JP2003269296A - Oil feeder for high pressure fuel pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reliably lubricate each part including the inside of a lifter 28 while suppressing an oil pressure fluctuation in an overall lubrication system. <P>SOLUTION: A pump plunger 26 is pressed vertically by a camshaft via the lifter 28 to pressurize fuel. The lifter 28 is shaped to a bottomed cylinder and slidably fitted in a guide hole 41 in a lifter guide 23. An inner wall surface of the guide hole 41 has oiling holes 51, which supply lubricating oil to a clearance 55 against the lifter 28. The oiling holes 51 are arranged in a pair on opposite sides out of a high bearing pressure region defined by the direction of rotation of the camshaft, and can supply lubricating oil to the high bearing pressure region without reducing a pressure bearing area. When the lifter 28 is in a bottom dead center position, a part of the oiling holes 51 is in a height position opened by a chamber portion 52, and a part of lubricating oil lubricates the inside of the lifter 28. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a high-pressure fuel pump in which a cam is driven by a rotary motion to drive a plunger,
In particular, the present invention relates to an oil supply device for lubricating a lifter that abuts on a cam and reciprocates.

[0002]

2. Description of the Related Art As a high-pressure fuel pump used in, for example, a high-pressure injection type internal combustion engine, there is known a high-pressure fuel pump configured to reciprocate a pump plunger through a bottomed cylindrical lifter by a cam provided on a camshaft. Has been.
In such a high-pressure fuel pump, an oil supply device that lubricates a lifter that slides inside the lifter guide is necessary. For example, Japanese Patent Laid-Open No. 8-49632 discloses a sliding surface between the lifter guide and the lifter. Disclosed is an oil supply device having a structure in which an oil supply hole is formed on an inner wall surface of a lifter guide so as to supply lubricating oil, and the oil supply hole is opened / closed by the lifter itself as a valve as the lifter moves up and down. There is.

[0003]

However, in the above-mentioned conventional structure, since the oil supply hole is completely opened at the top dead center or the bottom dead center of the lifter, the hydraulic system of the internal combustion engine as a whole is operated when the pump is operating. Oil pressure fluctuations will increase,
The amount of oil supplied to the other sliding portions may fluctuate, and seizure or wear may occur in the other sliding portions during the period when the amount of lubricating oil in the entire hydraulic system is small. To avoid this,
A flow rate control means such as an orifice is required, which causes an increase in cost.

Further, when the pump is operated, a predetermined surface pressure distribution is generated on the side surface of the lifter, which is determined by the relationship with the rotation direction of the cam. However, the apparatus of the above publication does not consider the relationship with this surface pressure. When the oil supply hole is arranged at a position where the surface pressure is high, the pressure receiving area is reduced by the area of the oil supply hole, and the surface pressure may be further increased. Further, the surface pressure becomes higher than the oil supply pressure, and the amount of oil supplied to the side surface of the lifter may be insufficient. As a result, seizure and wear easily occur on the lifter and the lifter guide.

[0005]

According to a first aspect of the present invention, as in claim 1, a pump plunger which is driven up and down to pressurize fuel, and a pump plunger which is provided so as to face a lower end of the pump plunger, High-pressure fuel provided with a bottomed cylindrical lifter fitted in a lifter guide so as to be slidable up and down, and a cam that abuts the bottom surface of the lifter and rotates to move the lifter up and down. In the pump,
An oil supply hole for supplying lubricating oil to the sliding surface between the lifter guide and the lifter is formed in the inner wall surface of the lifter guide, and the oil supply hole is formed when the lifter is at the bottom dead center. , A part of which is opened from the upper edge of the lifter and the rest is provided at a height position where it is covered by the outer peripheral surface of the lifter.

Thus, when the lifter reaches the bottom dead center, a part of the lubricating oil is supplied from the oil supply hole into the lifter to lubricate, for example, the contact portion between the lower end of the pump plunger and the lifter. Then, a part of the lubricating oil is supplied to the sliding surface between the lifter and the lifter guide, that is, the clearance therebetween. Since the oil supply hole is partially opened in this way, the decrease in hydraulic pressure is small.

Particularly, in the invention of claim 2, a chamfered portion is provided on the upper edge of the lifter, and at the bottom dead center, a part of the oil supply hole is opened through the chamfered portion. It has become. That is, the lubricating oil is supplied into the lifter through the chamfered portion.

According to the second aspect of the invention, as in claim 3, the oil supply hole is provided on the lower side. That is, an oil supply hole for supplying lubricating oil is formed in the inner wall surface of the lifter guide on the sliding surface between the lifter guide and the lifter, and the oil supply hole is located at the top dead center of the lifter. Sometimes, a part is opened from the lower edge of the lifter and the rest is provided at a height position where it is covered by the outer peripheral surface of the lifter.

As a result, when the lifter reaches the top dead center, a part of the lubricating oil is jetted downward from the oil supply hole to lubricate a contact portion between the cam and the lifter. Then, a part of the lubricating oil is supplied to the sliding surface between the lifter and the lifter guide, that is, the clearance therebetween. Since the oil supply hole is partially opened in this way, the decrease in hydraulic pressure is small.

