GB2552328A - Transfer pump - Google Patents
Transfer pump Download PDFInfo
- Publication number
- GB2552328A GB2552328A GB1612421.6A GB201612421A GB2552328A GB 2552328 A GB2552328 A GB 2552328A GB 201612421 A GB201612421 A GB 201612421A GB 2552328 A GB2552328 A GB 2552328A
- Authority
- GB
- United Kingdom
- Prior art keywords
- liner
- chamber
- liner member
- pump
- rotary vane
- 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- Withdrawn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
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
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
- F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
-
- 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
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
-
- 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
- F04C2/3441—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 one line or continuous surface substantially parallel to the axis of rotation
- F04C2/3442—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 one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
-
- 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
-
- 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
- F01C2021/16—Other regulation or control
-
- 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
- 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
- F04C2240/00—Components
- F04C2240/30—Casings or housings
-
- 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
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/802—Liners
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
A rotary vane pump 12, eg a transfer pump in diesel fuel injection equipment, has a rotor 24 with vanes 28 which follow a cam profile defined by a liner member 38. The liner member 38 is arranged to move within the pump body 22, eg in a liner chamber 40, under the influence of the outlet pressure between a maximum-flow position and a zero-flow position, the displacements of the liner member 38 varying the relative volumes of the peripheral pump chambers 50, 52, 54, 56 thus providing a self-regulating flow means to the pump. The liner 38 may be biased by a spring 77 toward the maximum flow position eg in which side 44 of the liner 38 abuts side 72 of the liner chamber 40.
Description
(54) Title of the Invention: Transfer pump
Abstract Title: Rotary vane transfer pump with movable liner for self-regulation of flow (57) A rotary vane pump 12, eg a transfer pump in diesel fuel injection equipment, has a rotor 24 with vanes 28 which follow a cam profile defined by a liner member 38. The liner member 38 is arranged to move within the pump body 22, eg in a liner chamber 40, under the influence of the outlet pressure between a maximum-flow position and a zero-flow position, the displacements of the liner member 38 varying the relative volumes of the peripheral pump chambers 50, 52, 54, 56 thus providing a self-regulating flow means to the pump. The liner 38 may be biased by a spring 77 toward the maximum flow position eg in which side 44 of the liner 38 abuts side 72 of the liner chamber 40.
58
FIG. 2 /5
FIG. 1
2/5
FIG. 2
3/5
FIG. 3
4/5
co co
5/5 ο
co co
FIG. 6 FIG. 7 FIG.
Transfer pump
TECHNICAL FIELD
The present invention relates to a rotary vane pump and more particularly when used as a transfer pump in a diesel fuel injection equipment.
BACKGROUND OF THE INVENTION
The rotor of a rotary vane pump is provided with radially sliding vanes, or blades, sliding against an inner cam profde, or circular profde, of a liner member. The vanes split the annular volume comprised between the rotor and the liner into a plurality of peripheral chambers in which open a fuel inlet and a fuel outlet. The rotor and the cam profile have parallel and offset axes and, the throughput flow transferred by such well-known rotary vane pump varies as a function of the rotational speed of the rotor, the inlet flow being typically at atmospheric pressure and the outlet flow being at a few bars pressure for diesel transfer pump and may be higher up 100 bars for other applications.
In a diesel injection equipment of an internal combustion engine, such pumps is used as transfer pump sucking fuel from a tank and flowing it to a high pressure pump. A metering valve arranged between the outlet of the transfer pump and the inlet of the high pressure pump adjusts and restricts the flow as per the need of the engine, the remaining pressurized flow is recirculated back to transfer pump inlet representing a waste of energy of the transfer pump generating temperature build up in the fuel, an increased wear of the vanes as a result of higher pumping loads, deterioration and formation of debris in fuel, etc.
SUMMARY OF THE INVENTION
Accordingly, it is an object of the present invention to resolve the above mentioned problems in providing a rotary vane pump for transferring a flow between an inlet and an outlet said pump having a body wherein a rotor is adapted to rotate about a main axis, said rotor being provided with vanes outwardly biased against a cam profile defined within a liner member, the vanes splitting in a plurality of peripheral chambers the space comprised between the rotor and the liner member, space in which open the fluid inlet and the fluid outlet.
Advantageously, the liner member is arranged to move under the influence of the outlet pressure between a maximum-flow position and a zeroflow position, said displacements of the liner member varying the relative volumes of said peripheral chambers thus providing a self-regulating flow means to the pump. Also, the liner member is slidably arranged in a liner chamber defined within the body and wherein said liner member is biased by a spring toward the maximum-flow position.
