CN100378319C - turbo fuel pump - Google Patents

turbo fuel pump Download PDF

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Publication number
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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fuel
impeller
blade
chamfer
root
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CN1693693A (en
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本岛淳一
饭岛正昭
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Hitachi Ltd
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Hitachi Ltd
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Abstract

涡轮燃油泵包括一个具有多个叶片的叶轮,每个叶片包括沿叶轮径向直线延伸的直线叶片部分,和从直线叶片部分的头部开始、向着从叶轮转动的方向看的在前一侧圆形地弯曲延伸的弯曲叶片部分组成。直线叶片部分的长度为(1/3至2/3)×H,其中H是叶轮的总长度。

The turbo fuel pump includes an impeller having a plurality of blades, each of which includes a straight blade portion extending linearly in the radial direction of the impeller, and a circular blade on the front side from the head of the straight blade portion toward the direction of rotation of the impeller. It consists of a curved blade section that extends in a curved manner. The length of the straight blade portion is (1/3 to 2/3) x H, where H is the total length of the impeller.

Description

涡轮燃油泵 turbo fuel pump

本申请是申请号为03136325.3的发明专利申请的分案申请。原申请的申请日为2003年05月28日,发明名称为“涡轮燃油泵”。This application is a divisional application of the invention patent application with application number 03136325.3. The filing date of the original application was May 28, 2003, and the title of the invention was "turbine fuel pump".

技术领域 technical field

本发明涉及适合用于,例如为汽车发动机的喷射阀等输送燃油的涡轮燃油泵。The invention relates to turbo fuel pumps suitable for use, for example, in delivering fuel to injection valves and the like of motor vehicle engines.

背景技术 Background technique

通常,为了给发动机输送燃油,在小客车上安装电子控制的燃油喷射系统,燃油喷射系统有把燃油喷射到发动机燃烧室的喷射阀,把例如在车辆后部等的油箱中的燃油输送给喷射阀的燃油泵。最近,由于全球环境保护的社会需要,因此增加了对改进车辆燃油消耗的需求。因此,对于由电动机驱动的燃油泵的重要挑战是实现提高效率(即减少电能消耗)和减小尺寸和重量。Usually, in order to deliver fuel to the engine, an electronically controlled fuel injection system is installed on the passenger car. The fuel injection system has an injection valve that injects fuel into the combustion chamber of the engine, and delivers the fuel in the fuel tank, such as at the rear of the vehicle, to the injection valve for the fuel pump. Recently, there has been an increased demand for improvement in fuel consumption of vehicles due to social demands for global environmental protection. Therefore, an important challenge for electric motor driven fuel pumps is to achieve increased efficiency (ie reduced electrical power consumption) and reduced size and weight.

在通常的使用中,燃油泵包括涡轮燃油泵,涡轮燃油泵具有一个容纳电动机的圆筒形外壳,一个安装于外壳一端的上盖,一个安装于外壳另一端的用于支承电动机并有在进油口和出油口之间的环形燃油通道的壳体,以及一个转动地安装于壳体内的叶轮,当叶轮被电动机转动时,叶轮把从进油口吸进的燃油通过燃油通道送到出油口。In normal use, the fuel pump includes a turbo fuel pump, the turbo fuel pump has a cylindrical housing for accommodating the electric motor, an upper cover mounted on one end of the housing, and a cover mounted on the other end of the housing for supporting the motor and having a The casing of the annular fuel passage between the oil port and the oil outlet, and an impeller rotatably installed in the casing. When the impeller is rotated by the motor, the impeller sends the fuel sucked in from the oil inlet through the fuel passage to the outlet. oil port.

叶轮的形状像一个圆盘,有在外围沿圆周排列并径向延伸的叶片和在叶片之间形成的叶片凹槽。从进油口被吸进的燃油通过燃油通道被引进叶片凹槽内,以接受来自叶片的动能,然后又被排向通道。排向燃油通道的燃油在通道内循环,然后燃油又被引到叶片凹槽内。在通道内的燃油在流入和流出的重复中增加压力,并且通过出口被排出。The impeller is shaped like a disc with radially extending vanes arranged circumferentially on the outer periphery and vane grooves formed between the vanes. The fuel sucked in from the oil inlet is introduced into the vane groove through the fuel channel to receive the kinetic energy from the vane, and then is discharged to the channel. The fuel discharged to the fuel passages circulates in the passages, and then the fuel is directed into the vane grooves. Fuel in the passage builds up pressure in repeated inflow and outflow, and is expelled through the outlet.

改善燃油泵的效率对提高电动机的效率和泵部分的效率都是重要的。特别是,叶轮被在燃油中转动的电动机驱动,由于燃油的粘性而产生转矩损失。当在壳体内转动时,叶轮也由于燃油的粘性而产生转矩损失。这些转矩损失与rpm(每分钟转数)的平方成正比地增加,因此当燃油泵以高的rpm运转时转矩损失变得非常大,导致泵效率的降低。Improving the efficiency of the fuel pump is important to improving both the efficiency of the electric motor and the efficiency of the pump section. In particular, the impeller is driven by an electric motor turning in fuel, with torque losses due to the viscosity of the fuel. The impeller also suffers torque losses due to the viscosity of the fuel when turning within the housing. These torque losses increase in proportion to the square of rpm (revolutions per minute), so torque losses become very large when the fuel pump operates at high rpm, resulting in a reduction in pump efficiency.

通过设置泵部分的尺寸规格,就能在低rpm下达到需要的流速,转矩损失就能受到遏制。然而在这种情况下,驱动叶轮所需要的转矩增加。By sizing the pump section, the desired flow rate can be achieved at low rpm and torque losses can be contained. In this case, however, the torque required to drive the impeller increases.

此外,由于需要减小燃油泵的尺寸,电动机也要减小尺寸。如上所述,在低rpm下产生高转矩需要电动机在低效率范围内运转。借此,不仅通过设置泵部分的尺寸规格以便使转矩损失最小对提高泵效率是重要的,而且设置电动机的尺寸规格使之能在高效率范围内工作也是重要的。In addition, due to the need to reduce the size of the fuel pump, the electric motor is also reduced in size. As mentioned above, generating high torque at low rpm requires the motor to operate in a low efficiency range. Thus, not only is it important to improve pump efficiency by sizing the pump section so that torque loss is minimized, but also sizing the motor so that it can operate within a high efficiency range.

在改善涡轮燃油泵效率方面,提出了各种改进叶轮的方案。改进方案之一公开在JP-A8-100780中,在其中叶轮的每个叶片都有一个沿叶轮的转动方向看向后弯曲的根部,并且头部从弯曲部分直线地向后倾斜地沿径向向外伸出。甚至在相对低的rpm范围内,叶片的这种形状也能使燃油从叶片凹槽平滑地流向通道,防止流速随rpm降低,提高了低压性能和流速控制能力。In terms of improving the efficiency of turbo fuel pumps, various impeller improvements have been proposed. One of the improvements is disclosed in JP-A8-100780, in which each blade of the impeller has a root that is bent backward as viewed in the direction of rotation of the impeller, and the head is inclined linearly backward from the curved portion radially stick out. Even in the relatively low rpm range, this shape of the vanes allows for a smooth flow of fuel from the vane grooves to the passages, preventing the flow rate from decreasing with rpm, improving low pressure performance and flow rate control.

在JP-A8-100780中公开的燃油泵,如上所述,叶轮的每个叶片都有一个从叶轮的转动方向看向后弯曲的根部,并且头部从弯曲部分直线地向后倾斜地沿径向向外伸出。用这种方式,叶轮能防止在相对低的rpm范围内流速随rpm降低。但是,由于叶轮有直线地向后倾斜的头部。燃油在后面的方向从叶片凹槽流出,不能给燃油较高的动能。借此,要达到相对大的流速需要相当大地增加rpm。这就导致在相对大的流速范围内转矩损失的增加,产生降低泵效率的问题。In the fuel pump disclosed in JP-A8-100780, as mentioned above, each blade of the impeller has a root portion bent backward as viewed from the direction of rotation of the impeller, and the head is linearly inclined backward from the curved portion along the radial direction. Stretch out. In this way, the impeller prevents the flow rate from decreasing with rpm in the relatively low rpm range. However, since the impeller has a rectilinearly inclined head. The fuel flows out of the vane grooves in the rear direction, which cannot give the fuel high kinetic energy. Thereby, a considerable increase in rpm is required to achieve a relatively large flow rate. This leads to an increase in torque loss over a relatively large flow rate range, creating a problem of lowering pump efficiency.

发明内容 Contents of the invention

因此,本发明的目标是提供一种能在整个运行范围内提高泵效率的涡轮燃油泵。It is therefore an object of the present invention to provide a turbo fuel pump which improves pump efficiency over the entire operating range.

本发明通常提供一种燃油泵,它具有:一个容纳电动机的外壳,装在外壳上的壳体,壳体具有在入口和出口之间的环形通道;能转动地安装在壳体内的叶轮,叶轮具有排列在叶轮外圆周并沿其径向延伸的叶片,当叶片被电动机转动时,输送燃油通过通道,每个叶片具有一个沿叶轮的径向延伸的直线部分和一个从叶轮的转动方向看从直线部分的头部成圆形地向叶轮的在前一侧弯曲延伸的弯曲部分,直线部分有预先确定的长度,该预先确定的长度为(1/3至2/3)×H,其中H是叶轮的总长度。The present invention generally provides a kind of fuel pump, and it has: a casing that accommodates electric motor, is contained on casing, and casing has the annular channel between inlet and outlet; It has blades arranged on the outer circumference of the impeller and extending radially along it. When the blades are rotated by the motor, the fuel is delivered through the channel. Each blade has a straight line extending along the radial direction of the impeller and a The head of the straight portion is curved in a circle toward the curved portion extended on the front side of the impeller, and the straight portion has a predetermined length, which is (1/3 to 2/3)×H, where H is the total length of the impeller.

本发明的一个方面是提供一种涡轮燃油泵,它具有:一个容纳电动机的外壳,装在外壳上的壳体,壳体具有在入口和出口之间的环形通道;能转动地安装在壳体内的叶轮,叶轮具有排列在叶轮外圆周并沿其径向延伸的叶片,当叶片被电动机转动时,输送燃油通过通道,每个叶片有一个截面基本为矩形的板体,该板体有位于叶轮在前一侧的前面,位于叶轮在后一侧的后面,以及在前面和后面之间的一对侧面,每个叶片有位于叶片根部一侧一侧沿叶轮的径向延伸的倒角,这个倒角是通过倾斜地切掉叶片侧面和后面之间的角得到的,倒角有预先确定的长度,其中预先确定的长度为(2/5至3/5)×L,其中L是通道的径向长度。One aspect of the present invention is to provide a turbo fuel pump, which has: a housing containing the motor, a housing mounted on the housing, the housing has an annular passage between the inlet and the outlet; rotatably mounted in the housing The impeller has blades arranged on the outer circumference of the impeller and extending radially along it. When the blades are rotated by the motor, the fuel is delivered through the channel. Each blade has a plate with a substantially rectangular cross-section. In front of the front side, behind the impeller on the rear side, and on a pair of sides between the front and back, each blade has a chamfer extending radially of the impeller on the side of the blade root, the The chamfer is obtained by obliquely cutting off the corner between the side and the rear of the blade, and the chamfer has a predetermined length, where the predetermined length is (2/5 to 3/5)×L, where L is the length of the channel radial length.

