FUEL PUMP

Abstract

A fuel pump has a casing and an impeller. The impeller is substantially disk shaped having an upper surface and a lower surface The impeller is rotatable within the casing around a rotational axis. A plurality of impeller depressions is formed in at least the lower surface of the impeller. The plurality of impeller depressions is located on at least one of the inside and the outside of a group of concavities. The plurality of impeller depressions is arranged on a circle around the rotational axis of the impeller. Each of the impeller depressions has its deepest portion in a rear half thereof with respect to the rotational direction of the impeller.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 schematically shows a cross-sectional view of the pump unit of the fuel pump of the first embodiment.

FIG. 2 schematically shows a plan view of the impeller of the first embodiment that is a cross-sectional view taken along the II-II line in FIG. 1.

FIG. 3 schematically shows a cross-sectional view of the depressions provided in the impeller that is a cross-sectional view taken along the III-III line in FIG. 2.

FIG. 4 schematically shows a cross-sectional view of the depressions and the connection hole provided in the impeller of the fuel pump of the second embodiment.

FIG. 5 schematically shows a cross-sectional view of the through hole in the impeller of the fuel pump of the third embodiment.

FIG. 6 schematically shows a cross-sectional view of a combined hole in the impeller of the fuel pump of a modification example of the third embodiment.

FIG. 7 schematically shows a cross-sectional view of the combined hole in the impeller of the fuel pump of a modification example of the third embodiment.

FIG. 8 schematically shows a cross-sectional view of the combined hole in the impeller of the fuel pump of a modification example of the third embodiment.

FIG. 9 schematically shows a cross-sectional view of the combined hole in the impeller of the fuel pump of a modification example of the third embodiment.

FIG. 10 schematically shows a cross-sectional view of the pump unit of the fuel pump of the fourth embodiment.

FIG. 11 schematically shows a plan view of the upper casing that is a cross-sectional view taken along the XI-XI line in FIG. 10.

FIG. 12 schematically shows a plan view of the lower casing that is a cross-sectional view taken along the XII-XII line in FIG. 10.

FIG. 13 schematically shows a cross-sectional view of the upper casing, lower casing, and impeller that is a cross-sectional view taken along the XIII-XIII line in FIGS. 11, 12.

FIG. 14 schematically shows a cross-sectional view of the conventional fuel pump.

FIG. 15 schematically shows a plan view of the conventional impeller.

FIG. 16 schematically shows a cross-sectional view of the depression provided in the conventional impeller.

DETAILED DESCRIPTION OF THE INVENTION

The preferred features of the present invention will be described below.

• (First preferred feature) Pressure generating means is provided in the fuel pump that causes a fuel located between an impeller and a casing to flow in a direction of generating pressure for separating the impeller from the casing.
• (Second preferred feature) The opening width of an impeller depression decreases toward the edge on the rear side in the impeller rotational direction.
• (Third preferred feature) The opening width of a casing depression decreases toward the edge on the front side in the impeller rotational direction.

First Embodiment

A first embodiment of the fuel pump of the present invention will be described below with reference to FIG. 1 to FIG. 3. FIG. 1 schematically shows a cross-sectional view of a pump unit of the fuel pump of the present embodiment.

In a fuel pump 1 such as shown in FIG. 1, a motor unit and a pump unit 3 are accommodated in a common housing. Because the motor unit and the common housing are similar to that of the conventional fuel pump, explanation thereof is herein omitted. The pump unit 3 comprises an impeller 10 and a casing 60 (an upper casing 20 and a lower casing 30).

The impeller 10 is substantially disk shaped and comprises a central opening 10a in the center thereof for receiving a motor shaft 2a so that the motor shaft 2a cannot rotate relative to the impeller 10. When the motor shaft 2a rotates, the impeller 10 also rotates in the casing 60. In the vicinity of outer circumference of an impeller upper surface 17, boost ports 12 (concavities) are formed repeatedly along the outer circumference. In the vicinity of outer circumference of an impeller lower surface 19, boost ports 14 are formed repeatedly along the outer circumference.

In a surface 37 (referred to hereinbelow as “first surface 37”) of the lower casing 30 that faces the impeller lower surface 19, a first boost groove 34 is formed facing a plurality of boost ports 14 formed in the lower surface 19 of the impeller 10. In a surface 27 (referred to hereinbelow as “second surface 27”) of the upper casing 20 that faces the impeller upper surface 17, a second boost groove 22 is formed facing a plurality of boost ports 12 formed in the upper surface 17 of the impeller 10. In a plan view of the first and second surfaces 27, 37, the first boost groove 34 and the second boost groove 22 are formed to have an almost C-like shape from an upstream end to a downstream end along the rotational direction of the impeller 10. A first boost path 44 is formed by a plurality of boost ports 14 provided in the lower surface 19 of the impeller 10 and the first boost groove 34 formed in the lower casing 30. A second boost path 42 is formed by a plurality of boost ports 12 provided in the upper surface 17 of the impeller 10 and the second boost groove 22 formed in the upper casing 20. A fuel intake hole 32 connected to the first boost groove 34 is formed at the upstream end of the first boost groove 34. A fuel discharge hole 24 connected to the second boost groove 22 is formed at the downstream end of the second boost groove 22.

