CN100378319C - Turbine type fuel pump - Google Patents
Turbine type fuel pump Download PDFInfo
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- CN100378319C CN100378319C CNB2005100763352A CN200510076335A CN100378319C CN 100378319 C CN100378319 C CN 100378319C CN B2005100763352 A CNB2005100763352 A CN B2005100763352A CN 200510076335 A CN200510076335 A CN 200510076335A CN 100378319 C CN100378319 C CN 100378319C
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Abstract
A turbine fuel pump includes an impeller having blades, each including a linear blade portion extending linearly in the radial direction of the impeller and a curved blade portion extending circularly curvedly from the head of the linear blade portion to the forward side of the impeller as viewed in the direction of rotation of the impeller. The linear blade portion has a length of (1/3 to 2/3)xH, where H is an overall length of the impeller.
Description
The application is that application number is dividing an application of 03136325.3 application for a patent for invention.The applying date of original application is on 05 28th, 2003, and denomination of invention is " turbine fuel pump ".
Technical field
The present invention relates to be suitable for, for example is the turbine fuel pump of the conveying fuel oils such as injection valve of motor car engine.
Background technique
Usually, in order to carry fuel oil to motor, electronically controlled fuel injection system is installed on minibus, and the fuel injection of fuel injection system handlebar is to the injection valve of engine chamber, the fuel delivery in the fuel tank of vehicle rear etc. for example to the fuel pump of injection valve.Recently, because therefore the society need of global environmental protection has increased improving the demand of vehicle fuel consume.Therefore, be to realize raising the efficiency (promptly reducing power consumption) and reducing size and weight for significant challenge by electric motor driven fuel pump.
In common use, fuel pump comprises turbine fuel pump, turbine fuel pump has a cylindrical housing that holds motor, a loam cake that is installed on shell one end, one is installed on being used for supporting motor and the housing of the annular fuel gallery between filler opening and oil outlet being arranged of the shell the other end, and an impeller that is installed on rotationally in the housing, when impeller was rotated by motor, impeller was delivering to oil outlet from the fuel oil of filler opening inspiration by the fuel gallery.
The shape of impeller has in the periphery along circumferential arrangement and blade that radially extends and the blade groove that forms between blade as a disk.Be introduced in the blade groove by the fuel gallery from the indrawn fuel oil of filler opening,, arranged to passage again then to accept kinetic energy from blade.Row is circulated in passage to the fuel oil of fuel gallery, and fuel oil is introduced to again in the blade groove then.Fuel oil in passage is boost pressure in the repetition that flows into and flow out, and is discharged from by outlet.
The efficient of improving fuel pump all is important to efficient and the pump efficient partly that improves motor.Particularly, impeller is by the motoring of being rotated in fuel oil, owing to the viscosity of fuel oil produces torque loss.When rotating in housing, impeller is also owing to the viscosity of fuel oil produces torque loss.These torque loss and rpm (rpm) square increase with being directly proportional, and therefore torque loss becomes very big when fuel pump turns round with high rpm, causes the reduction of pump efficiency.
By the Dimensions of pump part is set, just can be issued to the flow velocity that needs at low rpm, torque loss just can be contained.Yet in this case, the needed torque of drives impeller increases.
In addition, owing to need reduce the size of fuel pump, motor also will reduce size.As mentioned above, producing high torque (HT) under low rpm needs motor to turn round in inefficient scope.Whereby, not only the Dimensions by pump part is set is so that making the torque loss minimum is important to improving pump efficiency, and the Dimensions that motor is set to make it to work in the high efficiency scope also be important.
Improving aspect the turbine fuel pump efficient, proposing the scheme of various improvement impellers.One of improvement project is disclosed among the JP-A8-100780, and each blade of impeller all has a sense of rotation along impeller to see recurvate root therein, and head retreats tiltedly radially protruding point-blank from curved section.Even in low relatively rpm scope, this shape of blade also can make fuel oil flow to passage smoothly from the blade groove, prevents that flow velocity from reducing with rpm, has improved low-pressure performance and flow speed control ability.
Disclosed fuel pump in JP-A8-100780, as mentioned above, each blade of impeller all has a sense of rotation from impeller to see recurvate root, and head retreats tiltedly radially protruding point-blank from curved section.In this way, impeller can prevent that flow velocity reduces with rpm in low relatively rpm scope.But, because impeller has sweptback point-blank head.Fuel oil flows out from the blade groove in the direction of back, can not give the higher kinetic energy of fuel oil.Whereby, big relatively flow velocity be reached and rpm need be increased considerably.The increase that this just causes in big relatively flow rates internal torque loss produces the problem that reduces pump efficiency.
Summary of the invention
Therefore, target of the present invention provides a kind of turbine fuel pump that can improve pump efficiency in the whole service scope.
The present invention provides a kind of fuel pump usually, and it has: a shell that holds motor, be contained in the housing on the shell, and housing has the annular pass between entrance and exit; Can be installed in the impeller in the housing rotationally, impeller has and is arranged in the impeller outer circumference and along its blade that radially extends, when blade is rotated by motor, carry fuel oil to pass through passage, each blade has one to be seen from the head of straight section circularly to the curved section at last lateral bending Qu Yanshen of impeller along the straight section that radially extends of impeller and sense of rotation from impeller, straight section has predetermined length, this predetermined length is (1/3 to 2/3) * H, and wherein H is the total length of impeller.
