EP2578883A2 - Cartridge style binary vane pump - Google Patents
Cartridge style binary vane pump Download PDFInfo
- Publication number
- EP2578883A2 EP2578883A2 EP12187369.9A EP12187369A EP2578883A2 EP 2578883 A2 EP2578883 A2 EP 2578883A2 EP 12187369 A EP12187369 A EP 12187369A EP 2578883 A2 EP2578883 A2 EP 2578883A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- undervane
- vane pump
- vanes
- port
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Images
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
- F04C2/3446—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 inner and outer member being in contact along more than one line or surface
Definitions
- the following description relates to a vane pump, and in particular, a binary vane pump with a variable output.
- a conventional vane pump may include a thrust plate, ring and pressure plate.
- the vane pump may be configured as a balanced cartridge design having two pumping chambers.
- Each pumping chamber includes an intake port formed in the ring and a discharge port formed in the pressure plate.
- the respective intake ports and discharge ports are symmetrically arranged. Due at least in part to this arrangement, forces generated at one side of the pump are counteracted by the other side.
- two pumping chambers formed in the ring are connected to a common output circuit. That is, the two pumping chambers discharge fluid to a common circuit via respective discharge ports. As a result, the pumping chambers both push against a common resistance in the common circuit, thereby providing a high flow rate even when a high flow rate may not be necessary.
- the common resistance on the two pumping chambers may require more mechanical torque/power to drive the pump.
- a binary vane pump which separates the two pumping chambers and respective discharge ports so that the pump chambers are discharged to different flow paths.
- flow output from the pump may be selectively controlled and the mechanical torque/power required to the drive the pump may be reduced.
- a binary vane pump having a pressure plate including a first discharge port, a thrust plate including a second discharge port, a ring positioned axially between the pressure plate and thrust plate, the ring having an inner cam surface and a rotor rotatably disposed within the ring, the rotor comprising a plurality of slots and a plurality of vanes, vanes of the plurality vanes corresponding to respective slots of the plurality of slots and radially movable with the respective slots.
- a first pump chamber and a second pump chamber are disposed within the ring and the second pump chamber is separated from the first pump chamber by the rotor, vanes, pressure plate and thrust plate.
- the first pump chamber is configured to discharge fluid to the first discharge port and the second pump chamber configured to discharge fluid to the second discharge port.
- a shaft extends through the pressure plate, thrust plate, ring and rotor and is configured to rotate the rotor so the vanes are rotatable in the first and second pumping chambers.
- FIG. 1 is a perspective view of a binary vane pump according to one aspect of the present invention
- FIG. 2 is an exploded view a binary vane pump according to one aspect of the present invention.
- FIG. 3 illustrates an inner side of a pressure plate according to one aspect of the present invention
- FIG. 4 illustrates an outer side of the pressure plate of FIG. 3 according to one aspect of the present invention
- FIG. 5 illustrates an inner side of a pressure plate according to another aspect of the present invention
- FIG. 6 illustrates an outer side of the pressure plate of FIG. 5 according to another aspect of the present invention
- FIG. 7 illustrates an inner side of a thrust plate according to one aspect of the present invention
- FIG. 8 illustrates an inner side of a thrust plate according to another aspect of the present invention.
- FIG. 9 illustrates an outer side of a pressure plate according to another exemplary embodiment of the present invention.
- FIGS. 1 and 2 show a binary vane pump 20 in accordance with an exemplary embodiment of the present invention.
- the binary vane pump includes a ring 30, rotor 40, pressure plate 50, and thrust plate 60.
- FIG. 2 shows an exploded view of the binary vane pump 20 according to an exemplary embodiment of the present invention.
- the ring 30, rotor 40, pressure plate 50 and thrust plate 60 are positioned along an axis 'A'.
- the ring 30 includes a plurality of intakes 32.
- the ring 30 includes four intakes 32.
- a first two intakes may be positioned on axially opposite sides of the ring 30.
- a second two intakes may be positioned on a diametrically opposite side of the ring from the first two intakes, and may be positioned on axially opposite sides of the ring 30.
- An inner circumferential surface of the ring 30 includes an inner cam surface 34.
- the inner cam surface 34 is defines a generally oblong or elongated shape such that ring includes a generally oblong or elongated main chamber 36 having a minor diameter and a major diameter.
- the rotor 40 is positioned in the main chamber 36 of the ring 30.
- the rotor 40 includes an opening 41 configured to receive a rotating shaft 42.
- the rotating shaft 42 extends along an axis 'A' and causes the rotor 40 rotate about the axis 'A'.
- the rotor 40 includes a plurality of radially extending slots 44 which receive respective vanes 46.
- the vanes 46 are movable in a radial direction of the rotor 40 within respective slots 44 so that the vanes 46 may contact the inner cam surface 34 during rotation of the rotor 40.
- the rotor 40 is positioned within the main chamber 36 such that a variable clearance is formed between the rotor 40 and inner cam surface 34.
- the vanes 46 extend across the variable clearance and are movable with respect slots 44 to accommodate variances in the clearance.
- the variable clearance is at a minimum value along the minor diameter.
- the variable clearance increases toward the major diameter and is at a maximum along the major diameter.
- the variable clearance decreases moving from the major diameter toward to the minor diameter.