When the motor is driven, the impeller 10 rotates between the upper casing 20 and the lower casing 30, the fuel is sucked in from the fuel intake hole 32 into the pump unit 3 and introduced into the first boost path 44 and the second boost path 42. The fuel whose pressure increases while it flows in the first boost path 44 and the second boost path 42 is pumped out from the fuel discharge hole 24 into the motor unit. The fuel that is pumped out into the motor unit passes through the motor unit and is pumped out to the outside from a port (not shown in the figure) formed in the upper part of the fuel pump 1.

A plurality of depressions 18 for reducing the frictional force acting upon the impeller 10 when it rotates is formed in the lower surface 19 of the impeller 10. The plurality of depressions 18 is formed on the inside of the plurality of boost ports 14. A plurality of depressions 16 for reducing the frictional force acting upon the impeller 10 when it rotates is formed in the upper surface 17 of the impeller 10. The plurality of depressions 16 is formed on the inside of the plurality of boost ports 12. The shape of depressions 16, 18 is described below.

FIG. 2 is a plan view of the impeller 10 obtained when the impeller 10 is viewed from below as shown in FIG. 1. Eight depressions 18 are formed equidistantly in the circumferential direction in the lower surface 19 of the impeller 10. Each of the depressions 18 is formed to have an almost trapezoidal shape in the plan view thereof. Each of the depressions is formed such that the width of an edge at the rear side of the depression (length of the trapezoid on the rear side) in the impeller rotational direction (direction shown by an arrow in FIG. 2) is less than the width on the front side (length of the trapezoid on the front side). Eight depressions 16 (not shown in the figure) are also formed in the upper surface 17 of the impeller 10, similarly to the depressions 18 in the lower surface 19 shown in FIG. 2. Similarly to the depressions 18, each of the depressions 16 in the upper surface 17 of the impeller 10 is formed to have an almost trapezoidal shape in the plan view thereof. Each of the depressions is formed such that the width thereof at the rear side in the impeller rotational direction is less than the width of the edge at the front side.

FIG. 3 is a cross-sectional view taken along the III-III line in FIG. 2. The depressions 16, 18 have the deepest portion P closer to the rear side edge (left side in FIG. 3) in the impeller rotational direction. A bottom surface from a front edge F1 to the deepest portion P and a bottom surface from the deepest portion P to the rear edge B1 are formed as smooth surfaces. The inclination of the bottom surface from the front edge F1 to the deepest portion P is more gradual than that of the bottom surface from the deepest portion P to the rear edge B1. Each of the depressions 16, 18 is formed such that the cross section area thereof decreases from the deepest portion P toward the rear edge B1. Both the width and depth of each of the depressions 16, 18 decrease from the deepest portion P toward the rear edge B1.

In a region between the upper surface 17 of the impeller 10 and the upper casing 20 wherein the second boost path 42 is not formed, and in a region between the lower surface 19 of the impeller 10 and the lower casing 30 wherein the first boost path 44 is not formed, the fuel is carried along by the impeller 10 rotating at a high rate, due to its own viscosity, at a certain rate (according to the level of viscosity thereof) in the impeller rotational direction. However, the rotation rate of the impeller 10 is obviously higher than the rotation rate of the fuel being pulled by the impeller 10. Therefore, part of the fuel rotating with the rotation rate lower than that of the impeller 10 is introduced, as shown in FIG. 3, into the depressions 16 in the upper surface 17 of the impeller 10 and the depressions 18 in the lower surface 19 of the impeller 10 and flows inside the depressions 16, 18 along the bottom wall surface of the depressions 16, 18 in the direction opposite to the impeller rotational direction (counter-flows). The depressions 16, 18 are formed such that the deepest portions P are formed in the rear half of the depressions 16, 18 with respect to the impeller rotational direction. Therefore, the fuel introduced into the depression 18 flows from the deepest portion P of the depression 18 toward the first surface 37 of the lower casing 30. As a result, a pressure is generated in the direction of separating the impeller 10 from the lower casing 30. Further, the fuel introduced into the depression 16 flows from the deepest portion P of the depression 16 toward the second surface 27 of the upper casing 20. As a result, a pressure is generated in the direction of separating the impeller 10 from the upper casing 20. The impeller 10 is located at a height where the two pressures are balanced. The impeller 10 is rotated in a state of being separated from the upper casing 20 and the lower casing 30. As a result, the impeller 10 is prevented from rotating in a state of being pressed against the upper casing 20 or the lower casing 30, and frictional force acting upon the impeller 10 when the impeller is rotates is reduced.