One aspect of the present invention provides a kind of turbine fuel pump, and it has: a shell that holds motor, be contained in the housing on the shell, and housing has the annular pass between entrance and exit; Can be installed in the impeller in the housing rotationally, impeller has and is arranged in the impeller outer circumference and along its blade that radially extends, when blade is rotated by motor, carry fuel oil to pass through passage, it is the plate body of rectangle substantially that each blade has a cross section, this plate body has and is positioned at the front of impeller in last side, be positioned at the back of impeller in back one side, and in front and a pair of side between the back, each blade has and is positioned at the chamfering of radially extending of root of blade one side one side along impeller, this chamfering is to obtain by the angle of cutting away obliquely between blade side and the back, chamfering has predetermined length, wherein predetermined length is (2/5 to 3/5) * L, and wherein L is the radial length of passage.
Description of drawings
From following description with reference to accompanying drawing, other targets of the present invention and feature are conspicuous, wherein:
Fig. 1 is the sectional arrangement drawing according to first embodiment of turbine fuel pump of the present invention;
Fig. 2 is the partial enlarged view of Fig. 1;
Fig. 3 is the sectional drawing along the intercepting of the III-III line in Fig. 2;
Fig. 4 is the enlarged perspective of impeller blade;
Fig. 5 is the planimetric map of impeller blade;
Fig. 6 is the plotted curve that the relation of the start position of bending blade part and pump efficiency is shown;
Fig. 7 is and Fig. 6 similar graph, and the plotted curve that partly turns forward and concern between the angle of length and the pump efficiency corresponding to bending blade is shown;
Fig. 8 and Fig. 2 are similar, and second embodiment of the present invention is shown;
Fig. 9 is the further zoomed-in view of Fig. 8;
Figure 10 and Fig. 4 are similar, and the blade of impeller is shown;
Figure 11 and Fig. 5 are similar, and a plurality of blades of impeller are shown;
Figure 12 and Fig. 3 are similar, are the sectional drawings of XII-XII line in Figure 11;
Figure 13 is the plotted curve that is similar to Fig. 7, and the angle of inclination of chamfered part of root one side and the relation between the pump efficiency are shown;
Figure 14 is the plotted curve that is similar to Figure 13, and the length of chamfered part of root one side and the relation between the pump efficiency are shown;
Figure 15 is similar to Fig. 1, and the 3rd embodiment of the present invention is shown;
Figure 16 is similar to Fig. 8, and the major component of Figure 15 is shown;
Figure 17 is similar to Figure 12, is the sectional drawing of XVII-XVII line in Figure 16;
Figure 18 is similar to Fig. 9, and the major component of Figure 17 is shown;
Figure 19 and Figure 10 are similar, and a plurality of blades of impeller are shown;
Figure 20 and Figure 11 are similar, and a plurality of blades of impeller are shown;
Figure 21 is similar to Figure 17, is the sectional drawing of XXI-XXI line in Figure 20;
Figure 22 is the plotted curve that is similar to Figure 14, and the angle of inclination of chamfered part of root one side and the relation between the pump efficiency are shown;
Figure 23 is the plotted curve that is similar to Figure 22, and the length of chamfered part of root one side and the relation between the pump efficiency are shown;
Figure 24 and Figure 18 are similar, and first kind of modification of the 3rd embodiment is shown; And
Figure 25 and Figure 19 are similar, and second kind of modification of the 3rd embodiment is shown.
Embodiment
With reference to accompanying drawing, illustrate and implement turbine fuel pump of the present invention.
With reference to Fig. 1-7, first embodiment of the present invention is shown.With reference to Fig. 1, turbine fuel pump has a columnar shell 1, and its constitutes the shell of pump, and has to be transferred and cover 2 and the axial end portion that seals of pump case 9.
There is the conveying lid 2 of the cylinder of lid to be assemblied in an end of shell 1.As shown in Figure 1, conveying is covered 2 and is provided with delivery pipe 2A and connector 2B and the downward bearing housing 2C that extends at the center that projects upwards.
With reference to Fig. 2, axle bush 4 by chimeric be installed in to carry cover in 2 the bearing housing 2C, and axle bush 5 is by in the chimeric stepped bore 12E that is installed in inner housing 12. Axle bush 4,5 is formed the bearing of supporting rotating shaft 6 rotationally.
Running shaft 6 by axle bush 4,5 be supported in carry cover 2 and pump case 9 between.As shown in Figure 2, running shaft 6 extends so that the rotor 7B of rotatably support motor 7 etc. vertically along axes O-O in shell 1.With reference to Fig. 3, process plane (chamfer) 6A in the lower end of running shaft 6 so that mesh with the spline state with impeller 2.
With regard to motor 7, when by carrying when cover 2 connector 2B, brush and commutator 7C and giving rotor 7B power supply, rotor 7B rotates with running shaft 6, so as drives impeller 20 in to high rpm, i.e. rotation in the scope of 5000-8000rpm.
Between the yoke 7A of motor 7 and rotor 7B, constitute fuel gallery 8, be used for the fuel oil that the oil outlet 14 from pump case 9 is discharged to shell 1 is recycled to carry by the gap between yoke 7A and the rotor 7B covering 2.
As illustrated in fig. 1 and 2, the frame 10 of pump case 9 securely is assemblied in the lower end of shell 1 by the such means of fixation of for example joint filling (calking), from outside closed casing 1.Frame 10 is an integral body with filler opening 11.