附图说明 Description of drawings

从以下参照附图的描述,本发明的其他目标和特征是显而易见的,其中:Other objects and features of the invention will be apparent from the following description with reference to the accompanying drawings, in which:

图1是依据本发明的涡轮燃油泵的第一个实施例的纵剖面图;Fig. 1 is a longitudinal sectional view of a first embodiment of a turbo fuel pump according to the present invention;

图2是图1的局部放大视图;Figure 2 is a partially enlarged view of Figure 1;

图3是沿着在图2中的III-III线截取的剖面图;Fig. 3 is a sectional view taken along line III-III in Fig. 2;

图4是叶轮叶片的放大透视图;Figure 4 is an enlarged perspective view of the impeller blade;

图5是叶轮叶片的平面图;Figure 5 is a plan view of the impeller blade;

图6是示出叶片弯曲部分的起点位置和泵效率的关系的曲线图;6 is a graph showing the relationship between the position of the starting point of the curved portion of the blade and the pump efficiency;

图7是与图6类似曲线图,示出对应于叶片弯曲部分向前倾斜长度的角度和泵效率之间关系的曲线图;Fig. 7 is a graph similar to Fig. 6, showing a graph corresponding to the relationship between the angle of the curved portion of the vane and the pump efficiency;

图8与图2类似,示出本发明的第二个实施例;Fig. 8 is similar to Fig. 2, shows the second embodiment of the present invention;

图9是图8的进一步的放大视图;Figure 9 is a further enlarged view of Figure 8;

图10与图4类似,示出叶轮的叶片;Figure 10 is similar to Figure 4, showing the blades of the impeller;

图11与图5类似,示出叶轮的多个叶片;Figure 11 is similar to Figure 5, showing a plurality of blades of the impeller;

图12与图3类似,是沿着图11中XII-XII线的剖面图;Fig. 12 is similar to Fig. 3 and is a sectional view along line XII-XII in Fig. 11;

图13是类似于图7的曲线图,示出根部一侧的倒角部分的倾斜角度和泵效率之间的关系;Fig. 13 is a graph similar to Fig. 7, showing the relationship between the inclination angle of the chamfered portion on the root side and the pump efficiency;

图14是类似于图13的曲线图,示出根部一侧的倒角部分的长度和泵效率之间的关系;Fig. 14 is a graph similar to Fig. 13, showing the relationship between the length of the chamfered portion on the root side and the pump efficiency;

图15类似于图1,示出本发明的第三个实施例;Fig. 15 is similar to Fig. 1, shows the third embodiment of the present invention;

图16类似于图8,示出图15的主要部分;Fig. 16 is similar to Fig. 8, shows the main part of Fig. 15;

图17类似于图12,是沿着图16中XVII-XVII线的剖面图;Fig. 17 is similar to Fig. 12, is a sectional view along line XVII-XVII in Fig. 16;

图18类似于图9,示出图17的主要部分;Fig. 18 is similar to Fig. 9, shows the main part of Fig. 17;

图19与图10类似,示出叶轮的多个叶片;Figure 19 is similar to Figure 10, showing a plurality of blades of the impeller;

图20与图11类似,示出叶轮的多个叶片;Figure 20 is a view similar to Figure 11, showing a plurality of blades of the impeller;

图21类似于图17,是沿着图20中XXI-XXI线的剖面图;Fig. 21 is similar to Fig. 17, is the sectional view along XXI-XXI line in Fig. 20;

图22是类似于图14的曲线图,示出根部一侧的倒角部分的倾斜角度和泵效率之间的关系;Fig. 22 is a graph similar to Fig. 14, showing the relationship between the inclination angle of the chamfered portion on the root side and the pump efficiency;

图23是类似于图22的曲线图,示出根部一侧的倒角部分的长度和泵效率之间的关系;Fig. 23 is a graph similar to Fig. 22, showing the relationship between the length of the chamfered portion on the root side and the pump efficiency;

图24与图18类似,示出第三个实施例的第一种变型;以及Figure 24 is similar to Figure 18, showing a first modification of the third embodiment; and

图25与图19类似,示出第三个实施例的第二种变型。Fig. 25 is similar to Fig. 19 and shows a second modification of the third embodiment.

具体实施方式 Detailed ways

参照附图,说明实施本发明的涡轮燃油泵。A turbo fuel pump embodying the present invention will be described with reference to the drawings.

参照图1-7,示出本发明的第一个实施例。参照图1,涡轮燃油泵有一个圆筒形的外壳1,它构成泵的外壳,并且有被输送盖2和泵壳体9封闭的轴向端部。Referring to Figures 1-7, a first embodiment of the present invention is shown. Referring to FIG. 1, the turbo fuel pump has a cylindrical casing 1 which constitutes the casing of the pump and has axial ends closed by a delivery cover 2 and a pump housing 9. Referring to FIG.

有盖的圆筒的输送盖2装配在外壳1的一端。如图1所示,输送盖2设有向上突出的输送管2A和连接器2B以及在中心向下延伸的轴承套2C。A capped cylinder delivery cap 2 is fitted at one end of the housing 1 . As shown in FIG. 1 , the delivery cover 2 is provided with a delivery pipe 2A and a connector 2B protruding upward, and a bearing sleeve 2C extending downward at the center.

止回阀3安装在输送管2A中用于保持剩余压力。在电动机7转动过程中,止回阀3被流入外壳1中的燃油打开,以便使燃油能从输送管2A压到外面的燃油管中(未示出)。当电动机停止时,止回阀3关闭,以防止燃油管内的燃油流回外壳1,这样使燃油管中保持一个预定的剩余压力。A check valve 3 is installed in the delivery pipe 2A for maintaining residual pressure. During the rotation of the electric motor 7, the check valve 3 is opened by the fuel flowing into the housing 1, so that the fuel can be pressed from the delivery pipe 2A into an external fuel pipe (not shown). When the motor stops, the check valve 3 is closed to prevent the fuel in the fuel pipe from flowing back into the casing 1, so that a predetermined residual pressure is maintained in the fuel pipe.

参照图2,轴衬4被嵌合安装在输送盖2的轴承套2C内,而轴衬5被嵌合安装在内壳体12的阶梯形孔12E内。轴衬4,5组成能转动地支承旋转轴6的轴承。Referring to FIG. 2 , the bushing 4 is fitted in the bearing sleeve 2C of the delivery cover 2 , and the bushing 5 is fitted in the stepped hole 12E of the inner casing 12 . The bushes 4, 5 constitute a bearing that rotatably supports the rotary shaft 6.

旋转轴6通过轴衬4,5被支承在输送盖2和泵壳体9之间。如图2所示,旋转轴6在外壳1内沿轴线O-O沿轴向延伸以便可转动地支承电动机7的转子7B等。参照图3,在旋转轴6的下端加工出平面(chamfer)6A以便与叶轮2以止转状态啮合。The rotary shaft 6 is supported between the delivery cover 2 and the pump housing 9 via bushings 4 , 5 . As shown in FIG. 2, the rotary shaft 6 extends axially along the axis O-O inside the casing 1 so as to rotatably support a rotor 7B of the motor 7 and the like. Referring to FIG. 3 , a chamfer 6A is machined at the lower end of the rotating shaft 6 so as to engage with the impeller 2 in a non-rotating state.

电动机7被装在外壳1中,并且有一个在输送盖2和泵壳体9之间装配在外壳1内的圆筒形轭7A,用于支承具有永久磁铁的定子(未示出),转子7B和换向器7C有间隙地安装在轭7A内,并且装配在旋转轴6上与之一起转动,一对电刷(未示出)滑动地与换向器7C接触。The motor 7 is housed in the housing 1 and has a cylindrical yoke 7A fitted in the housing 1 between the delivery cover 2 and the pump housing 9 for supporting a stator (not shown) with permanent magnets, a rotor 7B and a commutator 7C are mounted with a gap in the yoke 7A, and are fitted on the rotary shaft 6 to rotate therewith, and a pair of brushes (not shown) are in sliding contact with the commutator 7C.

就电动机7来说,当通过输送盖2的连接器2B、电刷和换向器7C给转子7B供电时,转子7B与旋转轴6一起转动,以便驱动叶轮20在中到高的rpm,即5000-8000rpm的范围内转动。As far as the motor 7 is concerned, when power is supplied to the rotor 7B through the connector 2B of the delivery cover 2, the brushes and the commutator 7C, the rotor 7B rotates together with the rotating shaft 6 so as to drive the impeller 20 at a medium to high rpm, i.e. Rotate within the range of 5000-8000rpm.

在电动机7的轭7A和转子7B之间构成燃油通道8,用于把从泵壳体9的出油口14排到外壳1中的燃油通过轭7A和转子7B之间的间隙循环到输送盖2。A fuel channel 8 is formed between the yoke 7A and the rotor 7B of the motor 7, which is used to circulate the fuel discharged from the oil outlet 14 of the pump housing 9 into the casing 1 to the delivery cover through the gap between the yoke 7A and the rotor 7B 2.

泵壳体9安装在外壳1的另一端或下端,通过垂直邻接外壳体10和内壳体12得到。泵壳体9用于转动地容纳叶轮20。The pump housing 9 is installed at the other or lower end of the outer housing 1 , obtained by vertically adjoining the outer housing 10 and the inner housing 12 . The pump housing 9 serves to rotatably accommodate an impeller 20 .

如图1和2所示,泵壳体9的外壳体10通过例如填缝(calking)这样的固定方式紧固地装配在外壳1的下端,从外侧封闭外壳1。外壳体10与进油口11是一个整体。As shown in FIGS. 1 and 2 , the outer casing 10 of the pump casing 9 is firmly fitted on the lower end of the casing 1 by a fixing means such as caulking to close the casing 1 from the outside. The outer casing 10 and the oil inlet 11 are integral.

外壳体10在轴中心(轴线O-O)有一个圆形凹部10A,有一个大体上半圆形截面的圆形凹槽10B,对应于叶轮20的外圆周以轴线O-O为中心沿圆周延伸。如图3所示,圆形凹槽10B在角θ的范围内沿圆周延伸,并且与内壳体12的外围壁凹槽12D一起构成下对接侧通道18The outer casing 10 has a circular recess 10A at the center of the shaft (axis O-O), and a circular recess 10B of substantially semicircular cross-section extending circumferentially around the axis O-O corresponding to the outer circumference of the impeller 20 . As shown in FIG. 3 , the circular groove 10B extends circumferentially within the range of the angle θ, and together with the peripheral wall groove 12D of the inner housing 12 constitutes the lower butt side channel 18

内壳体12用作为壳体部件和外壳体10一起组成泵壳体9。内壳体12以与外壳体10对接的状态被装配在外壳1中。The inner housing 12 is used as housing part to form the pump housing 9 together with the outer housing 10 . The inner case 12 is fitted in the outer case 1 in a state of butting against the outer case 10 .

