KR20160122821A - Fuel pump - Google Patents

Abstract

A plurality of pump chambers 40 are formed between the inner teeth 300 of the outer gear 30 and the outer teeth 200 of the inner gear 20 nearest to each other. The reference axis Ae is defined by the eccentric direction De and the declination angle? From the reference axis Ae is defined by the rotation direction Rig of the inner gear 20, Axis Ao which gives the angle of confrontation &thetas; In this case, the offset angle? Of the center position P in the rotation direction Rig of the suction port 120 is set to the smaller angle side than the orthogonal axis Ao and the suction port 120 is set to the offset angle? Is arranged on the orthogonal axis Ao from the peak angle at which the volume expansion amount of each pump chamber 40 per unit angle becomes the maximum amount, deviating from the incineration degree side.

Description

Fuel pump {FUEL PUMP}

Cross reference of related application

The present application is based on Japanese Patent Application No. 2014-229156 filed on November 11, 2014, the disclosure of which is incorporated herein by this disclosure.

The present disclosure relates to a fuel pump that sucks fuel from an intake port to a pump chamber and discharges the fuel from the pump chamber.

BACKGROUND OF THE INVENTION [0002] A positive displacement fuel pump that forms a pump chamber between an outer gear having a plurality of internal teeth and an internal gear having external teeth is well known in the art.

For example, in the fuel pump disclosed in Patent Documents 1 and 2, the inner gear is eccentrically eccentrically engaged with the outer gear and rotated while the volume of the pump chamber between both gears is enlarged and reduced. At this time, the fuel is sucked into the pump chamber on the side where the volume is enlarged, and the pump chamber is moved to the side where the volume decreases with the rotation of both the gears, whereby the fuel is discharged in a pressurized state. Since a plurality of pump chambers are formed between the inner teeth of the outer gear and the outer teeth of the inner gear, the fuel can be sucked and discharged simultaneously in the respective pump chambers.

However, in the fuel pump disclosed in Patent Documents 1 and 2, a pump housing rotatably accommodating both gears is provided with a suction port for sucking fuel into the pump chamber. In the fuel pump disclosed in Patent Documents 1 and 2, when the reference axis is defined as the eccentric direction, the angle of deviation from the reference axis is defined in the rotational direction of the internal gear, and the orthogonal axis having a diagonal angle orthogonal to the reference axis is defined, The range of the declination angle at which the suction port is arranged with respect to the axis and the orthogonal axis are different from each other.

Specifically, in the fuel pump disclosed in Patent Document 1, the entire range of the suction port is arranged in a range deviated from the orthogonal axis on the smaller angle side with respect to the angle of declination. In such an arrangement, since the small-sized pump chamber on the side of incineration angle of the opposite angle faces the intake port, the amount of fuel actually sucked into the opposite pump chamber of the intake port becomes small. As a result, in the pump chamber whose angle of deviation is larger on the angle side than the suction port, the amount of fuel supplied from the opposite pump chamber of the suction port decreases between the pump housing and both gears, so that the pump efficiency is reduced.

On the other hand, in the fuel pump disclosed in Patent Document 2, the angle of inclination of the center position of the intake port in the rotational direction of the internal gear is set at a right angle, so that the intake port is disposed on the orthogonal axis. In such an arrangement, the amount of fuel that can be sucked into the pump chamber is increased because the large-capacity pump chamber on the orthogonal axis faces the intake port. However, in order to apply a large opening area for suppressing the pressure loss to the intake port on the orthogonal axis, in the pump chamber opposed to the intake port, the volume enlargement amount per unit angle relative to the angle of deflection is excessively increased. Therefore, . As a result, in the pump chamber whose diagonal angle is diagonal to the intake port, the amount of fuel supplied from the opposite pump chamber of the intake port is reduced between the pump housing and both gears.

In such a situation, the inventor of the present invention paid attention to a peak angle at which the volume enlargement amount of each pump chamber per unit angle with respect to the angle of deflection becomes the maximum, and by setting the declination angle range in which the inlet port is arranged to be optimal for the peak angle and the orthogonal axis, Can be improved.

Patent Document 1: Japanese Patent Application Laid-Open No. H09-197709 Patent Document 2: Japanese Patent Application Laid-Open No. 2011-132894

The present disclosure has been made in view of the above points, and its object is to provide a fuel pump with improved pump efficiency.