(axes O-O) a circular depressions 10A is arranged there is a circular groove 10B of semi-circular cross-section substantially to frame 10, is that the center circumferentially extends corresponding to the excircle of impeller 20 with axes O-O at the axle center.As shown in Figure 3, circular groove 10B circumferentially extends in the scope of angle θ, and constitutes butt joint side canal 18 down with the peripheral wall groove 12D of inner housing 12
As shown in Figure 2, the shape of inner housing 12 is as a flat cylinder with cover, and has cylindrical portions may 12A that forms the cylindrical shape peripheral wall and the lid part 12B that covers cylindrical portions may 12A from the top.Cylindrical portions may 12A is formed with the dimple that holds impeller 13 of a circle at inward flange, and its opening is in the side of the mating face 12C of cylindrical portions may 12A and frame 10.In addition, cylindrical portions may 12A is formed with the peripheral wall groove 12D that is under the annular projection 16.The circular groove 10B of peripheral wall groove 12D on frame 10 forms butt joint side canal 18.Be formed with stepped bore 12E on the lid part 12B, be inserted with axle bush 5 therein, the outward edge of lid part 12B has vertically extending oil outlet 14.
Forming annular passs 15 at the outward edge of the dimple 13 that holds impeller by pump case 9, is that the center circumferentially extends with the axes O in the mode of C shape roughly, as shown in Figure 3.Fuel gallery 15 has the two-part that vertically are divided into by annular projection 16, i.e. internal channel 17 and butt joint side canal 18.
15 tops, fuel gallery are connected with filler opening 11, and terminal is connected with oil outlet 14.In addition, there is an oil inlet passage part 15A fuel gallery 15 at top, is used for the fuel oil that sucks by filler opening 11 is directed to fuel gallery 15 smoothly.
The shape of impeller 20, for example roughly as a disk of being made by the plastic material that strengthens, and the impeller that can be installed in pump case 9 rotationally holds in the dimple 13.Impeller 20 is being with along the direction of the arrow A in Figure 3 by motor 7 and is being rotated, and the fuel oil that sucks by filler opening 11 is delivered to oil outlet 14 through fuel gallery 15.
(axes O-O) engaging hole 21 is arranged, running shaft 6 is assemblied in this hole impeller 20 in center of rotation.A plurality of (for example three) through hole 22 be arranged in engaging hole 21 around.Referring to Fig. 4, impeller 20 has many blades 23 that radially extend along circumferential array at its circumference.The groove 24 that a pair of circle is arranged between adjacent vanes 23, each groove 24 have roughly corresponding to the round-shaped curvature of the passage 17,18 of pump case 9.
Referring to Fig. 5, each blade 23 all has a linear blade part 23A who is positioned at root one side and extends along the radial alignment of impeller 20, with a head from linear blade part 23A, along in rotational direction seeing, be the direction of arrow A, towards the curved vane part 23B to last side circular bend extension of impeller 20.
Below, the shape of detailed description blade 23.As shown in Figure 5, the length from the root position B of linear blade part 23A to the head position C of curved vane part 23B, promptly whole length of blade 23 are known as total length H; Starting point position D from the root position B of linear blade part 23A to curved vane part 23B in this beginning, promptly the length of the head position D of linear blade part 23A is known as straight section length H1; From the starting point position D of curved vane part 23B to the end the length of portion position C be known as curved section length H2.
The length that turns forward of curved vane part 23B between forward facing position E that in rotational direction turns forward and linear blade part 23A is in order to the center of rotation (axes O-O) illustrate for the angle [alpha] of benchmark of impeller 20.
In first embodiment, demonstrate the total length H with respect to blade 23 as the straight section length H1 of linear blade part 23A, that is, the starting point position D of curved vane part 23B when being provided with, can obtain fabulous pump efficiency according to following formula (1):
1/3≤(H1/H)≤2/3 …(1)
In this respect, when demonstrating within the H1/H in formula (1) is set at the scope that is provided by following formula (2), can obtain better pump efficiency:
2/5≤(H1/H)≤3/5 …(2)
In addition, demonstrate when angle [alpha] and when being provided with, can obtain fabulous pump efficiency according to following formula (3) corresponding to the length that turns forward of curved vane part 23B:
0.5≤α≤2.0 …(3)
In this respect, when demonstrating within the α in formula (3) is set at the scope that is provided by following formula (4), can obtain better pump efficiency:
1.0≤α≤1.5 …(4)
Below, first embodiment's operation is described.When by carrying when cover 2 connector 2B and powering to pump from the outside, the driving current that flows to the rotor 7B of motor 7 rotates rotor 7B and running shaft 6 together, the impeller 20 that driven pump housing 9 is interior.When impeller 20 rotated, the fuel oil in the fuel tank (not shown) was inhaled into fuel gallery 15 by filler opening 11, and fuel oil 15 is carried along the fuel gallery by the blade 23 of impeller 20 then, and is pressed onto in the shell 1 by oil outlet 14.
Be forced into fuel oil in the shell 1 and in shell 1, be passed to carry by fuel gallery 8 and cover 2, so that open the safety check 3 among the delivery pipe 2A.Then, fuel oil by outer oil pipe (not shown), for example with the pressure of 200-500kPa and the flow velocity of 30-200L/h, is transported to the injection valve (not shown) of engine main body from delivery pipe 2A.
As our result of study to the ratio of the total length H of the straight section length H1 of linear blade part 23A and blade 23, confirm when ratio H1/H is set in the scope of the shown 1/3-2/3 of formula (1), best, in the time of in the scope of the shown 2/5-3/5 of formula (2), can access as the shown higher pump efficiency of Fig. 6 characteristic curve.In this case, the angle [alpha] corresponding to the length that turns forward of curved vane part 23B is set at about 1.2 °.