The oil supply hole of the first invention and the oil supply hole of the second invention can be provided at the same time as in claim 4. That is, in the invention of claim 4, the upper oil supply hole and the lower oil supply port for supplying the lubricating oil to the sliding surface between the lifter guide and the lifter are respectively formed on the inner wall surface of the lifter guide. When the lifter is at the bottom dead center, the upper oil supply hole is provided at a height position where a part of the lifter is opened from the upper edge of the lifter and the rest is covered by the outer peripheral surface of the lifter. Is provided at a height position where a part of the lifter is opened from the lower edge of the lifter and the rest is covered by the outer peripheral surface of the lifter when the lifter is at the top dead center.

As a result, a part of the lubricating oil is supplied from the upper oil supply hole into the lifter to lubricate the contact portion between the lower end of the pump plunger and the lifter, and the lower oil supply hole to the lower part of the lifter. Lubricating oil is ejected to lubricate the contact area between the cam and lifter.

Preferably, the upper oil supply hole and the lower oil supply hole are arranged as in claim 5. That is, in the circumferential direction of the lifter guide, the lower oil supply hole is located on the side where the cam lobe initially contacts the lifter bottom surface along the cam rotation direction, and the upper oil supply hole is opposite to the lower oil supply hole. It is desirable to be located in.

This is because the tilt of the lifter due to the cam action is taken into consideration. Generally, the cam is arranged so as to press almost the center of the bottom surface of the lifter at the time of its peak lift. At the moment of initial contact with the bottom surface, a position deviated from the center of the lifter bottom surface to one side is pressed upward. Therefore, the lifter tilts in the lifter guide, the upper edge of the lifter approaches the opposite side in the circumferential direction from the initial contact point, and conversely, the lower edge of the lifter moves in the direction in which the initial contact point is located. Approach. Therefore, by disposing the upper oil supply hole at the position where the upper edge approaches and the lower oil supply hole at the position where the lower edge approaches, good lubrication can be performed for each.

Next, in a third aspect of the invention, as in claim 6 or claim 9, the lubrication holes for supplying lubricating oil to the sliding surface between the lifter guide and the lifter have inner wall surfaces of the lifter guide. This oiling hole is formed in the circumferential direction of the lifter guide, avoiding the high surface pressure area at the intersection of the cam rotating surface and the lifter guide inner wall surface, and opening at a position adjacent to this area. There is.

Since the lifter moves up and down by the rotating cam, the surface pressure becomes highest in the direction along the rotating surface of the cam, and the surface pressure is basically 0 in the direction orthogonal to the rotating surface of the cam. Become. Since the lifter is tilted as described above, high surface pressure regions are generated in two directions along the rotating surface of the cam. By opening the oil supply hole while avoiding the high surface pressure area, it is possible to avoid a decrease in the pressure receiving area in the high surface pressure area and thus an increase in the surface pressure.

Particularly, in the invention of claim 7, the oil supply hole is
The lifter guide is composed of a pair of oil supply holes which are arranged symmetrically with respect to the radial line of the lifter guide and are located at the same height.
Thereby, for example, it is possible to avoid the above-mentioned high surface pressure area and dispose the oil supply holes on both sides of the area, and it is possible to reliably supply oil to the high surface pressure area while avoiding the reduction of the pressure receiving area in the high surface pressure area. It will be possible.

According to the invention of claim 8, the pair of oil supply holes are located on both sides of a high surface pressure region which is an intersection of the cam rotating surface and the lifter guide inner wall surface, and the center of each opening. With respect to the radial line of the lifter guide passing through, they are formed so as to be inclined inward with respect to each other so as to be directed to the high surface pressure region side.

Since the oil supply hole is inclined with respect to the radius line of the lifter guide, the lubricating oil supplied to the clearance between the lifter guide and the lifter tends to flow along the inclination. Therefore, the lubricating oil is positively fed from both sides toward the high surface pressure area sandwiched by the pair of oil supply holes, and the high surface pressure area is reliably lubricated.

[0019]

According to the oil supply device for a high-pressure fuel pump according to the present invention, when the oil supply hole is opened at the top dead center or the bottom dead center of the lifter, only part of the oil supply hole is opened and the remaining part is opened. Is covered with the lifter, the hydraulic pressure fluctuation of the hydraulic system is relatively small, and adverse effects on other sliding parts can be avoided.

Further, by disposing the oil supply hole adjacent to the high surface pressure region while avoiding the high surface pressure region as in claim 6 or 9, it is possible to further reduce the surface pressure due to the reduction of the pressure receiving area in the high surface pressure region. Can be prevented, and reliable lubrication in a high surface pressure area can be achieved.

In particular, by disposing the upper and lower oil supply holes as in the fifth aspect, it is possible to reliably lubricate between the lifter and the lifter guide which receive the thrust force due to the rotation of the cam, and the local portion thereof. Wear and seizure can be prevented.