In the present disclosure, an outer gear having a plurality of internal teeth, an internal gear having a plurality of external teeth eccentrically eccentrically eccentric with the external gear, and an intake port for sucking fuel are formed, And a pump housing for accommodating the fuel pump. The outer gear and the inner gear are rotated while expanding and contracting the volume of the pump chamber formed between the both gears, thereby sucking the fuel from the inlet to the pump chamber and discharging the fuel from the pump chamber. A plurality of pump chambers are formed between the inner teeth and the outer teeth, which are closest to each other. Defining a reference axis in the eccentric direction, defining a deviation angle from the reference axis in the rotation direction of the internal gear, and defining an orthogonal axis giving a deviation angle perpendicular to the reference axis. In this case, the angle of inclination of the central position in the direction of rotation of the intake port is set to the side of the incineration angle with respect to the orthogonal axis, and the angle of incidence is set from the peak angle at which the volume- And is disposed on the orthogonal axis.

According to the configuration of the fuel pump, the intake port having the angle of incidence at the central position in the rotation direction of the inner gear is disposed on the orthogonal axis on the incinerator side, but the volume expansion amount of each pump chamber per unit angle with respect to the angle of deviation is the maximum Is deviated from the incidence angle side from the peak angle. According to this, the amount of the fuel that can be sucked into the pump chamber increases because the large pump chamber on the orthogonal axis faces the suction port. In addition, in the pump chamber opposed to the suction port, the amount of volume expansion per unit angle is suppressed to be smaller than the maximum amount, so that the actual amount of fuel sucked in accordance with the volume increase amount can be suppressed. According to this, in the pump chamber whose angle of deviation is diagonal to the intake port, the amount of fuel to be supplied from the opposite pump chamber of the intake port can be ensured through the space between the pump housing and the both gears.

1 is a partial sectional front view showing a fuel pump according to an embodiment of the present disclosure;
2 is a cross-sectional view taken along a line II-II in Fig. 3, showing a fuel pump according to an embodiment.
3 is an end view along the line III-III in Fig.
4 is a sectional view taken along the line IV-IV in Fig.
5 is a cross-sectional view taken along the line V-V in Fig.
6 is a sectional view taken along the line VI-VI in Fig.
7 is a schematic diagram for explaining the detailed configuration of the fuel pump according to the embodiment.
8 is a graph for explaining the characteristics of the fuel pump according to the embodiment.
9 is a graph for explaining the pump efficiency of the fuel pump according to one embodiment.

Hereinafter, one embodiment of the present disclosure will be described with reference to the drawings.

As shown in Figure 1, the fuel pump 1 according to one embodiment of the present disclosure is a positive displacement trochoid pump. The fuel pump 1 includes a pump main body 3 and an electric motor 4 accommodated in a cylindrical pump body 2. The pump main body 2 has a cylindrical shape. The fuel pump 1 is provided with a side cover 5 protruding outward from the end opposite to the pump main body 3 with the electric motor 4 interposed therebetween in the axial direction among the pump main body 2, Respectively. Here, the side cover 5 integrally has an electric connector 5a for energizing the electric motor 4 and a discharge port 5b for discharging the fuel. In this fuel pump 1, the electric motor 4 is rotationally driven by energization from an external circuit through the electric connector 5a. As a result, the fuel sucked and pressurized by the pump main body 3 by using the rotational force of the electric motor 4 is discharged from the discharge port 5b. As the fuel pump 1, gasoline may be discharged as fuel, or diesel fuel may be discharged as fuel.

Hereinafter, the pump main body 3 will be described in detail. 1 and 2, the pump body 3 is provided with a pump housing 10, an inner gear 20 and an outer gear 30. The pump housing 10, Here, the pump housing 10 is formed by overlapping the pump cover 12 and the pump casing 14.

The pump cover 12 is made of metal and formed into a disc shape. The pump cover 12 protrudes outward from the side of the pump body 2 opposite to the side cover 5 with the electric motor 4 therebetween in the axial direction.

As shown in FIGS. 1, 3 and 4, the pump cover 12 has a suction hole 120 in the form of a cylindrical hole and a suction passage 122 in the form of an arc groove for sucking fuel from the outside. The suction port 120 penetrates a specific portion Ss of the pump cover 12 eccentric from the inner center line Cig of the inner gear 20 along the axial direction of the pump cover 12. The suction passage 122 is opened to the pump casing 14 side of the pump cover 12. 4, the inner peripheral portion 122a of the suction passage 122 extends to a length of less than half a circle along the rotation direction Rig (see Fig. 6) of the inner gear 20 . The outer peripheral portion 122b of the suction passage 122 extends along the rotation direction Rog of the outer gear 30 (see also Fig.