In addition, as us to result of study corresponding to the angle [alpha] of the length that turns forward of curved vane part 23B, confirm when angle [alpha] is set in the scope of shown 0.5-2.0 ° of formula (3), best, in the time of in the scope of shown 1.0-1.5 ° of formula (4), can access as the shown higher pump efficiency of Fig. 7 characteristic curve.In this case, the ratio of the total length H of the straight section length H1 of linear blade part 23A and blade 23 is set at about 1/2.
In this respect, the ratio that demonstrates as the total length H of the straight section length H1 of linear blade part 23A and blade 23 is set at about 1/2 in the scope of 2/5-3/5, and in 1.0-1.5 ° scope, be set at about 1.2 ° corresponding to the angle [alpha] of the length that turns forward of curved vane part 23B, can access the highest pump efficiency.
Therefore in first embodiment, begin crooked starting point position D at the curved section 23B of the blade 23 of impeller 20, promptly, straight section length H1, be set at the position with respect to the 2/5-3/5 (about 1/2) of the total length H of blade 23, the angle [alpha] of while corresponding to the length that turns forward of curved vane part 23B is set at 1.0-1.5 ° (about 1.2 °).
This makes blade 23 can have one to relax curved vane part 23B crooked, that have the suitable length that turns forward that the sense of rotation at impeller 20 obtains from length direction middle part.
As a result of, when impeller 20 rotates, even in low relatively flow rates, also can access from the blade groove between the blade 23 to the fuel gallery 15 level and smooth fuel flow, prevented to reduce with respect to the flow velocity of rpm.In addition, impeller 20 provides suitable kinetic energy to fuel oil, can stop the increase in big relatively flow rates internal torque loss, and pump is turned round in the high efficiency scope of motor 7, causes reaching higher pump efficiency in the whole service scope of pump.
In addition, form because the curved vane part 23B of blade 23 is circular bend, fuel oil energy flows smoothly along the circular surface of curved vane part 23B, and fuel oil is flowed out smoothly from the blade groove between the blade 23.
Referring to Fig. 8-14, second embodiment of the present invention is shown here, remove and cut away obliquely outside the side of the blade 35 of blade 35 roots one side and the chamfering 39 of radially extending along impeller 20 that the angle between the back obtains, second embodiment and first embodiment's structure is basic identical.
Referring to Fig. 8 and 9, annular fuel gallery 31 is positioned at the position of first embodiment's fuel gallery 15.Fuel gallery 31 comprises the circular groove 10B of frame 10, and forming one is passage that the center circumferentially extends, C vertical length tee section, bigger with axes O-O.
There is the upper and lower end of the circle of being shaped as fuel gallery 31, and fuel oil flows along their forms with circulation shown in arrow among Fig. 9, and when fuel oil was carried by fuel gallery 31, the circumference at the circular portion center of fuel gallery 31 formed the F of channel center like this.The F of channel center is with respect to 31 inner 31A is positioned at the distance L 1 of distance inner 31A about 1/2 to outer end 31B radial length L from the fuel gallery.The top of fuel gallery 31 is connected with filler opening 11, and terminal is connected with oil outlet 14.
The shape of impeller 32, for example, roughly as a disk of being made by the plastic material that strengthens, and the impeller that can be installed in pump case 9 rotationally holds in the dimple 13.
(axes O-O) has the engaging hole 33 of an assembling running shaft 6 to impeller 32 in center of rotation.A plurality of (for example three) through hole 34 be arranged in engaging hole 33 around.Referring to Figure 10, impeller 20 is with many blades 35 that also radially extend along circumferential arrangement outside it.Between adjacent vanes 35, each groove 36 has roughly the round-shaped curvature corresponding to the fuel gallery 31 of pump case 9 to a pair of circular groove 36 with the form of chevron.
Referring to Figure 10 and 11, blade 35 is configured as the plate body in substantial rectangular cross section, having the impeller of being located at 32 sense of rotation sees, it is the direction of arrow A, at the front of last side 35A, be positioned at as in rotational direction seeing, at the back 35B of back one side, and a pair of side 35C between front 35A and back 35B.
A pair of chamfering 39 is positioned at the radially extension of root one side of blade 35 along impeller 32.Referring to Figure 10-12, each chamfering 39 is to obtain by side 35C that cuts away blade 35 obliquely and the angle between the 35B of back.The total length T of chamfering 39 is set to approximate greatly from the fuel gallery 31 the inner 31A distance L 1 to the F of channel center, that is, the value of (2/5 to 3/5) * L, wherein L is the radial length of fuel gallery 31, according to following formula (5):
2/5≤(T/L)≤3/5 …(5)
The total length T of chamfering 39, the best value that is set at (9/20 to 11/20) * L according to following formula (6):
9/20≤(T/L)≤11/20 …(6)
The total length T of chamfering 39 is set in the scope that is provided by formula (5) and (6), and is best, in 1/2 value with respect to the radial length L of fuel gallery 31.Whereby, the F of channel center that forms when chamfering 39 constitutes and extends to fuel oil and flow through fuel gallery 31 with the circulation form enables to reach the optimum efficiency that fuel oil flows into the blade groove between the blade 35 smoothly.
The chamfered part 39A of root one side forms by cutting away an angle, to have constant chamfering width, obtains the level and smooth fuel oil stream from the blade groove between its root one side inflow blade 36, can reduce the resistance of fuel oil stream.On the other hand, the chamfered part 39B of head one side constitutes the chamfering width that reduces gradually towards its head, be implemented in the level and smooth connection between the chamfered part 39A of the back 35B of blade 35 and side 35C and root one side, fuel oil energy is flow through therebetween smoothly.
