WO2009014661A1 - Pompe à palettes articulées ayant de multiples palettes pour entraîner un rotor externe et transmettre un meilleur rapport de contact - Google Patents

Pompe à palettes articulées ayant de multiples palettes pour entraîner un rotor externe et transmettre un meilleur rapport de contact Download PDF

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Publication number
WO2009014661A1
WO2009014661A1 PCT/US2008/008827 US2008008827W WO2009014661A1 WO 2009014661 A1 WO2009014661 A1 WO 2009014661A1 US 2008008827 W US2008008827 W US 2008008827W WO 2009014661 A1 WO2009014661 A1 WO 2009014661A1
Authority
WO
WIPO (PCT)
Prior art keywords
vanes
inner rotor
chambers
outer rotor
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.)
Ceased
Application number
PCT/US2008/008827
Other languages
English (en)
Inventor
Keith V. Feldt
Mark Kopec
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.)
BorgWarner Inc
Original Assignee
BorgWarner 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 BorgWarner Inc filed Critical BorgWarner Inc
Publication of WO2009014661A1 publication Critical patent/WO2009014661A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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

Definitions

  • the present invention relates to the area of vane pumps, and providing a contact ratio of greater than 1.0.
  • AVP articulated vane pumps
  • vanes positioned in a series of corresponding chambers in an inner rotor with the vanes also being connected to an outer rotor to pump fluid as the inner rotor is driven by a shaft.
  • the inner rotor and outer rotor are on parallel offset axes, and as the inner rotor rotates, the vanes slide in and out of the chambers drawing in fluid from an inlet port as the vanes slide out of the chambers and driving fluid into an outlet port as the vanes slide into the chambers.
  • the vanes and inner rotor In addition to performing the function of pumping fluid, the vanes and inner rotor also perform the function of driving, or transferring a rotational force to the outer rotor.
  • the shape of the vane, along with the chambers, allows the angle of each of the vanes to change relative to the chamber as both the inner rotor and outer rotor rotate.
  • one vane at a time is used to transfer the rotational force from the inner rotor to the outer rotor.
  • the load is transferred from the inner rotor to each of the vanes in a sequential manner as the inner rotor rotates.
  • the maximum amount of load that can be transferred through the pump correlates directly to the amount of load that each vane can withstand.
  • the present invention is an improvement over a conventional articulated vane pump (AVP).
  • the present invention includes an inner rotor rotatable about a first axis, the inner rotor having plurality of chambers for receiving a plurality of vanes, and an outer rotor pivotably connected to the plurality of vanes, the outer rotor rotatable about a second axis and circumscribing the inner rotor.
  • the plurality of vanes When the inner rotor rotates about the first axis and provides rotational force to the plurality of vanes, the plurality of vanes transfer rotational force to the outer rotor, causing the outer rotor to rotate about the second axis.
  • the plurality of vanes are in contact with the plurality of chambers as the inner rotor applies rotational force to the plurality of vanes.
  • the plurality of vanes in contact with the plurality of chambers forms a contact ratio greater than 1.0.
  • Figure 1 is a side sectional view of an articulated vane pump, having a contact ratio greater than 1.0; and Figure 2 is a detailed view of the portion shown in area 2 of Figure 1 , according to the present invention.
  • the AVP 10 has a cover (not shown) which includes an inlet port and an outlet port.
  • the AVP 10 also includes an input shaft 12; the input shaft 12 rotates about a first axis 14 and drives an inner rotor 16.
  • the inner rotor 16 is circumscribed by a series of equally spaced chambers 18.
  • the chambers 18 receive a series of vanes 20; the vanes 20 have a base portion 22, a neck portion 24, a shelf 26, and a vane head 28.
  • the base portion 22 has a first radius 30 and a second radius 32 located about a first center point 34.
  • the vane head 28 is located about a second center point 36.
  • the neck portion 24 includes a constant speed cam surface 38, and a coast surface 40.
  • the chambers 18 have an upper edge 42, which is preferably a radius or curve, to define the shape of the constant speed cam surface 38.
  • the inner rotor 16 is surrounded by an outer rotor 44 which has a series of recesses 46 for receiving the vane heads 28 of the vanes 20.
  • the vane heads 28 are permanently affixed to the recesses 46, but are allowed to swivel therein.
  • the outer rotor 44 rotates on a second axis 48 which is parallel to the axis 14 of the inner rotor 16, but is selectively offset to create a pumping action which will be described further.