- the rotor 40 and the vanes 46 divide the main chamber 36 into a first pumping chamber 37 and a second pumping chamber 38.
- a pumping chamber refers to a volume between the rotor 40 and the inner cam surface 34 of the ring which includes at least one intake 32 and at least one discharge, as described further below.
- the first pumping chamber 37 is separated from the second pumping chamber 38 at or near the minor diameter by the rotor 40 and vanes 46 extending from the rotor 40.
- the pressure plate 50 and thrust plate 60 provide axial boundaries of the first pumping chamber 37 and second pumping chamber 38. Accordingly, in an exemplary embodiment, the first pumping chamber 37 is positioned diametrically opposite from the second pumping chamber 38 in the ring 30.
- FIG. 3 illustrates an inner side of the pressure plate 50 according to an exemplary embodiment of the present invention.
- the pressure plate 50 includes an opening 51 centered on the axis 'A'.
- the inner side of the pressure plate 50 faces the ring 30, chamber 36, first pumping chamber 37, second pumping chamber 38, rotor 40 and vanes 46.
- the pressure plate 50 is substantially rotationally fixed relative to the ring 30 and serves as an axial boundary for the first and second pumping chambers 37, 38 ( FIG. 2 ).
- the pressure plate 50 includes a first discharge port 52.
- the first discharge port 52 is positioned on the pressure plate 50 at a location where fluid may be discharged from the first pumping chamber 37.
- the first discharge port 52 allows fluid to flow from the first pumping chamber 37 to a hydraulic load positioned downstream from the binary vane pump 20 via a first flow path.
- a high system pressure is applied on an outer surface of the pressure plate 50 to compress the pressure plate 50 and ring 30 together to minimize leakage paths.
- the high system pressure results from resistance to the flow from the first pumping chamber 37 to into the first flow path.
- a pumping volume is defined between two adjacent vanes 46, the rotor 40, the inner cam surface 34, the pressure plate 50 and the thrust plate 60.
- the pumping volume increases as adjacent vanes 46 rotate from the minor diameter toward the major diameter.
- the pumping volume becomes at least partially filled with the fluid during rotation.
- the pumping volume then decreases as the rotor 40 rotates and the adjacent vanes 46 move from the major diameter toward the minor diameter.
- the decrease in pumping volume causes an increase in pressure on the fluid.
- the increased pressure causes the fluid to flow from the pumping volume out through the first discharge port 52.
- the first discharge port 52 is positioned adjacent to the first pumping chamber 37 at a location where pressure within the pumping volume is sufficient to force the fluid to flow from the first pumping chamber 37 through the first discharge port 52 to the first flow path.
- the inner side of the pressure plate 50 further includes a first undervane port 54.
- the first undervane port 54 may be formed as an opening extending through the pressure plate 50 and is configured to communicate the high system pressure applied on an outer or back surface of the pressure plate 50 to the vanes 46, to urge the vanes 48 radially outward from the rotor 40 and into contact with the inner cam surface 34. That is, high system pressure from outside the main chamber 36 may be exerted on the vanes 46 as an undervane pressure to act behind the vanes and urge the vanes 46 into contact with the inner cam surface 34 in the first pumping chamber 37. The vanes 46 are also urged into contact with the inner cam surface 34 due a centripetal force resulting from rotation of the rotor 40.
- FIG. 4 illustrates an outer side of the pressure plate 50 shown in FIG. 3 .
- the outer side of the pressure plate 50 faces away from the main chamber 36 according to an exemplary embodiment.
- the first discharge port 52 and first undervane port 54 are shown as openings extending completely through the pressure plate 50.
- the first undervane port 54 may be formed as a groove or recess in the pressure plate rather than an opening extending though the pressure plate 50. By replacing an opening with a groove or recess, the stiffness of the pressure plate 50 may be improved.
- the first undervane port 54 is connected to the first discharge port 52 by a first channel 56. Accordingly, high system pressure may communicate with the first undervane port 54 via the first discharge port 52 and the first channel 56 so that the undervane pressure may be exerted on the vanes 46.
- FIG. 6 illustrates an outer side of the pressure plate 50 shown in FIG. 5 .
- the first discharge port 52 extends completely through the pressure plate 50.
- High system pressure communicates with the inner side of the plate 50 via the first discharge portion 52, first channel 56 and first undervane port 54 as described above.
- a first bushing 57 may be positioned about the shaft 42.
- the first bushing 57 is press fit within the opening 51 of the pressure plate 50. Accordingly, the shaft 42 and first bushing 57 extending through the opening 51 in the pressure plate 50.
- the inner side of the pressure plate 50 may further include a first bushing feed or bleed passage 58.
- the first bushing feed or bleed passage 58 is formed as an aperture in the pressure plate 50. The first bushing feed or bleed passage allows lubrication to flow between the first bushing 57 and the shaft 42.
- FIG. 7 shows the thrust plate 60 in accordance with an exemplary embodiment of the present invention.
- the thrust plate 60 includes an opening 61 centered along axis 'A'.
- the thrust plate extends in an axial direction and includes a circumferential wall 62 and an inner face 64.
- a second discharge port 66 and a second undervane port 68 are formed in the inner face 64.
