WO2018065319A1 - Vane pump - Google Patents
Vane pump Download PDFInfo
- Publication number
- WO2018065319A1 WO2018065319A1 PCT/EP2017/074825 EP2017074825W WO2018065319A1 WO 2018065319 A1 WO2018065319 A1 WO 2018065319A1 EP 2017074825 W EP2017074825 W EP 2017074825W WO 2018065319 A1 WO2018065319 A1 WO 2018065319A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- blade
- pump
- slot
- inlet
- inner end
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0854—Vane tracking; control therefor by fluid means
- F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0023—Axial sealings for working fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
-
- 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
- F04C2210/00—Fluid
- F04C2210/20—Fluid liquid, i.e. incompressible
- F04C2210/203—Fuel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/11—Kind or type liquid, i.e. incompressible
Definitions
- the present invention relates to a blade pump and more particularly to means for maintaining fluid pressure around the blades of the pump.
- communication is provided to enable fluid to inwardly flow toward the bottom of the slot in order to compensate for pressure drops and spikes when the blade moves.
- blade pumps are typically utilized as feed pump drawing fuel from a low pressure tank and delivering it to a high pressure pump.
- pressure spikes are observed around the blade generating cavitation erosion at the rotor and disturbing the blade displacements and the feed pump operation.
- a blade pump having a housing with an inner plate, an outer plate and a peripheral liner defining an inner space in which a rotor is adapted to rotate about a main axis.
- the rotor has a first face sliding against the inner plate, a second face sliding against the outer plate and a peripheral cylindrical face.
- the rotor is provided with a plurality of slots which open in said peripheral face, a blade being slidably arranged in each slot and, a spring being compressed at the bottom, or inner end, of said slot, against the inner end of the blade, outwardly biasing said blade so that, the blade protrudes outside the slot and the outer end of the blade slides against said liner of the housing thus defining a plurality of arcuate chambers between the peripheral face of the rotor, the liner and the outer end of the blades.
- the volume of said chambers cyclically varies between large and small as the rotor rotates.
- the blade pump is further provided with an inlet opening in a large volume chamber and, an outlet opening in the small volume chamber so that in use, a fluid entering the inlet fills a large volume and is compressed and pushed toward the outlet.
- the blade pump is further provided with a second inlet opening in the inner end of the slot so that, in use, said fluid flows into the chamber via the first inlet and, into the volume wherein a spring is compressed via the second opening.
- the second inlet extends over an angular width enabling, in use, the inner end of the slot to be filled over an extended rotational angle of the rotor.
- Said angular width is substantially two third of the angle between two consecutive slots.
- said second opening has an arcuate shape.
- the rotor is further provided with grooves dug in its first side face, each groove opening at an entry end in the inner end of the slot and extending in said first side face toward a closed end so that, in use, fluid entering via said second inlet flows into said groove toward the inner end of the slot while said inner end is no longer facing said second inlet.
- the groove extends over an angular width W enabling, in operation of the pump, the inner end of the slot to be filled over an extended time.
- the angular width of the groove is substantially two third of the angle between two consecutive slots.
- each blade is having an outer end with two sealing tip edges, sliding against the liner and, a fluid communication channel extending through the blade from its inner end, where said channel opens in the inner end of the slot where the spring is compressed, to the outer end where said channel opens between said tip edges.
- the invention further extends to a fuel pump assembly adapted to be arranged in a fuel injection equipment, said fuel pump assembly comprising a feed pump for drawing fuel from a low pressure tank and for delivering it to a high pressure pump, said feed pump being a blade pump as described above.
- Figure 1 is a section of a diesel pump comprising a blade pump and a high pressure pump.
- Figure 2 is an axial section of the blade pump of figure 1 adapted to rotate about a main axis XI .
- Figure 3 is a magnified view of a portion of figure 2, said view detailing the area of a blade in an axial XI section.
- Figure 4 is a radial section of the blade pump of figure 2, said section enabling view of a first side face of the pump.
- Figure 5 is a magnified view of figure 4 of an inlet area arranged in said first side face.