  • the chambers 18 have an upper edge 42 which is used to define the shape of the constant speed cam surface 38.
  • the constant speed cam surface 38 is used for receiving rotational force from the chamber 18, as well as providing a smooth transition between the vanes 20, as the vanes 20 receive rotational force from the chamber 18 in a sequential manner.
  • the upper edge 42 of the chamber 18 will slide along a portion of the constant speed cam surface 38 as the inner rotor 16 rotates.
  • the shape of the constant speed cam surface 38 transitions into the shelf 26, and is long enough such that two vanes 20 are allowed to be in contact with chambers 18 at the same time, yielding a contact ratio of greater than 1.0.
  • the location of the first center point 34, second center point 36, the width of the chamber 18 (which defines where the upper edge 42 will be relative to the first and second center points 34,36) all have an effect on the shape of the constant speed cam surface 38.
  • the shape of the constant speed cam surface 38 is defined by how the position of the upper edge 42 changes relative to the first center point 34 and the second center point 36 as the inner rotor 16 and outer rotor 44 rotate.
  • the constant speed cam surface 38 is shaped such that at least one vane 20, and preferably two vanes 20, receive force from the inner rotor 16 at all times.
  • the inner rotor 16 In operation, as the input shaft 12 rotates in a first direction, which in this case would be counterclockwise in Figure 1 , the inner rotor 16 will also be forced to rotate. It should be noted that the following description for the motion of one of the vanes 20 relative to a corresponding chamber 18 applies to all the vanes 20 and their corresponding chambers 18, with the only difference being that each vane 20 is at a different position relative to its corresponding chamber 18, depending on the point of rotation of the inner rotor 16.
  • the inner rotor 16 applies force to each of the vanes 20 in sequential manner. For example, as the inner rotor 16 rotates in a counterclockwise direction, the vane 20 located toward the bottom in Figure 1 will begin to move in an outward direction relative to its respective chamber 18. This motion will create a suction which draws fluid into the chamber 18 from the inlet port as the vane 20 moves past the inlet port. Fluid will then flow from the inlet port into the chamber 18.
  • the vane 20 Once the vane 20 has moved past the inlet port, it will be at its maximum extended position relative to the chamber 18, and the maximum amount of fluid will be in the chamber 18. This is shown by the vane 20 toward the top of Figure 1. As the inner rotor 16 continues to rotate counterclockwise in Figure 1 , the vane 20 will then begin to slide back into the chamber 18 toward the input shaft 12, and begin to compress the fluid. As the fluid is compressed, the vane 20 will begin to slide across the outlet port. The compressed fluid will then flow into the outlet port. The vanes 20 are allowed to move in a sliding direction either into or out of each respective chamber 18, and are also allowed to pivot in the recesses 46.
  • the space 50 between the inner rotor 16 and the outer rotor 44 is also used to pump fluid as well.
  • the space 50 located over the inlet port will begin to expand due to the axis of the inner rotor 16 being offset from the axis of the outer rotor 44.
  • This also creates a suction which draws fluid into the space 50, as the inner rotor 16 continues to rotate, the space 50 will begin to contract near the outlet port. This motion between the inner rotor 16 and the outer rotor 44 will force the fluid in space 50 into the outlet port.
  • the vanes 20 have a second function outside of pumping fluid, which is to rotate the outer rotor 44. Force is applied from the inner rotor 16, to the vane 20 located in the left-most position in Figure 1. As the inner rotor 16 rotates, the angle of the vanes 20 changes relative to their respective chambers 18. The vanes 20 receive force in three locations from the inner rotor 16 and the outer rotor 44. The position of the three locations where force is applied to the vanes 20 is designated as a first contact position 52, a second contact position 54, and a third contact position 56, best seen in Figure 2.
  • the first contact position 52 is the point where the upper edge 42 of the chamber 18 applies force to the constant speed cam surface 38.
  • the location of the first contact position 52 changes as the upper edge 42 moves along the constant speed cam surface 38 vane 20 slides into and out of the chamber 18.
  • the upper edge 42 does not apply force to the vane 20 during the entire period of rotation.
  • the angle of each of the vanes 20 changes such that at a certain predetermined range of rotation, the angle of the vane 20 will be in a position where the upper edge 42 will apply force to the vanes 20.