如图2所示,内壳体12的形状像一个带盖的平的圆筒,并且具有形成圆筒形外围壁的圆筒部分12A和从上边盖住圆筒部分12A的盖子部分12B。圆筒部分12A在内边缘成形有一个圆形的容纳叶轮的凹座13,其开口在圆筒部分12A和外壳体10的接合面12C的一侧。此外,圆筒部分12A成形有处于环形突起16之下的外围壁凹槽12D。外围壁凹槽12D与外壳体10上的圆形凹槽10B一起形成对接侧通道18。盖子部分12B上成形有阶梯形孔12E,在其中插有轴衬5,盖子部分12B的外边缘有垂直延伸的出油口14。As shown in FIG. 2, the inner case 12 is shaped like a covered flat cylinder, and has a cylindrical portion 12A forming a cylindrical peripheral wall and a lid portion 12B covering the cylindrical portion 12A from above. The inner edge of the cylindrical portion 12A is formed with a circular impeller-accommodating recess 13 which opens on the side of the joint surface 12C of the cylindrical portion 12A and the outer casing 10 . Furthermore, the cylindrical portion 12A is formed with a peripheral wall groove 12D under the annular protrusion 16 . The peripheral wall groove 12D together with the circular groove 10B on the outer housing 10 forms a butt side channel 18 . The cover portion 12B is formed with a stepped hole 12E into which the bushing 5 is inserted, and has an oil outlet 14 extending vertically on the outer edge of the cover portion 12B.

在容纳叶轮的凹座13的外边缘通过泵壳体9形成环形通道15,以大致C形的方式以轴线O为中心沿圆周延伸,如图3所示。燃油通道15具有被环形突起16垂直地分割成的两部分,即内通道17和对接侧通道18。An annular passage 15 is formed through the pump housing 9 at the outer edge of the impeller-accommodating recess 13 , extending circumferentially centered on the axis O in a substantially C-shaped manner, as shown in FIG. 3 . The fuel passage 15 has two parts, namely an inner passage 17 and a butt side passage 18 , which are vertically divided by the annular protrusion 16 .

燃油通道15始端与进油口11连接,终端与出油口14连接。此外,燃油通道15在始端有一个进油通道部分15A,用于把通过进油口11吸入的燃油平滑地引导到燃油通道15中。The beginning end of the fuel passage 15 is connected with the oil inlet 11 , and the end is connected with the oil outlet 14 . In addition, the fuel passage 15 has an inlet passage portion 15A at the beginning for smoothly guiding the fuel sucked through the inlet 11 into the fuel passage 15 .

环形突起16形成在内壳体12的圆筒部分12A上。如图2所示,环形突起16以山脉的形状从圆筒部分12A沿径向向内,凸向叶轮20的外围,如剖面图所示,在叶轮20的轴向把燃油通道15分为上和下两部分,即内通道17和对接侧通道18。An annular protrusion 16 is formed on the cylindrical portion 12A of the inner housing 12 . As shown in FIG. 2 , the annular protrusion 16 is radially inward from the cylindrical portion 12A in the shape of a mountain range, and protrudes toward the periphery of the impeller 20 . And the next two parts, that is, the inner channel 17 and the butt side channel 18.

内通道17是以内壳体12的圆筒部分2A和盖子部分12B之间的内角形成的C形截面的槽。对接侧通道18是由外壳体10的圆形凹槽10B和内壳体12的外缘壁凹槽12D形成的C形截面的槽。The inner passage 17 is a C-shaped cross-sectional groove formed at an inner corner between the cylindrical portion 2A and the cover portion 12B of the inner housing 12 . The butting-side channel 18 is a C-shaped cross-sectional groove formed by the circular groove 10B of the outer casing 10 and the outer edge wall groove 12D of the inner casing 12 .

环形突起16,与通道17、18一起,沿叶轮20的圆周方向在角度θ(例等于250-270°)的范围内延伸,如图3所示,这样防止流经燃油通道15的燃油的停滞等等的出现。The annular protrusion 16, together with the passages 17, 18, extends along the circumferential direction of the impeller 20 within the range of an angle θ (e.g. equal to 250-270°), as shown in FIG. Wait for it to appear.

内壳体12在圆筒部分12A一侧有一个密封隔壁19。如图3所示,密封隔壁19成一个圆形的突起从内壳体12的圆筒部分12A凸向邻近叶轮20外圆周的点。密封隔壁19密封住进油口11和出油口14之间的叶轮20的外围,使通过进油口11吸入的燃油必定沿着燃油通道15流动。The inner housing 12 has a sealing partition 19 on the cylindrical portion 12A side. As shown in FIG. 3 , the sealing partition 19 protrudes from the cylindrical portion 12A of the inner housing 12 to a point adjacent to the outer circumference of the impeller 20 as a circular protrusion. The sealing partition 19 seals the periphery of the impeller 20 between the oil inlet 11 and the oil outlet 14 , so that the fuel sucked through the oil inlet 11 must flow along the fuel passage 15 .

叶轮20的形状,例如大致像一个由增强的塑性材料制造的圆盘,并且被能转动地安装在泵壳体9的叶轮容纳凹座13内。叶轮20被电动机7带着沿图3中箭头A的方向转动,把通过进油口11吸入的燃油经过燃油通道15送到出油口14。The impeller 20 is shaped, for example, approximately like a disc made of reinforced plastic material and is mounted rotatably in the impeller receiving recess 13 of the pump housing 9 . The impeller 20 is driven by the motor 7 to rotate in the direction of arrow A in FIG. 3 , and the fuel sucked through the fuel inlet 11 is sent to the fuel outlet 14 through the fuel passage 15 .

叶轮20在转动中心(轴线O-O)有一个啮合孔21,旋转轴6装配在这个孔中。多个(例如三个)通孔22布置在啮合孔21的周围。参看图4,叶轮20在其圆周有许多沿周向排列径向延伸的叶片23。在相邻的叶片23之间有一对圆形的凹槽24,每个凹槽24有大致对应于泵壳体9的通道17、18圆形形状的曲率。The impeller 20 has an engaging hole 21 at the center of rotation (axis O-O), and the rotating shaft 6 is fitted into this hole. A plurality of (for example, three) through holes 22 are arranged around the engagement hole 21 . Referring to FIG. 4, the impeller 20 has a plurality of radially extending blades 23 arranged in the circumferential direction on its circumference. Between adjacent vanes 23 there is a pair of circular grooves 24 each having a curvature substantially corresponding to the circular shape of the passages 17 , 18 of the pump housing 9 .

叶轮20,与旋转轴6一起,被电动机11驱动,在叶轮容纳凹座13内叶轮20的上和下面被浮动地密封在外壳体10的上面和盖子部分12B的下面之间。叶轮20的每个通孔22都有使在外壳体10的圆形凹部10A和内壳体12的阶梯形孔12E之间的燃油压力等等均匀化的功能。The impeller 20, together with the rotating shaft 6, is driven by the motor 11, and the upper and lower surfaces of the impeller 20 are floatingly sealed between the upper surface of the outer casing 10 and the lower surface of the cover portion 12B in the impeller receiving recess 13. Each of the through holes 22 of the impeller 20 has a function of equalizing the fuel pressure, etc., between the circular recess 10A of the outer casing 10 and the stepped hole 12E of the inner casing 12 .

参看图5,每个叶片23都有一个位于根部一侧并且沿叶轮20的径向直线延伸的直线叶片部分23A,和一个从直线叶片部分23A的头部开始,沿沿转动方向看,即箭头A的方向,向着叶轮20的向前一侧圆形弯曲延伸的弯曲叶片部分23B。Referring to Fig. 5, each blade 23 has a linear blade portion 23A that is positioned at the root side and extends linearly along the radial direction of the impeller 20, and starts from the head of the linear blade portion 23A, viewed along the direction of rotation, i.e. the arrow In the direction of A, the curved blade portion 23B extends circularly toward the front side of the impeller 20 .

下面,详细说明叶片23的形状。如图5所示,从直线叶片部分23A的根部位置B到弯曲叶片部分23B的头部位置C的长度,即叶片23的全部长度,被称作总长度H;从直线叶片部分23A的根部位置B到弯曲叶片部分23B的在该处开始的开始点位置D,即直线叶片部分23A的头部位置D的长度,被称作直线部分长度H1;从弯曲叶片部分23B的开始点位置D到头部位置C的长度被称作弯曲部分长度H2。Next, the shape of the blade 23 will be described in detail. As shown in FIG. 5, the length from the root position B of the straight blade portion 23A to the head position C of the curved blade portion 23B, that is, the entire length of the blade 23, is referred to as a total length H; B to the starting point position D of the curved blade portion 23B, that is, the length of the head position D of the straight blade portion 23A, is referred to as a straight portion length H1; from the starting point position D of the curved blade portion 23B to the head position D. The length of the portion position C is referred to as the bent portion length H2.

弯曲叶片部分23B在沿转动方向向前倾斜的最向前位置E与直线叶片部分23A之间的向前倾斜的长度用以叶轮20的转动中心(轴线O-O)为基准的角度α示出。The forwardly inclined length of the curved blade portion 23B between the forwardmost position E inclined forwardly in the rotational direction and the straight blade portion 23A is shown by an angle α with reference to the rotational center (axis O-O) of the impeller 20 .

在第一个实施例中,显示出当直线叶片部分23A的直线部分长度H1相对于叶片23的总长度H,即,弯曲叶片部分23B的开始点位置D按照下面的公式(1)设置时,能获得极好的泵效率:In the first embodiment, it is shown that when the straight portion length H1 of the straight blade portion 23A is set with respect to the total length H of the blade 23, that is, the starting point position D of the curved blade portion 23B according to the following formula (1), Excellent pump efficiency can be obtained:

1/3≤(H1/H)≤2/3               …(1)1/3≤(H1/H)≤2/3 …(1)

在这方面,显示出当在公式(1)中的H1/H被设置在由下面的公式(2)给出的范围之内时,能够获得更好的泵效率:In this regard, it was shown that better pump efficiency can be obtained when H1/H in the formula (1) is set within the range given by the following formula (2):

2/5≤(H1/H)≤3/5               …(2)2/5≤(H1/H)≤3/5 …(2)

此外,显示出当对应于弯曲叶片部分23B的向前倾斜长度的角度α按照下面的公式(3)设置时,能获得极好的泵效率:Furthermore, it was shown that excellent pump efficiency can be obtained when the angle α corresponding to the forwardly inclined length of the curved blade portion 23B is set according to the following formula (3):

0.5≤α≤2.0                  …(3)0.5≤α≤2.0 …(3)

在这方面,显示出当在公式(3)中的α被设置在由下面的公式(4)给出的范围之内时,能够获得更好的泵效率:In this regard, it was shown that better pump efficiency can be obtained when α in formula (3) is set within the range given by the following formula (4):

1.0≤α≤1.5                  …(4)1.0≤α≤1.5 ...(4)

下面,说明第一个实施例的运行。当通过输送盖2的连接器2B从外边给泵供电时,输送给电动机7的转子7B的驱动电流使转子7B和旋转轴6一起转动,驱动泵壳体9内的叶轮20。在叶轮20转动时,油箱(未示出)内的燃油通过进油口11被吸入燃油通道15,然后燃油被叶轮20的叶片23沿着燃油通道15输送,并且通过出油口14压到外壳1中。Next, the operation of the first embodiment will be explained. When the pump is powered from the outside through the connector 2B of the delivery cover 2, the drive current delivered to the rotor 7B of the motor 7 makes the rotor 7B rotate with the rotating shaft 6, driving the impeller 20 in the pump housing 9. When the impeller 20 rotates, the fuel in the fuel tank (not shown) is sucked into the fuel passage 15 through the oil inlet 11, and then the fuel is conveyed along the fuel passage 15 by the blade 23 of the impeller 20, and is pressed to the casing through the oil outlet 14 1 in.