- the second discharge port 66 extends axially and radially within the thrust plate 60 and includes an exit 67 formed in the circumferential wall 62.
- the second undervane port 68 extends axially within the thrust plate 60.
- a passage 70 within the thrust plate 60 fluidly connects the second undervane port 68 to the second discharge port 66.
- the second undervane port 68 may be at least partially filled in so the second undervane port 68 is formed as a groove or recess in the inner face 64 of the thrust plate.
- the passage 70 may be replaced with a second channel 72 formed in the inner face 64 of the thrust plate 60. The second channel 72 extends between the second undervane port 68 and the second discharge port 66 so that the second undervane port 68 may fluidly communicate with the second discharge port 66.
- a second bushing 74 may be positioned around the shaft 42.
- the second bushing 74 is press fit to the thrust plate in the opening 61, such that the second bushing 74 and shaft 42 extend through the opening 61 of the thrust plate 60.
- the inner face 64 of the thrust plate 60 may further include a second bushing feed or bleed passage 76.
- the second bushing feed or bleed passage 76 is formed as an aperture in the thrust plate 60.
- the second bushing feed or bleed passage 76 allows lubrication to flow between the second bushing 74 and the shaft 42.
- first bushing 57 and second bushing 74 are described separately in the exemplary embodiments above, it is understood that if second bushing 74 is of sufficient length and can support a sufficient load, then first bushing 57 may be omitted.
- the pressure plate 50 and the thrust plate 60 are positioned on axially opposite sides of the ring 30, rotor 40 and vanes 46.
- the first discharge port 52 and first undervane port 54 of the pressure plate 50 are positioned adjacent to the first pumping chamber 37 such that fluid may flow from the first pumping chamber 37 through the first discharge port 52.
- the second discharge port 66 and second undervane port 68 of the thrust plate 60 are positioned adjacent to the second pumping chamber 38 such that fluid may flow from the second pumping chamber 38 through second discharge port 66. Fluid is pumped through the second chamber 38 and discharged through the second discharge port 66 in a manner similar to that in the first pumping chamber 37 described above, i.e., by decreasing a pumping volume between adjacent vanes during rotation of a rotor.
- the second discharge port 66 is fluidly coupled with a second flow path such that fluid is discharged from the second pumping chamber 38 to the second flow path via the second discharge port 66.
- the second flow path may include a valve to selectively direct flow from the second discharge port 66 to the hydraulic load.
- the binary vane pump 10 works to pump fluid from the first pumping chamber 37 and second pumping chamber 38 through the first discharge port 52 and second discharge port 66, respectively, to the hydraulic load.
- both pumping chambers 37, 38 are combined to act on the hydraulic load.
- this configuration may be used in high load scenarios.
- the vanes 46 of the rotor 40 extend from the slots 44 and are urged into contact with the inner cam surface 34 in both the first pumping chamber 37 and second pump chamber 38.
- the vanes 46 are urged into contact with the inner cam surface 34 in the second pumping chamber 38 by a second undervane pressure applied via the second undervane port 68 from high system pressure in the second flow path.
- the valve of the second flow path may be actuated so that fluid discharged from the second discharge port 66 flows through the second flow path but does not act on the hydraulic load. That is, with the valve in this position, the second flow path does not communication with the high system pressure.
- the second flow path operates as a low pressure conduit.
- the binary vane pump 10 works against a lower pressure to discharge fluid from the second pumping chamber 38 than the first pumping chamber 37. In this condition, it is the fluid from the first pumping chamber 37 acts on the hydraulic load. In an exemplary embodiment, this configuration may be used in low load scenarios.
- the vanes 46 are urged into contact with the inner cam surface 34 by a low pressure applied through the second undervane port 68. Because of the low pressure applied through the second undervane port 68, sliding friction, vane tip wear and inner cam surface 34 wear may be reduced.
- the second undervane port 68 may be arranged in the pressure plate 50 and positioned adjacent to the second pumping chamber 38.
- undervane pressure is applied to the vanes 46 in the second pumping chamber 38 from the high system pressure outside of the pressure plate 50.
- the first undervane port 54 and the second undervane port 68 may be formed in the pressure plate 50 to supply undervane pressure to the vanes 46 in the first pumping chamber 37 and second pumping chamber 38, respectively.
- the thrust plate 60 may not include an undervane port.
- the binary vane pump 20 of the present invention may also include a seal 80 positioned on the outer or back side of the pressure plate 50.
- the seal 80 seals between high and low pressure areas of the system.
- the seal is positioned against a seat 82 on the pressure plate 50.
- the diameter of the seat 82 may be selected during manufacturing so the pressure applied by the seal 80 on the seat 82 is at an acceptable level depending on a particular application. Accordingly, deflection of the pressure plate 50 during operation may be tuned by selecting a diameter of the seat 82 to control the pressure applied thereto.
- the integration of the features above may be utilized to effectively achieve better control over flow and pressure, and thus, provide a more efficient use of mechanical torque/power.
- the binary vane pump 20 of the exemplary embodiment above may be used together with, for example, an automatic transmission system. That is, the hydraulic load described above may be a component of an automatic transmission system. It is understood that the binary vane pump 20 of the exemplary embodiments above may be used together with other hydraulic systems as well, and in particular, hydraulic systems where it may be advantageous to selectively control the flow from the pump.
