CN101225785B - Fuel pump and fuel feed apparatus having the same - Google Patents
Fuel pump and fuel feed apparatus having the same Download PDFInfo
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- CN101225785B CN101225785B CN2007101967924A CN200710196792A CN101225785B CN 101225785 B CN101225785 B CN 101225785B CN 2007101967924 A CN2007101967924 A CN 2007101967924A CN 200710196792 A CN200710196792 A CN 200710196792A CN 101225785 B CN101225785 B CN 101225785B
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- fuel
- fuel tank
- pump channel
- impeller
- pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/04—Feeding by means of driven pumps
- F02M37/08—Feeding by means of driven pumps electrically driven
- F02M37/10—Feeding by means of driven pumps electrically driven submerged in fuel, e.g. in reservoir
- F02M37/106—Feeding by means of driven pumps electrically driven submerged in fuel, e.g. in reservoir the pump being installed in a sub-tank
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0076—Details of the fuel feeding system related to the fuel tank
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/04—Feeding by means of driven pumps
- F02M37/18—Feeding by means of driven pumps characterised by provision of main and auxiliary pumps
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention provides a fuel pump and fuel feed apparatus having the same. The fuel pump includes an impeller (70) having first and second vane grooves (74, 76) each arranged along a rotative direction. The second vane groove (76) is located on a radially inner side of the first vane groove (74). The fuel pump (30) includes a pump case (50, 52) rotatably accommodating the impeller (70) and having first and second pump passages (202, 206). The first pump passage (202) is defined along the first vane groove (74) for supplying fuel from a sub-tank (20) to an engine (500). The second pump passage (206) is defined along the second vane groove (76) for supplying fuel from the fuel tank (2) to the sub-tank (20). The first and second pump passages (202, 206) respectively have cross sectional areas S1, S2, and respectively have diameters D1, D2 with respect to a direction of a rotation axis of the impeller (70). The S1, D1, S2, and D2 satisfy: 0.6<=(S2 * D2)/(S1 * D1)<=0.95.
Description
Technical field
The present invention relates to a kind of petrolift that has impeller, impeller wherein has two row blade grooves, and in the radial direction, two row blade grooves are on the mutually different position.The invention still further relates to a kind of fuel supplying device, it has petrolift, is used for fuel is flowed to motor from secondary fuel tank, simultaneously fuel is transported to the secondary fuel tank from fuel tank.
Background technique
As known in the art, in order to give internal-combustion engine from secondary fuel tank pumping, in secondary fuel tank, be provided with petrolift, and secondary fuel tank is accommodated in the fuel tank with fuel.For example, the the 5596970th and No. 6179579 (JP-A-2002-500718) U. S. Patent discloses such petrolift, two kinds of petrolifts in the above-mentioned document all comprise such fuel pump apparatus: it is transported to fuel the secondary fuel tank from fuel tank, and does not use jet pump.
In two patent documentation US 5596970 and US 6179579, petrolift all comprises impeller, this impeller has two row blade grooves, this two row blade groove is in the mutually different radial position, petrolift also has pump case, it is holding impeller rotationally, and has along the formed pump channel of two row blade grooves.Wheel rotation and fuel is pumped out from secondary fuel tank, and fuel flowed to motor through the pump channel that the blade groove in the outside radially extends.Impeller also pumps out fuel from fuel tank, so that fuel is flowed to secondary fuel tank through the pump channel that radially inboard blade groove extends.
The fuel quantity that petrolift is carried to motor is Q1, is Q2 to the quantity delivered of secondary fuel tank.In such petrolift, even be thereby that the peak output operating mode needs under the situation of maximum flow fuel at motor, Q1 value and Q2 value also need to satisfy relation: Q2 〉=Q1.If flow to the fuel quantity Q2 of secondary fuel tank (Q2≤Q1), then the liquid level of secondary fuel tank will reduce, and the result is exactly that petrolift can not aspirate out fuel from secondary fuel tank less than the fuel quantity Q1 that flows to motor from secondary fuel tank from fuel tank.Thereby petrolift need be designed to have two row blade groove and two pump channels, satisfying relation Q2 〉=Q1, and stops the decline of secondary fuel tank liquid level.
Be higher than the fuel pressure that is pumped into secondary fuel tank from fuel tank significantly for the pressure of the fuel of motor from secondary fuel tank pumping.Thereby, on the sense of rotation of impeller, be used for fuel is greater than for the pressure reduction of the pump channel of motor to be used for from secondary fuel tank pumping fuel is pumped into pressure reduction the pump channel of secondary fuel tank from fuel tank.When the pressure reduction in two pump channels becomes big, will with the direction of direction of rotation on apply active force to fuel, thereby the pumping efficiency of petrolift can descend.In addition, when fuel was pressurized to high pressure conditions, the fuel quantity that clearance leakage is gone out between pump case and impeller will become greatly, thereby the efficient of petrolift can descend.Thereby the design of petrolift will consider that also the fuel pressure that is caused by pump channel increases except needs are considered the fuel delivery of petrolift.Herein, the efficient of pump is defined as: η=(P * Q)/(T * R).In the formula, T is the moment of torsion that the motor part branch of petrolift produces, and R is the rotating speed of motor part, and P is flow through a head pressure behind the pump channel of fuel, and Q is flow through a discharge flow rate behind the pump channel of fuel.
No matter be US 5596970, or USP 6179579 does not have based on the petrolift that the consideration of fuel pressure in the pump channel is proposed be suitable for to stop secondary fuel tank liquid level to descend.
Summary of the invention
Consider above-mentioned problem and other problem, an object of the present invention is to design a kind of petrolift, it comprises the impeller with two row blade grooves, and has considered the pressure of fuel in the pump channel, thereby is suitable for the fuel quantity that is transported to secondary fuel tank from fuel tank is controlled.Another object of the present invention is a kind of fuel supplying device of design, and it has and is used for fuel is flowed to motor, fuel is transported to the petrolift of secondary fuel tank from fuel tank simultaneously from secondary fuel tank.