Also, the liner member is centrally holed to define the cam profile, a second fluid communication being defined between the outlet and a compressive chamber defined in the liner chamber in a space outward the liner member.
Also, a first fluid communication is defined between the inlet and a low pressure chamber arranged in the liner chamber outward the liner member in a space opposite to the compressive chamber.
Also, the liner member has two lateral parallel straight sides adapted to slide against complementary lateral sides faces of the liner chamber thus defining guiding means for the liner member to move within the body.
Also, the liner member translates following said guiding means along a sliding axis perpendicular to the main axis.
Also, the compressive chamber is defined between the second side of the liner member and the second side of the liner chamber, the pressure in said compressive chamber biasing the liner member toward the zero-flow position against the spring.
Also, the spring is compressed between the liner member and the liner chamber and biases the liner member toward the maximum-flow position.
Also, the spring force can be adjusted by a screw type adjusting mechanism.
The invention further extends to a fuel pump module comprising a rotary vane pump as described above, a valve adapted to adjust, in use, the output flow and, a high pressure pump wherein a piston displaces following a pumping cycle.
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 an isometric view of a fuel pump as per the invention.
Figure 2 is a section transverse to a main axis of the transfer pump arranged on the fuel pump of figure 1.
Figure 3 is a 3D view of another embodiment of the transfer pump as per the invention.
Figure 4 and 5 are example of distinct liners of the transfer pump.
Figure 6, 7 and 8 are similar as figure 2 and aligned to present three distinct phases of operation of the transfer pump.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
In reference to figure 1 is presented a fuel pump module 10 of a diesel injection equipment of an internal combustion engine, not shown. The fuel pump module 10 integrally comprises a transfer pump 12, an inlet metering valve 14, hereafter IMV 14, and two high pressure pumps 16, all fixed to a body 18 of the said fuel pump module 10. Further components, such as a filter, fuel pipes, are not represented on the figure. A driveshaft 20, driven by the crankshaft of the engine or any other drive arrangement, is adapted to extend and rotate in said body 18 about a main axis Al.
In use, the driveshaft 20 drives the transfer pump 12 in rotation and, it also imparts displacements to a piston of the high pressure pumps 16, said piston following a pumping cycle for pressurizing fuel and delivering it to fuel injectors.
More in details, the transfer pump 12 is a rotary vane pump comprising its own body 22 adapted to be fixed to the body 18 of the fuel pump, said rotary vane pump body 22 defining an inner volume wherein a rotor 24 is engaged and fixed at an end of the driveshaft 20. In the embodiment described, said rotor 24 is provided with radial slots 26, four being represented on the embodiment of figure 2 although another quantity is possible and, in each slot 26 is slidably engaged a vane 28 outwardly pushed by a spring 30 compressed between the bottom end of the slot 26 and an inner edge 32 of the vane. Opposed to the inner edge 32, each vane has an outer edge 34 slidably following a cam profile 36 defined by a liner member 38 arranged in a liner chamber 40.
As visible on the two embodiments of liner members 38 represented on figures 4 and 5, said liner 38 has substantially a semi-oblong shape and is provided with a central opening which inner border defines said cam profile 36. In figure 4 said profile is strictly circular and, in figure 5 the profile is slightly noncircular but in any case, said central opening accepts a liner axis A2 that is parallel to the main axis Al. By semi-oblong is meant a four-sides closed shape comprising three straight sides 42, 44, 46 arranged at right angle from each other and, a fourth side 48 having a semi-circular profile. The second straight side 44, shown on the top of the figure, is perpendicular to the lateral first 42 and third 46 straight lateral sides that are parallel to each other and, is opposed to the fourth 48 semi-circular side shown on the bottom of the figure.
As visible on figure 2, the annular space comprised between the rotor 24 and the cam profile 36 is divided by the vanes 28 in four peripheral chambers 50, 52, 54, 56 each chamber having a specific volume.
The rotary vane pump 12 is further provided with an inlet channel 58 extending from an outer opening 60 to an inner opening 62 that opens in said divided volume substantially in the top of it and also with, an outlet channel 64 also extending from an outer opening 66 to an inner opening 68 that also opens in said divided space but opposite in the bottom part of it to the inlet inner opening 62 and therefore, the inlet inner opening 62 and the outlet inner opening 68 open in different peripheral chambers 50, 52, 54, 56.