Referring to Figure 12, the shape of the chamfered part 39A of root one side of detailed description chamfering 39.The chamfered part 39A of root one side is set at according to the formula (7) of bottom with respect to the angle of inclination beta of the side 35C of blade 35 in 30-70 ° the scope:
30≤β≤70 …(7)
Angle of inclination beta in the formula (7) is preferably disposed in 40-60 ° the scope according to following formula (8):
40≤β≤60 …(8)
Referring to Fig. 9, the total length T of the length T 1 relative chamfering 39 of the chamfered part 39A of root one side is set to the value of (1/5 to 4/5) * T according to the formula (9) of bottom:
1/5≤(T1/T)≤4/5 …(9)
The length T 1 of the chamfered part 39A of root one side preferably is set to the value of (2/5-3/5) according to the formula (10) of bottom:
2/5≤(T1/T)≤3/5 …(10)
As to the chamfered part 39A of root one side result of study with respect to the angle of inclination beta of the side 35C of blade 35, confirm to be set in 30-70 ° the scope that illustrates as formula (7) when angle of inclination beta, best, in 40-60 ° the scope that illustrates as formula (8), can obtain the higher pump efficiency shown in the characteristic curve among Figure 13.
In this case, the ratio of the total length T of the length T 1 of the chamfered part 39A of root one side and chamfering 39 is set at and is approximately 1/2.Whereby, the angle of inclination beta of the chamfered part 39A of root one side just can be set to equal substantially the flow angle of the fuel oil that flows from the side 35C of blade 35 to its back 35B, causes forming the level and smooth fuel flow along the chamfered part 39A of root one side.
In addition, as to the length T 1 of the chamfered part 39A of root one side and the result of study of the ratio of the total length T of chamfering 39, confirm when ratio T1/T is set in the scope of the 1/5-4/5 that illustrates as formula (9), best, in the time of in the scope of the 2/5-3/5 that illustrates as formula (10), can access the higher pump efficiency shown in the characteristic curve among Figure 14.
In this case, the chamfered part 39A of root one side is set at about 50 ° with respect to the angle of inclination beta of the side 35C of blade 35.Whereby, the chamfered part 39A of the root one side containment big groove by constant width flows into fuel oil at the issuable eddy current of root one side of blade 35 smoothly.
In addition, we studies show that, because the chamfered part 39B of head one side has the chamfering width that reduces gradually towards head, guaranteed the level and smooth connection between the chamfered part 39A of the back 35B of blade 35 and side 35C and root one side, fuel oil energy flows to the chamfered part 39A of root one side smoothly from the side 35C of blade 35, and flow to back 35B from the chamfered part 39A of root one side, can access higher pump efficiency.
In this respect, the ratio T/L that demonstrates as the radial length L of the total length T of chamfering 39 and fuel gallery 31 is set at 1/2 in the scope of 9/20-11/20, the chamfered part 39A of root one side is set at 50 ° with respect to the angle of inclination beta of the side 35C of blade 35 in 40-60 ° scope, and the ratio T1/T of the length T 1 of the chamfered part 39A of root one side and the total length T of chamfering 39 was set in scope 2/5-3/5 1/2 o'clock, can obtain the highest pump efficiency.
In second embodiment, the chamfering 39 that obtains by the angle of cutting away obliquely between side 35C and the back 35B is positioned at the side of impeller 32.Therefore, when impeller 32 rotated, chamfering 39 made fuel oil energy flow smoothly along the chamfered part 39A and the head one side chamfered part 39B of root one side.
In addition, design chamfering 39 like this, promptly be set to 9/20-11/20 (being preferably 1/2) along the ratio of the radial length L of its total length T that radially extends and fuel gallery 31 at impeller 32, the chamfered part 39A of root one side is set to 40-60 ° (being preferably 50 °) with respect to the angle of inclination beta of the side 35C of blade 35, and the ratio of the total length T of the length T 1 of the chamfered part 39A of root one side and chamfering 39 is set to 2/5-3/5 (being preferably 1/2).
Whereby, in second embodiment, the tilt angle of the position of chamfering 39 (the chamfered part 39A of root one side) and length and root one side chamfering 39A can be provided with by the inflow position that fuel gallery 31 flows into the blade groove between the blade 35 corresponding to fuel oil, size is according to the level and smooth needs that flow into, angle makes it possible to level and smooth inflow, make and compare, can flow to fuel gallery 31 from the blade groove between the blade 35 more smoothly, can reach higher pump efficiency with first embodiment.
Referring to Figure 15-23, these illustrate the 3rd embodiment of the present invention.Referring to Figure 15, turbine fuel pump has a cylindrical shell 101, and its constitutes the shell of pump, and has to be transferred and cover 102 and the axial end portion that seals of pump case 109.
The conveying lid 102 of covered cylinder shape is positioned at an end of shell 101.As shown in figure 15, the 102 bearing housing 102C that are provided with delivery pipe 102A and the connector 102B that projects upwards and are positioned at the downward extension in center are covered in conveying.
In delivery pipe 102A, be provided with safety check 103 and be used to keep residual pressure.When motor 107 rotated, the fuel oil that safety check 103 is flowed in the shell 101 was opened, so that fuel oil is conveyed into outside fuel pipe (not shown) from delivery pipe 102A.When motor 107 stopped, safety check 103 was closed preventing that the fuel oil in the oil pipe from flowing back to shell 101, thereby fuel pipe is remained on predetermined residual pressure.