According to an aspect of the present invention, provide a kind of being used for that fuel is flowed to secondary fuel tank that is contained in wherein and the petrolift that fuel is flowed to motor from secondary fuel tank from fuel tank, this petrolift comprises impeller, this impeller has a plurality of first blade grooves and a plurality of second blade groove, and these blade grooves are all arranged along the sense of rotation of impeller.With respect to the radial direction of impeller, a plurality of second blade grooves are positioned at the radially inner side of a plurality of first blade grooves.Petrolift also comprises pump case, and it is holding impeller rotationally, and has first pump channel and second pump channel that in rotational direction forms.First pump channel forms along first blade groove, is used for fuel is flowed to motor from secondary fuel tank.Second pump channel forms along second blade groove, is used for fuel is transported to secondary fuel tank from fuel tank.The cross-section area of first, second pump channel is respectively S1, S2.With respect to the direction of wheel rotation axis, the diameter of first, second pump channel is respectively D1, D2.Cross-section area S1, S2 and diameter D1, D2 satisfy and to concern 0.6≤(S2 * D2)/(S1 * D1)≤0.95.
According to a further aspect in the invention, provide a kind of being used for that fuel is transported to the fuel supplying device of motor from fuel tank, this fuel supplying device comprises the secondary fuel tank that is contained in the fuel tank.Fuel supplying device also comprises the petrolift that is arranged in the secondary fuel tank, and it is used for fuel is transported to secondary fuel tank, simultaneously fuel is flowed to motor from secondary fuel tank from fuel tank.Petrolift comprises impeller, and this impeller has a plurality of first blade grooves and a plurality of second blade groove, and these blade grooves all arrange that along the sense of rotation of impeller a plurality of second blade grooves are positioned at the radially inner side of a plurality of first blade grooves.Petrolift also comprises pump case, and it is holding impeller rotationally, and has first pump channel and second pump channel that in rotational direction forms.First pump channel extends along first blade groove.First pump channel is communicated with the import that is positioned at secondary fuel tank inside, so that suction of fuel, and is communicated with outlet, is used for fuel is flowed to motor.Second pump channel extends along second blade groove.Second pump channel be arranged in the import of secondary fuel tank outside and opening and be communicated with at fuel tank, be used for from the fuel tank suction of fuel, and be communicated with the outlet of opening in secondary fuel tank, be used for fuel is flowed to secondary fuel tank.The cross-section area of first, second pump channel is respectively S1, S2.With respect to the direction of wheel rotation axis, the diameter of first, second pump channel is respectively D1, D2.Cross-section area S1, S2 and diameter D1, D2 satisfy and to concern 0.6≤(S2 * D2)/(S1 * D1)≤0.95.
Description of drawings
From the detailed description of hereinafter doing, can more be expressly understood foregoing and other purpose of the present invention, feature and advantage with reference to accompanying drawing.In the accompanying drawings:
Sectional view among Fig. 1 has been represented the pump channel according to the petrolift of first mode of execution;
Sectional view among Fig. 2 has been represented the fuel supplying device according to first mode of execution;
Figure line among Fig. 3 has been represented numerical value Q2/Q1 and the numerical value (S2 * D2)/(relation between the S1 * D1);
Figure line among Fig. 4 has been represented the relation between numerical value H/t and the pump efficiency η;
Figure line among Fig. 5 has been represented the relation between numerical value W/H and the pump efficiency η;
Sectional view among Fig. 6 has been represented the pump channel according to the petrolift of second mode of execution;
Sectional view among Fig. 7 has been represented the fuel supplying device according to second mode of execution;
Fig. 8 is the plan view of impeller;
Figure line among Fig. 9 has been represented the relation between sealed width a1, pump efficiency η and the numerical value Q2/Q1; And
Figure line among Figure 10 has represented that thickness improves than the relation between V2/V1 and the numerical value Q2/Q1 than B2/B1, speed.
Embodiment
(first mode of execution)
First mode of execution is described to Fig. 5 with reference to Fig. 1 below.Fig. 2 has represented the petrolift according to first mode of execution.In Fig. 2, heavy line has been represented the flow direction of fuel.Secondary fuel tank 20 at fuel supplying device 10 is holding under the situation of petrolift 30, and fuel supplying device 10 is arranged in the fuel tank 2.Petrolift 30 is type pumps in the case, and it is set at the inside of vehicle fuel tank, and vehicle wherein for example is two-wheeled vehicle or four-wheeled vehicle.
Petrolift 30 comprises motor part 32 and pump housing part 34.32 pairs of pump housing parts 34 of motor part drive.Housing 36 is contained in motor part 32 and pump housing part 34 wherein.Two axial ends of housing 36 crimping respectively are fixed on end cap 38 and the pump case 50.End cap 38 is formed from a resin.End cap 38 has drainage port 39, and petrolift 30 is given internal-combustion engine 500 through this drainage port with fuel-pumping.
As shown in Figure 1, impeller 70 has annular portion 72, and this annular portion defines the outer shroud week of impeller.Impeller 70 has a plurality of blade grooves 74 that are positioned at annular portion 72 radially inner sides, and blade groove 74 is arranged with respect to sense of rotation.Blade groove 74 is as first blade groove 74.Impeller 70 has a plurality of blade grooves 76 that are positioned at blade groove 74 radially inner sides.Blade groove 76 is arranged with respect to sense of rotation.With respect to the radial direction of impeller 70, blade groove 76 residing positions are different with the position of blade groove 74.Blade groove 76 is as second blade groove 76.
Blade groove 74,76 is set on two axial side of impeller 70.Be arranged on the blade groove the 75, the 76th of 70 liang of axial side of impeller, be interconnected.Fuel flow in the blade groove 74,76, and fuel is being arranged in blade groove 74, the 76 formation eddy current 300 of diaxon to side.Close blade groove 74,76 is separated by next door 75,77 respectively mutually on sense of rotation.