被压到外壳1中的燃油通过燃油通道8在外壳1中流通到输送盖2,以便打开输送管2A中的止回阀3。然后,燃油从输送管2A通过外油管(未示出),例如以200-500kPa的压力和30-200L/h的流速,输送到发动机主体的喷射阀(未示出)。The fuel pressed into the housing 1 flows through the fuel passage 8 in the housing 1 to the delivery cap 2 in order to open the non-return valve 3 in the delivery line 2A. Then, the fuel is delivered from the delivery pipe 2A through an outer oil pipe (not shown), for example, at a pressure of 200-500 kPa and a flow rate of 30-200 L/h, to an injection valve (not shown) of the engine body.

作为我们对直线叶片部分23A的直线部分长度H1和叶片23的总长度H的比值的研究结果,证实当比值H1/H被设置在公式(1)所示出的1/3-2/3的范围内时,最好,在公式(2)所示出的2/5-3/5的范围内时,能够得到如图6特性曲线所示出的较高的泵效率。在这种情况下,对应于弯曲叶片部分23B的向前倾斜长度的角度α被设置在大约1.2°。As a result of our study on the ratio of the straight portion length H1 of the straight blade portion 23A to the total length H of the blade 23, it was confirmed that when the ratio H1/H is set at 1/3-2/3 shown in the formula (1), When it is in the range, preferably, when it is in the range of 2/5-3/5 shown in the formula (2), a higher pump efficiency as shown in the characteristic curve in FIG. 6 can be obtained. In this case, the angle α corresponding to the forwardly inclined length of the curved blade portion 23B is set at about 1.2°.

此外,作为我们对对应于弯曲叶片部分23B的向前倾斜长度的角度α的研究结果,证实当角度α被设置在公式(3)所示出的0.5-2.0°的范围内时,最好,在公式(4)所示出的1.0-1.5°的范围内时,能够得到如图7特性曲线所示出的较高的泵效率。在这种情况下,直线叶片部分23A的直线部分长度H1和叶片23的总长度H的比值被设置在大约1/2。Furthermore, as a result of our studies on the angle α corresponding to the forwardly inclined length of the curved blade portion 23B, it was confirmed that when the angle α is set within the range of 0.5-2.0° shown in the formula (3), it is best, When it is in the range of 1.0-1.5° as shown in the formula (4), a higher pump efficiency as shown in the characteristic curve of FIG. 7 can be obtained. In this case, the ratio of the straight portion length H1 of the straight blade portion 23A to the total length H of the blade 23 is set at approximately 1/2.

在这方面,显示出当直线叶片部分23A的直线部分长度H1和叶片23的总长度H的比值在2/5-3/5的范围内被设置在大约1/2,而对应于弯曲叶片部分23B的向前倾斜长度的角度α在1.0-1.5°的范围内被设置在大约1.2°,能够得到最高的泵效率。In this regard, it is shown that when the ratio of the straight portion length H1 of the straight blade portion 23A to the total length H of the blade 23 is set at about 1/2 in the range of 2/5-3/5, while the corresponding curved blade portion The angle α of the forwardly inclined length of 23B is set at about 1.2° in the range of 1.0-1.5°, enabling the highest pump efficiency.

因此在第一个实施例中,在叶轮20的叶片23的弯曲部分23B开始弯曲的开始点位置D,即,直线部分长度H1,被设置在相对于叶片23的总长度H的2/5-3/5(大约1/2)的位置,同时对应于弯曲叶片部分23B的向前倾斜长度的角度α被设置在1.0-1.5°(大约1.2°)。Therefore, in the first embodiment, the starting point position D at which the curved portion 23B of the blade 23 of the impeller 20 starts to bend, that is, the straight portion length H1, is set at 2/5- 3/5 (approximately 1/2) position while the angle α corresponding to the forwardly inclined length of the curved blade portion 23B is set at 1.0-1.5° (approximately 1.2°).

这使得叶片23能够有一个从长度方向中部缓和弯曲的、具有在叶轮20的转动方向得到的合适的向前倾斜长度的弯曲叶片部分23B。This enables the blade 23 to have a curved blade portion 23B that is gently curved from the middle in the length direction and has an appropriate forward inclination length obtained in the rotation direction of the impeller 20 .

作为结果,当叶轮20转动时,甚至在相对低的流速范围内,也能够得到从叶片23之间的叶片凹槽到燃油通道15的平滑的燃油流动,防止了相对于rpm的流速降低。此外,叶轮20提供合适的动能给燃油,能够阻止在相对大的流速范围内转矩损失的增加,并且能使泵在电动机7的高效率范围内运转,导致在泵的整个运行范围内达到较高的泵效率。As a result, when the impeller 20 rotates, smooth fuel flow from the vane grooves between the vanes 23 to the fuel passage 15 can be obtained even in a relatively low flow velocity range, preventing a decrease in flow velocity with respect to rpm. In addition, the impeller 20 provides suitable kinetic energy to the fuel, can prevent the increase of torque loss in a relatively large flow rate range, and can make the pump operate in the high efficiency range of the electric motor 7, resulting in a higher efficiency in the entire operating range of the pump. High pump efficiency.

此外,由于叶片23的弯曲叶片部分23B是圆形弯曲形成的,燃油能沿着弯曲叶片部分23B的圆形表面平滑地流动,能使燃油从叶片23之间的叶片凹槽平滑地流出。In addition, since the curved vane portion 23B of the vane 23 is formed with a circular bend, the fuel can flow smoothly along the circular surface of the curved vane portion 23B, enabling the fuel to flow smoothly from the vane groove between the vanes 23 .

参看图8-14,这里示出本发明的第二个实施例,除去倾斜地切掉位于叶片35根部一侧的叶片35的侧面和后面之间的角得到的沿叶轮20径向延伸的倒角39之外,第二个实施例与第一个实施例的构造基本相同。Referring to FIGS. 8-14 , a second embodiment of the present invention is shown here, except that the angle between the side and the rear side of the blade 35 located at the blade 35 root side is obliquely cut off, and the inverted blade extending radially along the impeller 20 is removed. Except for angle 39, the construction of the second embodiment is basically the same as that of the first embodiment.

参看图8和9,环形燃油通道31位于第一个实施例的燃油通道15的位置。燃油通道31包含外壳体10的圆形凹槽10B,形成一个以轴线O-O为中心沿圆周延伸的、C形截面的、较大的垂直长度的通道。8 and 9, the annular fuel passage 31 is located at the position of the fuel passage 15 of the first embodiment. The fuel channel 31 includes the circular groove 10B of the outer shell 10, forming a channel with a C-shaped cross-section and a relatively large vertical length extending circumferentially around the axis O-O.

燃油通道31有形状为圆形的上和下端部,燃油沿着它们如图9中箭头所示以环流的形式流动,这样当燃油通过燃油通道31输送时,燃油通道31的圆形部分中心的圆周形成通道中心F。通道中心F相对于从燃油通道31的内端31A到外端31B径向长度L位于距离内端31A大约1/2的距离L1处。燃油通道31的始端与进油口11连接,而终端与出油口14连接。The fuel passage 31 has circular upper and lower ends, along which the fuel flows in the form of a circular flow as shown by the arrows in Figure 9, so that when the fuel is delivered through the fuel passage 31, the center of the circular part of the fuel passage 31 The circumference forms the channel center F. The passage center F is located at a distance L1 of about 1/2 from the inner end 31A with respect to the radial length L from the inner end 31A to the outer end 31B of the fuel passage 31 . The beginning of the fuel passage 31 is connected to the fuel inlet 11 , and the end is connected to the fuel outlet 14 .

叶轮32的形状,例如,大致像一个由增强的塑性材料制成的圆盘,并且被能转动地安装在泵壳体9的叶轮容纳凹座13内。The impeller 32 is shaped, for example, substantially like a disc made of reinforced plastic material and is rotatably mounted in the impeller receiving recess 13 of the pump housing 9 .

叶轮32在转动中心(轴线O-O)有一个装配旋转轴6的啮合孔33。多个(例如三个)通孔34排列在啮合孔33的周围。参看图10,叶轮20在其外围有许多沿圆周排列并沿径向延伸的叶片35。一对圆形凹槽36以山形的形式位于相邻的叶片35之间,每个凹槽36具有大致对应于泵壳体9的燃油通道31的圆形形状的曲率。The impeller 32 has an engaging hole 33 in which the rotating shaft 6 is fitted at the center of rotation (axis O-O). A plurality of (for example, three) through holes 34 are arranged around the engagement hole 33 . Referring to Fig. 10, the impeller 20 has a plurality of blades 35 arranged in the circumference and extending in the radial direction at its periphery. A pair of circular grooves 36 are located between adjacent vanes 35 in the form of a mountain, each groove 36 having a curvature substantially corresponding to the circular shape of the fuel passage 31 of the pump housing 9 .

参看图10和11,叶片35成形为基本上矩形截面的板体,具有位于在叶轮32转动方向看,即箭头A的方向,在前一侧的前面35A,位于如沿转动方向看,在后一侧的后面35B,和位于前面35A和后面35B之间的一对侧面35C。Referring to Figures 10 and 11, the blade 35 is shaped as a plate body with a substantially rectangular cross-section, and has a front face 35A on the front side as viewed in the direction of rotation of the impeller 32, ie, the direction of arrow A, and a front 35A located on the rear side as viewed in the direction of rotation. A rear face 35B on one side, and a pair of side faces 35C located between the front face 35A and the rear face 35B.

叶片35在根部一侧有沿叶轮32径向直线延伸的直线叶片部分37,而在头部一侧有沿叶轮32的转动方向看在前一侧圆形弯曲的弯曲叶片部分38。叶片部分37、38的形状和尺寸按照上边关于第一个实施例说明的公式(1)和(3),最好是,公式(2)和(4)设置。The blade 35 has, on the root side, a straight blade portion 37 extending linearly in the radial direction of the impeller 32, and on the head side, a curved blade portion 38 that is circularly curved on the front side as viewed in the direction of rotation of the impeller 32. The shape and size of the vane portions 37, 38 are set according to formulas (1) and (3), preferably, formulas (2) and (4) described above with respect to the first embodiment.