Referring to Figure 16, axle bush 104 is installed in to carry and covers among 102 the bearing housing 102C, and axle bush 105 is installed among the stepped bore 112D of inner housing 112.Axle bush 104,105 is formed the bearing of supporting rotating shaft 106 rotationally.
Running shaft 106 by axle bush 104,105 be supported in carry cover 102 and pump case 109 between.As shown in figure 16, running shaft 106 extends axially along axes O-O in shell 101, so that rotor 107B of supporting motor 107 etc. rotationally.Referring to Figure 17, constitute a plane (chamfer) 106A in the lower end of running shaft 106, so that assemble with the engagement of spline state with impeller 117.
For motor 107, when the connector 102B, brush and the commutator 107C that cover 102 by conveying gave rotor 107B power supply, rotor 107B rotated with running shaft 106, with impeller 117, for example rotates with 5000-8000rpm.
Between the yoke 107A of motor 107 and rotor 107B, form fuel gallery 108, be used for the fuel oil of pressing to shell 101 from the oil outlet 114 of pump case 101 being passed to carry covering 102 by the gap between yoke 107A and the rotor 107B.
Shown in Figure 15 and 16, the frame 110 of pump case 109 by such as crimping means of fixation interlocks such as (calking) be assemblied in the lower end of shell 101, from outside closed casing 101.Frame 110 constitutes an integral body with filler opening 111.
In addition, cylindrical shape part 112A has annular fuel gallery 115 in the surface within it.Lid part 112B constitutes the stepped bore 112D that axle bush 105 inserts wherein, and its outer edges has vertically extending oil outlet 114.
There is the upper and lower end of the circle of being shaped as fuel gallery 115, and fuel oil flows with the form of circulation as shown in figure 18 along them, and when fuel oil was carried by fuel gallery 115, the circumference at the center of the circular portion of fuel gallery 115 formed the C of channel center like this.The C of channel center is with respect to 115 inner 115A is positioned at the distance of the about 1/2L1 of the inner 115A of distance to the radial length L of its outer end 115B from the fuel gallery.
There is the top that is connected with filler opening 111 fuel gallery 115, with the terminal that is connected with oil outlet 114.In addition, one side has oil inlet passage part 115C at top in fuel gallery 115, is used for the fuel oil that sucks by filler opening 111 is introduced fuel gallery 115 smoothly.
Sealing next door 116 is arranged on cylindrical shape part 112A one side of inner housing 112.As shown in figure 17, sealing next door 116 constitutes from the circular projection of the protruding point to adjacent impeller 117 excircles of the cylindrical shape part 112A of inner housing 112.Sealing next door 116 seals up the periphery of the impeller 117 between filler opening 111 and the oil outlet 114, and the fuel oil that sucks through filler opening 111 necessarily 115 is flowed along the fuel gallery.
The shape of impeller 117 for example, roughly as a disk of being made by the plastic material that strengthens, and can be installed in the dimple that holds impeller 113 of pump case 109 rotationally.Impeller 117 with rotating along the direction of arrow A among Figure 17, is transported to oil outlet 114 to the fuel oil that sucks through filler opening 111 through fuel gallery 115 by motor 107.
(axes O-O) has the engaging hole 118 of an assembling running shaft 106 to impeller 117 in center of rotation.A plurality of (for example three) through hole 119 be arranged in engaging hole 118 around.Referring to Figure 19, impeller 117 is with many blades 120 that radially extend along circumferential array outside it.A pair of circular groove 121 is between adjacent vanes 120, and each groove 121 has roughly the round-shaped curvature corresponding to the passage 115 of pump case 109.
Referring to Figure 19 and 20, blade 120 constitutes the plate body that the cross section is essentially rectangle, have to be positioned at and see along the wheel rotation direction, it is the direction of arrow A, at the front of last side 120A, be positioned at along the wheel rotation direction and see, at the back 120B of back one side, and a pair of side 120C between front 120A and back 120B.
A pair of chamfering 124 is positioned at root one side of blade 120, along the radially extension of impeller 117.Referring to Figure 19-21, each chamfering 124 is to obtain by side 120C that cuts away blade 120 obliquely and the angle between the 120B of back.The total length H of chamfering 124 is set to approximate greatly from the fuel gallery 115 the inner 115A distance L 1 to the C of its channel center, that is, (2/5-3/5) * value of L, wherein L is the radial length of fuel gallery 31, according to following formula (11):
2/5≤(T/L)≤3/5 …(11)
The total length H of chamfering 124, the best value that is set at (9/20-11/20) * L according to following formula (12):
9/20≤(T/L)≤11/20 …(12)
The total length H of chamfering 124 is set in the scope that is provided by formula (11) and (12), and is best, in 1/2 value with respect to the radial length L of fuel gallery 115.Whereby, the C of channel center that forms when chamfering 124 constitutes and extends to fuel oil and flow through fuel gallery 115 with the circulation form enables to reach the optimum efficiency that fuel oil flows into the blade groove between the blade 120 smoothly.
The chamfered part 124A of root one side constitutes by cutting away an angle, and has constant substantially chamfering width, obtains the level and smooth fuel oil stream from the blade groove between its root one side inflow blade 120, the feasible resistance that can reduce fuel flow.On the other hand, the chamfered part 124B of head one side constitutes the chamfering width that reduces gradually to its head, is implemented in the level and smooth connection between the chamfered part 124A of back 120B and side 120C and root one side, and fuel oil energy is flow through therebetween smoothly.
