates or reduces the centrifugal effect. Noise, vibration, and harshness (NVH) is improved because the vanes 18 are more dynamically balanced, and there is an increased resistance to contamination which can inhibit performance.
  • NDH Noise, vibration, and harshness
  • FIGS. 7-10 An alternate embodiment of the present invention is shown in FIGS. 7-10 , wherein like numbers refer to like elements.
  • the pump 10 shown in FIGS. 7-10 includes a straddle support inner rotor, generally shown at 60 .
  • the inner rotor 60 also includes a series of slots 62 .
  • the slots 62 of this embodiment differ from the first embodiment in that two of the slots 62 are elongated slots 64 , and two of the slots 62 are not elongated slots 66 .
  • the inner rotor 60 also includes two hub portions 68 , and a series of vane supports 70 , which are used to support a series of vanes.
  • two of the vanes are multi-piece vanes 76
  • two of the vanes are single piece vanes 78
  • the single piece vanes 78 are similar to the first vane 52 and fourth vane 58 , respectively, of the first embodiment.
  • the multi-piece vanes 76 are similar to the second vane 54 and third vane 56 , respectively, with the exception that the multi-piece vanes 76 are divided into two parts.
  • the extensions 26 are divided in half.
  • the multi-piece vanes 76 are inserted into the non-elongated slots 66 , and the single piece vanes 78 are inserted into the elongated slots 64 .
  • the function of the elongated slots 64 is to allow the single piece vanes 78 to be inserted through the inner rotor 60 . More specifically, the elongated slots 64 allow the widest part of the vane 78 to be inserted through the rotor 60 without being blocked by or receiving any interference from the extensions 26 of any of the other vanes.
  • the housing 36 will prevent the vanes from sliding out of the slots 62 because the inside surface of the housing 36 will be in sliding contact with each of the vanes.
  • the inner rotor 60 is supported on both sides of the vane supports 70 by the hub portions 68 ; this provides additional structural support and allows for an increased pressure capacity of the pump 10 .
  • the inner rotor 60 is driven by the shaft; the rotor 60 turns and applies force to the vanes, and the vanes in turn apply force to the recesses 32 , driving the outer rotor 60 in a similar manner compared to the previous embodiment.
  • the flange 44 is inserted into a recess 80 of a piston 82 .
  • the piston 82 includes a hollow portion 84 which receives a portion of a return spring 86 .
  • On the opposite side of the piston 82 is a flat portion 88 which receives pressure from fluid.

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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)
US12/594,277 2007-04-10 2008-04-10 Variable displacement dual vane pump Abandoned US20100119396A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US12/594,277 US20100119396A1 (en) 2007-04-10 2008-04-10 Variable displacement dual vane pump

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US92268307P 2007-04-10 2007-04-10
US12/594,277 US20100119396A1 (en) 2007-04-10 2008-04-10 Variable displacement dual vane pump
PCT/US2008/004616 WO2008124174A1 (en) 2007-04-10 2008-04-10 Variable displacement dual vane pump

Publications (1)

Publication Number Publication Date
US20100119396A1 true US20100119396A1 (en) 2010-05-13

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ID=39831294

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/594,277 Abandoned US20100119396A1 (en) 2007-04-10 2008-04-10 Variable displacement dual vane pump

Country Status (5)

Country Link
US (1) US20100119396A1 (ja)
EP (1) EP2150702A1 (ja)
JP (1) JP2010523896A (ja)
CN (1) CN101605995A (ja)
WO (1) WO2008124174A1 (ja)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120174619A1 (en) * 2010-07-08 2012-07-12 Panasonic Corporation Rotary compressor and refrigeration cycle apparatus
CN103321896A (zh) * 2012-03-22 2013-09-25 日立汽车系统株式会社 叶片泵
CN103321895A (zh) * 2012-03-22 2013-09-25 日立汽车系统株式会社 叶片泵
US8985984B2 (en) 2010-07-08 2015-03-24 Panasonic Intellectual Property Management Co., Ltd. Rotary compressor and refrigeration cycle apparatus
CN104903582A (zh) * 2012-12-27 2015-09-09 Vhit公司 可变排量叶片泵和调节其排量的方法
DE102015213099B3 (de) * 2015-07-13 2016-08-04 Joma-Polytec Gmbh Kunststoffrotor für Vakuumpumpe

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CN102788013B (zh) * 2011-05-19 2015-07-08 北汽福田汽车股份有限公司 变量泵、发动机及汽车
CN104295489B (zh) * 2013-07-15 2017-03-01 上海通用汽车有限公司 一种可变排量叶片泵
CN108825491B (zh) * 2018-06-26 2019-12-06 苏州理合文科技有限公司 一种节约汽车燃油的方法
CN108825494B (zh) * 2018-06-26 2019-12-06 海南葆润石油化工有限公司 一种石油化工用转子泵
CN109538466B (zh) * 2018-09-28 2020-04-10 浙江大学 高压多叶片泵
CN109441710B (zh) * 2018-09-28 2020-04-10 浙江大学 高性能多叶片马达
CN109538410B (zh) * 2018-09-28 2020-04-17 浙江大学 高速大扭矩多叶片马达
CN109469610B (zh) * 2018-09-28 2021-04-06 浙江大学 高性能多叶片泵
CN109441800B (zh) * 2018-09-28 2020-06-23 浙江大学 高压大流量变量叶片泵
CN109185040B (zh) * 2018-09-28 2020-02-07 浙江大学 一种高性能多叶片液压马达
CN109185125B (zh) * 2018-09-28 2020-02-07 浙江大学 高性能变量多叶片泵
CN109185039B (zh) * 2018-09-28 2020-04-10 浙江大学 一种高性能多叶片马达
CN111980914B (zh) * 2020-08-05 2022-04-08 宁波圣龙汽车动力系统股份有限公司 一种变排量双作用叶片泵