Here, the suction passage 122 extends from the starting end portion 122c toward the terminating portion 122d of the rotation direction Rig or Rog. The suction port 120 opens to a specific portion Ss of the groove bottom 122e of the suction passage 122 so that the suction passage 122 communicates with the suction port 120. [ 3 and 4, the width Wip of the suction passage 122 in the radial direction in the entire region of the specific portion Ss in which the suction port 120 is opened is smaller than the diameter W of the suction port 120 Ø).

As shown in FIG. 2, the pump casing 14 is made of metal and formed into a cylindrical shape having a bottom. The opening portion 140 of the pump casing 14 is closed by the pump cover 12 to seal the entire circumferential extent. The inner peripheral portion 147 of the pump casing 14 is formed into a cylindrical hole shape eccentric from the inner center line Cig of the inner gear 20 as shown in Figs.

1 and 5, in order to discharge the fuel from the discharge port 5b through the fuel passage 6 between the pump body 2 and the electric motor 4, Shaped discharge passage 142 is formed. The discharge passage 142 passes through the concave bottom 141 of the pump casing 14 in the axial direction. 5, the inner peripheral portion 142a of the discharge passage 142 extends along the rotation direction Rig of the inner gear 20 to a length less than half of a half. The outer peripheral portion 142b of the discharge passage 142 extends along the rotation direction Rog of the outer gear 30 to a length less than half of a half.

Here, the discharge passage 142 is reduced from the starting end 142c toward the end 142d of the rotating direction Rig or Rog. The discharge passage 142 is divided by the reinforcing rib 143 provided to suppress the radial deformation of the pump casing 14 toward the end 142c side and the end 142d side. )do. The discharge passage 142 communicates with the fuel passage 6 shown in Fig. 1 on both the first end 142c side and the second end 142d side.

As shown in Figs. 1 and 5, the suction passage 122 and the pump chamber 40 between the gears 20 and 30 of the concave bottom portion 141 of the pump casing 14, In the opposite portion, a suction groove 144 having an arc groove shape is formed corresponding to the shape in which the suction passage 122 is projected in the axial direction. Accordingly, in the pump casing 14, the discharge passage 142 is provided in line symmetry with the suction groove 144. 1 and 4, an arc groove-shaped discharge groove 124 is formed in a portion of the pump cover 12 opposed to the discharge passage 142 with the pump chamber 40 therebetween, (142) in the axial direction. Accordingly, in the pump cover 12, the suction passage 122 is provided in line symmetry with the discharge groove 124.

1 and 2, on the inner center line Cig of the concave bottom portion 141 of the pump casing 14, a radial bearing (not shown) is mounted on the inner peripheral surface of the rotary shaft 4a in order to radially receive the rotary shaft 4a of the electric motor 4 radial bearing 146 is fitted and fixed. On the other hand, a thrust bearing 126 is fitted and fixed on the inner center line Cig of the pump cover 12 in order to axially support the rotary shaft 4a.

2 and 6, the concave bottom portion 141 and the inner circumference portion 147 of the pump casing 14 are formed by pumping the receiving space 148, which accommodates the inner gear 20 and the outer gear 30, And is partitioned by the cover (12). The profiles of the teeth 200 of the inner gear 20 and the teeth 300 of the outer gear 30 form a trochoidal curve. That is, the inner gear 20 and the outer gear 30 are trochoid gears.

The inner gear 20 is arranged eccentrically in the accommodation space 148 by making the inner center line Cig common with the rotary shaft 4a. The inner peripheral portion 202 of the inner gear 20 is radially supported by the radial bearing 146 and is axially supported by the concave bottom portion 141 of the pump casing 14 and the pump cover 12 in the axial direction. It is supported. The inner gear 20 is rotatable in a constant rotation direction Rig about the inner center line Cig by the shaft bearings thereof.

The inner gear 20 has a plurality of external teeth 200 on the outer circumferential portion 204 arranged at equal intervals along the rotation direction Rig. Since the external teeth 200 are axially opposed to the passages 122 and 142 and the grooves 124 and 144 in accordance with the rotation of the internal gear 20 as shown in Figs. 1 and 6, The attachment of the inner gear 20 to the concave bottom portion 141 and the pump cover 12 is suppressed.