Referring to Figure 21, the shape of the chamfered part 124A of root one side of detailed description chamfering 124.The chamfered part 124A of root one side is set at according to the formula (13) of bottom with respect to the inclined angle alpha of the side 120C of blade 120 in 30-70 ° the scope:
30≤α≤70 …(13)
Inclined angle alpha in the formula (7) preferably is set in 40-60 ° the scope by following formula (8):
40≤α≤60 …(14)
Referring to Figure 18, the length H1 of the chamfered part 124A of root one side is set at the value of (1/5≤4/5) * T according to the formula (15) of bottom with respect to the total length H of chamfering 124:
1/5≤(H1/H)≤4/5 …(15)
The length H1 of the chamfered part 124A of root one side preferably is set to the value of (2/5-3/5) * H according to the formula (16) of bottom:
2/5≤(H1/H)≤3/5 …(16)
Below, the 3rd embodiment's operation is described.When by carrying when cover 102 connector 102B and powering to pump from the outside, the driving current that flows to the rotor 107B of motor 107 rotates rotor 107B and running shaft 106 together, the impeller 117 that driven pump housing 109 is interior.When impeller 117 rotated, the fuel oil in the fuel tank (not shown) was inhaled into fuel gallery 115 by filler opening 111, and fuel oil 115 is carried along the fuel gallery by the blade 120 of impeller 117 then, and is pressed onto in the shell 101 by oil outlet 114.
The fuel oil that is forced in the shell 101 is passed to oil outlet 102 by fuel gallery 108 grades in shell 1, so that open the safety check 103 among the delivery pipe 102A.Then, fuel oil by outer transport pipe (not shown), for example, with the transporting velocity of pressure and the 30-200L/h of 200-500kPa, is transported to the injection valve (not shown) of engine main body from delivery pipe 102A.
As us to the chamfered part 124A of root one side result of study with respect to the angle α of the side 120C of blade 120, confirm to be set within 30-70 ° the scope that formula (13) illustrates as angle α, best, in the time of within 40-60 ° the scope that formula (14) illustrates, can access under the condition of 300kPa discharge pressure and 80L/h transporting velocity by the higher pump efficiency shown in the characteristic curve among Figure 22.
In this case, the ratio of the total length H of the length H1 of the chamfered part 124A of root one side and chamfering 124 is set at about 1/2.Whereby, the inclined angle alpha of the chamfered part 124A of root one side can be set to equal substantially to flow to from the side 120C of blade 120 flow angle of the fuel oil of its back 120B, realize that fuel oil flows smoothly along the chamfered part 124A of root one side, causes the reduction of fuel flow resistance.
In addition, as our result of study to the ratio of the total length H of the length H1 of the chamfered part 124A of root one side and chamfering 124, confirm in the scope that ratio H1/H is arranged on the 1/5-4/5 that formula (15) illustrates, best, in the time of in the scope of the 2/5-3/5 that formula (16) illustrates, can access the higher pump efficiency shown in the characteristic curve among Figure 23.
In this case, the chamfered part 124A of root one side is set to about 50 ° with respect to the inclined angle alpha of the side 120C of blade 120.Whereby, the chamfered part 124A of root one side has contained through the big groove of constant width can reduce the resistance of fuel flow at the eddy current that root one side of blade 120 may occur.
In addition, we studies show that, because the chamfered part 124B of head one side has the chamfering width that reduces gradually towards head, this has guaranteed the level and smooth connection between the chamfered part 124A of the back 120B of blade 120 and side 120C and root one side, fuel oil energy flows to the chamfered part 120A of root one side and flows to back 120B from the chamfered part 120A of root one side from the side 120C of blade 120 smoothly, can access higher pump efficiency.
In this respect, the ratio H/L that demonstrates as the radial length L of the total length H of chamfering 124 and fuel gallery 115 is set at 1/2 in the scope of 9/20-11/20, the chamfered part 124A of root one side is set at 50 ° with respect to the inclined angle alpha of the side 120C of blade 120 in 40-60 ° scope, and the ratio H1/H of the total length H of the length H1 of the chamfered part 124A of root one side and chamfering 124 was set in scope 2/5-3/5 1/2 o'clock, can obtain the highest pump efficiency.
In the 3rd embodiment, the chamfering 124 that obtains by the angle of cutting away obliquely between side 120C and the back 120B is positioned at the side of impeller 117.Design chamfering 124 like this, promptly the ratio of the radial length L of total length H that radially extends at impeller 117 and fuel gallery 115 is set to 9/20-11/20 (being preferably 1/2), the chamfered part 124A of root one side is set to 40-60 ° (being preferably 50 °) with respect to the inclined angle alpha of the side 120C of blade 120, and the ratio of the total length H of the length H1 of the chamfered part 124A of root one side and chamfering 124 is set to 2/5-3/5 (being preferably 1/2).
Whereby, in the 3rd embodiment, the tilt angle of the position of chamfering 124 (the chamfered part 124A of root one side) and length and root one side chamfered part 124A can be provided with by the inflow position that fuel gallery 115 flows into the blade groove between the blade 120 corresponding to fuel oil, size is according to the level and smooth needs that flow into, and angle makes it possible to level and smooth inflow.
Consequently, when impeller 117 rotates, chamfering 124 makes that fuel oil can be along the chamfered part 124A of root one side and the chamfered part 124B smooth flow of head one side, so that reduce the fuel flow resistance, realize that fuel oil transfers to oil outlet 114 expeditiously by fuel gallery 115, cause the raising of pump efficiency.
In the 3rd embodiment, fuel gallery 115 is configured as the passage of a big vertical length and C tee section.Best, referring to Figure 24, in first kind of modification, fuel gallery 131 may be by vertically being divided into two parts by the annular projection 132 that radially protrudes inwards from the center 133 of fuel gallery, and promptly internal channel 133 and butt joint side canal 134 are formed.