Also, the liner member 38 is slidably arranged in the liner chamber 40 defined in the transfer pump body 22, said chamber 48 having a similar semioblong shape as the liner member and comprising three straight sides 70, 72, 74 arranged at right angle from each other and, a fourth side 76 having a semicircular profile. The second straight side 72, shown on the top of the figure, is perpendicular to the lateral first 70 and third 74 straight sides that are parallel to each other and, is opposed to the fourth 76 semi-circular side shown on the bottom of the figure.
While the width of liner member 38, measured between its lateral sides 42, 46 is slidably adjusted to the width of the liner chamber 40, measured between its lateral sides 70, 74 and, the height of the liner member perpendicular to its width, is slightly smaller than the height of the liner chamber therefore, the liner member 38 is adapted to slide along a sliding axis A3 parallel to said lateral sliding faces and perpendicular to the main axis Al and to the liner axis A2.
Furthermore a spring 77 is compressed in a low pressure chamber 79 defined between the fourth side 48 of the liner member and the fourth side 76 of the liner chamber 40, said low pressure chamber 79 being in direct and permanent first fluid communication 81 with the inlet channel 58. An adjustment screw 78 connected to the spring 77 enable to ajdjust the preload of the spring 77. Turning this screw 78 increases and decreases the preload on the spring 77. If the preload is higher maximum pressure of the pump is higher, therefore, the same pump 12 can be employed in different applications, just adjusting the screw 77. The pump 12 may have higher flow rates at same outlet pressure by increasing the preload or, lower flow rates at same outlet pressure by decreasing the preload.
Therefore the liner member 38 is adapted to slide, along said sliding axis A3, in the liner chamber 40 between a first position Pl where the compression of the spring 77 is minimal, the second side 44 of the liner abutting against the second side 72 of the chamber and, a second position P2 where the compression of the spring 77 is maximal, the second side 44 of the liner being distant from the second side 72 of the chamber. A compressive chamber 80 is defined between said second sides 44, 72 of the liner member and of the liner chamber, said compressive chamber 80 having a direct and permanent second fluid communication 82 with the outlet channel 64.
In the first position Pl, the volume of the compressive chamber 80 is minimal and the volume of the low pressure chamber 79 is maximal and, in the second position P2, the volume of the compressive chamber 80 is maximal and the volume of the low pressure chamber 79 is minimal.. Furthermore, in the first position, the main axis Al and the liner axis A2 are parallel and distinct and, in the second position P2 said axes Al, A2 coincide.
In a first embodiment shown on figure 2, the second side 44 of the liner is not exactly straight but comprises a slopped portion, on the left of the figure as per the arbitrary orientation of the figure, the compressive chamber 80 having a triangular shape.
In a second embodiment shown on figure 3, the second side 44 of the liner is straight and, the first fluid communication 81 between the inlet and the low pressure chamber 79 is arranged adjacent to said chamber 79, via a first cavity 84. Also, the second fluid communication 82 between the outlet and the compressive chamber 80 is arranged right above the second side 72 of the liner chamber via a cavity 86, the compressive chamber 80 being rectangular extending along the complete width to the liner chamber.
Also, the liner member 38 and the liner chamber 40 are both described semi-oblong, thus defining a low pressure chamber 79 having semi-circular or “moon-like” shape but, straight fourth sides 48, 76 are also possible and, the semicircular profile, although easing the overall packaging of the transfer pump, is not mandatory to the invention.
In reference to the figures 6, 7 and 8 is now described the operation of the transfer pump 12.
In a first stage, figure 6, the IMV 14 is fully open. The pressure in the compressive chamber 80 is minimal and the spring 77 biases the liner member 38 in the first position Pl, or maximum flow position, where the volume of the peripheral chambers 50, 52, 54, 56 vary from maximum for the top chamber wherein opens the inlet inner opening 62, to minimal for the bottom chamber wherein opens the outlet inner opening 68. The volume difference VD between said inlet chamber and outlet chamber is maximum VD1 and therefore in this first stage configuration, the inlet flow and the outlet flow are maximum.
In a second stage, figure 7, the IMV 14 is partially closed restricting said outlet flow. The pressure in the compressive chamber 80 rises and the liner member 38 downwardly slides by distance D further compressing the spring 77. Although the volume difference VD between said inlet chamber and outlet chamber remains, said difference VD2 has decreased relative to the first stage, the downward displacement D of the liner member 38 having reduced the inlet peripheral chamber volume and having raised the outlet peripheral chamber volume. Therefore in the second stage configuration, the inlet flow sucked is reduced, and so is the outlet flow.