- Figure 6 is a magnified view detailing the blade in an radial XI section.
- Figure 7 is a 3D view of a rotor of the pump of figure 2.
- a pump assembly 10 represented on figure 1 is adapted to draw fuel from a low pressure tank, to pressurize and to deliver said fuel to a high pressure reservoir from which it is distributed to fuel injectors.
- the fuel pump assembly 10 which in the example chosen is a diesel pump, comprises a transfer pump 12 and a high pressure pump 14, both pumps being fixed to a cambox 16.
- a camshaft 18, adapted to rotate in said cambox 16, imparts rotational movement to the transfer pump 12 and reciprocal linear movements to one or more pistons of the high pressure pump 14.
- the transfer pump 12 now described is a blade pump 12 represented and described in reference to the figures 2 to 7.
- the typical blade pump 12 has a housing with peripheral walls defining an inner space S in which a rotor 20 rotates about a main axis XI .
- the peripheral walls comprise an inner plate 22, also identified as distribution plate 22, transverse to said main axis XI, an outer plate 24 also transverse to said main axis XI and, a peripheral liner 26 that defines a cylindrical track.
- the rotor 20 has a cylindrical shape and it has a first face 28 adapted to slide against the inner face of the inner plate 22 of the housing, a parallel second face 30 adapted to slide against the inner face of the outer plate 24 of the housing and, a peripheral cylindrical face 32 distant from the liner 26.
- the rotor 20 is provided with a plurality of slots 34 radially extending from an outer opening 36 in the peripheral face 32 to an inner end 38 closer to the axis XI .
- each slot 34 is slidably arranged a blade 40 extending from an inner end 42 close to the inner end 38 of the slot, to an outer end 44 protruding from the slot through the outer opening 36 in the peripheral face of the rotor.
- Each blade 40 is outwardly pushed by a spring 46 compressed between the inner end 38 of the slot and an inner end 42 of the blade, the outer end 44 of the blade being biased in contact and sliding, in use, against the liner 26 of the housing.
- the main axis XI and the liner axis X2 being offset, the arrangement of the rotor in the housing defines between the peripheral face 32 of the rotor, the liner 26 of the housing and the outer end 44 of the blades, a plurality of arcuate chambers C which, in use as the rotor rotates, volume cyclically varies between a large volume and a small volume.
- the blade pump 12 further comprises an inlet 48 and an outlet 50, both provided in the inner plate 22 of the housing, the inlet 48 opening in a first chamber CI that volumes increases and, the outlet 50 opening in a second chamber C2 which volume decreases.
- the offset between the main axis XI and the liner axis X2 is set so the top of the rotor 20 is almost tangent to the liner and so the chamber at the top has a volume almost null while the volume of the chamber at the bottom is maximum.
- each blade 40 is provided with a double tip edge 52, 54 and with an inner channel 56 radially extending between the inner end 42 of the blade, where said channel opens in the spring compartment and, the outer end 44 of the blade, where said channel 52 opens between said two tip edges 52, 54, each of said tip edges 52, 54 sliding against the liner 26.
- the blades 40 cyclically slide in and out of their respective slot 34 and, fuel flows through said channel 56 avoiding pressure drops and pressure spikes in the inner end 38 of the slots.
- the inlet 48 and the outlet 50 are, as visible in the rear view of figure 4, elongated and arcuate openings diametrically opposed and arranged to cover an angular width that, in the exemplary embodiment chosen of a blade pump having four blades at 90° from each other, is approximately 90°.
- the blade pump 12 is further provided with a second inlet 58 radially and inwardly arranged parallel to the first inlet 48.
- said second inlet 58 also has an elongated and arcuate shape and also an angular width W58 of 90°.
- the second inlet 58 can be a simple hole.
- the radial distance between the first inlet 48 and the second inlet 58 is substantially the length of the slot 34 so that, as the first inlet 48 fills the first chamber CI, the second inlet 58 directly fills in the spring compartment at the inner end 38 of the slot bypassing the channel 56.