The pump case 50,52 that is positioned at 70 liang of axial side of impeller has formed first pump channel 202 respectively and second pump channel, 206, two pump channels form along blade groove 74,76 on sense of rotation on the impeller 70, and is essentially C shape.First pump channel 202 is as first pump channel that is communicated with blade groove 74.Second pump channel 206 is as second pump channel that is communicated with blade groove 76.
Referring to Fig. 2, it is the fuel inlet 201 that first pump channel 202 is provided with that pump case 50 has.Pump case 52 has the fuel outlet 203 of first pump channel 202.Fuel inlet 201 openings are to the inside of secondary fuel tank 20.The fuel chambers 208 of fuel outlet 203 openings in motor part 32 of first pump channel 202.Fuel inlet 201 is provided with suction strainer, is used for removing the contained foreign matter of fuel that comes from secondary fuel tank 20 streams.
The fuel inlet 205 and the fuel outlet 207 that have second pump channel 206 on the pump case 50.Fuel inlet 205 is the through holes that extend through secondary fuel tank 20 diapires 22.Fuel inlet 205 openings are to the outside of secondary fuel tank 20, and also opening is in the inside of fuel tank 2.Fuel outlet 207 openings are to the inside of secondary fuel tank 20.The bottom inside ring perimembranous of secondary fuel tank 20 diapires 22 has formed through hole, and fuel inlet 205 extends through this through hole.Be provided with the resilient member made from elastic material 64 between the bottom inside ring perimembranous of diapire 22 and the fuel inlet 205, this member is essentially cylindrical shape.Resilient member 64 has played the effect of sealing component.Resilient member 64 has limited fuel and has leaked out from the through hole of diapire 22.Fuel inlet 205 is provided with check valve 66, is used for stoping fuel to flow back to fuel tank 2 from secondary fuel tank 20.Check valve 66 is set in the fuel inlet 205, thereby, stoped fuel to flow back to the fuel tank 2 from petrolift 30.Thereby under petrolift 30 out-of-work situations, it can accumulate fuel.Thereby when petrolift 30 was started working, it can come up fuel apace through fuel inlet 205 suctions, and fuel is transported to the secondary fuel tank 20 from fuel tank 2.Fuel inlet 205 is provided with suction strainer 62, is used for the foreign matter that the fuel that comes from fuel tank 2 is contained and removes.Suction strainer 62 is arranged in the space 210 that forms between secondary fuel tank 20 diapires 22 and fuel tank 2 diapires 3.
Referring to Fig. 2, when armature 40 work, impeller 70 rotates with rotating shaft 42, thereby fuel is drawn in first, second pump channel 202,206 through fuel inlet 201,205.Fuel is flowing between the blade groove 74,76 of side at the blade groove 74,76 of forward side and in the back and is flowing out, forward side wherein and back to side for sense of rotation.Fuel repeats this and goes out stream, the process that becomes a mandarin, thereby forms eddy current 300, and eddy current is squeezed and flows through from first, second pump channel 202,206.
The rotation of impeller 70 pumps out from secondary fuel tank 20 fuel through fuel inlet 201, and pressurization is flowed through fuel to be positioned at first pump channel 202 of both sides (for rotation axis).Fuel imports and is arranged in motor part and divides fuel outlet 203 32 1 sides, on the pump case 52.Thereby fuel is discharged in the fuel chambers 208 of motor part 32 through fuel outlet 203.Be discharged to fuel in the fuel chambers 208 gap between the perimembranous in armature 40 peripheral parts and the permanent magnet of flowing through through fuel outlet 203.Like this, fuel has just flowed to motor 500 by the exhaust port on the end cap 38 39.In this operation, the flow through inside of motor part 32 of the fuel of pressurization in pump housing part 34, thus fuel can cool off motor part 32, and divide the sliding parts of 32 inside to be lubricated to being positioned at motor part.
Be about 20L/h～300L/h for the fuel quantity of motor 500 through exhaust port 39 dispatch.The fuel quantity of carrying through exhaust port 39 equals the fuel quantity of discharging through the fuel outlet 203 of first pump channel 202.The rotating speed of impeller 70 is about 4000 to 15000rpm.
Under this condition, the fuel quantity that transports from first pump channel 202 is Q1.With respect to the rotation axis of impeller 70, the diameter of first pump channel 202 is D1.The cross-section area of first pump channel 202 is S1.The fuel quantity that transports from second pump channel 206 that is positioned at first pump channel, 202 radially inner sides is Q2.With respect to the rotation axis of impeller 70, the diameter of second pump channel 206 is D2.The cross-section area of second pump channel 206 is S2.The rotating speed of impeller per minute is R rpm.Numerical value Q1, Q2 are determined by following formula (1), (2).In this structure, with respect to rotation axis, first, second pump channel 202,206 is set at the both sides of impeller 70, and numerical value S1, S2 are the summations of the cross-section area that is positioned at impeller 70 both sides of first, second pump channel 202,206.
Q1＝π×S1×D1×R (1)
Q2＝π×S2×D2×R (2)
Thereby, when from secondary fuel tank 20 during to motor 500 transfer the fuels, need not to consider the pressure of fuel in first, second pump channel 202,206, the fuel quantity of first, second pump channel 202,206 of only considering to flow through, the condition of Q2 〉=Q1 is enough to keep the liquid level in the secondary fuel tank 20.That is to say that following formula (3) is enough to keep the liquid level of secondary fuel tank 20.
Q2≥Q1
π×S2×D2×R≥π×S1×D1×R
(S2×D2)/(S1×D1)≥1 (3)
But the pressure first pump channel 202 that the fuel that is transported to motor 500 from secondary fuel tank 20 is pressurizeed is higher than the pressure second pump channel 206 that the fuel that is transported to secondary fuel tank 20 from fuel tank 2 is pressurizeed.Thereby, determine by formula (1), in first pump channel 202 discharge capacity Q1 decrease greater than determine by formula (2), the decrease of discharge capacity Q2 in second pump channel 206.Therefore, if cross-section area S1, S2 and diameter D1, D2 are defined as satisfying formula (3) simply, then the actual numerical value of discharge capacity Q2 will become excessively greater than the actual value of discharge capacity Q1.The result is exactly that the fuel that is transported to secondary fuel tank 20 from fuel tank 2 is excessive.