一对倒角39位于叶片35的根部一侧沿着叶轮32的径向延伸。参看图10-12,每个倒角39是通过倾斜地切掉叶片35的侧面35C和后面35B之间的角得到的。倒角39的总长度T被设置为大约等于从燃油通道31的内端31A到通道中心F的距离L1,即,(2/5至3/5)×L的值,其中L是燃油通道31的径向长度,按照下面的公式(5):A pair of chamfers 39 are located on the root side of the blade 35 and extend along the radial direction of the impeller 32 . 10-12, each chamfer 39 is obtained by obliquely cutting off the corner between the side 35C and the rear 35B of the blade 35. Referring to FIGS. The total length T of the chamfer 39 is set approximately equal to the distance L1 from the inner end 31A of the fuel passage 31 to the passage center F, that is, a value of (2/5 to 3/5)×L, where L is the fuel passage 31 The radial length of , according to the following formula (5):

2/5≤(T/L)≤3/5                     …(5)2/5≤(T/L)≤3/5 …(5)

倒角39的总长度T,最好按照下面的公式(6)设定为(9/20至11/20)×L的值:The total length T of the chamfer 39 is preferably set to a value of (9/20 to 11/20)×L according to the following formula (6):

9/20≤(T/L)≤11/20                  …(6)9/20≤(T/L)≤11/20 …(6)

倒角39的总长度T被设置在由公式(5)和(6)给出的范围内,最好,在相对于燃油通道31的径向长度L的1/2值。借此,倒角39构成为延伸到燃油以环流形式流过燃油通道31时形成的通道中心F,使能达到燃油平滑地流入叶片35之间的叶片凹槽的最佳效果。The total length T of the chamfer 39 is set within the range given by equations (5) and (6), preferably, at a value of 1/2 relative to the radial length L of the fuel passage 31 . Thereby, the chamfer 39 is configured to extend to the channel center F formed when the fuel flows through the fuel channel 31 in a circular flow, so as to achieve the best effect of fuel smoothly flowing into the vane grooves between the vanes 35 .

倒角39有位于根部一侧、并且有基本不变的倒角宽度的大致矩形的根部一侧的倒角部分39A,以及有从根部一侧的倒角部分39A逐渐减小的倒角宽度的大致三角形的头侧倒角部分39B。The chamfer 39 has a substantially rectangular root-side chamfer portion 39A that is located on the root side and has a substantially constant chamfer width, and has a chamfer width that gradually decreases from the root-side chamfer portion 39A. The substantially triangular head-side chamfered portion 39B.

根部一侧的倒角部分39A通过切掉一个角来形成,以具有不变的倒角宽度,得到从其根部一侧流入叶片36之间的叶片凹槽的平滑的燃油流,能减小燃油流的阻力。另一方面,头部一侧的倒角部分39B构成有向着其头部逐渐减小的倒角宽度,实现在叶片35的后面35B和侧面35C以及根部一侧的倒角部分39A之间的平滑的连接,使燃油能平滑地流过其间。The chamfered portion 39A on the root side is formed by cutting off a corner to have a constant chamfer width to obtain a smooth flow of fuel flowing into the blade grooves between the blades 36 from the root side thereof, which can reduce the fuel flow. flow resistance. On the other hand, the chamfered portion 39B on the head side is formed with a gradually decreasing chamfer width toward the head thereof, achieving smoothness between the rear face 35B and the side face 35C of the blade 35 and the chamfered portion 39A on the root side. connection so that fuel can flow smoothly through it.

参看图12,详细说明倒角39的根部一侧的倒角部分39A的形状。根部一侧的倒角部分39A相对于叶片35的侧面35C的倾斜角β按照下边的公式(7)被设置在30-70°的范围内:Referring to FIG. 12, the shape of the chamfered portion 39A on the root side of the chamfer 39 will be described in detail. The inclination angle β of the chamfered portion 39A on the root side with respect to the side surface 35C of the blade 35 is set in the range of 30-70° according to the following formula (7):

30≤β≤70                   …(7)30≤β≤70 …(7)

公式(7)中的倾斜角β最好设置在按照下边公式(8)的40-60°的范围内:The inclination angle β in the formula (7) is preferably set in the range of 40-60° according to the following formula (8):

40≤β≤60                   …(8)40≤β≤60 ...(8)

参看图9,根部一侧的倒角部分39A的长度T1相对倒角39的总长度T按照下边的公式(9)被设置为(1/5至4/5)×T的值:9, the length T1 of the chamfered portion 39A on the root side is set to a value of (1/5 to 4/5)×T with respect to the total length T of the chamfer 39 according to the following formula (9):

1/5≤(T1/T)≤4/5             …(9)1/5≤(T1/T)≤4/5 …(9)

根部一侧的倒角部分39A的长度T1最好按照下边的公式(10)被设置为(2/5-3/5)的值:The length T1 of the chamfered portion 39A on the root side is preferably set to a value of (2/5-3/5) according to the following formula (10):

2/5≤(T1/T)≤3/5             …(10)2/5≤(T1/T)≤3/5 …(10)

作为对根部一侧的倒角部分39A相对于叶片35的侧面35C的倾斜角β的研究结果,证实当倾斜角β被设置在如公式(7)示出的30-70°的范围内,最好,在如公式(8)示出的40-60°的范围内,能得到如图13中的特性曲线示出的较高的泵效率。As a result of research on the inclination angle β of the chamfered portion 39A on the root side with respect to the side surface 35C of the blade 35, it was confirmed that when the inclination angle β is set within the range of 30-70° as shown in the formula (7), the most Well, in the range of 40-60° as shown in formula (8), higher pump efficiency as shown in the characteristic curve in FIG. 13 can be obtained.

在这种情况下,根部一侧的倒角部分39A的长度T1与倒角39的总长度T的比值被设置在大约为1/2。借此,根部一侧的倒角部分39A的倾斜角β就可以被设置为大体上等于从叶片35的侧面35C到其后面35B流动的燃油的流动角,导致形成沿着根部一侧的倒角部分39A的平滑的燃油流动。In this case, the ratio of the length T1 of the chamfered portion 39A on the root side to the total length T of the chamfer 39 is set at about 1/2. Thereby, the inclination angle β of the chamfered portion 39A on the root side can be set substantially equal to the flow angle of the fuel flowing from the side face 35C of the blade 35 to the rear face 35B thereof, resulting in the formation of the chamfer along the root side. Smooth fuel flow for part 39A.

此外,作为对根部一侧的倒角部分39A的长度T1与倒角39的总长度T的比值的研究结果,证实当比值T1/T被设置在如公式(9)示出的1/5-4/5的范围内时,最好,在如公式(10)示出的2/5-3/5的范围内时,能够得到如图14中的特性曲线示出的较高的泵效率。Furthermore, as a result of studies on the ratio of the length T1 of the chamfered portion 39A on the root side to the total length T of the chamfer 39, it was confirmed that when the ratio T1/T is set at 1/5- In the range of 4/5, preferably, in the range of 2/5-3/5 as shown in formula (10), a higher pump efficiency as shown in the characteristic curve in FIG. 14 can be obtained.

在这种情况下,根部一侧的倒角部分39A相对于叶片35的侧面35C的倾斜角β被设置在大约50°。借此,根部一侧的倒角部分39A遏制通过不变宽度的大凹槽在叶片35的根部一侧可能产生的涡流,使燃油平滑地流入。In this case, the angle of inclination β of the chamfered portion 39A on the root side with respect to the side face 35C of the blade 35 is set at approximately 50°. Thereby, the chamfered portion 39A on the root side suppresses a vortex that may be generated on the root side of the vane 35 by the large groove of constant width, allowing the fuel to flow in smoothly.

此外,我们的研究表明,由于头部一侧的倒角部分39B具有向着头部逐渐减小的倒角宽度,保证了叶片35的后面35B和侧面35C以及根部一侧的倒角部分39A之间的平滑的连接,燃油能平滑地从叶片35的侧面35C流向根部一侧的倒角部分39A,以及从根部一侧的倒角部分39A流向后面35B,能够得到较高的泵效率。In addition, our research has shown that since the chamfered portion 39B on the head side has a chamfered width that gradually decreases toward the head, the gap between the rear face 35B and the side 35C of the blade 35 and the chamfered portion 39A on the root side is guaranteed With the smooth connection, the fuel can smoothly flow from the side 35C of the vane 35 to the chamfered portion 39A on the root side, and from the chamfered portion 39A on the root side to the rear 35B, so that a higher pump efficiency can be obtained.

在这方面,显示出当倒角39的总长度T与燃油通道31的径向长度L的比值T/L在9/20-11/20的范围内被设置在1/2,根部一侧的倒角部分39A相对于叶片35的侧面35C的倾斜角β在40-60°的范围内被设置在50°,以及根部一侧的倒角部分39A的长度T1与倒角39的总长度T的比值T1/T在范围2/5-3/5内被设置在1/2时,能得到最高的泵效率。In this regard, it is shown that when the ratio T/L of the total length T of the chamfer 39 to the radial length L of the fuel passage 31 is set at 1/2 in the range of 9/20-11/20, the root side The inclination angle β of the chamfered portion 39A with respect to the side surface 35C of the blade 35 is set at 50° in the range of 40-60°, and the length T1 of the chamfered portion 39A on the root side is equal to the total length T of the chamfered portion 39. When the ratio T1/T is set at 1/2 within the range of 2/5-3/5, the highest pump efficiency can be obtained.

在第二个实施例中,通过倾斜地切掉侧面35C和后面35B之间的角得到的倒角39位于叶轮32的侧面。因此,当叶轮32转动时,倒角39使燃油能沿着根部一侧的倒角部分39A和头部一侧倒角部分39B平滑地流动。In the second embodiment, a chamfer 39 obtained by obliquely cutting off the corner between the side surface 35C and the rear surface 35B is located on the side surface of the impeller 32 . Therefore, when the impeller 32 rotates, the chamfer 39 allows the fuel to flow smoothly along the chamfered portion 39A on the root side and the chamfered portion 39B on the head side.

此外,这样设计倒角39,即把在叶轮32沿其径向延伸的总长度T与燃油通道31的径向长度L的比值设置为9/20-11/20(最好为1/2),根部一侧的倒角部分39A相对于叶片35的侧面35C的倾斜角β设置为40-60°(最好为50°),以及根部一侧的倒角部分39A的长度T1与倒角39的总长度T的比值设置为2/5-3/5(最好为1/2)。In addition, the chamfer 39 is designed in such a way that the ratio of the total length T extending radially of the impeller 32 to the radial length L of the fuel passage 31 is set to 9/20-11/20 (preferably 1/2) , the angle of inclination β of the chamfered portion 39A on the root side with respect to the side face 35C of the blade 35 is set to 40-60° (preferably 50°), and the length T1 of the chamfered portion 39A on the root side is the same as that of the chamfered angle 39 The ratio of the total length T is set to 2/5-3/5 (preferably 1/2).

借此,在第二个实施例中,倒角39(根部一侧的倒角部分39A)的位置和长度以及根部一侧倒角39A的倾斜角可以对应于燃油通过燃油通道31流入叶片35之间的叶片凹槽的流入位置设置,尺寸根据平滑流入的需要,角度使得能够平滑流入,使得与第一个实施例相比,能更平滑地从叶片35之间的叶片凹槽流到燃油通道31,能够达到更高的泵效率。Thus, in the second embodiment, the position and length of the chamfer 39 (the chamfered portion 39A on the root side) and the inclination angle of the chamfer 39A on the root side can correspond to the point where the fuel flows into the vane 35 through the fuel passage 31. The inflow position of the vane groove between the blades is set, the size is according to the needs of smooth inflow, and the angle enables smooth inflow, so that it can flow from the vane groove between the vanes 35 to the fuel passage more smoothly compared with the first embodiment 31, able to achieve higher pump efficiency.