In the depressions 16, 18, a region from the deepest portion P to the rear edge B1 in the impeller rotational direction is a region where the aforementioned pressure is generated. In the depressions 16, 18 of the fuel pump 1 of the present embodiment, the figure of this region is required to initiate a flow of fuel from the deepest portion P toward the casing, so this region is not required to be formed with any particular high degree of dimensional accuracy and an allowable margin of error becomes large. Accordingly, the cost of forming the depressions 16, 18 can be reduced. As a result, the production cost of the fuel pump 1 can be reduced.

In the depressions 16, 18, the width of the front edge F1 in the impeller rotational direction widens, thereby facilitating the introduction of fuel into the depressions 16, 18. Further, the width of the rear edge B1 narrows and the cross-sectional area thereof decreases from the deepest portion P toward the rear edge B1. Therefore, the fuel introduced into the depressions 16, 18 is pushed into the narrowing channel and flows under a comparatively strong force from the deepest portion P toward the casings. As a result, a comparatively large pressure can be generated in the direction of separating the impeller 10 from the casings.

Further, the depressions 16, 18 are formed on the inner circumferential side of the boost ports 12, 14 that are formed close to the outer periphery. The region on the inside of the boost ports 12, 14 is wider than the region on the outside. Therefore, the depressions 16, 18 can be easily formed.

Further, pluralities of depressions 16, 18 are formed equidistantly in the circumferential direction in the impeller 10. The pressures generated by each of the depressions 16 are added up to obtain a resultant pressure corresponding to the number of depressions 16 (eight in the present embodiment). The pressures generated by the depressions 18 are added up to obtain a resultant pressure corresponding to the number of depressions 18 (eight in the present embodiment). Therefore, a comparatively large pressure is generated in the direction of separating the impeller 10 from the upper casing 20 and the lower casing 30.

In the present embodiment, a case is explained in which depressions 16 are formed in the upper surface 17 of the impeller 10, and depressions 18 are also formed in the lower surface 19 of the impeller 10, but it is also possible to form only the depressions 18 in the lower surface 19. Generally, part of the fuel under high pressure that is pumped out to the motor unit of the fuel pump is refluxed into the space between the upper casing 20 and the lower casing 30 via the clearance around the motor shaft. This high-pressure fluid acts upon the upper surface 17 of the impeller 10 and pushes the impeller 10 down. As a result, the impeller 10 can be easily caused to rotate in a state of being pressed against the lower casing 30. To prevent such a state, it is sometimes sufficient to form the depressions 18 only in the lower surface 19 of the impeller 10. In this case, the number of depressions can be decreased and cost of the depression formation process can be reduced.

The depressions 16, 18 may also not be disposed along the circumferential direction of the impeller 10 (that is, in the direction along the boost ports 12, 14).

Further, in the embodiment described hereinabove, the depressions 16, 18 have a trapezoidal shape in a planar view thereof, but the shapes of the depressions 16, 18 are not limited, and the depressions may have any shape. The depressions 16, 18 may be of a shape in which the width of the rear edge B1 in the impeller rotational direction is less than the width of the front edge F1. For example, the edge on the rear side in the impeller rotational direction may have an arched shape, and the edge on the front side may have a linear shape.

Second Embodiment

The second embodiment of the fuel pump of the present invention will be described below. The components that differ from those of the fuel pump 1 of the first embodiment will be mainly explained. FIG. 4 schematically shows a cross sectional view of depressions and a connection hole provided in the impeller. A plurality of depressions 16a is formed in an upper surface 17a of an impeller 10a of a fuel pump 1a, in the same manner as in the impeller 10 of the first embodiment (see also FIG. 2). Further, a plurality of depressions 18a is formed in a lower surface 19a of the impeller 10a. The depression 16a and depression 18a are formed in identical positions in the circumferential direction of the upper surface 17a and lower surface 19a. Each of the depressions 16a and corresponding one of depressions 18a are connected by a connection hole 11 at the front side of the depressions 16a, 18a in the impeller rotational direction.

As shown in FIG. 4, part of the fuel located between the upper surface 17a of the impeller 10a and the upper casing 20 is introduced into the depression 16a of the impeller upper surface 17a. The fuel introduced into the depression 16a flows along the bottom wall surface of the depression 16a in the direction opposite to the impeller rotational direction (counter-flow).

Further, part of the fuel located between the lower surface 19a of the impeller 10a and the lower casing 30 is introduced into the depression 18a of the impeller lower surface 19a. The fuel introduced into the depression 18a flows along the bottom wall surface of the depression 18a in the direction opposite to the impeller rotational direction (counter-flows).

Further, when a gap between the upper surface 17a of the impeller 10a and the upper casing 20 is wider than a gap between the lower surface 19a of the impeller 10a and the lower casing 30, part of the fuel located between the upper surface 17a of the impeller 10a and the upper casing 20 is introduced into the depression 18a through the connection hole 11 (solid line arrow shown in FIG. 4). The flows of fuel that are thus introduced merge in the depression 18a. In most cases the impeller 10a receives pressure from above that originates from the fuel with boosted pressure, and therefore in most cases the gap between the upper surface 17a of the impeller 10a and the upper casing 20 is wider.