- the rotor 20 of the blade pump is provided with arcuate grooves 60 dug in the first face 28 of the rotor and extending from a large entry 62 opening in the inner end 38 of each slot toward a distant closed pointy end 64. As visible in the 3D view of figure 7, the grooves 60 extend on an arc of
- the groove 60 passes in front of the second inlet 58 and, when a slot 34 exits the openings of the first 48 and second 58 inlets, the groove 60 continues to face the second inlet 58 keeping open a fluid communication from said second inlet 58 to the inner end 38 of the slot.
- the inner end 38 of the groove remains in fluid communication with the inlet for an extended time corresponding roughly to a rotation of the rotor of about 170°.
- the angular width W58 of the second inlet opening 58 is approximately of said angle 360°/N and, the angular width W60 of the groove 60 is slightly shorter than said angle 360°/N.
- the grooves 60 may have a constant width.
- the grooves 60 follow the slots 34 meaning that, in use, the slot 34 passes first in front of the inlet and, the groove 60 follows.
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
A blade pump having a housing with an inner plate (22), an outer plate and a peripheral liner (26) and, a rotor (20) provided with a plurality of slots which open in said peripheral face, a blade (40) being slidably arranged in each slot and, a spring being compressed at the bottom of said slot outwardly biasing said blade (40) so that, the blade slides against said liner (26) of the housing 10 defining a plurality of arcuate chambers (C). The blade pump is provided with an inlet (48) opening in said chamber (C) and also with a second inlet (58) opening in the inner end (38) of the slot.
Description
VANE PUMP TECHNICAL FIELD
The present invention relates to a blade pump and more particularly to means for maintaining fluid pressure around the blades of the pump.
BACKGROUND OF THE INVENTION
In a blade pump, blades radially sliding in the slots of a rotor move in and out of their slots as a function of the rotation of the rotor. A fluid
communication is provided to enable fluid to inwardly flow toward the bottom of the slot in order to compensate for pressure drops and spikes when the blade moves.
In diesel injection equipment, blade pumps are typically utilized as feed pump drawing fuel from a low pressure tank and delivering it to a high pressure pump. Under certain conditions of the engine equipment, for instance at high RPM and low atmospheric pressure, pressure spikes are observed around the blade generating cavitation erosion at the rotor and disturbing the blade displacements and the feed pump operation.
SUMMARY OF THE INVENTION
Accordingly, it is an object of the present invention to resolve the above mentioned problems in providing a blade pump having a housing with an inner plate, an outer plate and a peripheral liner defining an inner space in which a rotor is adapted to rotate about a main axis. The rotor has a first face sliding against the inner plate, a second face sliding against the outer plate and a peripheral cylindrical face. The rotor is provided with a plurality of slots which open in said peripheral face, a blade being slidably arranged in each slot and, a spring being compressed at the bottom, or inner end, of said slot, against the inner end of the blade, outwardly biasing said blade so that, the blade protrudes outside the slot and the outer end of the blade slides against said liner of the housing thus defining a plurality of arcuate chambers between the peripheral face of the rotor, the liner and the outer end of the blades. The volume of said chambers cyclically varies between large and small as the rotor rotates.
The blade pump is further provided with an inlet opening in a large volume chamber and, an outlet opening in the small volume chamber so that in use, a fluid entering the inlet fills a large volume and is compressed and pushed toward the outlet.
The blade pump is further provided with a second inlet opening in the inner end of the slot so that, in use, said fluid flows into the chamber via the first inlet and, into the volume wherein a spring is compressed via the second opening.
Also, the second inlet extends over an angular width enabling, in use, the inner end of the slot to be filled over an extended rotational angle of the rotor.
Said angular width is substantially two third of the angle between two consecutive slots.
Also, said second opening has an arcuate shape.
Also, the rotor is further provided with grooves dug in its first side face, each groove opening at an entry end in the inner end of the slot and extending in said first side face toward a closed end so that, in use, fluid entering via said second inlet flows into said groove toward the inner end of the slot while said inner end is no longer facing said second inlet.