参看图15-23,这些图示出本发明的第三个实施例。参看图15,涡轮燃油泵有一个圆筒形壳体101,它构成泵的外壳,并且有被输送盖102和泵壳体109封闭的轴向端部。Referring to Figures 15-23, a third embodiment of the present invention is shown. Referring to FIG. 15, the turbo fuel pump has a cylindrical housing 101 which constitutes the pump casing and has axial ends closed by a delivery cover 102 and a pump housing 109. Referring to FIG.

带盖圆筒形的输送盖102位于外壳101的一端。如图15所示,输送盖102设有向上突出的输送管102A和连接器102B以及位于中心向下延伸的轴承套102C。A cylindrical delivery cover 102 with a cover is located at one end of the housing 101 . As shown in FIG. 15 , the delivery cover 102 is provided with a delivery tube 102A and a connector 102B protruding upward, and a bearing sleeve 102C extending downward at the center.

在输送管102A中设有止回阀103用于保持剩余压力。当电动机107转动时,止回阀103被流入外壳101内的燃油打开,以便把燃油从输送管102A输送入外部的燃油管(未示出)。当电动机107停止时,止回阀103被关闭以防止油管中的燃油流回外壳101,从而将燃油管保持在预定的剩余压力。A check valve 103 is provided in the delivery pipe 102A for maintaining residual pressure. When the motor 107 is rotated, the check valve 103 is opened by the fuel flowing into the housing 101 to deliver the fuel from the delivery pipe 102A to an external fuel pipe (not shown). When the motor 107 is stopped, the check valve 103 is closed to prevent the fuel in the fuel pipe from flowing back into the casing 101, thereby maintaining the fuel pipe at a predetermined residual pressure.

参看图16,轴衬104安装在输送盖102的轴承套102C中,而轴衬105安装在内壳体112的阶梯形孔112D中。轴衬104、105组成能转动地支承旋转轴106的轴承。Referring to FIG. 16 , the bushing 104 is installed in the bearing housing 102C of the delivery cover 102 , and the bushing 105 is installed in the stepped hole 112D of the inner casing 112 . The bushings 104, 105 constitute a bearing that rotatably supports the rotary shaft 106. As shown in FIG.

旋转轴106通过轴衬104、105被支承在输送盖102和泵壳体109之间。如图16所示,旋转轴106在外壳101内沿着轴线O-O轴向延伸,以便能转动地支承电动机107的转子107B等。参看图17,在旋转轴106的下端构成有一个平面(chamfer)106A,以便与叶轮117以止转状态啮合装配。The rotary shaft 106 is supported between the delivery cover 102 and the pump housing 109 via bushings 104 , 105 . As shown in FIG. 16, the rotary shaft 106 extends axially along the axis O-O inside the casing 101 to rotatably support the rotor 107B of the motor 107 and the like. Referring to Fig. 17, a flat surface (chamfer) 106A is formed at the lower end of the rotating shaft 106 so as to engage with the impeller 117 in a non-rotating state.

电动机107装在外壳101中,并且具有一个圆筒形轭107A,轭107A装配在外壳101内在输送盖102和泵壳体109之间,用于支承由永久磁铁制成的定子(未示出),转子107B和换向器107C与轭107A有间隙安装在轭107A内,转子107B和换向器107C装配在旋转轴106上以便一起整体转动,一对电刷(未示出)与换向器107C滑动地接触。The motor 107 is housed in the casing 101, and has a cylindrical yoke 107A fitted inside the casing 101 between the delivery cover 102 and the pump housing 109 for supporting a stator (not shown) made of permanent magnets. , the rotor 107B and the commutator 107C are installed in the yoke 107A with a gap between the yoke 107A, the rotor 107B and the commutator 107C are assembled on the rotating shaft 106 so as to rotate integrally together, a pair of brushes (not shown) and the commutator 107C is in sliding contact.

对于电动机107,当通过输送盖102的连接器102B、电刷以及换向器107C给转子107B供电时,转子107B与旋转轴106一起转动,以带动叶轮117,例如以5000-8000rpm转动。For the motor 107, when the rotor 107B is powered by the connector 102B, the brush and the commutator 107C of the delivery cover 102, the rotor 107B rotates together with the rotating shaft 106 to drive the impeller 117, for example, at 5000-8000rpm.

在电动机107的轭107A和转子107B之间形成燃油通道108,用于通过轭107A和转子107B之间的间隙把从泵壳体101的出油口114压向外壳101的燃油流通到输送盖102。A fuel passage 108 is formed between the yoke 107A and the rotor 107B of the electric motor 107 for passing the fuel pressed from the oil outlet 114 of the pump housing 101 to the casing 101 to the delivery cover 102 through the gap between the yoke 107A and the rotor 107B. .

泵壳体109设置在外壳101的另一端或下端,并且通过垂直地邻接外壳体110和内壳体112得到。泵壳体109用于能转动地容纳叶轮117。The pump housing 109 is provided at the other or lower end of the outer housing 101 and is obtained by vertically adjoining the outer housing 110 and the inner housing 112 . The pump housing 109 serves to rotatably accommodate an impeller 117 .

如图15和16所示,泵壳体109的外壳体110通过诸如卷边(calking)等固定方式咬合地装配在外壳101的下端,从外侧封闭外壳101。外壳体110与进油口111构成一个整体。As shown in FIGS. 15 and 16 , the outer casing 110 of the pump casing 109 is snap-fitted on the lower end of the casing 101 by a fixing means such as calking to close the casing 101 from the outside. The outer shell 110 and the oil inlet 111 form an integral body.

外壳体110有一个在轴中心(轴线O-O)形成的圆形凹部110A,和一个大体半圆形截面构成的对应于叶轮117的外围的、以轴线O-O为中心沿圆周延伸的圆形凹槽10B。The outer casing 110 has a circular recess 110A formed at the center of the shaft (axis O-O), and a circular recess 10B formed of a substantially semicircular section corresponding to the periphery of the impeller 117 and extending circumferentially around the axis O-O. .

内壳体112位于外壳体110上,并且以对接在外壳体110上的状态装配在外壳101内。如图16所示,内壳体112的形状像一个带盖的平的圆筒,并且具有形成圆筒形的周围的壁的圆筒形部分112A和从上边盖住圆筒形部分112A的盖子部分112B。圆筒形部分112A在其内周面有一个容纳叶轮的圆形凹座113,它在圆筒形部分112A和外壳体110的接合面112C一侧开口。The inner housing 112 is located on the outer housing 110 and assembled in the outer housing 101 in a state of being docked on the outer housing 110 . As shown in FIG. 16, the inner housing 112 is shaped like a flat cylinder with a cover, and has a cylindrical portion 112A forming a cylindrical peripheral wall and a cover covering the cylindrical portion 112A from above. Section 112B. The cylindrical portion 112A has an impeller-accommodating circular recess 113 on its inner peripheral surface, which is open on the side of the joint surface 112C of the cylindrical portion 112A and the outer casing 110 .

此外,圆筒形部分112A在其内表面有环形燃油通道115。盖子部分112B构成有轴衬105插入其中的阶梯形孔112D,在外边缘有垂直延伸的出油口114。In addition, the cylindrical portion 112A has an annular fuel passage 115 on its inner surface. The cover portion 112B is formed with a stepped hole 112D into which the bushing 105 is inserted, and has a vertically extending oil outlet 114 at the outer edge.

在容纳叶轮的凹座113的外边缘通过泵壳体109形成燃油通道115,燃油通道115以轴线O为中心沿圆周延伸大致成C的形状,如图16和18所示。燃油通道115包含外壳体110的圆形凹槽110B。A fuel passage 115 is formed through the pump housing 109 at the outer edge of the recess 113 for accommodating the impeller. The fuel passage 115 extends around the axis O in a substantially C shape, as shown in FIGS. 16 and 18 . The fuel passage 115 includes a circular groove 110B of the outer housing 110 .

燃油通道115有形状为圆形的上和下端部,燃油沿着它们如图18所示以环流的形式流动,这样当燃油通过燃油通道115输送时,燃油通道115的圆形部分的中心的圆周形成通道中心C。通道中心C相对于从燃油通道115的内端115A到其外端115B的径向长度L位于距离内端115A大约1/2L1的距离处。The fuel passage 115 has circular upper and lower ends along which the fuel flows in a circular flow as shown in FIG. Form the channel center C. The passage center C is located at a distance of about 1/2L1 from the inner end 115A with respect to the radial length L from the inner end 115A of the fuel passage 115 to the outer end 115B thereof.

燃油通道115有与进油口111连接的始端,和与出油口114连接的终端。此外,燃油通道115在始端一侧有进油通道部分115C,用于把通过进油口111吸入的燃油平滑地引入燃油通道115。The fuel passage 115 has a beginning connected to the fuel inlet 111 and a terminal connected to the fuel outlet 114 . Further, the fuel passage 115 has an inlet passage portion 115C on the start side for smoothly introducing the fuel sucked through the inlet 111 into the fuel passage 115 .

密封隔壁116设置在内壳体112的圆筒形部分112A一侧。如图17所示,密封隔壁116构成为从内壳体112的圆筒形部分112A凸向邻近叶轮117外圆周的点的圆形突起。密封隔壁116密封住进油口111和出油口114之间的叶轮117的外围,使经进油口111吸入的燃油一定沿着燃油通道115流动。The sealing partition 116 is provided on the cylindrical portion 112A side of the inner housing 112 . As shown in FIG. 17 , the seal partition 116 is formed as a circular protrusion protruding from the cylindrical portion 112A of the inner housing 112 to a point adjacent to the outer circumference of the impeller 117 . The sealing partition 116 seals the periphery of the impeller 117 between the oil inlet 111 and the oil outlet 114 , so that the fuel sucked through the oil inlet 111 must flow along the fuel passage 115 .

叶轮117的形状,例如,大致像一个由增强的塑性材料制成的圆盘,并且被能转动地安装在泵壳体109的容纳叶轮的凹座113内。叶轮117被电动机107带着沿图17中箭头A的方向转动,把经进油口111吸入的燃油经过燃油通道115输送到出油口114。The impeller 117 is shaped, for example, substantially like a circular disk of reinforced plastic material, and is rotatably mounted in an impeller-accommodating recess 113 of the pump housing 109 . The impeller 117 is driven by the motor 107 to rotate in the direction of arrow A in FIG. 17 , and delivers the fuel sucked through the fuel inlet 111 to the fuel outlet 114 through the fuel passage 115 .