Hereinafter will the design load of impeller 70 and first pump channel 202 and second pump channel 206 be introduced.
In the scope of the external diameter of impeller 70 between 20mm-50mm.First, second pump channel 202,206 is confirmed as: along blade groove 74,76 on two side positions with respect to rotation axis.Being positioned at wherein with respect to rotation axis, the cross-section area of first pump channel 202 of a side is S1.The cross-section area that is positioned at second pump channel 206 of a side with respect to rotation axis is S2.Each cross-section area S1, S2 are confirmed as being in 2 square centimeters to 8 square centimeters the scope.The fuel discharge capacity of first pump channel 202 of flowing through is Q1, first pump channel 202 is D1 with respect to the diameter of impeller 70 rotation axiss, the fuel discharge capacity of second pump channel 206 of flowing through is Q2, and second pump channel 206 is D2 with respect to the diameter of impeller 70 rotation axiss, and the rotating speed of impeller 70 is R/ minute.The numerical value of discharge capacity Q1, Q2 is to be determined by above-mentioned formula (1), (2).In formula (1), (2), S1 is replaced with 2 * S1, and S2 is replaced with 2 * S2.Diameter D1 be first pump channel 202 width W 1 center 100 and with respect to the distance between the center 100 of impeller 70 this width W 1 in the radial direction.Diameter D2 be second pump channel 206 width W 2 center 102 and with respect to the distance between the center 102 of impeller 70 width W 2 in the radial direction.
Under this condition, though from secondary fuel tank 20 to motor 500 transfer the fuels that are positioned at fuel tank 2 outsides, the condition of Q2 〉=Q1 also is enough to keep the liquid level in the secondary fuel tank 20.That is to say that formula (3) is enough to suppress the decline of liquid level in the secondary fuel tank 20.
The flow through pressure of first pump channel 202 of fuel pressurized is higher than the flow through pressure of second pump channel 206 of its pressurized.The flow through pressure of first pump channel 202 of fuel pressurized is P1, and these fuel are flowed to motor 500 from petrolift 30.Fuel also by with the pressure of P2 through the pumping of pressurizeing of second pump channel 206, so that flow to secondary fuel tank 20 from petrolift 30.For example, need fuel pressure P1 in 200kPa arrives the scope of 800kPa, relative therewith, required fuel pressure P2 is 50kPa to the maximum.Therefore, on sense of rotation, all produce pressure reduction in first, second pump channel 202,206, and then caused fuel in first, second pump channel 202,206 to apply active force with direction of rotation.Opposition in first pump channel 202 is greater than the opposition in second pump channel 206.This pressure reduction has also caused fuel to produce leakage in first, second pump channel 202,206, and this leakage is that the gap between pump case 50,52 and impeller 70 takes place.The leakage rate that fuel lets out from first pump channel 202 is greater than the leakage rate of second pump channel 206.Thereby the decrease of the discharge capacity Q1 of first pump channel of being determined by formula (1) 202 is greater than the decrease of the discharge capacity Q2 of second pump channel of being determined by formula (2) 206.Therefore, if cross-section area S1, S2 and diameter D1, D2 are defined as satisfying formula (3) simply, then the actual numerical value of discharge capacity Q2 will become excessively greater than the actual value of discharge capacity Q1.The result is exactly that the fuel discharge capacity Q2 that is transported to secondary fuel tank 20 from fuel tank 2 will become excessive.And it is just enough to make that to the fuel that secondary fuel tank 20 is carried the liquid level of secondary fuel tank 20 is maintained.That is to say, needn't be from fuel tank 2 to secondary fuel tank 20 transfer the fuel excessively.
Thereby, determine (S2 * D2)/(need consider the scope of fuel pressurized stream during the scope of S1 * D1) through the pressure P 1 of first pump channel 202.Thereby pressurized first pump channel 202 of flowing through be transported to from petrolift 30 motor 500 fuel pressure P 1 for example at 200kPa in the scope of 800kPa.Thereby (S2 * D2)/(scope of S1 * D1) need be confirmed as like this: make fuel pressure P1 for example become and be in 200kPa in the scope of 800kPa, and the actual value of Q2/Q1 may become 1.Obtained following formula (4) from Fig. 3.
0.6≤(S2×D2)/(S1×D1)≤0.95 (4)
Can utilize formula (4) come to determine that (S2 * D2)/(scope of S1 * D1), so that fuel pressure P1 is in 200kPa between the 800kPa, and the actual value of Q2/Q1 can be 1.
In addition, preferably, be circular along first pump channel 202 and blade groove 74 mobile eddy current 300.In addition, also be preferably circle along second pump channel 206 and blade groove 76 mobile eddy current 300.If eddy current 300 is substantially circle, then can be by reducing the pumping efficiency η that kinetic energy rejection improves eddy current 300, wherein, the rapid change of eddy current 300 flow directions can cause described kinetic energy rejection.
On the direction of impeller 70 rotation axiss, the degree of depth of first, second pump channel 202,206 is respectively H1, H2.Making depth H 1, the H2 of first, second pump channel 202,206 equal the degree of depth of blade groove 74,76 on impeller 70 thickness directions basically respectively just is enough to form and is substantially circular eddy current 300.The depth H 1 of first, second pump channel 202,206, H2 are 1/2 of impeller 70 thickness t basically.Thereby formula (5), (6) are enough to form the basic circular eddy current 300 that is.