  • the relationship between the constant speed cam surface 38 and the upper edge 40 is such that a smooth transition occurs as the upper edge 42 applies force to the constant speed cam surface 38.
  • the second contact position 54 is the point where the vane head 28 of the vane 20 transfers force to the outer rotor 44 and the outer rotor 44 applies a reactive force to the vane head 28.
  • the location of the second contact position 54 will vary as the inner rotor 16 rotates because the upper edge 42 of the chamber 18 will slide along the constant speed cam surface 38 as the upper edge 42 applies rotational force to the constant speed cam surface 38, and the vane 20 pivots in the recess 46.
  • the third contact position 56 is the point where the chamber 18 applies force to the vane 20 at the location of the first radius 30. This is also a reactive force which results from the upper edge 42 applying force to the vane 20. Once again, the third contact position 56 changes as the vane 20 pivots and moves in the chamber 18.
  • the angle of the vane 20 will change such that the chamber 18 will no longer apply force to the vane 20.
  • the first radius 30 and the second radius 32 of the base 22 will still be in contact with the chamber 18, but the first radius 30 will not receive force from the inner rotor 16.
  • first radius 30 and the second radius 32 are in contact with the chamber 18 during the entire rotation of the inner rotor 16.
  • the chamber 18 only applies the reactive force to the vane 20 at the location of the first radius 30 as described above when the upper edge 42 of the chamber 18 is applying force to the vane 20.
  • the vane 20 will not receive any type of load.
  • the first radius 30 and the second radius 32 of the base portion 22 will still be in contact with the chamber 18, the point on the first radius 30 and the second radius 32 which contacts the chamber 18 will change, but no load will be applied to the vane 20.
  • the constant speed cam surface 38 is shaped such that at least one vane 20, and preferably two vanes 38, receive force from the inner rotor 16 at all times.
  • the shape of the constant speed cam surface 38 can be changed to affect how many vanes 20 are in continuous contact with the inner rotor 16.
  • the average number of vanes 20 driving the outer rotor 44 is defined as the contact ratio.
  • the AVP 10 of the present invention has a contact ratio of greater than 1.0. If the contact ratio is 1.0, then there will only be one vane 20 driving the outer rotor 44 at all times.
  • the advantage of the present invention is that there is a transition of the application of force from one vane 20 to the next as the inner rotor 16 rotates. For example, if the contact ratio is 1.2, even though one of the vanes 20 will always be driving the outer rotor 44, 20% of the time two vanes 20 will be driving the outer rotor 44, and 80% of the time only one vane 20 will be driving the outer rotor 44.
  • the period of time where two vanes 20 are driving the outer rotor 44 is the period of time where the rotational force being applied from the inner rotor 16 through the vanes 20 to the outer rotor 44 is transitioning from one vane 20 to the next. This reduces the amount of noise produced, and provides a more robust design.
  • Another example of a contact ratio is 1.5, where 50% of the time two vanes 20 will be driving the outer rotor 44, and 50% of the time, one vane 20 will be driving the outer rotor 44.
  • the inner rotor 16 rotates about the first axis 14, and the outer rotor 44 rotates about the second axis 48, which can be offset and parallel to each other, or aligned with one another.
  • Changing the position of the inner rotor 16 relative to the outer rotor 44 changes the eccentricity between the outer rotor 44 and inner rotor 16 and therefore the displacement of the AVP 10.
  • the eccentricity between the inner rotor 16 and outer rotor 44 is what creates the pumping action through the AVP 10.
  • the eccentricity of the AVP 10 can also be changed to vary the amount of fluid being pumped.
  • the outer rotor 44 is connected to an eccentric ring or slider (not shown) which is used to reposition the outer rotor 44 relative to the inner rotor 16.
  • the eccentric ring or slider can be used to control or vary the position of the outer rotor 44 anywhere between a position of zero eccentricity (minimum displacement) such that there is zero eccentricity between the inner rotor 16 and outer rotor 44 so that no fluid is displaced, or the outer rotor 44 can be repositioned to create a maximum amount of eccentricity (maximum displacement) shown in Figure 1 , where the maximum amount of fluid is pumped by the AVP 10.
  • the displacement of the AVP 10 can be varied between minimum displacement, maximum displacement, or any position in between.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