叶轮117在转动中心(轴线O-O)有一个装配旋转轴106的啮合孔118。多个(例如三个)通孔119排列在啮合孔118的周围。参看图19,叶轮117在其外围有许多沿周向排列径向延伸的叶片120。一对圆形凹槽121位于相邻的叶片120之间,每个凹槽121具有大致对应于泵壳体109的通道115的圆形形状的曲率。The impeller 117 has an engaging hole 118 in which the rotating shaft 106 is fitted at the center of rotation (axis O-O). A plurality of (for example, three) through holes 119 are arranged around the engagement hole 118 . Referring to Fig. 19, the impeller 117 has a plurality of radially extending blades 120 arranged in the circumferential direction on its periphery. A pair of circular grooves 121 are located between adjacent vanes 120 , each groove 121 having a curvature generally corresponding to the circular shape of the channel 115 of the pump housing 109 .

叶轮117,与旋转轴106一起,被电动机107驱动,在容纳叶轮的凹座13内叶轮117的上和下面被浮动地密封在外壳体110的上面和盖子部分112B的下面之间。叶轮117的每个通孔119都有使在外壳体110的圆形凹部110A和内壳体112的阶梯形孔112D之间的燃油压力均匀化的功能。The impeller 117, together with the rotating shaft 106, driven by the motor 107, is floatingly sealed between the upper surface of the outer casing 110 and the lower surface of the cover portion 112B in the impeller-accommodating recess 13 above and below the impeller 117. Each through hole 119 of the impeller 117 has a function of equalizing the fuel pressure between the circular recess 110A of the outer casing 110 and the stepped hole 112D of the inner casing 112 .

参看图19和20,叶片120构成为截面基本上为矩形的板体,具有位于沿叶轮转动方向看,即箭头A的方向,在前一侧的前面120A,位于沿叶轮转动方向看,在后一侧的后面120B,和位于前面120A和后面120B之间的一对侧面120C。Referring to Figures 19 and 20, the blade 120 is formed as a plate with a substantially rectangular cross-section. A rear face 120B on one side, and a pair of side faces 120C between the front face 120A and the rear face 120B.

叶片120在根部一侧有沿叶轮117径向直线延伸的直线叶片部分122,而在头部一侧有向着所示的叶轮117的转动方向在前一侧圆形弯曲的弯曲叶片部分123。直线叶片部分122和弯曲叶片部分123大约是叶片120总长度的一半。The blade 120 has a straight blade portion 122 on the root side extending linearly in the radial direction of the impeller 117, and a curved blade portion 123 on the head side that is circularly curved on the front side toward the rotation direction of the impeller 117 as shown. The straight blade portion 122 and the curved blade portion 123 are about half the total length of the blade 120 .

一对倒角124位于叶片120的根部一侧,沿着叶轮117的径向延伸。参看图19-21,每个倒角124是通过倾斜地切掉叶片120的侧面120C和后面120B之间的角得到的。倒角124的总长度H被设置为大约等于从燃油通道115的内端115A到其通道中心C的距离L1,即,(2/5-3/5)×L的值,其中L是燃油通道31的径向长度,按照下面的公式(11):A pair of chamfers 124 are located at the root side of the blade 120 and extend along the radial direction of the impeller 117 . Referring to FIGS. 19-21 , each chamfer 124 is obtained by obliquely cutting off the corner between the side 120C and the rear 120B of the blade 120 . The total length H of the chamfer 124 is set approximately equal to the distance L1 from the inner end 115A of the fuel passage 115 to the passage center C thereof, that is, a value of (2/5−3/5)×L, where L is the fuel passage The radial length of 31, according to the following formula (11):

2/5≤(T/L)≤3/5                …(11)2/5≤(T/L)≤3/5 …(11)

倒角124的总长度H,最好按照下面的公式(12)设定为(9/20-11/20)×L的值:The total length H of the chamfer 124 is preferably set to a value of (9/20-11/20)×L according to the following formula (12):

9/20≤(T/L)≤11/20             …(12)9/20≤(T/L)≤11/20 …(12)

倒角124的总长度H被设置在由公式(11)和(12)给出的范围内,最好,在相对于燃油通道115的径向长度L的1/2值。借此,倒角124构成为延伸到燃油以环流形式流过燃油通道115时形成的通道中心C,使能达到燃油平滑地流入叶片120之间的叶片凹槽的最佳效果。The total length H of the chamfer 124 is set within the range given by equations (11) and (12), preferably, at a value of 1/2 relative to the radial length L of the fuel passage 115 . Thus, the chamfer 124 is configured to extend to the channel center C formed when the fuel flows through the fuel channel 115 in a circular flow, so that the best effect of fuel flowing smoothly into the vane grooves between the vanes 120 can be achieved.

倒角124有位于根部一侧并且有大体不变的倒角宽度的大致矩形的根部一侧的倒角部分124A,以及有从根部一侧的倒角部分124A逐渐减小的倒角宽度的大致三角形的头部一侧的倒角部分124B。The chamfer 124 has a substantially rectangular root-side chamfer portion 124A located on the root side and having a substantially constant chamfer width, and a substantially rectangular chamfer width gradually decreasing from the root-side chamfer portion 124A. The chamfered portion 124B on the head side of the triangle.

根部一侧的倒角部分124A通过切掉一个角构成,并具有大体不变的倒角宽度,得到从其根部一侧流入叶片120之间的叶片凹槽的平滑的燃油流,使得能减小燃油流动的阻力。另一方面,头部一侧的倒角部分124B构成向其头部逐渐减小的倒角宽度,实现在后面120B和侧面120C以及根部一侧的倒角部分124A之间的平滑的连接,使燃油能平滑地流过其间。The chamfered portion 124A on the root side is formed by cutting off a corner and has a substantially constant chamfer width to obtain a smooth fuel flow from the root side thereof into the blade grooves between the blades 120, making it possible to reduce Resistance to fuel flow. On the other hand, the chamfered portion 124B on the head side constitutes a chamfered width gradually decreasing toward the head thereof, realizing a smooth connection between the rear face 120B and the side face 120C and the chamfered portion 124A on the root side, so that Fuel flows smoothly through it.

参看图21,详细说明倒角124的根部一侧的倒角部分124A的形状。根部一侧的倒角部分124A相对于叶片120的侧面120C的倾斜角α按照下边的公式(13)被设置在30-70°的范围内:Referring to FIG. 21, the shape of the chamfered portion 124A on the root side of the chamfer 124 will be described in detail. The inclination angle α of the chamfered portion 124A on the root side with respect to the side surface 120C of the blade 120 is set in the range of 30-70° according to the following formula (13):

30≤α≤70                 …(13)30≤α≤70 …(13)

公式(7)中的倾斜角α最好被设置为按下边公式(8)的40-60°的范围内:The inclination angle α in the formula (7) is preferably set within the range of 40-60° according to the following formula (8):

40≤α≤60                 …(14)40≤α≤60 …(14)

参看图18,根部一侧的倒角部分124A的长度H1相对于倒角124的总长度H按照下边的公式(15)被设置在(1/5≤4/5)×T的值:18, the length H1 of the chamfered portion 124A on the root side is set at the value of (1/5≤4/5)×T with respect to the total length H of the chamfer 124 according to the following formula (15):

1/5≤(H1/H)≤4/5                 …(15)1/5≤(H1/H)≤4/5 …(15)

根部一侧的倒角部分124A的长度H1最好按照下边的公式(16)被设置为(2/5-3/5)×H的值:The length H1 of the chamfered portion 124A on the root side is preferably set to a value of (2/5-3/5)×H according to the following formula (16):

2/5≤(H1/H)≤3/5                 …(16)2/5≤(H1/H)≤3/5 …(16)

下面,说明第三个实施例的运行。当通过输送盖102的连接器102B从外边给泵供电时,输送给电动机107的转子107B的驱动电流使转子107B和旋转轴106一起转动,驱动泵壳体109内的叶轮117。在叶轮117转动时,油箱(未示出)内的燃油通过进油口111被吸入燃油通道115,然后燃油被叶轮117的叶片120沿着燃油通道115输送,并且通过出油口114压到外壳101中。Next, the operation of the third embodiment will be explained. When the pump is powered from the outside through the connector 102B of the delivery cover 102 , the drive current delivered to the rotor 107B of the motor 107 makes the rotor 107B rotate together with the rotating shaft 106 to drive the impeller 117 in the pump housing 109 . When the impeller 117 rotates, the fuel in the fuel tank (not shown) is sucked into the fuel passage 115 through the oil inlet 111, then the fuel is conveyed along the fuel passage 115 by the blade 120 of the impeller 117, and is pressed to the casing through the oil outlet 114 101 in.

被压到外壳101中的燃油通过燃油通道108等在外壳1中流通到出油口102,以便打开输送管102A中的止回阀103。然后,燃油从输送管102A通过外输油管(未示出),例如,以200-500kPa的压力和30-200L/h的输送速度,输送到发动机主体的喷射阀(未示出)。The fuel pressed into the casing 101 flows through the fuel passage 108 and the like in the casing 1 to the fuel outlet 102 to open the check valve 103 in the delivery pipe 102A. Then, the fuel is delivered from the delivery pipe 102A through an external delivery pipe (not shown), for example, at a pressure of 200-500 kPa and a delivery rate of 30-200 L/h, to an injection valve (not shown) of the engine body.

作为我们对根部一侧的倒角部分124A相对于叶片120的侧面120C的角α的研究结果,证实当角α被设置在公式(13)示出的30-70°的范围之内,最好,在公式(14)示出的40-60°的范围之内时,能够得到在300kPa输送压力和80L/h输送速度的条件下由图22中的特性曲线示出的较高的泵效率。As a result of our research on the angle α of the chamfered portion 124A on the root side with respect to the side surface 120C of the blade 120, it was confirmed that when the angle α is set within the range of 30-70° shown in formula (13), it is best , within the range of 40-60° shown in formula (14), higher pump efficiency shown by the characteristic curve in Figure 22 can be obtained under the conditions of 300kPa delivery pressure and 80L/h delivery speed.

在这种情况下,根部一侧的倒角部分124A的长度H1与倒角124的总长度H的比值被设置在大约1/2。借此,根部一侧的倒角部分124A的倾斜角α能够被设置为大体等于从叶片120的侧面120C流到其后面120B的燃油的流动角,实现燃油沿着根部一侧的倒角部分124A平滑地流动,导致燃油流动阻力的降低。In this case, the ratio of the length H1 of the chamfered portion 124A on the root side to the total length H of the chamfer 124 is set at approximately 1/2. Thereby, the inclination angle α of the chamfered portion 124A on the root side can be set to be substantially equal to the flow angle of the fuel flowing from the side surface 120C of the blade 120 to the rear surface 120B thereof, so that the fuel oil flows along the chamfered portion 124A on the root side. Flows smoothly, resulting in reduced resistance to fuel flow.

此外,作为我们对根部一侧的倒角部分124A的长度H1与倒角124的总长度H的比值的研究结果,证实当把比值H1/H设置在公式(15)示出的1/5-4/5的范围内,最好,在公式(16)示出的2/5-3/5的范围内时,能够得到如图23中的特性曲线示出的较高的泵效率。Furthermore, as a result of our study on the ratio of the length H1 of the chamfered portion 124A on the root side to the total length H of the chamfer 124, it was confirmed that when the ratio H1/H is set at 1/5- In the range of 4/5, preferably, in the range of 2/5-3/5 shown in formula (16), a higher pump efficiency as shown in the characteristic curve in FIG. 23 can be obtained.