Also, the groove extends over an angular width W enabling, in operation of the pump, the inner end of the slot to be filled over an extended time.
The angular width of the groove is substantially two third of the angle between two consecutive slots.
Also, each blade is having an outer end with two sealing tip edges, sliding against the liner and, a fluid communication channel extending through the blade from its inner end, where said channel opens in the inner end of the slot where the spring is compressed, to the outer end where said channel opens between said tip edges.
The invention further extends to a fuel pump assembly adapted to be arranged in a fuel injection equipment, said fuel pump assembly comprising a feed pump for drawing fuel from a low pressure tank and for delivering it to a high pressure pump, said feed pump being a blade pump as described above.
BRIEF DESCRIPTION OF THE DRAWINGS
The present invention is now described by way of example with reference to the accompanying drawings in which:
Figure 1 is a section of a diesel pump comprising a blade pump and a high pressure pump.
Figure 2 is an axial section of the blade pump of figure 1 adapted to rotate about a main axis XI .
Figure 3 is a magnified view of a portion of figure 2, said view detailing the area of a blade in an axial XI section.
Figure 4 is a radial section of the blade pump of figure 2, said section enabling view of a first side face of the pump.
Figure 5 is a magnified view of figure 4 of an inlet area arranged in said first side face.
Figure 6 is a magnified view detailing the blade in an radial XI section. Figure 7 is a 3D view of a rotor of the pump of figure 2.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
In an internal combustion engine provided with a direct fuel injection equipment, a pump assembly 10 represented on figure 1 is adapted to draw fuel from a low pressure tank, to pressurize and to deliver said fuel to a high pressure reservoir from which it is distributed to fuel injectors.
The fuel pump assembly 10, which in the example chosen is a diesel pump, comprises a transfer pump 12 and a high pressure pump 14, both pumps being fixed to a cambox 16. A camshaft 18, adapted to rotate in said cambox 16, imparts rotational movement to the transfer pump 12 and reciprocal linear movements to one or more pistons of the high pressure pump 14.
The transfer pump 12 now described is a blade pump 12 represented and described in reference to the figures 2 to 7.
The typical blade pump 12 has a housing with peripheral walls defining an inner space S in which a rotor 20 rotates about a main axis XI . The peripheral walls comprise an inner plate 22, also identified as distribution plate 22, transverse to said main axis XI, an outer plate 24 also transverse to said main axis XI and, a peripheral liner 26 that defines a cylindrical track.
The rotor 20 has a cylindrical shape and it has a first face 28 adapted to slide against the inner face of the inner plate 22 of the housing, a parallel second face 30 adapted to slide against the inner face of the outer plate 24 of the housing and, a peripheral cylindrical face 32 distant from the liner 26.
The rotor 20 is provided with a plurality of slots 34 radially extending from an outer opening 36 in the peripheral face 32 to an inner end 38 closer to the axis XI . In each slot 34 is slidably arranged a blade 40 extending from an inner end 42 close to the inner end 38 of the slot, to an outer end 44 protruding from the slot through the outer opening 36 in the peripheral face of the rotor. Each blade 40 is outwardly pushed by a spring 46 compressed between the inner end 38 of the slot and an inner end 42 of the blade, the outer end 44 of the blade being biased in contact and sliding, in use, against the liner 26 of the housing. The main axis XI and the liner axis X2 being offset, the arrangement of the rotor in the housing defines between the peripheral face 32 of the rotor, the liner 26 of the housing and the outer end 44 of the blades, a plurality of arcuate chambers C which, in use as the rotor rotates, volume cyclically varies between a large volume and a small volume.
The blade pump 12 further comprises an inlet 48 and an outlet 50, both provided in the inner plate 22 of the housing, the inlet 48 opening in a first chamber CI that volumes increases and, the outlet 50 opening in a second chamber C2 which volume decreases. The offset between the main axis XI and the liner axis X2 is set so the top of the rotor 20 is almost tangent to the liner and so the chamber at the top has a volume almost null while the volume of the chamber at the bottom is maximum.