In addition, in the 3rd embodiment, each blade 120 has the linear blade part 122 of extending along impeller 117 radial alignment in root one side, sees to the crooked circularly curved vane part 123 in front side and have along the sense of rotation of impeller 117 in head one side.As selection, referring to Figure 25, in second kind of modification, each blade 141 has linearly extended linear structure from the root to the head.As an alternative, blade 120 has from the root to the head in rotational direction the warp architecture of circular bend forward.
According to after embodiment has done explanation to the present invention intuitively, be noted that the present invention is not limited thereto, can in not departing from the scope of the present invention, make various changes and modifications.
At this, whole instructions of Japanese patent application P2002-257988 that submits on September 3rd, 2002 and the Japanese patent application P2002-165946 that submitted on June 6th, 2002 all merge, in order to reference.
Claims (8)
1. turbine fuel pump, it has:
The shell that holds motor;
Be contained in the housing on the shell, this housing has the annular pass between filler opening and oil outlet; And
Be installed in rotation on the impeller in the housing, this impeller has a plurality of blades of arranging that radially extend along impeller on excircle, when blade is rotated by motor, carry fuel oil by passage;
Each blade has the plate body in a general rectangular cross section, and from the sense of rotation of impeller, this plate body has a front and a back, and a pair of side between the front and back;
Each blade has one to be positioned at the chamfering that root of blade one side is radially extended along impeller, this chamfering is to obtain by side of cutting away blade obliquely and the angle between the back, this chamfering has predetermined length, and this predetermined length is (2/5 to 3/5) * L, and wherein L is the radial length of passage.
2. according to the described turbine fuel pump of claim 1, it is characterized in that the predetermined length of chamfering is (9/20 to 11/20) * L.
3. according to the described turbine fuel pump of claim 1, it is characterized in that, chamfering comprises root one side part and head one side part, and root one side partly has constant substantially chamfering width and predetermined length, and head one side partly has the chamfering width that reduces gradually from the head of root one side part.
4. according to the described turbine fuel pump of claim 3, it is characterized in that the predetermined length of root one side part is (1/5 to 4/5) * T, wherein T is the total length of chamfering.
5. according to the described turbine fuel pump of claim 4, it is characterized in that the predetermined length of root one side part is (2/5 to 3/5) * T.
6. according to the described turbine fuel pump of claim 5, it is characterized in that root one side partly has the predetermined tilt angle with respect to blade side, wherein Yu Ding tilt angle is 30 ° to 70 °.
7. according to the described turbine fuel pump of claim 6, it is characterized in that the predetermined tilt angle of root one side part is 40 ° to 60 °.
8. according to the described turbine fuel pump of claim 7, it is characterized in that the predetermined length of chamfering is (1/2) * L, the predetermined length of root one side part is (1/2) * T, and the predetermined tilt angle of root one side part is 50 °.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP165946/2002 | 2002-06-06 | ||
| JP2002165946A JP4177602B2 (en) | 2002-06-06 | 2002-06-06 | Turbine type fuel pump |
| JP257988/2002 | 2002-09-03 |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB031363253A Division CN100526652C (en) | 2002-06-06 | 2003-05-28 | Turbine fuel pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1693693A CN1693693A (en) | 2005-11-09 |
| CN100378319C true CN100378319C (en) | 2008-04-02 |
Family
ID=30433664
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100763352A Expired - Fee Related CN100378319C (en) | 2002-06-06 | 2003-05-28 | Turbine type fuel pump |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4177602B2 (en) |
| CN (1) | CN100378319C (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5407318A (en) * | 1992-12-08 | 1995-04-18 | Nippondenso Co., Ltd. | Regenerative pump and method of manufacturing impeller |
| US5513950A (en) * | 1994-12-27 | 1996-05-07 | Ford Motor Company | Automotive fuel pump with regenerative impeller having convexly curved vanes |
| US5527149A (en) * | 1994-06-03 | 1996-06-18 | Coltec Industries Inc. | Extended range regenerative pump with modified impeller and/or housing |
| JP2002130173A (en) * | 2000-09-11 | 2002-05-09 | Walbro Corp | Turbine type fuel pump |
| JP2002276580A (en) * | 2001-03-15 | 2002-09-25 | Denso Corp | Turbine type fuel pump |
-
2002
- 2002-06-06 JP JP2002165946A patent/JP4177602B2/en not_active Expired - Fee Related
-
2003
- 2003-05-28 CN CNB2005100763352A patent/CN100378319C/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5407318A (en) * | 1992-12-08 | 1995-04-18 | Nippondenso Co., Ltd. | Regenerative pump and method of manufacturing impeller |
| US5527149A (en) * | 1994-06-03 | 1996-06-18 | Coltec Industries Inc. | Extended range regenerative pump with modified impeller and/or housing |
| US5513950A (en) * | 1994-12-27 | 1996-05-07 | Ford Motor Company | Automotive fuel pump with regenerative impeller having convexly curved vanes |
| JP2002130173A (en) * | 2000-09-11 | 2002-05-09 | Walbro Corp | Turbine type fuel pump |
| JP2002276580A (en) * | 2001-03-15 | 2002-09-25 | Denso Corp | Turbine type fuel pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2004011528A (en) | 2004-01-15 |
| CN1693693A (en) | 2005-11-09 |
| JP4177602B2 (en) | 2008-11-05 |
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|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
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Granted publication date: 20080402 Termination date: 20180528 |