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US1719134A (en) * 1926-08-19 1929-07-02 Rotary Machine & Engineering C Rotary pump
US2127968A (en) * 1935-09-03 1938-08-23 Robert L Bailey Rotary steam engine
US3000324A (en) * 1958-10-06 1961-09-19 Rosaen Filter Co Vane for rotary pumps
US3065760A (en) * 1960-02-12 1962-11-27 Dimitrios J Cailas Stabilizing attachment for tank washing machines
US3158103A (en) * 1959-02-09 1964-11-24 Eickmann Karl Vane assembly in rotary fluid machines
US4342545A (en) * 1978-07-24 1982-08-03 General Motors Corporation Variable displacement pump
US4551079A (en) * 1982-09-28 1985-11-05 Plenty Limited Rotary vane pump with two axially spaced sets of vanes
US5100308A (en) * 1989-03-25 1992-03-31 Gebr. Becker Gmbh & Co. Vane pump with adjustable housing and method of assembly
US6022201A (en) * 1996-05-14 2000-02-08 Kasmer Hydristor Corporation Hydraulic vane pump with flexible band control
US6913446B2 (en) * 2001-04-03 2005-07-05 Visteon Global Technologies, Inc. Method for improving the efficiency of a variable displacement pump
US20060191360A1 (en) * 2003-11-08 2006-08-31 Gunther Beez Oscillating slide machine
WO2007039013A1 (de) * 2005-10-06 2007-04-12 Joma-Hydromechanic Gmbh Flügelzellenpumpe
WO2007101457A1 (de) * 2006-10-10 2007-09-13 Joma-Hydromechanic Gmbh Flügelzellenmaschine, insbesondere flügelzellenpumpe

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CN100557244C (zh) * 2001-04-05 2009-11-04 阿果技术公司 具有旋转凸轮环的变量泵
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Publication number Priority date Publication date Assignee Title
US1594035A (en) * 1923-01-08 1926-07-27 Austin F Burdick Rotary motor
US1719134A (en) * 1926-08-19 1929-07-02 Rotary Machine & Engineering C Rotary pump
US2127968A (en) * 1935-09-03 1938-08-23 Robert L Bailey Rotary steam engine
US3000324A (en) * 1958-10-06 1961-09-19 Rosaen Filter Co Vane for rotary pumps
US3158103A (en) * 1959-02-09 1964-11-24 Eickmann Karl Vane assembly in rotary fluid machines
US3065760A (en) * 1960-02-12 1962-11-27 Dimitrios J Cailas Stabilizing attachment for tank washing machines
US4342545A (en) * 1978-07-24 1982-08-03 General Motors Corporation Variable displacement pump
US4551079A (en) * 1982-09-28 1985-11-05 Plenty Limited Rotary vane pump with two axially spaced sets of vanes
US5100308A (en) * 1989-03-25 1992-03-31 Gebr. Becker Gmbh & Co. Vane pump with adjustable housing and method of assembly
US6022201A (en) * 1996-05-14 2000-02-08 Kasmer Hydristor Corporation Hydraulic vane pump with flexible band control
US6913446B2 (en) * 2001-04-03 2005-07-05 Visteon Global Technologies, Inc. Method for improving the efficiency of a variable displacement pump
US20060191360A1 (en) * 2003-11-08 2006-08-31 Gunther Beez Oscillating slide machine
WO2007039013A1 (de) * 2005-10-06 2007-04-12 Joma-Hydromechanic Gmbh Flügelzellenpumpe
WO2007101457A1 (de) * 2006-10-10 2007-09-13 Joma-Hydromechanic Gmbh Flügelzellenmaschine, insbesondere flügelzellenpumpe

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120174619A1 (en) * 2010-07-08 2012-07-12 Panasonic Corporation Rotary compressor and refrigeration cycle apparatus
US8985984B2 (en) 2010-07-08 2015-03-24 Panasonic Intellectual Property Management Co., Ltd. Rotary compressor and refrigeration cycle apparatus
US8985985B2 (en) * 2010-07-08 2015-03-24 Panasonic Intellectual Property Management Co., Ltd. Rotary compressor and refrigeration cycle apparatus
CN103321896A (zh) * 2012-03-22 2013-09-25 日立汽车系统株式会社 叶片泵
CN103321895A (zh) * 2012-03-22 2013-09-25 日立汽车系统株式会社 叶片泵
CN104903582A (zh) * 2012-12-27 2015-09-09 Vhit公司 可变排量叶片泵和调节其排量的方法
DE102015213099B3 (de) * 2015-07-13 2016-08-04 Joma-Polytec Gmbh Kunststoffrotor für Vakuumpumpe
US10138888B2 (en) 2015-07-13 2018-11-27 Joma-Polytec Gmbh Plastic Rotor for a vacuum pump

Also Published As

Publication number Publication date
EP2150702A1 (en) 2010-02-10
CN101605995A (zh) 2009-12-16
JP2010523896A (ja) 2010-07-15
WO2008124174A1 (en) 2008-10-16

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