In use fuel fills the first chamber C 1 and, as the rotor 20 rotates about the main axis XI, said fuel is moved toward the outlet 50 and compressed. Exiting via the outlet 50, the fuel is delivered to the high pressure pump 14. Also as visible in figure 4 and magnified in figure 6, each blade 40 is provided with a double tip edge 52, 54 and with an inner channel 56 radially extending between the inner end 42 of the blade, where said channel opens in the spring compartment and, the outer end 44 of the blade, where said channel 52 opens between said two tip edges 52, 54, each of said tip edges 52, 54 sliding against the liner 26. In use, the blades 40 cyclically slide in and out of their respective slot 34 and, fuel flows through
said channel 56 avoiding pressure drops and pressure spikes in the inner end 38 of the slots.
The inlet 48 and the outlet 50 are, as visible in the rear view of figure 4, elongated and arcuate openings diametrically opposed and arranged to cover an angular width that, in the exemplary embodiment chosen of a blade pump having four blades at 90° from each other, is approximately 90°. The rotor 20 rotating in the clockwise direction of figure 4, the narrowing tail of the first chamber CI is visible through the inlet 48 while the narrowing head of the second chamber C2 is visible through the outlet 50.
The blade pump 12 is further provided with a second inlet 58 radially and inwardly arranged parallel to the first inlet 48. In the embodiment presented, said second inlet 58 also has an elongated and arcuate shape and also an angular width W58 of 90°. In other embodiments the second inlet 58 can be a simple hole. The radial distance between the first inlet 48 and the second inlet 58 is substantially the length of the slot 34 so that, as the first inlet 48 fills the first chamber CI, the second inlet 58 directly fills in the spring compartment at the inner end 38 of the slot bypassing the channel 56.
Furthermore, the rotor 20 of the blade pump is provided with arcuate grooves 60 dug in the first face 28 of the rotor and extending from a large entry 62 opening in the inner end 38 of each slot toward a distant closed pointy end 64. As visible in the 3D view of figure 7, the grooves 60 extend on an arc of
approximately slightly shorter than 80° at a substantially constant radial distance from the main axis XI and they have a shape narrowing as approaching said pointy end 64. As shown on the figures 4 and 5, the groove 60 passes in front of the second inlet 58 and, when a slot 34 exits the openings of the first 48 and second 58 inlets, the groove 60 continues to face the second inlet 58 keeping open a fluid communication from said second inlet 58 to the inner end 38 of the slot. In combining the angular width W58 of the second inlet 58 and the angular width W60 of the groove 60, in use, the inner end 38 of the groove remains in fluid communication with the inlet for an extended time corresponding roughly to a rotation of the rotor of about 170°. In a general case of a pump having N blades spread every 360°/N, the angular width W58 of the second inlet opening 58 is approximately of said angle 360°/N and, the angular width W60 of the groove 60
is slightly shorter than said angle 360°/N. Other embodiments are possible for the grooves 60 that instead of a narrowing shape may have a constant width. Also, in the figures, the grooves 60 follow the slots 34 meaning that, in use, the slot 34 passes first in front of the inlet and, the groove 60 follows.