- the first pumping chamber 37 is arranged to work against a high system pressure.
- the second pumping chamber may selectively work against the high system pressure or a low system pressure, depending on the amount of flow needed to operate the hydraulic load.
- power supplied to the binary vane pump 20 may be reduced.
- exposing the second pumping chamber 38 to a lower pressure may reduce wear on the vanes 46 and the inner cam surface 34, and also reduce sliding friction between the vanes 46 and the inner cam surface 34.
Landscapes
- 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
- The following description relates to a vane pump, and in particular, a binary vane pump with a variable output.
- A conventional vane pump may include a thrust plate, ring and pressure plate. The vane pump may be configured as a balanced cartridge design having two pumping chambers. Each pumping chamber includes an intake port formed in the ring and a discharge port formed in the pressure plate. The respective intake ports and discharge ports are symmetrically arranged. Due at least in part to this arrangement, forces generated at one side of the pump are counteracted by the other side.
- In the conventional vane pump, two pumping chambers formed in the ring are connected to a common output circuit. That is, the two pumping chambers discharge fluid to a common circuit via respective discharge ports. As a result, the pumping chambers both push against a common resistance in the common circuit, thereby providing a high flow rate even when a high flow rate may not be necessary. The common resistance on the two pumping chambers may require more mechanical torque/power to drive the pump.
- Accordingly, it is desirable to provide a binary vane pump which separates the two pumping chambers and respective discharge ports so that the pump chambers are discharged to different flow paths. As such, flow output from the pump may be selectively controlled and the mechanical torque/power required to the drive the pump may be reduced.
- According to one aspect, there is provided a binary vane pump having a pressure plate including a first discharge port, a thrust plate including a second discharge port, a ring positioned axially between the pressure plate and thrust plate, the ring having an inner cam surface and a rotor rotatably disposed within the ring, the rotor comprising a plurality of slots and a plurality of vanes, vanes of the plurality vanes corresponding to respective slots of the plurality of slots and radially movable with the respective slots. A first pump chamber and a second pump chamber are disposed within the ring and the second pump chamber is separated from the first pump chamber by the rotor, vanes, pressure plate and thrust plate. The first pump chamber is configured to discharge fluid to the first discharge port and the second pump chamber configured to discharge fluid to the second discharge port. A shaft extends through the pressure plate, thrust plate, ring and rotor and is configured to rotate the rotor so the vanes are rotatable in the first and second pumping chambers.
- These and other advantages and features will become more apparent from the following description taken in conjunction with the drawings.
- The subject matter which is regarded as the invention is particularly pointed out and distinctly claimed in the claims at the conclusion of the specification. The foregoing and other features, and advantages of the invention are apparent from the following detailed description taken in conjunction with the accompanying drawings in which:
-
FIG. 1 is a perspective view of a binary vane pump according to one aspect of the present invention; -
FIG. 2 is an exploded view a binary vane pump according to one aspect of the present invention; -
FIG. 3 illustrates an inner side of a pressure plate according to one aspect of the present invention; -
FIG. 4 illustrates an outer side of the pressure plate ofFIG. 3 according to one aspect of the present invention; -
FIG. 5 illustrates an inner side of a pressure plate according to another aspect of the present invention; -
FIG. 6 illustrates an outer side of the pressure plate ofFIG. 5 according to another aspect of the present invention; -
FIG. 7 illustrates an inner side of a thrust plate according to one aspect of the present invention; -
FIG. 8 illustrates an inner side of a thrust plate according to another aspect of the present invention; and -
FIG. 9 illustrates an outer side of a pressure plate according to another exemplary embodiment of the present invention. - Referring now to the Figures, where the invention will be described with reference to specific embodiments, without limiting same,
FIGS. 1 and2 show abinary vane pump 20 in accordance with an exemplary embodiment of the present invention. The binary vane pump includes aring 30,rotor 40,pressure plate 50, andthrust plate 60. -
FIG. 2 shows an exploded view of thebinary vane pump 20 according to an exemplary embodiment of the present invention. With reference toFIG. 2 , thering 30,rotor 40,pressure plate 50 andthrust plate 60 are positioned along an axis 'A'. Thering 30 includes a plurality ofintakes 32. In an exemplary embodiment, thering 30 includes fourintakes 32. A first two intakes may be positioned on axially opposite sides of thering 30. A second two intakes may be positioned on a diametrically opposite side of the ring from the first two intakes, and may be positioned on axially opposite sides of thering 30. - An inner circumferential surface of the
ring 30 includes an inner cam surface 34. The inner cam surface 34 is defines a generally oblong or elongated shape such that ring includes a generally oblong or elongatedmain chamber 36 having a minor diameter and a major diameter. - The