La présente invention est un perfectionnement d'une pompe à palettes articulées (AVP) classique. La présente invention comprend un rotor interne qui peut tourner autour d'un premier axe, le rotor interne ayant plusieurs chambres pour recevoir plusieurs palettes, et un rotor externe raccordé en pivotement aux différentes palettes, le rotor externe pouvant tourner autour d'un second axe et circonscrivant le rotor interne. Lorsque le rotor interne tourne autour du premier axe et transmet une force de rotation aux différentes palettes, les différentes palettes transfèrent la force de rotation au rotor externe, amenant le rotor externe à tourner autour du second axe. Les différentes palettes sont en contact avec les différentes chambres à mesure que le rotor interne applique la force de rotation aux différentes palettes, et les palettes en contact avec les chambres forment un rapport de contact supérieur à 1,0.
PCT/US2008/008827 2007-07-20 2008-07-18 Pompe à palettes articulées ayant de multiples palettes pour entraîner un rotor externe et transmettre un meilleur rapport de contact Ceased WO2009014661A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US96152607P 2007-07-20 2007-07-20
US60/961,526 2007-07-20

Publications (1)

Publication Number Publication Date
WO2009014661A1 true WO2009014661A1 (fr) 2009-01-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2008/008827 Ceased WO2009014661A1 (fr) 2007-07-20 2008-07-18 Pompe à palettes articulées ayant de multiples palettes pour entraîner un rotor externe et transmettre un meilleur rapport de contact

Country Status (1)

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WO (1) WO2009014661A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012116962A3 (fr) * 2011-03-02 2013-08-29 Mahle International Gmbh Pompe a palettes
EP2868926A1 (fr) * 2013-11-05 2015-05-06 TRW Automotive Italia S.r.l. Pompe pendulaire, en particulier pour l'alimentation d'huile sous pression vers un dispositif final

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08277786A (ja) * 1995-04-05 1996-10-22 Tatsuo Kushiro 回転ポンプ
JPH11148476A (ja) * 1997-11-17 1999-06-02 Sato Takeshi 回転ピストン構造の容積形ピストン機構
EP1225337B1 (fr) * 2001-01-20 2004-12-22 Günther Beez Pompe à palettes à déplacement variable
US20060191360A1 (en) * 2003-11-08 2006-08-31 Gunther Beez Oscillating slide machine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08277786A (ja) * 1995-04-05 1996-10-22 Tatsuo Kushiro 回転ポンプ
JPH11148476A (ja) * 1997-11-17 1999-06-02 Sato Takeshi 回転ピストン構造の容積形ピストン機構
EP1225337B1 (fr) * 2001-01-20 2004-12-22 Günther Beez Pompe à palettes à déplacement variable
US20060191360A1 (en) * 2003-11-08 2006-08-31 Gunther Beez Oscillating slide machine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012116962A3 (fr) * 2011-03-02 2013-08-29 Mahle International Gmbh Pompe a palettes
EP2868926A1 (fr) * 2013-11-05 2015-05-06 TRW Automotive Italia S.r.l. Pompe pendulaire, en particulier pour l'alimentation d'huile sous pression vers un dispositif final
ITBO20130603A1 (it) * 2013-11-05 2015-05-06 Trw Automotive Italia S R L Pompa a pendoli, in particolare per alimentare olio in pressione ad una utenza

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