When the gap between the lower surface 19a of the impeller 10a and the lower casing 30 is wider than the gap between the upper surface 17a of the impeller 10a and the upper casing 20, part of the fuel located between the lower surface 19a of the impeller 10a and the lower casing 30 is introduced into the depression 16a through the connection hole 11 (dotted line arrow shown in FIG. 4). Thus the flows of fuel that are introduced merge in the depression 16a.

In the depressions 16a, 18a, the deepest portion P is formed in the rear half thereof with respect to the impeller rotational direction. Therefore, the fuel introduced into the depression 16a flows from the deepest portion P of the depression 16a toward a second surface 27 of the upper casing 20. As a result, pressure is generated in the direction of separating the impeller 10a from the upper casing 20. Further, the fuel introduced into the depression 18a flows from the deepest portion P of the depression 18a toward a first surface 37 of the lower casing 30. As a result, pressure is generated in the direction of separating the impeller 10a from the lower casing 30. The height of the impeller 10a is adjusted to the height where the two pressures are balanced, and the impeller 10a is rotated in a state of being separated from the upper casing 20 and the lower casing 30. As a result, the impeller 10a is prevented from rotating in a state of being pressed against the upper casing 20 or the lower casing 30, and frictional force acting upon the impeller 10a when the impeller rotates is reduced.

In the present embodiment, for example, where depressions 18a are formed in the impeller lower surface 19a, the fuel on the side of the upper surface 17a of the impeller 10a is also introduced into the depressions 18a via the connection holes 11. Therefore, the amount of fuel introduced into the depressions 18a is increased and a comparatively large pressure can be generated in the direction of separating the impeller 10a from the lower casing 30.

In the present embodiment, a case is explained in which depressions 16a are formed in the upper surface 17a of the impeller 10a, and depressions 18a are also formed in the lower surface 19a of the impeller 10a, but it is also possible to form only the depressions 18a in the lower surface 19a.

Third Embodiment

The third embodiment of the fuel pump of the present invention will be described below. The components that differ from those of the fuel pump 1 of the first embodiment will be mainly explained. The fuel pump of the third embodiment has through holes of an almost wedge-like cross section that pass through the upper and lower surfaces of the impeller on the inside of the group of boost ports formed in the impeller.

FIG. 5 is a cross-sectional view of a through hole 13 provided in the impeller. A plurality of through holes 13 is formed repeatedly with a spacing in the circumferential direction in an impeller 10b of a fuel pump 1b. In the through hole 13, an opening S1 formed in an upper surface 17b is larger than an opening S2 formed in a lower surface 19b. An inner wall surface 13b on the rear side in the impeller rotational direction (arrow direction shown in FIG. 5) is perpendicular to the upper surface 17b of the impeller 10b and also perpendicular to the lower surface 19b of the impeller 10b. Further, an inner wall surface 13a on the front side is inclined forward from the lower surface 19b of the impeller 10b toward the upper surface 17b of the impeller 10b along the impeller rotational direction.

In the fuel pump, part of the fuel located between the upper surface 17b of the impeller 10b and the upper casing 20 is introduced from the larger opening S1 formed in the upper surface 17b of the impeller 10b into the through hole 13. The fuel introduced into the through hole 13 flows, while being pushed into a narrowing channel toward the smaller opening S2 in the lower surface 19b of the impeller 10b. The pushed fuel is further pushed, and flows toward the first surface 37 of the lower casing 30 via the smaller opening S2. Therefore, a pressure is generated in the direction of separating the lower surface 19b of the impeller 10b from the lower casing 30. As a result, the impeller 10b is prevented from rotating in a state of being pressed against the lower casing 30.

In the present embodiment, a case is explained in which the inner wall surface 13b on the rear side is perpendicular to the impeller upper surface 17b and lower surface 19b, but the present invention is not limited to this configuration. For example, the inner wall surface 13b on the rear side may be inclined forward from the lower surface 19b of the impeller 10b toward the upper surface 17b of the impeller 10b along the impeller rotational direction. At this case, an inclination angle of the inner wall surface 13a on the front side with respect to the lower surface 19b of the impeller 10b should be smaller than an inclination angle of the inner wall surface 13b on the rear side with respect to the lower surface 19b of the impeller 10b so that an opening of the through hole 13 formed in the upper surface 17b is larger than an opening formed in the lower surface 19b. A pressure is generated in the direction of separating the lower surface 19b of the impeller 10b from the lower casing 30.