H1/t＝0.5 (5)
H2/t＝0.5 (6)
In fact, if each numerical value of H1/t and H2/t is in when comprising 0.5 prespecified range, each eddy current 300 is may not can too smooth.Can obtain following formula (7), (8) from Fig. 4, to determine satisfy condition the respectively H1/t of η 1 〉=40% and η 2 〉=10% and the scope of H2/t.The scope of being determined by formula (7), (8) comprises that respectively making pumping efficiency η 1 in first, second pump channel 202 and 206, η 2 is peaked situation.
0.3≤H1/t≤0.6 (7)
0.2≤H2/t≤0.6 (8)
Pumping efficiency in second pump channel 206 is less than the pumping efficiency in first pump channel 202, thereby, preferably, especially to satisfy formula (8).
Just be enough to form the basic circular eddy current 300 that is if make the twice of two pump channel depth value H1, H2 be substantially equal to first, second pump channel 202,206 respectively at impeller 70 width W 1, W2 in the radial direction.That is to say that formula (9), (10) are enough to form the basic circular eddy current 300 that is.
2＝W1/H1 (9)
2＝W2/H2 (10)
In fact, if the numerical value of W1/H1 and W2/H2 is in when comprising 2 prespecified range, the flow direction of each eddy current 300 is may not can too smooth.Can obtain following formula (11), (12) from Fig. 5, to determine satisfy condition the respectively W1/H1 of η 1 〉=40% and η 2 〉=10% and the scope of W2/H2.The scope of being determined by formula (11), (12) comprises that respectively making pumping efficiency η 1 in first, second pump channel 202 and 206, η 2 is peaked situation.
1.5≤W1/H1≤2.1 (11)
1.9≤W2/H2≤2.5 (12)
In this embodiment, blade groove 74,76 radial direction with respect to impeller 70 of petrolift 30 are on the different positions.Petrolift 30 flows to motor 500 with fuel from secondary fuel tank 20, and fuel is flowed to secondary fuel tank 20 from fuel tank 2.In petrolift 30, the cross-section area of first, second pump channel 202,206 is respectively S1, S2, and first, second pump channel 202,206 is D1, D2 with respect to the diameter of impeller 70 axial directions.In addition, particularly, consider the pressure in first pump channel 202 that the fuel that flows to motor 500 is pressurizeed, (S2 * D2)/(scope of S1 * D1) is confirmed as satisfying formula (3).Thereby, can prevent that the fuel level in the secondary fuel tank 20 from descending, and can prevent that the fuel quantity that is transported to secondary fuel tank 20 from fuel tank 2 from excessively increasing.In addition, the thickness t of the depth H 1 of first, second pump channel 202,206, H2 and impeller 70 is appropriately determin out, so that H1/t and H2/t are in formula (7), (8) institute restricted portion.The depth H 1 of first, second pump channel 202,206, H2 and first, second pump channel 202,206 are appropriately determin out with respect to width W 1, W2 in the radial direction, so that W1/H1 and W2/H2 are in formula (11), (12) institute restricted portion.Therefore, can stop the shape of the eddy current that forms 300 between first pump channel 202 and the blade groove 74 to become flat.In addition, the shape that also can prevent the eddy current that forms 300 between second pump channel 206 and the blade groove 76 becomes flat.So just improved pumping efficiency.
In the above-described embodiment, consider the fuel pressure in first, second pump channel 202,206, cross-section area S1, the S2 of first, second pump channel 202,206 and diameter D1, D2 are confirmed as satisfying formula (4).
0.6≤(S2×D2)/(S1×D1)≤0.95 (4)
Thereby, by satisfying relation: 0.6≤(S2 * D2)/(S1 * D1), can prevent to become undue less than the fuel quantity Q1 that is transported to motor 500 from secondary fuel tank 20 from the fuel quantity Q2 that fuel tank 2 is carried to secondary fuel tank 20.Concern by satisfying in addition, (S2 * D2)/(S1 * D1)≤0.95, can prevent to become undue greater than the fuel quantity Q1 that is transported to motor 500 from secondary fuel tank 20 from the fuel quantity Q2 that fuel tank 2 is carried to secondary fuel tank 20.Thereby, be defined as satisfiable formula (4) by cross-section area S1, S2 and diameter D1, D2 with first, second pump channel 202,206, can prevent that the fuel quantity that is transported to secondary fuel tank 20 from fuel tank 2 from becoming excessive, and can prevent that the liquid level of secondary fuel tank 20 from descending.
The fuel pressure of carrying from first pump channel is P (kPa), and it satisfies relation: 200≤P≤800.Be in fuel pressure under the situation of 200≤P≤800 scopes, be defined as satisfiable formula (4) by cross-section area S1, S2 and diameter D1, D2 with first, second pump channel 202,206, can prevent that the fuel quantity that is transported to secondary fuel tank 20 from fuel tank 2 from becoming excessive, and can prevent that the liquid level of secondary fuel tank 20 from descending.
Rotation along with impeller 70, fuel in first, second pump channel 202,206 repeatedly flows out from the blade groove 74,76 that is arranged in forward side, and flow into and be arranged in the back to the blade groove 74,76 of side, thereby, fuel can form eddy current by pressurized the time, forward side wherein and the back to side for sense of rotation.Preferably, in each passage, the cross section of eddy current 300 is circular, and passage wherein comprises first, second pump channel 202,206 and blade groove 74,76.It is circular that the cross section of eddy current 300 is essentially, thereby rapid change appears in the flow direction that can prevent eddy current 300, and then can keep the kinetic energy of eddy current 300.Thereby, can improve pumping efficiency η 1 and η 2 in first, second pump channel 202,206.Make depth H 1, the H2 of first, second pump channel 202,206 be substantially equal to the degree of depth of each blade groove 74,76 on impeller 70 thickness directions and just be enough to form the basic circular eddy current 300 that is.As the qualification of formula (5), (6), first, second pump channel 202,206 depth H 1, H2 separately is substantially equal to 1/2 of impeller 70 thickness t respectively.In fact, when H/t is in when comprising 0.5 prespecified range, eddy current 300 can be too not flat.