rotor 40 is positioned in themain chamber 36 of thering 30. Therotor 40 includes an opening 41 configured to receive a rotating shaft 42. The rotating shaft 42 extends along an axis 'A' and causes therotor 40 rotate about the axis 'A'. Therotor 40 includes a plurality of radially extending slots 44 which receive respective vanes 46. The vanes 46 are movable in a radial direction of therotor 40 within respective slots 44 so that the vanes 46 may contact the inner cam surface 34 during rotation of therotor 40. - The
rotor 40 is positioned within themain chamber 36 such that a variable clearance is formed between therotor 40 and inner cam surface 34. The vanes 46 extend across the variable clearance and are movable with respect slots 44 to accommodate variances in the clearance. In an exemplary embodiment, the variable clearance is at a minimum value along the minor diameter. The variable clearance increases toward the major diameter and is at a maximum along the major diameter. The variable clearance decreases moving from the major diameter toward to the minor diameter. - The
rotor 40 and the vanes 46 divide themain chamber 36 into afirst pumping chamber 37 and asecond pumping chamber 38. In an exemplary embodiment, a pumping chamber refers to a volume between therotor 40 and the inner cam surface 34 of the ring which includes at least oneintake 32 and at least one discharge, as described further below. In an exemplary embodiment, thefirst pumping chamber 37 is separated from thesecond pumping chamber 38 at or near the minor diameter by therotor 40 and vanes 46 extending from therotor 40. In addition, thepressure plate 50 andthrust plate 60 provide axial boundaries of thefirst pumping chamber 37 andsecond pumping chamber 38. Accordingly, in an exemplary embodiment, thefirst pumping chamber 37 is positioned diametrically opposite from thesecond pumping chamber 38 in thering 30. -
FIG. 3 illustrates an inner side of thepressure plate 50 according to an exemplary embodiment of the present invention. Thepressure plate 50 includes an opening 51 centered on the axis 'A'. The inner side of thepressure plate 50 faces thering 30,chamber 36,first pumping chamber 37,second pumping chamber 38,rotor 40 and vanes 46. Thepressure plate 50 is substantially rotationally fixed relative to thering 30 and serves as an axial boundary for the first andsecond pumping chambers 37, 38 (FIG. 2 ). - The
pressure plate 50 includes afirst discharge port 52. Thefirst discharge port 52 is positioned on thepressure plate 50 at a location where fluid may be discharged from thefirst pumping chamber 37. Thefirst discharge port 52 allows fluid to flow from thefirst pumping chamber 37 to a hydraulic load positioned downstream from thebinary vane pump 20 via a first flow path. - A high system pressure is applied on an outer surface of the
pressure plate 50 to compress thepressure plate 50 and ring 30 together to minimize leakage paths. In an exemplary embodiment, the high system pressure results from resistance to the flow from thefirst pumping chamber 37 to into the first flow path. - A pumping volume is defined between two adjacent vanes 46, the
rotor 40, the inner cam surface 34, thepressure plate 50 and thethrust plate 60. In operation, the pumping volume increases as adjacent vanes 46 rotate from the minor diameter toward the major diameter. The pumping volume becomes at least partially filled with the fluid during rotation. The pumping volume then decreases as therotor 40 rotates and the adjacent vanes 46 move from the major diameter toward the minor diameter. The decrease in pumping volume causes an increase in pressure on the fluid. The increased pressure causes the fluid to flow from the pumping volume out through thefirst discharge port 52. Thefirst discharge port 52 is positioned adjacent to thefirst pumping chamber 37 at a location where pressure within the pumping volume is sufficient to force the fluid to flow from thefirst pumping chamber 37 through thefirst discharge port 52 to the first flow path. - The inner side of the
pressure plate 50 further includes afirst undervane port 54. Thefirst undervane port 54 may be formed as an opening extending through thepressure plate 50 and is configured to communicate the high system pressure applied on an outer or back surface of thepressure plate 50 to the vanes 46, to urge the vanes 48 radially outward from therotor 40 and into contact with the inner cam surface 34. That is, high system pressure from outside themain chamber 36 may be exerted on the vanes 46 as an undervane pressure to act behind the vanes and urge the vanes 46 into contact with the inner cam surface 34 in thefirst pumping chamber 37. The vanes 46 are also urged into contact with the inner cam surface 34 due a centripetal force resulting from rotation of therotor 40. -
FIG. 4 illustrates an outer side of thepressure plate 50 shown inFIG. 3 . The outer side of thepressure plate 50 faces away from themain chamber 36 according to an exemplary embodiment. Thefirst discharge port 52 andfirst undervane port 54 are shown as openings extending completely through thepressure plate 50. - Alternatively, and with reference to
FIG. 5 , thefirst undervane port 54 may be formed as a groove or recess in the pressure plate rather than an opening extending though thepressure plate 50. By replacing an opening with a groove or recess, the stiffness of thepressure plate 50 may be improved. - In the exemplary embodiment shown in
FIG. 5 where thefirst undervane port 54 is formed as a groove or recess, thefirst undervane port 54 is connected to thefirst discharge port 52 by afirst channel 56. Accordingly, high system pressure may communicate with thefirst undervane port 54 via thefirst discharge port 52 and thefirst channel 56 so that the undervane pressure may be exerted on the vanes 46. -
FIG. 6 illustrates an outer side of thepressure plate 50 shown inFIG. 5 . In this exemplary embodiment, thefirst discharge port 52 extends completely through thepressure plate 50. High system pressure communicates with the inner side of theplate 50 via thefirst discharge portion 52,first channel 56 andfirst undervane port 54 as described above. - With reference to