在这种情况下,根部一侧的倒角部分124A相对于叶片120的侧面120C的倾斜角α被设置为大约50°。借此,根部一侧的倒角部分124A遏制了经过不变宽度的大凹槽在叶片120的根部一侧可能出现的涡流,能够降低燃油流动的阻力。In this case, the angle of inclination α of the chamfered portion 124A on the root side with respect to the side face 120C of the blade 120 is set to about 50°. In this way, the chamfered portion 124A on the root side restrains the vortex that may appear on the root side of the blade 120 through the large groove of constant width, which can reduce the resistance of fuel flow.

此外,我们的研究表明,由于头部一侧的倒角部分124B具有向着头部逐渐减小的倒角宽度,这保证了叶片120的后面120B和侧面120C以及根部一侧的倒角部分124A之间的平滑的连接,燃油能平滑地从叶片120的侧面120C流向根部一侧的倒角部分120A以及从根部一侧的倒角部分120A流向后面120B,能够得到较高的泵效率。In addition, our research has shown that since the chamfered portion 124B on the head side has a chamfered width that gradually decreases toward the head, it ensures Due to the smooth connection between them, the fuel can smoothly flow from the side 120C of the blade 120 to the chamfered portion 120A on the root side and from the chamfered portion 120A on the root side to the rear 120B, so that higher pump efficiency can be obtained.

在这方面,显示出当倒角124的总长度H与燃油通道115的径向长度L的比值H/L在9/20-11/20的范围内被设置在1/2,根部一侧的倒角部分124A相对于叶片120的侧面120C的倾斜角α在40-60°的范围内被设置在50°,以及根部一侧的倒角部分124A的长度H1与倒角124的总长度H的比值H1/H在范围2/5-3/5内被设置在1/2时,能得到最高的泵效率。In this regard, it is shown that when the ratio H/L of the total length H of the chamfer 124 to the radial length L of the fuel passage 115 is set at 1/2 in the range of 9/20-11/20, the root side The inclination angle α of the chamfered portion 124A with respect to the side surface 120C of the blade 120 is set at 50° in the range of 40-60°, and the length H1 of the chamfered portion 124A on the root side is equal to the total length H of the chamfered portion 124. When the ratio H1/H is set at 1/2 within the range of 2/5-3/5, the highest pump efficiency can be obtained.

在第三个实施例中,通过倾斜地切掉侧面120C和后面120B之间的角得到的倒角124位于叶轮117的侧面。这样设计倒角124,即把在叶轮117沿径向延伸的总长度H与燃油通道115的径向长度L的比值设置为9/20-11/20(最好为1/2),根部一侧的倒角部分124A相对于叶片120的侧面120C的倾斜角α设置为40-60°(最好为50°),以及根部一侧的倒角部分124A的长度H1与倒角124的总长度H的比值设置为2/5-3/5(最好为1/2)。In the third embodiment, a chamfer 124 obtained by obliquely cutting off the corner between the side surface 120C and the rear surface 120B is located on the side surface of the impeller 117 . Design the chamfer 124 like this, promptly the ratio of the total length H extending radially at the impeller 117 and the radial length L of the fuel passage 115 is set to 9/20-11/20 (preferably 1/2), root one The angle of inclination α of the chamfered portion 124A of the side relative to the side surface 120C of the blade 120 is set to 40-60° (preferably 50°), and the length H1 of the chamfered portion 124A on one side of the root and the total length of the chamfered angle 124 The ratio of H is set to 2/5-3/5 (preferably 1/2).

借此,在第三个实施例中,倒角124(根部一侧的倒角部分124A)的位置和长度以及根部一侧倒角部分124A的倾斜角可以对应于燃油通过燃油通道115流入叶片120之间的叶片凹槽的流入位置设置,尺寸根据平滑流入的需要,角度使得能够平滑流入。Thus, in the third embodiment, the position and length of the chamfer 124 (the chamfered portion 124A on the root side) and the inclination angle of the chamfered portion 124A on the root side can correspond to the flow of fuel into the vane 120 through the fuel passage 115 The inflow position of the blade groove between is set, the size is according to the need of smooth inflow, and the angle enables smooth inflow.

其结果是,当叶轮117转动时,倒角124使得燃油能够沿着根部一侧的倒角部分124A和头部一侧的倒角部分124B平滑流动,以便降低燃油流动阻力,实现燃油通过燃油通道115高效率地输向出油口114,导致泵效率的提高。As a result, when the impeller 117 rotates, the chamfer 124 enables the fuel to flow smoothly along the chamfered portion 124A on the root side and the chamfered portion 124B on the head side, so as to reduce the fuel flow resistance and realize the passage of fuel through the fuel passage. 115 is efficiently output to the oil outlet 114, resulting in an increase in pump efficiency.

在第三个实施例中,燃油通道115成形为一个大垂直长度和C形截面的通道。最好,参看图24,在第一种变型中,燃油通道131可能由被从燃油通道的中心133径向地向里凸出的环形突起132垂直地分成两个部分,即内通道133和对接侧通道134组成。In the third embodiment, the fuel passage 115 is shaped as a passage with a large vertical length and a C-shaped cross-section. Preferably, referring to Fig. 24, in a first modification, the fuel passage 131 may be divided into two parts vertically by an annular protrusion 132 protruding radially inward from the center 133 of the fuel passage, namely the inner passage 133 and the butt joint. Side channel 134 is formed.

此外,在第三个实施例中,每个叶片120在根部一侧具有沿叶轮117径向直线延伸的直线叶片部分122,而在头部一侧具有沿叶轮117的转动方向看向前侧圆形地弯曲的弯曲叶片部分123。作为选择,参看图25,在第二种变型中,每个叶片141可能有从根部到头部直线延伸的直线结构。作为替换,叶片120可能有从根部到头部沿转动方向向前的圆形弯曲的弯曲结构。Furthermore, in the third embodiment, each blade 120 has a linear blade portion 122 extending linearly in the radial direction of the impeller 117 on the root side, and has a circular blade portion 122 viewed from the front side in the direction of rotation of the impeller 117 on the head side. The curved blade portion 123 is curved in shape. Alternatively, referring to Fig. 25, in a second variation, each blade 141 may have a linear structure extending linearly from the root to the head. Alternatively, the blade 120 may have a curved configuration that is circularly curved forward in the direction of rotation from the root to the tip.

在按照直观的实施例对本发明做了说明之后,应该指出,本发明并不局限于此,可以在不脱离本发明的范围内作各种变化和改进。After the present invention has been described according to the intuitive embodiments, it should be pointed out that the present invention is not limited thereto, and various changes and improvements can be made without departing from the scope of the present invention.

在此,在2002年9月3日提交的日本专利申请P2002-257988和2002年6月6日提交的日本专利申请P2002-165946的全部教导都合并起来,以备参考。The entire teachings of Japanese Patent Application P2002-257988 filed on September 3, 2002 and Japanese Patent Application P2002-165946 filed on June 6, 2002 are hereby incorporated by reference.

Claims (8)

1.一种涡轮燃油泵,它具有:1. A turbo fuel pump having: 容纳电动机的外壳;housing housing the motor; 装在外壳上的壳体,该壳体有在进油口和出油口之间的环形通道;以及a casing mounted on the casing, the casing having an annular passage between the oil inlet and the oil outlet; and 可转动地安装在壳体内的叶轮,该叶轮具有多个在外圆周上排列的沿叶轮径向延伸的叶片,当叶片被电动机转动时,通过通道输送燃油;An impeller rotatably installed in the housing, which has a plurality of blades arranged on the outer circumference and extending radially along the impeller, and when the blades are rotated by the motor, fuel is delivered through the channel; 每个叶片有一个大体矩形截面的板体,从叶轮的转动方向看,该板体有一个前面和一个后面,以及一对位于前面和后面之间的侧面;Each blade has a plate body of generally rectangular cross-section, the plate body has a front face and a rear face as viewed from the direction of rotation of the impeller, and a pair of sides located between the front face and the rear face; 每个叶片有一个位于叶片根部一侧沿叶轮径向延伸的倒角,这个倒角是通过倾斜地切掉叶片的侧面和后面之间的角得到的,该倒角有预定的长度,这个预定的长度为(2/5至3/5)×L,其中L是通道的径向长度。Each blade has a chamfer extending radially along the impeller on one side of the blade root. This chamfer is obtained by obliquely cutting off the angle between the side and the rear of the blade. The chamfer has a predetermined length. The length of is (2/5 to 3/5) x L, where L is the radial length of the channel. 2.按照权利要求1所述的涡轮燃油泵,其特征在于,倒角的预定长度为(9/20至11/20)×L。2. The turbo fuel pump according to claim 1, wherein the predetermined length of the chamfer is (9/20 to 11/20)×L. 3.按照权利要求1所述的涡轮燃油泵,其特征在于,倒角包括根部一侧部分和头部一侧部分,根部一侧部分有基本不变的倒角宽度和预定长度,而头部一侧部分有从根部一侧部分的头部逐渐减小的倒角宽度。3. The turbo fuel pump according to claim 1, wherein the chamfer comprises a root side portion and a head side portion, the root side portion has substantially constant chamfer width and predetermined length, and the head portion The side part has a chamfer width that gradually decreases from the head of the side part at the root. 4.按照权利要求3所述的涡轮燃油泵,其特征在于,根部一侧部分的预定长度为(1/5至4/5)×T,其中T是倒角的总长度。4. The turbo fuel pump according to claim 3, wherein the predetermined length of the root side portion is (1/5 to 4/5) x T, where T is the total length of the chamfer. 5.按照权利要求4所述的涡轮燃油泵,其特征在于,根部一侧部分的预定长度为(2/5至3/5)×T。5. The turbo fuel pump according to claim 4, wherein the predetermined length of the root side portion is (2/5 to 3/5)*T. 6.按照权利要求5所述的涡轮燃油泵,其特征在于,根部一侧部分有相对于叶片侧面的预定的倾斜角,其中预定的倾斜角为30°至70°。6. The turbo fuel pump according to claim 5, wherein the root side portion has a predetermined inclination angle with respect to the blade side, wherein the predetermined inclination angle is 30° to 70°. 7.按照权利要求6所述的涡轮燃油泵,其特征在于,根部一侧部分的预定的倾斜角为40°至60°。7. The turbo fuel pump according to claim 6, wherein the predetermined inclination angle of the root side portion is 40[deg.] to 60[deg.]. 8.按照权利要求7所述的涡轮燃油泵,其特征在于,倒角的预定长度为(1/2)×L,根部一侧部分的预定长度为(1/2)×T,根部一侧部分的预定的倾斜角为50°。8. The turbo fuel pump according to claim 7, characterized in that, the predetermined length of the chamfer is (1/2)×L, the predetermined length of the part on one side of the root is (1/2)×T, and the one side of the root is The predetermined inclination angle of the section is 50°.
CNB2005100763352A 2002-06-06 2003-05-28 turbo fuel pump Expired - Fee Related CN100378319C (en)

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

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CN100378319C true CN100378319C (en) 2008-04-02

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Citations (5)

* Cited by examiner, † Cited by third party
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

Patent Citations (5)

* Cited by examiner, † Cited by third party
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

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