H1＝t/2
H2＝t/2
H1/t＝0.5 (5)
H2/t＝0.5 (6)
Make the twice of each depth value H1, H2 of each pump channel 202,206 be substantially equal to first, second pump channel 202,206 respectively and just be enough to form the basic circular eddy current 300 that is at impeller 70 width W 1, W2 in the radial direction.That is to say that formula (9), (10) are enough to form the basic circular eddy current 300 that is.In fact, when W/H is in when comprising in 2 the prespecified range, eddy current 300 can be too not flat.
2×H1＝W1
2×H2＝W2
2＝W1/H1 (9)
2＝W2/H2 (10)
(second mode of execution)
Fig. 6 has shown the fuel supplying device of the petrolift with second embodiment of the invention to Fig. 8.Referring to Fig. 6, in this embodiment, first cross-section area of first pump channel 302 is S1, and it is the dash area of representing with dot and dash line among the figure, and second cross-section area of second pump channel 306 is S2, and it is the dash area of representing with double dot dash line among the figure.Having formed sealed width between the first cross-section area S1 and the second cross-section area S2 is the hermetic unit of a1.Impeller 51 has rotation axis O.
Pumping efficiency η is defined as: η=(P * Q)/(T * R).In the formula, T is the moment of torsion that the motor part branch of petrolift produces, and R is the rotating speed of motor part, and P is flow through a head pressure behind the pump channel of fuel, and Q is flow through a discharge capacity behind the pump channel of fuel.Referring to Fig. 9, heavy line has been represented the relation between pumping efficiency η and the sealed width a1.The discharge capacity that fuel is flowed through behind first pump channel 302 is Q1, and the discharge capacity behind second pump channel 306 of flowing through is Q2.In Fig. 9, each bar dotted line has been represented the relation between numerical value Q2/Q1 and the sealed width a1.Dotted line relation represented, between numerical value Q2/Q1 and the sealed width a1 is aimed at diameter and is
20,
30,
40,
50 impeller 51.
In this embodiment, fuel is flowed through pressure P 1 behind first pump channel 302 also between 200kPa and 800kPa.The pressure P 2 that fuel is flowed through after second pump channel 306 is equal to or less than 50kPa.That is to say that fuel pressure P1 is greater than fuel pressure P2.In this structure, fuel can leak into second pump channel 306 from first pump channel 302, thereby pumping efficiency η can reduce.Can reduce the leakage of fuel by increase sealed width a1.If sealed width a1 is equal to or greater than 1mm, pumping efficiency η 1 will become and be equal to or greater than 40%, so just can reach enough pumping efficiency η 1.As alternative, if sealed width a1 less than 1mm, fuel just can leak into second pump channel 306 from first pump channel 302, thereby pumping efficiency η 1 sharply descends.As alternative, when sealed width a1 was equal to or greater than 2.5mm, pumping efficiency η 1 became constant situation basically, no longer increased.
In addition,, just can't guarantee that second pump channel 306 has the second enough cross-section area S2, and can't satisfy and concern Q2 〉=Q1 if sealed width a1 is excessive.If more than or equal to 1, just satisfying, the numerical value of Q2/Q1 concerns Q2 〉=Q1.To concern Q2 〉=Q1 in order satisfying, to be at the diameter of impeller 51
Under 50 the situation, sealed width a1 is set equal to or less than 8.5mm, when the diameter of impeller 51 is
Under 30 the situation, sealed width a1 is set equal to or less than 2.5mm.Diameter is
The 30th, conventional numerical value.Consider these preconditions, the optimum range of sealed width a1 is determined by following formula (13).
1≤a1≤2.5 (13)
From Fig. 7,8 as seen, in this embodiment, the thickness that forms each vane plate of radial outside blade groove 52a is B1, and the thickness of radially inner side vane plate is B2.Thickness B 1, the satisfied B2 〉=B1 that concerns of B2.
In the time of in being in fuel, being positioned at of the rate of expansion expansion of the vane plate of radially inner side on the impeller 51, and being positioned at of the rate of expansion expansion of the vane plate of radial outside on the impeller 51 with V1 with V2.The ratio of rate of expansion V2 and rate of expansion V1 is V2/V1.Along with the increase of impeller 51 surface areas, the rate of expansion of impeller 51 vane plates also increases, and the thickness of vane plate will diminish.The thickness that is positioned at the blade groove 52a of radial outside is B1, and the thickness that is positioned at the blade groove 52a of radially inner side is B2, and the ratio between two thickness is B2/B1.In Figure 10, heavy line represented rate of expansion than V2/V1 and thickness than the relation between the B2/B1.If rate of expansion is equal to or greater than 1 than V2/V1, that is to say, if rate of expansion V2 is equal to or greater than rate of expansion V1, be positioned at the required gap of the impeller 51 of radially inner side just greater than impeller 51 determined gaps based on radial outside.Thereby preferably, rate of expansion is equal to or less than 1 than V2/V1.If rate of expansion equals 1 than V2/V1, thickness just is 1.5 than B2/B1.
In Figure 10, dotted line has represented that numerical value Q2/Q1 and thickness are than the relation between the B2/B1.If the thickness B of vane plate 1, B2 increase, rate of expansion is with regard to step-down, yet the second cross-section area S2 of second pump channel 306 shown in Figure 6 just can not get having guaranteed fully, concerns Q2 〉=Q1 thereby can't satisfy.Thickness is equal to or less than 3 than B2/B1, concerns Q2 〉=Q1 so that satisfy.Thereby the thickness that meets fuel quantity in rate of expansion and the pump chamber is to be determined by following formula (14) than B2/B1.
1.5≤(B2/B1)≤3 (14)
In this embodiment, the sealed width of formed hermetic unit is W1 between first pump channel and second pump channel, its 1≤a1 that satisfies condition≤2.5.Sealed width a1 is determined to be equivalent to or greater than 1mm, thereby can stop fuel to leak into second pump channel 306 from first pump channel 302.In addition, by sealed width a1 is defined as being equal to or less than 2.5mm, the fuel quantity Q2 that is transported to secondary fuel tank 20 from fuel tank 2 is restricted and can be excessively greater than the fuel quantity Q1 that flows to motor 500 from secondary fuel tank 20.Like this, can improve the pumping efficiency η of pump channel.