In a third stage, figure 8, the IMV 14 is totally, or almost totally closed. The pressure in the compressive chamber 80 rises to a maximum value and the liner member 38 downwardly slides further to the second position P2, or zero flow position, fully compressing the spring 77 and, since liner axis A2 and main axis Al are concentric at the second position P2 the inlet chamber and outlet chamber have similar volume and the volume difference VD3 is canceled, the downward displacement D of the liner member 38 having equalized the inlet peripheral chamber volume and the outlet peripheral chamber volume. Therefore in the third stage configuration, the inlet sucked flow is canceled, and so is the outlet flow.
Thanks to this moveable liner member 38 varying the volume difference VD, the transfer pump 12 is provided with a self-regulating flow means that adjusts the flow to the need of the engine. Furthermore, the return valve that was mandatory in the prior art is no longer needed.
LIST OF REFERENCES
| Al | main axis |
| A2 | liner axis |
| A3 | sliding axis |
| Pl | first position of the liner |
| P2 | second position of the liner |
| D | distance |
| VD | volume difference |
| 10 | fuel pump |
| 12 | transfer pump - rotary vane pump |
| 14 | inlet metering valve - IMV |
| 16 | high pressure pump |
| 18 | body of the fuel pump |
| 20 | camshaft |
| 22 | body of the transfer pump |
| 24 | rotor |
| 26 | radial slots |
| 28 | vane |
| 30 | spring |
| 32 | inner edge of a vane |
| 34 | outer edge of a vane |
| 36 | cam profile |
| 38 | liner member |
| 40 | liner chamber |
first straight side of the liner member second straight side of the liner member third straight side of the liner member fourth side of the liner member peripheral chamber peripheral chamber peripheral chamber peripheral chamber inlet channel inlet outer opening inlet inner opening outlet channel outlet outer opening outlet inner opening first straight side of the liner chamber second straight side of the liner chamber third straight side of the liner chamber fourth side of the liner chamber spring screw low pressure chamber compressive chamber first fluid communication inlet/low pressure chamber second fluid communication outlet/compressive chamber first cavity second cavity
Claims (10)
1. Rotary vane pump (12) for transferring a flow between an inlet (58, 60, 62) and an outlet (64, 66, 68), said pump (12) having a body (22) wherein a rotor (24) is adapted to rotate about a main axis (Al), said rotor (24) being provided with vanes (28) outwardly biased against a cam profile (36) defined within a liner member (38), the vanes (28) splitting in a plurality of peripheral chambers (50, 52, 54, 56) the space comprised between the rotor (24) and the liner member (38), space in which open the fluid inlet (62) and the fluid outlet(68), characterized in that the liner member (38) is arranged to move under the influence of the outlet pressure between a maximum-flow position (Pl) and a zero-flow position (P2), said displacements of the liner member (38) varying the relative volumes of said peripheral chambers (50, 52, 54, 56) thus providing a self-regulating flow means to the pump.
2. Rotary vane pump (12) as claimed in the preceding claim wherein the liner member (38) is slidably arranged in a liner chamber (40) defined within the body (22) and wherein said liner member (38) is biased by a spring (77) toward the maximum-flow position (Pl).
3. Rotary vane pump (12) as claimed in claim 2 wherein the liner member (38) is centrally holed to define the cam profile (36), a second fluid communication (82) being defined between the outlet (64) and a compressive chamber (80) defined in the liner chamber (40) in a space outward the liner member (38).
4. Rotary vane pump (12) as claimed in claims 3 wherein a first fluid communication (81) is defined between the inlet (58) and a low pressure chamber (79) arranged in the liner chamber (40) outward the liner member (38)in a space opposite to the compressive chamber (80).
5. Rotary vane pump (12) as claimed in claim 4 wherein the liner member (38) has two lateral parallel straight sides (42, 46) adapted to slide against complementary lateral sides faces (70, 74) of the liner chamber thus defining guiding means for the liner member to move within the body (22).
6. Rotary vane pump (12) as claimed in claim 5 wherein the liner member (38) translates following said guiding means along a sliding axis (A3) perpendicular to the main axis (Al).
10
7. Rotary vane pump (12) as claimed in claim 6 wherein the compressive chamber (80) is defined between the second side (44) of the liner member and the second side (72) of the liner chamber, the pressure in said compressive chamber (80) biasing the liner member (38) toward the zero-flow position (P2) against the spring (77)
8. Rotary vane pump (12) as claimed in claim 7 wherein the spring (77) is compressed between the liner member (38) and the liner chamber (40) and biases the liner member (28) toward the maximum-flow position (Pl).