FIG. 2 , a first bushing 57 may be positioned about the shaft 42. In an exemplary embodiment, the first bushing 57 is press fit within theopening 51 of thepressure plate 50. Accordingly, the shaft 42 and first bushing 57 extending through theopening 51 in thepressure plate 50. - With reference to
FIGS. 3 and5 , the inner side of thepressure plate 50 may further include a first bushing feed or bleedpassage 58. In an exemplary embodiment, the first bushing feed or bleedpassage 58 is formed as an aperture in thepressure plate 50. The first bushing feed or bleed passage allows lubrication to flow between the first bushing 57 and the shaft 42. -
FIG. 7 shows thethrust plate 60 in accordance with an exemplary embodiment of the present invention. Thethrust plate 60 includes anopening 61 centered along axis 'A'. The thrust plate extends in an axial direction and includes acircumferential wall 62 and aninner face 64. Asecond discharge port 66 and asecond undervane port 68 are formed in theinner face 64. - The
second discharge port 66 extends axially and radially within thethrust plate 60 and includes anexit 67 formed in thecircumferential wall 62. In an exemplary embodiment, thesecond undervane port 68 extends axially within thethrust plate 60. Apassage 70 within thethrust plate 60 fluidly connects thesecond undervane port 68 to thesecond discharge port 66. - Alternatively, and with reference to
FIG. 8 , thesecond undervane port 68 may be at least partially filled in so thesecond undervane port 68 is formed as a groove or recess in theinner face 64 of the thrust plate. In addition, thepassage 70 may be replaced with asecond channel 72 formed in theinner face 64 of thethrust plate 60. Thesecond channel 72 extends between thesecond undervane port 68 and thesecond discharge port 66 so that thesecond undervane port 68 may fluidly communicate with thesecond discharge port 66. - Referring to
FIG. 2 , asecond bushing 74 may be positioned around the shaft 42. In an exemplary embodiment, thesecond bushing 74 is press fit to the thrust plate in theopening 61, such that thesecond bushing 74 and shaft 42 extend through theopening 61 of thethrust plate 60. - The
inner face 64 of thethrust plate 60 may further include a second bushing feed or bleedpassage 76. In an exemplary embodiment, the second bushing feed or bleedpassage 76 is formed as an aperture in thethrust plate 60. The second bushing feed or bleedpassage 76 allows lubrication to flow between thesecond bushing 74 and the shaft 42. - While the first bushing 57 and
second bushing 74 are described separately in the exemplary embodiments above, it is understood that ifsecond bushing 74 is of sufficient length and can support a sufficient load, then first bushing 57 may be omitted. - When assembled, the
pressure plate 50 and thethrust plate 60 are positioned on axially opposite sides of thering 30,rotor 40 and vanes 46. Thefirst discharge port 52 andfirst undervane port 54 of thepressure plate 50 are positioned adjacent to thefirst pumping chamber 37 such that fluid may flow from thefirst pumping chamber 37 through thefirst discharge port 52. Thesecond discharge port 66 andsecond undervane port 68 of thethrust plate 60 are positioned adjacent to thesecond pumping chamber 38 such that fluid may flow from thesecond pumping chamber 38 throughsecond discharge port 66. Fluid is pumped through thesecond chamber 38 and discharged through thesecond discharge port 66 in a manner similar to that in thefirst pumping chamber 37 described above, i.e., by decreasing a pumping volume between adjacent vanes during rotation of a rotor. - The
second discharge port 66 is fluidly coupled with a second flow path such that fluid is discharged from thesecond pumping chamber 38 to the second flow path via thesecond discharge port 66. The second flow path may include a valve to selectively direct flow from thesecond discharge port 66 to the hydraulic load. In this condition, the binary vane pump 10 works to pump fluid from thefirst pumping chamber 37 andsecond pumping chamber 38 through thefirst discharge port 52 andsecond discharge port 66, respectively, to the hydraulic load. Thus, both pumpingchambers - In this "high load" configuration, the vanes 46 of the
rotor 40 extend from the slots 44 and are urged into contact with the inner cam surface 34 in both thefirst pumping chamber 37 andsecond pump chamber 38. The vanes 46 are urged into contact with the inner cam surface 34 in thesecond pumping chamber 38 by a second undervane pressure applied via thesecond undervane port 68 from high system pressure in the second flow path. - The valve of the second flow path may be actuated so that fluid discharged from the
second discharge port 66 flows through the second flow path but does not act on the hydraulic load. That is, with the valve in this position, the second flow path does not communication with the high system pressure. As a result, in an exemplary embodiment, the second flow path operates as a low pressure conduit. Thus, the binary vane pump 10 works against a lower pressure to discharge fluid from thesecond pumping chamber 38 than thefirst pumping chamber 37. In this condition, it is the fluid from thefirst pumping chamber 37 acts on the hydraulic load. In an exemplary embodiment, this configuration may be used in low load scenarios. - In this "low load" configuration, the vanes 46 are urged into contact with the inner cam surface 34 by a low pressure applied through the
second undervane port 68. Because of the low pressure applied through thesecond undervane port 68, sliding friction, vane tip wear and inner cam surface 34 wear may be reduced. - Alternatively, and with reference to
FIG. 9 , thesecond undervane port 68 may be arranged in thepressure plate 50 and positioned adjacent to thesecond pumping chamber 38. In this embodiment, undervane pressure is applied to the vanes 46 in thesecond pumping chamber 38 from the high system pressure outside of thepressure plate 50. Thus, thefirst undervane port 54 and thesecond undervane port 68 may be formed in thepressure plate 50 to supply undervane pressure to the vanes 46 in thefirst pumping chamber 37 andsecond pumping chamber 38, respectively. Accordingly, thethrust plate 60 may not include an undervane port. - With further reference to