Further, as in an impeller 10c shown in FIG. 6, combined holes 15 may be adopted. Each of the combined holes 15 is formed by a through hole 13c and a depression 18c formed on a lower surface 19c of the impeller 10c. In the combined hole 15, a deepest portion P of the depression 18c is connected to the through hole 13c. Viewing the cross section of the impeller 10c, the inner wall surface 15a on the front side of the combined hole 15 has a projecting part (convex portion W) that projects toward the inner wall surface 15b on the rear side. The inner wall surface 15b on the rear side of the combined hole 15 is formed flat from the upper surface 17c of the impeller 10c toward the lower surface 19c. The inner wall surface 15b on the rear side of the combined hole 15 is inclined so as to recede from the front side toward the rear side in the impeller rotational direction as it approaches to the lower surface 19c of the impeller 10c.

In such the fuel pump 1c, part of the fuel located between the upper surface 17c of the impeller 10c and the upper casing 20 is introduced into the combined hole 15 from an opening S3 formed in the upper surface 17c of the impeller 10c. The fuel introduced into the combined hole 15 flows toward an opening S4 in the lower surface 19c of the impeller 10c (toward the lower casing 30), while being pushed into the channel that is narrowed in the intermediate portion thereof. Part of the fuel located between the lower surface 19c of the impeller 10c and the lower casing 30 is introduced into a depression 18c formed in the lower surface 19c of the impeller 10c. This fuel flows inside the depression 18c along the bottom wall surface of the depression 18c in the direction opposite to the impeller rotational direction (counter-flows). The fuel introduced into the depression 18c does not flow via the through hole 13c from the apex point Q of the convex portion W (portion where the combined hole 15 is the narrowest) toward the upper surface 17c of the impeller 10c. This is because the flow from the upper surface 17c of the impeller 10c toward the opening S4 on the lower surface 19c of the impeller 10c is stronger than the flow from the lower surface 19c of the impeller 10c toward the opening S3 on the upper surface 17c. The flow of fuel in the combined hole 15 from the opening S3 toward the opening S4 and the flow of fuel in the depression 18c merge, and pressure is generated at the opening S4 in the direction of separating the impeller 10c from the lower casing 30. This pressure prevents the impeller 10c from rotating in a state of being pressed against the lower casing 30, and when the impeller 10c rotates, frictional force acting thereupon is reduced.

In the present embodiment of the fuel pump 1c, the apex point Q of the convex portion W is disposed below a central line M (shown by a dot-dash line in FIG. 6) in the thickness direction of the impeller 10c. However, as in an impeller 10c shown in FIG. 7, the present invention also includes a configuration in which the apex point Q of the convex portion W is disposed above the central line M. And the present invention also includes a configuration in which the apex point Q of the convex portion W is disposed on the central line M.

In the present embodiment of the fuel pump 1c, the inner wall surface 15a on the front side that is positioned on the lower surface 19c side of the convex portion W is inclined gentler than the inner wall surface 15a that is positioned on the upper surface 17c side of the convex portion W. However, as in an impeller 10c shown in FIG. 8, the present invention also includes a configuration in which the inner wall surface 15a on the front side that is positioned on the upper surface 17c side of the convex portion W is inclined gentler than the inner wall surface 15a that is positioned on the lower surface 19c side of the convex portion W.

Further, in the present embodiment, an example is explained in which the inner wall surface 15b on the rear side is inclined forward from the lower surface 19c of the impeller 10c toward the upper surface 17c of the impeller 10c along the impeller rotational direction, but as in an impeller 10c shown in FIG. 9, the inner wall surface 15b on the rear side may be perpendicular to the upper surface 17c and the lower surface 19c of the impeller.

Fourth Embodiment

The fourth embodiment of the fuel pump of the present invention will be described below. The components that differ from those of the fuel pump 1 of the first embodiment will be mainly explained. In the fuel pump of the fourth embodiment, a plurality of depressions is provided in the inner surface of the casing that faces the impeller.

FIG. 10 schematically shows a cross-sectional view of a pump unit of the fuel pump of the present embodiment. As shown in FIG. 10, a pump unit of a fuel pump 1d comprises an impeller 10d, an upper casing 20d, a lower casing 30d, and a motor shaft. In FIG. 10, parts are shown at a disassembled position.

In the impeller 10d that is different from the impeller 10 of the first embodiment, depressions for reducing frictional force acting upon the impeller when the impeller rotates are not provided. Other features of the impeller 10d are identical to those of the impeller 10 and explanation thereof is herein omitted.