LIST OF REFERENCES
XI main axis
S inner space
C chamber
CI first chamber - inlet chamber
C2 second chamber - outlet chamber
W58 angular width of the inlet
W60 angular width of the groove
10 fuel pump assembly
12 transfer pump - blade pump
14 high pressure pump
16 cambox
18 camshaft
20 rotor
22 inner plate of the housing
24 outer plate of the housing
26 liner
28 first face of the rotor
30 second face of the rotor
32 peripheral face of the rotor
34 slot
36 outer opening
38 inner end
40 blade
42 inner end of the blade
44 outer end of the blade
46 spring
48 inlet
50 outlet
52 tip edge
54 tip edge
56 blade inner channel
58 second inlet
60 groove
62 large entry of the groove
64 pointy end of the groove - closed end
Claims
1. Vane pump (12) having a housing with an inner plate (22), an outer plate (24) and a peripheral liner (26) defining an inner space (S) in which a rotor (20) is adapted to rotate about a main axis (XI), the rotor (20) having a first face (28) sliding against the inner plate (22), a second face (30) sliding against the outer plate (24) and a peripheral cylindrical face (32), the rotor (20) being provided with a plurality of slots (34) which open in said peripheral face (32), a blade (40) being slidably arranged in each slot (34) and, a spring (46) being compressed at the bottom, or inner end (38), of said slot, against the inner end (42) of the blade, outwardly biasing said blade (40) so that, the blade protrudes outside the slot (34) and the outer end (44) of the blade slides against said liner (26) of the housing thus defining a plurality of arcuate chambers (C, CI, C2) between the peripheral face (32) of the rotor, the liner (26) and the outer end (44) of the blades, the volume of said chambers (C, CI, C2) cyclically varying between large and small as the rotor (20) rotates;
the blade pump (12) being further provided with an inlet (48) opening in a large volume chamber (CI) and, an outlet (50) opening in the small volume chamber (C2) so that in use, a fluid entering the inlet (48) fills a large volume and is compressed and pushed toward the outlet (50),
characterized in that
the blade pump (12) is further provided with a second inlet (58) opening in the inner end (38) of the slots so that, in use, said fluid flows into the chamber (CI) via the first inlet (48) and, into the volume wherein a spring is compressed via the second opening (58) and wherein,
the rotor (20) is further provided with grooves (60) dug in its first side face (28), each groove (60) opening at an entry end (62) in the inner end (38) of the slot and extending in said first side face toward a closed end (64) so that, in use, fluid entering via said second inlet (58) flows into said groove (60) toward the inner end (38) of the slot while said inner end (38) is no longer facing said second inlet (58).
2. Vane pump (12) as claimed in the preceding claim wherein the second inlet (58) extends over an angular width (W) enabling, in use, the inner end (28) of the slot to be filled over an extended rotational angle of the rotor.
3. Vane pump (12) as claimed in claim 2 wherein said angular width is substantially two third of the angle between two consecutive slots.
4. Vane pump (12) as claimed in any one of the preceding claims wherein said second opening (58) has an arcuate shape.
5. Vane pump (12) as claimed in claim 1 wherein said groove (60) extends over an angular width (W60) enabling, in operation of the pump (12), the inner end (38) of the slot to be filled over an extended time.
6. Vane pump (12) as claimed in claim 5 wherein said angular width (W60) of the groove is substantially two third of the angle between two consecutive slots (34).
7. Vane pump (12) as claimed in any one of the preceding claims wherein each blade (40) is having an outer end (44) with two sealing tip edges (52, 54) sliding against the liner (26) and, a fluid communication channel (56) extending through the blade (40) from its inner end (42), where said channel (56) opens in the inner end (38) of the slot where the spring (46) is compressed, to the outer end (44) where said channel (52) opens between said tip edges (52, 54).