FIGS. 2 and6 , thebinary vane pump 20 of the present invention may also include a seal 80 positioned on the outer or back side of thepressure plate 50. The seal 80 seals between high and low pressure areas of the system. The seal is positioned against aseat 82 on thepressure plate 50. The diameter of theseat 82 may be selected during manufacturing so the pressure applied by the seal 80 on theseat 82 is at an acceptable level depending on a particular application. Accordingly, deflection of thepressure plate 50 during operation may be tuned by selecting a diameter of theseat 82 to control the pressure applied thereto. - The integration of the features above may be utilized to effectively achieve better control over flow and pressure, and thus, provide a more efficient use of mechanical torque/power. The
binary vane pump 20 of the exemplary embodiment above may be used together with, for example, an automatic transmission system. That is, the hydraulic load described above may be a component of an automatic transmission system. It is understood that thebinary vane pump 20 of the exemplary embodiments above may be used together with other hydraulic systems as well, and in particular, hydraulic systems where it may be advantageous to selectively control the flow from the pump. - In the exemplary embodiments above, the
first pumping chamber 37 is arranged to work against a high system pressure. The second pumping chamber may selectively work against the high system pressure or a low system pressure, depending on the amount of flow needed to operate the hydraulic load. When thesecond pumping chamber 38 works against the low system pressure, power supplied to thebinary vane pump 20 may be reduced. In addition, exposing thesecond pumping chamber 38 to a lower pressure may reduce wear on the vanes 46 and the inner cam surface 34, and also reduce sliding friction between the vanes 46 and the inner cam surface 34. - While the invention has been described in detail in connection with only a limited number of embodiments, it should be readily understood that the invention is not limited to such disclosed embodiments. Rather, the invention can be modified to incorporate any number of variations, alterations, substitutions or equivalent arrangements not heretofore described, but which are commensurate with the spirit and scope of the invention. Additionally, while various embodiments of the invention have been described, it is to be understood that aspects of the invention may include only some of the described embodiments. Accordingly, the invention is not to be seen as limited by the foregoing description.
Claims (15)
- A binary vane pump comprising:a pressure plate including a first discharge port;a thrust plate including a second discharge port;a ring positioned axially between the pressure plate and thrust plate, the ring having an inner cam surface;a rotor rotatably disposed within the ring, the rotor comprising a plurality of slots and a plurality of vanes, vanes of the plurality vanes corresponding to respective slots of the plurality of slots and radially movable with the respective slots;a first pump chamber disposed within the ring;a second pump chamber disposed within the ring, separated from the first pump chamber by the rotor, vanes, pressure plate and thrust plate, the first pump chamber configured to discharge fluid to the first discharge port and the second pump chamber configured to discharge fluid to the second discharge port; anda shaft extending through the pressure plate, thrust plate, ring and rotor and configured to rotate the rotor so the vanes are rotatable in the first and second pumping chambers.
- The binary vane pump of claim 1, wherein the pressure plate further comprises a first undervane port configured to supply a first undervane pressure to the vanes in the first pumping chamber.
- The binary vane pump of claim 2, wherein the plurality of vanes in the first pumping chamber are urged into contact with the inner cam surface by the first undervane pressure.
- The binary vane pump of claim 2, wherein the first undervane port is configured as an opening extending through the pressure plate.
- The binary vane pump of claim 2, wherein the first undervane port is configured as groove formed on an inner face of the pressure plate facing the ring and fluidly communicates with the first discharge port.
- The binary vane pump of claim 5, further comprising a first channel formed on the inner face of the pressure plate extending between the first undervane port and the first discharge port.
- The binary vane pump of claim 2, wherein the pressure plate further comprises a second undervane port configured to supply a second undervane pressure to vanes in the second pumping chamber.
- The binary vane pump of claim 2, wherein the thrust plate further comprises a second undervane port configured to supply a second undervane pressure to the vanes in the second pumping chamber.
- The binary vane pump of claim 8, wherein the plurality of vanes in the second pumping chamber are urged into contact with the inner cam surface by the second undervane pressure.
- The binary vane pump of claim 9, wherein the first undervane pressure is greater than the second undervane pressure.
- The binary vane pump of claim 8, wherein the second undervane port is fluidly connected to the second discharge port.
- The binary vane pump of claim 8, wherein a second channel is formed on an inner surface of the thrust plate and extends between the second undervane port and the second discharge port to fluidly connect the second undervane port and second discharge port.
- The binary vane pump of claim 1, further comprising a bushing surrounding the shaft.