20
9. Rotary vane pump (12) as claimed in any one of the claims 2-8 wherein the spring (77) force can be adjusted by a screw type (78) adjusting mechanism.
10. Fuel pump module (10) comprising a rotary vane pump (12) as claimed in any one of the preceding claims, a valve 14 adapted to adjust, in use, the output
25 flow and, a high pressure pump (16) wherein a piston displaces following a pumping cycle.
Intellectual
Property
Office
Application No: GB1612421.6
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB1612421.6A GB2552328A (en) | 2016-07-18 | 2016-07-18 | Transfer pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB1612421.6A GB2552328A (en) | 2016-07-18 | 2016-07-18 | Transfer pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB201612421D0 GB201612421D0 (en) | 2016-08-31 |
| GB2552328A true GB2552328A (en) | 2018-01-24 |
Family
ID=56890473
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB1612421.6A Withdrawn GB2552328A (en) | 2016-07-18 | 2016-07-18 | Transfer pump |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2552328A (en) |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2551451A1 (en) * | 1975-11-15 | 1977-05-18 | Daimler Benz Ag | Rotary piston pump with eccentric rotor - has radially slidable seal strips, and stator hydraulically adjustable to vary eccentricity |
| JPS5970891A (en) * | 1982-10-16 | 1984-04-21 | Toyota Central Res & Dev Lab Inc | Variable capacity type vane pump |
| EP0902181A2 (en) * | 1997-09-11 | 1999-03-17 | Denso Corporation | Variable-discharge-rate high-pressure pump |
| WO2007015135A1 (en) * | 2005-08-02 | 2007-02-08 | Pierburg Pump Technology Italy S.P.A. | Two-setting variable-eccentricity vane pump |
| US20100192921A1 (en) * | 2007-09-18 | 2010-08-05 | Christian Langenbach | Fuel pump, in particular for a fuel system of a piston engine |
| WO2013093711A1 (en) * | 2011-12-22 | 2013-06-27 | Vhit S.P.A. | Rotary positive displacement pump and method of regulating its displacement |
| JP2014163337A (en) * | 2013-02-27 | 2014-09-08 | Toyooki Kogyo Co Ltd | Variable capacity type vane pump |
| WO2014198322A1 (en) * | 2013-06-13 | 2014-12-18 | Pierburg Pump Technology Gmbh | Variable lubricant vane pump |
| WO2015058783A1 (en) * | 2013-10-21 | 2015-04-30 | Pierburg Pump Technology Gmbh | Variable displacement lubricant pump |
| US20160115792A1 (en) * | 2014-10-27 | 2016-04-28 | Robert Bosch Gmbh | Hydrostatic Positive Displacement Machine |
-
2016
- 2016-07-18 GB GB1612421.6A patent/GB2552328A/en not_active Withdrawn
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2551451A1 (en) * | 1975-11-15 | 1977-05-18 | Daimler Benz Ag | Rotary piston pump with eccentric rotor - has radially slidable seal strips, and stator hydraulically adjustable to vary eccentricity |
| JPS5970891A (en) * | 1982-10-16 | 1984-04-21 | Toyota Central Res & Dev Lab Inc | Variable capacity type vane pump |
| EP0902181A2 (en) * | 1997-09-11 | 1999-03-17 | Denso Corporation | Variable-discharge-rate high-pressure pump |
| WO2007015135A1 (en) * | 2005-08-02 | 2007-02-08 | Pierburg Pump Technology Italy S.P.A. | Two-setting variable-eccentricity vane pump |
| US20100192921A1 (en) * | 2007-09-18 | 2010-08-05 | Christian Langenbach | Fuel pump, in particular for a fuel system of a piston engine |
| WO2013093711A1 (en) * | 2011-12-22 | 2013-06-27 | Vhit S.P.A. | Rotary positive displacement pump and method of regulating its displacement |
| JP2014163337A (en) * | 2013-02-27 | 2014-09-08 | Toyooki Kogyo Co Ltd | Variable capacity type vane pump |
| WO2014198322A1 (en) * | 2013-06-13 | 2014-12-18 | Pierburg Pump Technology Gmbh | Variable lubricant vane pump |
| WO2015058783A1 (en) * | 2013-10-21 | 2015-04-30 | Pierburg Pump Technology Gmbh | Variable displacement lubricant pump |
| US20160115792A1 (en) * | 2014-10-27 | 2016-04-28 | Robert Bosch Gmbh | Hydrostatic Positive Displacement Machine |
Also Published As
| Publication number | Publication date |
|---|---|
| GB201612421D0 (en) | 2016-08-31 |
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