2 and 6, the outer gear 30 is disposed coaxially in the receiving space 148 by becoming eccentric with respect to the inner center line Cig of the inner gear 20. [ Thus, with respect to the outer gear 30, the inner gear 20 is eccentric in the eccentric direction De as the radial direction. The outer peripheral portion 302 of the outer gear 30 is radially supported by the inner peripheral portion 147 of the pump casing 14 and is supported by the recessed bottom portion 141 of the pump casing 14 and the pump cover 12 And is axially supported by an axle. The outer gear 30 is rotatable in a constant rotation direction Rog around the outer center line Cog which is eccentric from the inner center line Cig.

The outer gear 30 has a plurality of internal teeth 300 arranged on the inner peripheral portion 304 at regular intervals along the rotation direction Rog. Here, the number of the internal teeth 300 in the external gear 30 is set to be one more than the number of the external teeth 200 in the internal gear 20. The inner teeth 300 can be axially opposed to the passages 122 and 142 and the grooves 124 and 144 in accordance with the rotation of the outer gear 30 as shown in Figs. 1 and 6, The attachment of the outer gear 30 to the bottom portion 141 and the pump cover 12 is suppressed.

The inner gear 20 is engaged with the outer gear 30 by a relative eccentricity in the eccentric direction De. 6, a plurality of pump chambers 40 are formed between the gears 20 and 30 of the accommodation space 148. As shown in Fig.

7, the reference axis Ae is defined as the eccentric direction De of the inner gear 20 with respect to the outer gear 30, and the reference axis Ae is defined with respect to the direction of rotation Rig of the inner gear 20 And defines a deviation angle ([theta]) from the reference axis Ae. The orthogonal axis Ao is defined as an orthogonal direction Do in which a declination angle? Of a right angle (90 degrees) with respect to the reference axis Ae is given. Further, a region having a declination angle [theta] of 0 degree to 180 degrees is defined as a suction region Ti. The outer teeth 200 of the inner gear 20 and the inner teeth 300 of the outer gear 30 are closest to each other in the suction region Ti to define a portion defining both ends of the pump chamber 40 as a positive integer (Sa [n]) using the least squares (n).

Under these definitions, each pump chamber 40 of the suction region Ti is located at the most approaching portion Sa [n] of the angle of inclination θ and the most approaching portion Sa [n- 1]), respectively. Therefore, in the suction area Ti, the pressure in the most proximate part Sa [n] on the diagonal side among the most approaching parts Sa [n] and Sa [n-1] that determine the both ends of each pump chamber 40 Is defined as the angle of deviation (hereinafter referred to as " pump deviation angle ")? R of each pump chamber 40. In Fig. 7, the most approaching portion Sa [n] is schematically shown by the two-dot chain line.

In the above definition, in the suction region Ti in which the deviation angle? From the reference axis Ae is in the range over the orthogonal axis Ao, the suction passage 122 and the suction groove 144 communicate with each other The larger the pump chamber angle? R as the angle of deviation? With respect to the pump chamber 40, the larger the volume. As a result, in the suction region Ti, the fuel is sucked from the suction port 120 to the pump chamber 40 through the suction passage 122. At this time, since the suction passage 122 is enlarged as the position from the starting end 122c toward the terminating end 122d (see FIG. 4), that is, the position with the larger declination angle? The amount of fuel to be sucked is dependent on the volume increase amount DELTA V of the pump chamber 40 shown in Fig. Therefore, in the suction region Ti, the unit angle ?? of the pump chamber angle? R is used to calculate the pump chamber angle at the pump chamber angle? R from the volume of the pump chamber 40 at the pump chamber angle? (40) is defined as a volume enlargement amount (? V) per unit angle??. Although the unit angle? Is set to 5 degrees in FIG. 8, the unit angle? May be set to 1 degree, for example.

The volume enlargement amount? V of each pump chamber 40 per unit angle? Is calculated from the peak angle? Rp as the pump chamber angle? R in the intake region Ti shown in FIG. 8 It becomes maximum. Therefore, in the present embodiment, the entire range Ta of the angle of inclination? At which the suction port 120 is disposed is set on the orthogonal axis Ao so as to deviate from the peak angle? Rp to a small angle side. Along with this, in this embodiment, the angle of confinement given to the center position P in the rotation direction Rig of the suction port 120 is set to an angle side smaller than the orthogonal axis Ao.