- The binary vane pump of claim 12, wherein the bushing comprises a first bushing press fit to the pressure plate and a second bushing press fit to the thrust plate
- The binary vane pump of claim 12, wherein the pressure plate includes a first feed/bleed passage and the thrust plate comprises a second feed/bleed passage, the first and second feed/bleed passages configured feed lubricant to the first bushing and second bushing, respectively.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201161544784P | 2011-10-07 | 2011-10-07 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2578883A2 true EP2578883A2 (en) | 2013-04-10 |
EP2578883A3 EP2578883A3 (en) | 2014-01-22 |
Family
ID=47142921
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12187369.9A Withdrawn EP2578883A3 (en) | 2011-10-07 | 2012-10-05 | Cartridge style binary vane pump |
Country Status (3)
Country | Link |
---|---|
US (1) | US20130089456A1 (en) |
EP (1) | EP2578883A3 (en) |
CN (1) | CN103032308B (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016200893A1 (en) * | 2016-01-22 | 2017-07-27 | Magna Powertrain Bad Homburg GmbH | pumps Fields |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3216363A (en) * | 1963-04-24 | 1965-11-09 | Sperry Rand Corp | Power transmission |
US3223044A (en) * | 1963-07-18 | 1965-12-14 | American Brake Shoe Co | Three-area vane type fluid pressure energy translating devices |
US3632238A (en) * | 1969-09-05 | 1972-01-04 | Eaton Yale & Towne | Pump assembly |
US4386891A (en) * | 1981-04-23 | 1983-06-07 | General Motors Corporation | Rotary hydraulic vane pump with undervane passages for priming |
EP0758716B1 (en) * | 1995-08-14 | 2003-12-10 | LuK Fahrzeug-Hydraulik GmbH & Co. KG | Vane pump |
US6503064B1 (en) * | 1999-07-15 | 2003-01-07 | Lucas Aerospace Power Transmission | Bi-directional low maintenance vane pump |
US6422845B1 (en) * | 2000-12-01 | 2002-07-23 | Delphi Technologies, Inc. | Rotary hydraulic vane pump with improved undervane porting |
US6655936B2 (en) * | 2001-11-14 | 2003-12-02 | Delphi Technologies, Inc. | Rotary vane pump with under-vane pump |
US7637724B2 (en) * | 2004-08-19 | 2009-12-29 | Hamilton Sundstrand Corporation | Variable displacement vane pump with pressure balanced vane |
US7628596B2 (en) * | 2006-09-22 | 2009-12-08 | Ford Global Technologies, Llc | Power steering pump |
JP2009047041A (en) * | 2007-08-17 | 2009-03-05 | Hitachi Ltd | Variable displacement vane pump |
JP5438554B2 (en) * | 2010-03-04 | 2014-03-12 | カヤバ工業株式会社 | Variable displacement vane pump |
JP5514068B2 (en) * | 2010-10-22 | 2014-06-04 | カヤバ工業株式会社 | Vane pump |
-
2012
- 2012-10-04 US US13/644,696 patent/US20130089456A1/en not_active Abandoned
- 2012-10-05 EP EP12187369.9A patent/EP2578883A3/en not_active Withdrawn
- 2012-10-07 CN CN201210460653.9A patent/CN103032308B/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
None |
Also Published As
Publication number | Publication date |
---|---|
CN103032308B (en) | 2016-06-22 |
CN103032308A (en) | 2013-04-10 |
US20130089456A1 (en) | 2013-04-11 |
EP2578883A3 (en) | 2014-01-22 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8535030B2 (en) | Gerotor hydraulic pump with fluid actuated vanes | |
US8708679B2 (en) | Vane pump for pumping hydraulic fluid | |
EP2018369B1 (en) | Gerotor motor and brake assembly | |
WO2015111550A1 (en) | Vane pump | |
JP5897945B2 (en) | Vane pump | |
US20160186623A1 (en) | Variable displacement vane pump with integrated fail safe function | |
JP2009264192A (en) | Variable displacement vane pump | |
US6558132B2 (en) | Variable displacement pump | |
JP2009257167A (en) | Variable displacement vane pump | |
JP6401509B2 (en) | Piston pump and piston pump valve plate | |
KR20070073792A (en) | Pump with selectable outlet pressure | |
US20140178239A1 (en) | Vane pump | |
JP2008057361A (en) | Vane pump | |
EP2578883A2 (en) | Cartridge style binary vane pump | |
WO2020110180A1 (en) | Internal gear pump | |
JPH0579469A (en) | Variable capacity type vane pump | |
US6478549B1 (en) | Hydraulic pump with speed dependent recirculation valve | |
JP2007120435A (en) | Vane pump | |
JP6897412B2 (en) | Oil pump | |
JP2017057737A (en) | Vehicular hydraulic device | |
WO2016027308A1 (en) | Vane pump | |
US20140271299A1 (en) | Hydraulically balanced stepwise variable displacement vane pump | |
US3065707A (en) | Vane type oil pump lubrication system | |
JP7466398B2 (en) | Vane Pump | |
JP2004232465A (en) | Vane pump and vane motor of bidirectional type |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F04C 2/344 20060101AFI20131219BHEP |
|
17P | Request for examination filed |
Effective date: 20140722 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
17Q | First examination report despatched |
Effective date: 20170828 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
|
18D | Application deemed to be withdrawn |
Effective date: 20180109 |