As shown in FIG. 11, in a second surface 27d of the upper casing 20d, a second boost groove 22d is formed facing a plurality of boost ports 12 in a upper surface 17d of the impeller 10d. As shown in FIG. 12, in a first surface 37d of the lower casing 30d, a first boost groove 34d is formed facing a plurality of boost ports 14 in a lower surface 19d of the impeller 10d. In a plan view, the second boost groove 22d and the first boost groove 34d are formed to have an almost C-like shape from the upstream end to the downstream end along the rotational direction of the impeller 10d. A second boost path 42d is formed by a plurality of boost ports 12 provided in the upper surface 17d of the impeller 10d and the second boost groove 22d formed in the upper casing 20d, and a first boost path 44d is formed by a plurality of boost ports 14 provided in the lower surface 19d of the impeller 10d and the first boost groove 34d formed in the lower casing 30d. A fuel intake hole 32 (see also FIG. 12) is formed at the upstream end of the first boost groove 34d so as to be connected to the first boost groove 34d. A fuel discharge hole 24 (see also FIG. 11) is formed at the downstream end of the second boost groove 22d so as to be connected to the second boost groove 22d.

When the impeller 10d rotates between the upper casing 20d and the lower casing 30d, the fuel is sucked in from the fuel intake hole 32 into the pump unit and introduced into the first boost path 44d and the second boost path 42d. The fuel whose pressure increases while it flows in the first boost path 44d and the second boost path 42d is pumped out from the fuel discharge hole 24 into the motor unit. The fuel that is pumped out into the motor unit passes through the motor unit and is pumped out to the outside from a port (not shown in the figure) formed in the upper part of the fuel pump 1d.

FIG. 11 schematically shows a cross-sectional view along the XI-XI line of the pump unit shown in FIG. 10, wherein the upper casing 20d as shown in FIG. 10 is viewed from below. In the fuel pump 1d, eight depressions 26 are formed in a region on the inside of the second boost groove 22d of the upper casing 20d. The depressions 26 are formed repeatedly and equidistantly in the circumferential direction in the second surface 27d of the upper casing 20d. The depressions 26 are formed to have an almost trapezoidal shape in the plan view thereof. The depressions 26 are formed such that the width of the front edge F2 of the depression 26 in the impeller rotational direction (direction shown by an arrow in FIG. 11) is less than the width of the rear edge B2.

FIG. 12 schematically shows a cross-sectional view along the XII-XII line of the pump unit shown in FIG. 10, wherein the lower casing 30d as shown in FIG. 10 is viewed from above. In the fuel pump 1d, eight depressions 36 are formed in a region on the inside of the first boost groove 34d of the lower casing 30d. The depressions 36 are formed repeatedly and equidistantly in the circumferential direction in the first surface 37d of the lower casing 30d. The depressions 36 are formed to have an almost trapezoidal shape in the plan view thereof. The depressions 36 are formed such that the width of the front edge F2 of the depression 36 in the impeller rotational direction (direction shown by an arrow in FIG. 12) is less than the width of the rear edge B2.

FIG. 13 shows a cross-sectional view along the XIII-XIII line of the depressions 26, 36 shown in FIG. 11 and FIG. 12. The deepest portions P of the depressions 26, 36 are formed on the front side in the impeller rotational direction. The depressions 26, 36 are formed such that the cross-sectional area thereof decreases from the deepest portion P toward the front edge F2.

When the impeller 10d rotates, in a region between the upper surface 17d of the impeller 10d and the upper casing 20d where the second boost path 42d is not formed, and in a region between the lower surface 19d of the impeller 10d and the lower casing 30d where the first boost path 44d is not formed, the fuel is carried along by the impeller 10d rotating at a high rate and the fuel itself rotates, due to its viscosity, with a certain rate in the impeller rotational direction. Because the upper casing 20d and the lower casing 30d are fixed, part of the fuel located between the upper surface 17d of the impeller 10d and the upper casing 20d is introduced into the depression 26 formed in the inner surface 27d of the upper casing 20d, as shown in FIG. 13. The fuel introduced into the depression 26 flows in the same direction as the impeller rotational direction along the bottom wall surface of the depression 26. In the depression 26, the deepest portion P is formed in the front half thereof with respect to the rotational direction of the impeller 10d, and the fuel introduced into the depression 26 flows from the deepest portion P of the depression 26 toward the upper surface 17d of the impeller. As a result, pressure is generated in the direction of separating the impeller 10d from the upper casing 20d.

Further, part of the fuel located between the lower surface 19d of the impeller 10d and the lower casing 30d is introduced into the depression 36 formed in the inner surface 37d of the lower casing 30d, as shown in FIG. 13. The fuel introduced into the depression 36 flows in the same direction as the impeller rotational direction along the bottom wall surface of the depression 36. In the depression 36, the deepest portion P is formed in the front half thereof with respect to the rotational direction of the impeller 10d, and the fuel introduced into the depression 36 flows from the deepest portion P of the depression 36 toward the lower surface 19d of the impeller 10d. As a result, pressure is generated in the direction of separating the impeller 10d from the lower casing 30d.

The height of the impeller 10d is adjusted to the height where the two pressures are balanced, and the impeller 10d is rotated in a state of being separated from the upper casing 20d and the lower casing 30d. As a result, the impeller 10d is prevented from rotating in a state of being pressed against the upper casing 20d or the lower casing 30d, and frictional force acting upon the impeller 10d when the impeller rotates is reduced.