On the other hand, an area having a deviation angle [theta] of 180 degrees to 360 degrees is defined as a discharge area To with respect to the suction area Ti described so far. In this discharge region To, the pump chamber angle? R as the angle of deviation? Defined according to the suction region Ti is set to be smaller than the pump chamber angle? Of the pump chamber 40 communicating with the discharge passage 142 and the discharge groove 124 The larger the volume, the smaller. As a result, in the discharge area To, the fuel is discharged from the pump chamber 40 through the discharge passage 142 to the fuel passage 6 simultaneously with the suction function in the suction area Ti. At this time, since the discharge passage 142 is reduced as the position from the starting end portion 142c toward the end portion 142d, that is, the position with the larger deviation angle?, The amount of fuel discharged through the discharge passage 142 becomes smaller 40). At this time, since the fuel passage 6 is communicated with the discharge port 5b, the discharged fuel to the fuel passage 6 through the discharge passage 142 is discharged from the discharge port 5b to the outside again.

9, the pump efficiency? Substantially proportional to the amount of fuel discharged through the discharge passage 142 is set to a value obtained by dividing the deviation angle? Of the center position P in the rotation direction Rig of the suction port 120 (?). 9, the pump efficiency? Shows a similar fluctuation tendency even when the number of revolutions Nr of the internal gear 20 is changed to 4000 rpm, 6000 rpm and 8000 rpm. Therefore, in the present embodiment, the angle? Of the central position P shown in Figs. 3, 4, 6 and 7 is set to a range Tp of 70 to 85 degrees with a high pump efficiency? do. 9 shows the relationship between the intake passage 122 (Fig. 9) and the axial direction of the pump housing 10, assuming that diesel fuel having a density of 843.6 kg / m3 and a viscosity coefficient of 2.53 x ^10-3 Pa- ) Is set to 1.5 mm.

(Action effect)

The operation and effect of the fuel pump 1 described above will be described below.

According to the fuel pump 1, the intake port 120 having a smaller angle θ of the central position P in the rotation direction Rig of the internal gear 20 than the orthogonal axis Ao is an orthogonal axis But the peak angle? Rp at which the volume increase amount? V of each pump chamber 40 per unit angle? Is set to the maximum amount with respect to the pump chamber angle? R as the angle angle? . The amount of fuel that can be sucked into the pump chamber 40 is increased because the large pump chamber 40 on the orthogonal axis Ao opposes the inlet port 120. [ Further, in the pump chamber 40 opposed to the intake port 120, the volume increase amount DELTA V per unit angle DELTA &thetas; is suppressed to be smaller than the maximum amount so that the amount of fuel actually sucked in accordance with the volume increase amount DELTA V is insufficient Can be suppressed. The pump chamber 40 having the diagonally opposite pump chamber angle θr is connected to the opposite pump chamber 40 of the suction port 120 through the space between the pump housing 10 and the gears 20 and 30 in the pump chamber 40, It is possible to secure the amount of fuel to be supplied from the pump. Thus, it becomes possible to improve the pump efficiency?.

According to the fuel pump 1, the angle? Of the central position P of the intake port 120 disposed on the orthogonal axis Ao is set in the range Tp of 70 to 85 degrees, The volume of the pump chamber 40 opposed to the pump chamber 120 can be secured as much as possible. The suction port 120 in which the declination angle? Of the central position P is in the range of 70 to 85 degrees Tp has the center position P even when the opening area is increased to suppress the pressure loss, It is possible to reliably realize an arrangement structure in which the entire area (Ta) deviates from the peak angle (rrp), as well as an arrangement structure that is closer to the incineration side than the area (Ao). Therefore, it is possible to ensure the reliability of the effect of increasing the pump efficiency?.

Further, according to the fuel pump 1, the suction passage 122 opposed to the pump chamber 40 in the suction region Ti for sucking the fuel from the suction port 120 is enlarged as the angle θ is larger. The pump chamber 40 on the side of the suction region Ti where the volume is enlarged increases as the angle of the pump chamber angle r as the angle of inclination θ increases as compared with the amount of fuel actually sucked from the suction port 120 It is possible to prevent the fuel in the pump chamber 40 from becoming insufficient. Therefore, it is possible to contribute to achieving a high pump efficiency (?) In addition to the action by the special arrangement structure of the suction port 120 opened to the suction passage 122.