It is B1 that impeller 51 has first vane plate and the thickness of each that form first blade groove.It is B2 that impeller 51 has second vane plate and the thickness of each that form second blade groove.B1 and B2 satisfy 1.5≤B2/B1≤3.Along with the less thick of each vane plate, rate of expansion increases.But along with the increase of each vane plate thickness, the cross-section area of pump channel will correspondingly diminish, thereby the fuel quantity of discharging from petrolift will descend.Thereby numerical value B2/B1 is set equal to or greater than 1.5, and the rate of expansion of each second vane plate is set equal to or less than the rate of expansion of each first vane plate.So just can keep the gap between impeller 51 and the pump case, thereby can prevent that impeller 51 and pump case are in contact with one another.In addition, can concern Q2 〉=Q1 so that satisfy by numerical value B2/B1 is defined as being equal to or less than 3.Thereby, can improve pumping efficiency η, and keep the liquid level of secondary fuel tank 20.
With respect to the rotation axis of impeller, formed a pump channel in a side of impeller.
In the first embodiment, the motor part branch comprises brushless electric machine.As possibility, the motor part can comprise the motor that has brush.
Can suitably make up the structure of the respective embodiments described above.
Under the precursor that does not deviate from core concept of the present invention, can make various forms of changes and replacement to above-mentioned mode of execution.
Claims (11)
1. one kind is used for fuel is flowed to the secondary fuel tank (20) that is contained in wherein and fuel is flowed to the petrolift (30) of motor (500) from secondary fuel tank (20) from fuel tank (2), and this petrolift (30) comprising:
Impeller (70,51), have a plurality of first blade grooves (74) and a plurality of second blade groove (76), each blade groove is all arranged along the sense of rotation of impeller (70,51), with respect to the radial direction of impeller (70,51), a plurality of second blade grooves (76) are positioned at the radially inner side of a plurality of first blade grooves (74); And
Pump case (50,52), holding impeller (70,51) rotationally, and have separately first pump channel (202,302) and second pump channel (206,306) that in rotational direction forms, first pump channel (202,302) forms along first blade groove (74), be used for fuel is flowed to motor (500) from secondary fuel tank (20), second pump channel (206,306) forms along second blade groove (76), is used for fuel is transported to secondary fuel tank (20) from fuel tank (2)
Wherein, the cross-section area of first and second pump channels (202,206,302,306) is respectively S1, S2;
With respect to the direction of impeller (70,51) rotation axis, the diameter of first and second pump channels (202,206,302,306) is respectively D1, D2; And
Cross-section area S1, S2 and diameter D1, D2 satisfy relation:
0.6≤(S2×D2)/(S1×D1)≤0.95。
2. petrolift according to claim 1 (30) is characterized in that: first pump channel (202,302) is suitable for the pressure P transfer the fuel; And
Pressure P satisfies relation: 200kPa≤P≤800kPa.
3. petrolift according to claim 1 (30) is characterized in that: with respect to the direction of wheel rotation axis, the degree of depth of second pump channel (206,306) is H2;
The thickness of impeller (70,51) is t; And
Depth H 2 and thickness t satisfy relation: 0.2≤H2/t≤0.6.
4. petrolift according to claim 3 (30) is characterized in that:
With respect to the direction of wheel rotation axis, the degree of depth of first pump channel (202,302) is H1;
Depth H 1 and thickness t satisfy relation: 0.3≤H1/t≤0.6.
5. according to the described petrolift of one of claim 1 to 4 (30), it is characterized in that:
With respect to the radial direction of impeller (70,51), the width of second pump channel (206,306) is W2;
With respect to the direction of wheel rotation axis, the degree of depth of second pump channel (206,306) is H2; And
Width W 2 satisfies relation with depth H 2: 1.9≤W2/H2≤2.5.
6. petrolift according to claim 5 (30) is characterized in that:
With respect to the radial direction of impeller, the width of first pump channel (202,302) is W1;
With respect to the direction of wheel rotation axis, the degree of depth of first pump channel (202,302) is H1; And
Width W 1 satisfies relation with depth H 1: 1.5≤W1/H1≤2.1.
7. according to the described petrolift of one of claim 1 to 4 (30), it is characterized in that:
Formed hermetic unit between first pump channel (202,302) and second pump channel (206,306), its sealed width is a1; And
Sealed width a1 satisfies: 1mm≤a1≤2.5mm.
8. according to the described petrolift of one of claim 1 to 4 (30), it is characterized in that:
Impeller (70,51) has a plurality of first vane plates, and they have formed a plurality of first blade grooves (74), and the thickness of each first vane plate is B1;
Impeller (70,51) has a plurality of second vane plates, and they have formed a plurality of second blade grooves (76), and the thickness of each second vane plate is B2; And
Thickness B 1 satisfies relation with thickness B 2: 1.5≤B2/B1≤3.
9. according to the described petrolift of one of claim 1 to 4 (30), it is characterized in that: also comprise:
Motor part (32) is used for drives impeller (70,51) and makes its rotation.
10. fuel supplying device comprises:
According to the described petrolift of one of claim 1 to 4 (30); And
The secondary fuel tank (20) that is holding petrolift (30), it is received within the fuel tank (2);
Wherein, first pump channel (202,302) has the import (201) that is positioned at secondary fuel tank (20) inside;
First pump channel (202,302) has the outlet (203) that is used for to motor (500) transfer the fuel;
Second pump channel (206,306) has and is arranged in the import (205) in fuel tank (2) of secondary fuel tank (20) outside and opening; And
Second pump channel (206,306) has the outlet (207) of opening in secondary fuel tank (20).