In the depressions 26, 36, a region from the deepest portion P toward the front edge F2 in the impeller rotational direction is a region where the aforementioned pressure is generated. In the depressions 26, 36 of the fuel pump 1d of the present embodiment, the figure of this region is requested to initiate only a flow of fuel from the deepest portion P toward the surfaces of the impeller 10d, so that this region is not required to be formed with any especially high dimensional accuracy and an allowable margin of error becomes large. Accordingly, a cost of forming the depressions 26, 28 can be reduced. As a result, the production cost of the fuel pump 1d can be reduced.

In the depressions 26, 36, the width of the rear edge B2 in the impeller rotational direction widens, thereby facilitating the introduction of fuel into the depressions 26, 36. Further, the width of the front edge F2 narrows and the cross-sectional area thereof decreases from the deepest portion P toward the front edge F2. Therefore, the fuel introduced into the depressions 26, 36 is pushed into the narrowing channel and flows under a comparatively strong force from the deepest portion P toward the impeller 10d. As a result, a comparatively large pressure can be generated in the direction of separating the impeller 10d from the casings.

Further, the depressions 26, 36 are formed on the inside of boost grooves 22d, 34d, these grooves being formed to have an almost C-like shape close to outer periphery. The region on the inside of the boost grooves 22d, 34d is wider than the region on the outside of the boost grooves 22d, 34d. Therefore, the depressions 26, 36 can be easily formed.

Further, pluralities of depressions 26, 36 are formed equidistantly in the circumferential direction in each casing. The pressures generated by the depressions 26 are added up to obtain a resultant pressure corresponding to the number of depressions 26 (eight in the present embodiment). The pressures generated by the depressions 36 are added up to obtain a resultant pressure corresponding to the number of depressions 36 (eight in the present embodiment). Therefore, a comparatively large pressure is generated in the direction of separating the impeller 10d from the upper casing 20d and the lower casing 30d.

In the present embodiment, a case is explained in which the depressions 26 are formed in the second surface 27d of the upper casing 20d, and the depressions 36 are formed in the first surface 37d of the lower casing 30d, but it is also possible to form only the depressions 36 in the first surface 37d of the lower casing 30d.

Further, in the embodiment described hereinabove, the depressions 26, 36 have a trapezoidal shape in a planar view thereof, but this shape of depressions 26, 36 is not limited, and the depressions may have any shape, provided that the width of the front edge F2 in the impeller rotational direction is less than the width of the rear edge B2. For example, the front edge F2 in the impeller rotational direction in a planar view thereof may have an arched shape, and the rear edge B2 may be formed to have a linear shape.

Further, in the above-described embodiments, fuel pumps were explained in which depressions were formed either in the impeller or in the casings, but the depressions may also be formed both in the impeller and in the casings.

Specific examples of the present invention are described above in detail, but these examples are merely illustrative and place no limitation on the scope of the patent claims. The technology described in the patent claims also encompasses various changes and modifications to the specific examples described above.

Furthermore, the technical elements explained in the present specification and drawings provide technical value and utility either independently or through various combinations. The present invention is not limited to the combinations described at the time the claims are filed. In addition, the purpose of the examples illustrated by the present specification and drawings is to satisfy multiple objectives simultaneously, and satisfying any one of those objectives gives technical value and utility to the present invention.

Claims

1. A fuel pump comprising a casing and an impeller, wherein: the impeller is substantially disk shaped having an upper surface and a lower surface, and is rotatable within the casing around a rotational axis;a group of concavities is formed in each of the upper and lower surfaces of the impeller, and is arranged on a circle around the rotational axis of the impeller;a first groove is formed in an inner surface of the casing, faces the group of concavities formed in the lower surface of the impeller, and extends from an upstream end to a downstream end along a rotational direction of the impeller;a second groove is formed in the inner surface of the casing, faces the group of concavities formed in the upper surface of the impeller, and extends from an upstream end to a downstream end along the rotational direction of the impeller;a fuel intake hole is formed in the casing and passes through the casing from the exterior of the casing to the upstream end of the first groove;a fuel discharge hole is formed in the casing and passes through the casing from the downstream end of the second groove to the exterior of the casing;a plurality of impeller depressions is formed in at least the lower surface of the impeller, located on at least one of the inside and the outside of the group of concavities, and arranged on a circle around the rotational axis of the impeller; andeach of the impeller depressions has its deepest portion in a rear half thereof with respect to the rotational direction of the impeller.

2. The fuel pump according to claim 1, wherein a width of the rear edge of each of the impeller depressions is narrower than a width of the front edge of each of the impeller depressions.

3. The fuel pump according to claim 1, wherein the plurality of impeller depressions is located on the inside of the group of concavities.

4. The fuel pump according to claim 1, wherein a plurality of through holes passing through the impeller from the upper surface to the lower surface is formed in the impeller; andeach of the through holes is connected with the front edge of each of the impeller depressions.