According to the fuel pump 1, the suction groove 144 is formed in the shape of projecting the suction passage 122 at the portion of the suction region Ti opposed to the suction passage 122 with the pump chamber 40 therebetween . The pump chamber angle θr is diagonally opposite to the intake port 120 in the pump chamber 40 through the suction groove 144 between the pump housing 10 and the gears 20 and 30, The amount of fuel to be supplied from the opposite pump chamber 40 can be surely secured. Therefore, the suction groove 144 opposed to the suction passage 122 is particularly effective for improving the pump efficiency?.

According to the fuel pump 1, the suction port 120 formed in the shape of a cylindrical hole has the entire area Ta of the specific portion Ss at which the suction port 120 is arranged, ). ≪ / RTI > Therefore, it is easy to realize such an arrangement structure that the entire area (Ta) deviates from the peak angle? Rp even if the opening area is increased to suppress the pressure loss. Therefore, in order to improve the pump efficiency [eta], the suction port 120 having the cylindrical hole shape becomes particularly effective.

(Other Embodiments)

Although the embodiment of the present disclosure has been described above, the present disclosure is not limited to the above embodiments, and various embodiments can be applied within the scope of not departing from the gist of the present disclosure.

Specifically, even if the angle? Of the central position P of the suction port 120 is set to an angle other than the range Tp in the range of 70 to 85 degrees as long as the angle is smaller than the orthogonal axis Ao in Modification Example 1 good. However, it is needless to say that even in the case of the modification 1, it is necessary to set the entire area Ta of the suction port 120 on the orthogonal axis Ao from the peak angle? Rp to the incineration degree side.

In the modified example 2, the width of the suction passage 122 may be set to a substantially constant width from the starting end 122c toward the terminating end 122d. In the third modification, the width of the discharge passage 142 may be set to a substantially constant width from the starting end portion 142c toward the end portion 142d.

In the modified example 4, the discharge passage 142, which is not divided between the both ends 142c and 142d, may be employed by not providing the reinforcing ribs 143 in the pump casing 14. [ In Modification 5, at least one of the suction groove 144 and the discharge groove 124 may not be provided.

In the modified example 6, the suction port 120 may be formed in a shape other than a cylindrical hole shape, for example, an elliptical hole shape or a rectangular hole shape. In the seventh modification, the suction port 120 may be passed through the pump cover 12 obliquely with respect to the axial direction.

Claims (5)

An outer gear 30 having a plurality of internal teeth 300,
An inner gear 20 having a plurality of external teeth 200 and eccentrically engaged with the external gear 30 in an eccentric direction De,
And a pump housing (10) forming an intake port (120) for sucking fuel and rotatably accommodating the outer gear (30) and the inner gear (20)
The outer gear 30 and the inner gear 20 are rotated while enlarging or reducing the volume of the pump chamber 40 formed between the outer gear 30 and the gears of the inner gear 20, 120 to the pump chamber 40 and discharges the pump chamber 40 from the pump chamber 40,
The pump chamber (40) formed between the internal teeth (300) and the external teeth (200)
Defining a reference axis Ae in the eccentric direction De and defining a deviation angle? And? R from the reference axis Ae in a rotation direction Rig of the internal gear 20, When defining an orthogonal axis Ao which gives the angle of inclination perpendicular to the plane Ae,
The angle of deviation of the center position P in the rotation direction Rig of the suction port 120 is set to be smaller in the angle of incidence on the orthogonal axis Ao,
The intake port 120 is deviated from the peak angle rp at which the volume increase amount DELTA V of each pump chamber 40 becomes the maximum amount per unit angle [Delta] [theta] with respect to the declination angle to the incineration degree side, Lt; RTI ID = 0.0 >
Fuel pump.
The method according to claim 1,
The declination angle of the center position P of the suction port 120 is set to a range Tp of 70 to 85 degrees
Fuel pump.
3. The method according to claim 1 or 2,
The pump housing 10 is formed with a suction passage 122 that is enlarged in a position where the angle of deviation is larger at a portion of the pump housing 40 opposed to the pump chamber 40 in a suction region Ti for sucking fuel from the suction port 120 and,
The suction port (120) is open to the suction passage (122)
Fuel pump.
The method of claim 3,
The pump housing 10 includes a suction groove 121 having a shape in which the suction passage 122 is projected in a portion of the suction region Ti opposed to the suction passage 122 with the pump chamber 40 interposed therebetween 144)
Fuel pump.
5. The method according to any one of claims 1 to 4,
The suction port 120 is formed in a cylindrical hole shape
Fuel pump.

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