11. a fuel supplying device is used for fuel is supplied with to motor (500) from fuel tank (2), this fuel supplying device comprises:
Be contained in the secondary fuel tank (20) in the fuel tank (2); And
Be contained in the petrolift (30) in the secondary fuel tank (20), be used for fuel is transported to secondary fuel tank (20) from fuel tank (2), simultaneously fuel is flowed to motor (500) from secondary fuel tank (20);
Petrolift wherein (30) comprising:
Impeller (70,51), have a plurality of first blade grooves (74) and a plurality of second blade groove (76), each blade groove is all arranged along the sense of rotation of impeller (70,51), with respect to the radial direction of impeller (70,51), a plurality of second blade grooves (76) are positioned at the radially inner side of a plurality of first blade grooves (74); And
Pump case (50,52) is holding impeller (70,51) rotationally, and has first and second pump channels (202,206,302,306) that in rotational direction form separately;
Wherein, first pump channel (202,302) extends along first blade groove (74);
First pump channel (202,302) is communicated with the import that is used for suction of fuel (201) that is arranged in secondary fuel tank (20), and is communicated with the outlet (203) that is used for to motor (500) transfer the fuel;
Second pump channel (206,306) extends along second blade groove (76);
Second pump channel (206,306) be arranged in the import (205) of secondary fuel tank (20) outside and opening and be communicated with in fuel tank (2), be used for from fuel tank (2) suction of fuel, and be communicated with the outlet (207) of opening in secondary fuel tank (20), be used for fuel is flowed to secondary fuel tank (20)
Wherein, the cross-section area of first and second pump channels (202,206,302,306) is respectively S1, S2;
With respect to the direction of impeller (70,51) rotation axis, the diameter of first and second pump channels (202,206,302,306) is respectively D1, D2; And
Cross-section area S1, S2 and diameter D1, D2 satisfy relation:
0.6≤(S2×D2)/(S1×D1)≤0.95。
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006329041 | 2006-12-06 | ||
| JP329041/2006 | 2006-12-06 | ||
| JP2007252941A JP2008163934A (en) | 2006-12-06 | 2007-09-28 | Fuel pump and fuel feed apparatus using the same |
| JP252941/2007 | 2007-09-28 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101225785A CN101225785A (en) | 2008-07-23 |
| CN101225785B true CN101225785B (en) | 2010-11-10 |
Family
ID=39693708
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007101967924A Expired - Fee Related CN101225785B (en) | 2006-12-06 | 2007-12-06 | Fuel pump and fuel feed apparatus having the same |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2008163934A (en) |
| KR (1) | KR100904601B1 (en) |
| CN (1) | CN101225785B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102007038144A1 (en) * | 2007-08-13 | 2009-02-19 | Continental Automotive Gmbh | Side channel pump for conveying fuel in a motor vehicle |
| US20140255149A1 (en) * | 2013-03-07 | 2014-09-11 | Airtex Products, Lp | Dual inlet turbine pump |
| CN103742443B (en) * | 2014-01-27 | 2016-03-30 | 广州竞标汽车零部件制造有限公司 | A kind of impeller module of fuel pump |
| KR101836580B1 (en) | 2015-12-09 | 2018-03-09 | 현대자동차주식회사 | Fuel pump system of hybrid vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5596970A (en) * | 1996-03-28 | 1997-01-28 | Ford Motor Company | Fuel pump for an automotive fuel delivery system |
| CN1268998A (en) * | 1998-07-02 | 2000-10-04 | 三菱电机株式会社 | Vehicle fuel supplying apparatus |
| US6179579B1 (en) * | 1998-03-18 | 2001-01-30 | Robert Bosch Gmbh | Multi-stage side-channel fuel pump for a motor vehicle |
| CN1327504A (en) * | 1999-09-07 | 2001-12-19 | 马沃尔系统公司 | Fuel drawing device for motor vehicle tank |
| US6854451B2 (en) * | 2002-11-28 | 2005-02-15 | Denso Corporation | Fuel feed apparatus having vibration damping structure |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6012904A (en) * | 1994-05-17 | 2000-01-11 | Walbro Corporation | Vented fuel module reservoir with two-stage pump |
| JP3591091B2 (en) * | 1995-11-07 | 2004-11-17 | 株式会社デンソー | Regenerative pump |
| US5580213A (en) | 1995-12-13 | 1996-12-03 | General Motors Corporation | Electric fuel pump for motor vehicle |
| DE10019911A1 (en) * | 2000-04-20 | 2001-10-25 | Mannesmann Vdo Ag | Feed pump esp. in surge chamber of motor vehicle fuel tank has rotor with several planes and rings of guide blades located in different planes |
-
2007
- 2007-09-28 JP JP2007252941A patent/JP2008163934A/en active Pending
- 2007-12-05 KR KR1020070125321A patent/KR100904601B1/en not_active IP Right Cessation
- 2007-12-06 CN CN2007101967924A patent/CN101225785B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5596970A (en) * | 1996-03-28 | 1997-01-28 | Ford Motor Company | Fuel pump for an automotive fuel delivery system |
| US6179579B1 (en) * | 1998-03-18 | 2001-01-30 | Robert Bosch Gmbh | Multi-stage side-channel fuel pump for a motor vehicle |
| CN1268998A (en) * | 1998-07-02 | 2000-10-04 | 三菱电机株式会社 | Vehicle fuel supplying apparatus |
| CN1327504A (en) * | 1999-09-07 | 2001-12-19 | 马沃尔系统公司 | Fuel drawing device for motor vehicle tank |
| US6854451B2 (en) * | 2002-11-28 | 2005-02-15 | Denso Corporation | Fuel feed apparatus having vibration damping structure |
Also Published As
| Publication number | Publication date |
|---|---|
| KR100904601B1 (en) | 2009-06-25 |
| CN101225785A (en) | 2008-07-23 |
| JP2008163934A (en) | 2008-07-17 |
| KR20080052429A (en) | 2008-06-11 |
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Granted publication date: 20101110 Termination date: 20111206 |