5. The fuel pump according to claim 1, wherein a plurality of casing depressions is formed in at least the inner surface of the casing that faces the lower surface of the impeller, located on at least one of the inside and the outside of the group of concavities formed in the lower surface of the impeller, and arranged on a circle around the rotational axis of the impeller; andeach of the casing depressions has its deepest portion in the front half thereof with respect to the rotational direction of the impeller.

6. The fuel pump according to claim 5, wherein a width of the front edge of each of the casing depressions is narrower than a width of the rear edge of each of the casing depressions.

7. A fuel pump comprising a casing and an impeller, wherein: the impeller is substantially disk shaped having an upper surface and a lower surface, and is rotatable within the casing around a rotational axis;a group of concavities is formed in each of the upper and lower surfaces of the impeller, and is arranged on a circle around the rotational axis of the impeller;a first groove is formed in an inner surface of the casing, faces the group of concavities formed in the lower surface of the impeller, and extends from an upstream end to a downstream end along a rotational direction of the impeller;a second groove is formed in the inner surface of the casing, faces the group of concavities formed in the upper surface of the impeller, and extends from an upstream end to a downstream end along the rotational direction of the impeller;a fuel intake hole is formed in the casing and passes through the casing from the exterior of the casing to the upstream end of the first groove;a fuel discharge hole is formed in the casing and passes through the casing from the downstream end of the second groove to the exterior of the casing;a plurality of casing depressions is formed in at least the inner surface of the casing that faces the lower surface of the impeller, located On at least one of the inside and the outside of the group of concavities formed in the lower surface of the impeller, and arranged on a circle around the rotational axis of the impeller; andeach of the casing depressions has its deepest portion in the front half thereof with respect to the rotational direction of the impeller.

8. A fuel pump comprising a casing and an impeller, wherein: the impeller is substantially disk shaped having an upper surface and a lower surface, and is rotatable within the casing around a rotational axis;a group of concavities is formed in each of the upper and lower surfaces of the impeller, and is arranged on a circle around the rotational axis of the impeller;a first groove is formed in an inner surface of the casing, faces the group of concavities formed in the lower surface of the impeller, and extends from an upstream end to a downstream end along a rotational direction of the impeller;a second groove is formed in the inner surface of the casing, faces the group of concavities formed in the upper surface of the impeller, and extends from an upstream end to a downstream end along the rotational direction of the impeller;a fuel intake hole is formed in the casing and passes through the casing from the exterior of the casing to the upstream end of the first groove;a fuel discharge hole is formed in the casing and passes through the casing from the downstream end of the second groove to the exterior of the casing;a plurality of through holes passing through the impeller from the upper surface to the lower surface thereof is formed in the impeller, located on at least one of the inside and the outside of the group of concavities formed in the impeller, and arranged on a circle around the rotational axis of the impeller;an opening of each of the through holes in the upper surface of the impeller is larger than an opening of each of the through holes in the lower surface of the impeller; andat least an inner wall surface on the front side of each of the through holes is inclined forward from the lower surface of the impeller toward the upper surface of the impeller along the rotational direction of the impeller.

9. The fuel pump according to claim 87 wherein an inner wall surface on the rear side of each of the through holes is also inclined forward from the lower surface of the impeller toward the upper surface of the impeller along the rotational direction of the impeller, andan inclination angle of the inner wall surface on the front side with respect to the lower surface of the impeller is smaller than an inclination angle of the inner wall surface on the rear side with respect to the lower surface of the impeller.

10. A fuel pump comprising a casing and an impeller, wherein: the impeller is substantially disk shaped having an upper surface and a lower surface, and is rotatable within the casing around a rotational axis;a group of concavities is formed in each of the upper and lower surfaces of the impeller, and is arranged on a circle around the rotational axis of the impeller;a first groove is formed in an inner surface of the casing, faces the group of concavities formed in the lower surface of the impeller, and extends from an upstream end to a downstream end along a rotational direction of the impeller;a second groove is formed in the inner surface of the casing, faces the group of concavities formed in the upper surface of the impeller, and extends from an upstream end to a downstream end along the rotational direction of the impeller;a fuel intake hole is formed in the casing and passes through the casing from the exterior of the casing to the upstream end of the first groove;a fuel discharge hole is formed in the casing and passes through the casing from the downstream end of the second groove to the exterior of the casing;a plurality of through holes passing through the impeller from the upper surface to the lower surface thereof is formed in the impeller, located on at least one of the inside and the outside of the group of concavities formed in the impeller, and arranged on a circle around the rotational axis of the impeller;an inner wall surface on the rear side of each of the through holes is almost perpendicular to the upper surface and the lower surface of the impeller or inclined forward from the lower surface of the impeller toward the upper surface of the impeller along the rotational direction of the impeller; andan inner wall surface on the front side of each of the through holes has a projecting part that projects toward the inner wall surface on the rear side.