8 Fuel pump assembly (10) adapted to be arranged in a fuel injection equipment, said fuel pump assembly (10) comprising a feed pump (12) for drawing fuel from a low pressure tank and for delivering it to a high pressure pump (14), said feed pump being a blade pump (12) as claimed in any one of the preceding claims.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201780060954.3A CN109804137B (en) | 2016-10-03 | 2017-09-29 | Vane pump |
KR1020197009537A KR102307758B1 (en) | 2016-10-03 | 2017-09-29 | vane pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB1616779.3A GB2554677B (en) | 2016-10-03 | 2016-10-03 | Pressure balancing vane pump |
GB1616779.3 | 2016-10-03 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2018065319A1 true WO2018065319A1 (en) | 2018-04-12 |
Family
ID=57571096
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2017/074825 WO2018065319A1 (en) | 2016-10-03 | 2017-09-29 | Vane pump |
Country Status (4)
Country | Link |
---|---|
KR (1) | KR102307758B1 (en) |
CN (1) | CN109804137B (en) |
GB (1) | GB2554677B (en) |
WO (1) | WO2018065319A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2581845B (en) * | 2019-03-01 | 2021-07-21 | Delphi Tech Ip Ltd | Vane pump |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2861517A (en) * | 1952-07-26 | 1958-11-25 | American Brake Shoe Co | Vane pump |
US2924182A (en) * | 1955-08-31 | 1960-02-09 | American Brake Shoe Co | Fluid pressure energy translating device |
US5188522A (en) * | 1990-10-25 | 1993-02-23 | Atsugi Unisia Corporation | Vane pump with a throttling groove in the rotor |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3024736A (en) * | 1959-05-14 | 1962-03-13 | Teves Kg Alfred | Rotary hydrostatic machine |
US3204565A (en) * | 1962-05-09 | 1965-09-07 | Sperry Rand Corp | Power transmission |
GB9202083D0 (en) * | 1992-01-31 | 1992-03-18 | Lucas Ind Plc | Rotary pump |
CN2405042Y (en) * | 1999-12-21 | 2000-11-08 | 孙宏磊 | Pump with multiple vane |
JP4927601B2 (en) * | 2007-03-05 | 2012-05-09 | 日立オートモティブシステムズ株式会社 | Variable displacement vane pump |
CN103671099A (en) * | 2013-12-25 | 2014-03-26 | 成都威特电喷有限责任公司 | Sliding-vane-type oil delivery pump |
-
2016
- 2016-10-03 GB GB1616779.3A patent/GB2554677B/en active Active
-
2017
- 2017-09-29 KR KR1020197009537A patent/KR102307758B1/en active IP Right Grant
- 2017-09-29 WO PCT/EP2017/074825 patent/WO2018065319A1/en active Application Filing
- 2017-09-29 CN CN201780060954.3A patent/CN109804137B/en active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2861517A (en) * | 1952-07-26 | 1958-11-25 | American Brake Shoe Co | Vane pump |
US2924182A (en) * | 1955-08-31 | 1960-02-09 | American Brake Shoe Co | Fluid pressure energy translating device |
US5188522A (en) * | 1990-10-25 | 1993-02-23 | Atsugi Unisia Corporation | Vane pump with a throttling groove in the rotor |
Also Published As
Publication number | Publication date |
---|---|
GB2554677B (en) | 2020-03-25 |
KR102307758B1 (en) | 2021-10-05 |
GB201616779D0 (en) | 2016-11-16 |
GB2554677A (en) | 2018-04-11 |
CN109804137A (en) | 2019-05-24 |
KR20190057311A (en) | 2019-05-28 |
CN109804137B (en) | 2021-01-05 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US9366251B2 (en) | Vane pump with a vane ring, a vane ring housing chamber and vane ring opposite pressure chambers | |
US9239050B2 (en) | Vane pump | |
US10024207B2 (en) | Variable displacement lubricant pump | |
US9759103B2 (en) | Lubricant vane pump | |
US10247186B2 (en) | Variable lubricant vane pump | |
US8740592B2 (en) | Adjustable vane cell pump with a slide comprising recesses | |
US8807974B2 (en) | Split discharge vane pump and fluid metering system therefor | |
US9206800B2 (en) | Multiple stage passive variable displacement vane pump | |
US4008002A (en) | Vane pump with speed responsive check plate deflection | |
WO2018065319A1 (en) | Vane pump | |
US9856873B2 (en) | Vane pump | |
JP2016121608A (en) | Variable capacity pump | |
CN109923313B (en) | Vane pump | |
US9909584B2 (en) | Lubricant vane pump | |
CN208502929U (en) | Vane pump and corresponding high pressure fuel pump and diesel engine | |
US20180306182A1 (en) | Vane pump | |
US20210270266A1 (en) | Rotary vane pump | |
US20230108147A1 (en) | Flow channeling structure | |
US3175505A (en) | Soltau pumps | |
JP2020533516A (en) | Single vane rotary vacuum pump with oil supply aisle channel |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 17777272 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 20197009537 Country of ref document: KR Kind code of ref document: A |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 17777272 Country of ref document: EP Kind code of ref document: A1 |