[0022]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings.

FIG. 1 shows a high pressure fuel pump 1 according to the present invention.
FIG. 2 shows a fuel system of a cylinder direct injection internal combustion engine in which the high-pressure fuel pump 1 is used.

In FIG. 2, 2 is a fuel tank, 3 is a low-pressure feed pump arranged in the fuel tank 2, 4
Indicates an electric motor for driving the feed pump 3, 5 indicates a fuel filter, and 6 indicates a low-pressure pressure regulator. The fuel discharged by the feed pump 3 is supplied to the low-pressure pressure regulator 6 at a predetermined pressure (for example, 0). The pressure is regulated to 3 to 0.5 MPa) and then introduced into the high pressure fuel pump 1 through the low pressure fuel passage 7. The high-pressure fuel pump 1 is mechanically driven by a camshaft 20 that interlocks with a crankshaft of an internal combustion engine, as will be described later, and has a high pressure (for example, 10 to 20 MPa at peak pressure) by the high-pressure fuel pump 1.
The pressurized fuel is supplied to the fuel injection valve 9 of each cylinder through the high-pressure fuel passage 8 and is injected into each cylinder according to the injection signal from the engine control module 11.
The fuel pressure in the high-pressure fuel passage 8 is detected by the fuel pressure sensor 10, and based on this, the high-pressure fuel pump 1
Is controlled so that the fuel pressure can be variably controlled to an arbitrary fuel pressure. A relief passage 12 from the high-pressure fuel passage 8 to the fuel tank 2 is provided together with a relief valve 13, and the low-pressure fuel leaked from the high-pressure fuel pump 1 returns to the fuel tank 2 via a return passage 14. ing.

The camshaft 20 is generally constructed so as to also serve as a camshaft of a valve train of an internal combustion engine, that is, a pair of pump driving shafts are provided at appropriate positions of the valve train camshaft 20. A cam lobe 21 is formed. Then, as shown in FIG. 1, the high-pressure fuel pump 1
Is attached to the upper part of the cylinder head 22, for example, so as to be above the camshaft 20. The high-pressure fuel pump 1 is provided with a lifter guide 23 that also serves as a pump mounting member, a pump housing 25 fixed to the lifter guide 23 via an oil seal 24, and a vertically movable unit at the center of the pump housing 25. The columnar pump plunger 26 and the electromagnetic control valve 27 for variably controlling the discharge amount as described above are provided.
The lower end 26a of the pump plunger 26, which protrudes downward from the pump housing 25, is pressed by the camshaft 20 via the lifter 28.
In addition, the upper end 26b pressurizes the fuel in the pressurizing chamber 29.
A seal member 31 seals between the pump plunger 26 and the pump housing 25. The pump housing 25 has a low-pressure fuel inlet 32 to which the low-pressure fuel passage 7 is connected, and a high-pressure fuel outlet 33 to which the high-pressure fuel passage 8 is connected. The control valve 27 is connected to the pressurizing chamber 29 via a valve body 27a, and the high-pressure fuel outlet 33 is connected to the pressurizing chamber 29 via a check valve 34. The electromagnetic control valve 27 variably controls the discharge amount discharged from the pressurizing chamber 29 to the high pressure fuel outlet 33 according to the stroke of the pump plunger 26 by controlling the opening / closing timing of the valve body 27a. .

The lifter 28 has a cylindrical side wall portion 28a.
And a bottom wall portion 28b at the lower end of the lifter guide 23 have a bottomed cylindrical shape and are slidably and rotatably fitted in the cylindrical guide hole 41 of the lifter guide 23. This lifter 28
Are arranged concentrically with respect to the pump plunger 26, and the lower end 26a of the pump plunger 26 is in contact with the inner side surface, that is, the upper surface of the bottom wall portion 28b. Further, the return spring 42 arranged on the inner peripheral side constantly urges the camshaft 20 toward the bottom wall portion 28b.
The bottom surface, that is, the lower surface, of the above is in contact with the cam lobe 21. Therefore, this lifter 28 is
By the cam action of the cam lobe 21 accompanying the rotation of the above, the pump plunger 26 reciprocates integrally with this. In addition, at the maximum lift of the cam lobe 21,
When viewed from the direction of FIG. 2, the center line of the cam shaft 20 and the center line of the lifter 28 are orthogonal to each other so that the cam lobe 21 presses the center of the lifter 28.

The space between the lifter 28 and the lifter guide 23 is lubricated by the lubricating oil of the internal combustion engine supplied through the lubricating oil passage 43 provided inside the cylinder head 22 and the lifter guide 23.

3 and 4 show details of the lifter 28 and the lubrication mechanism thereof. 5 and 6 are for explaining the behavior of the lifter 28 during the operation of the pump and the surface pressure generated thereby, in which the camshaft 20 rotates in the direction of the arrow ω as shown in FIG. Then, the initial contact point C of the cam lobe 21 on the bottom surface of the lifter 28 is on the right side of the drawing with respect to the center of the lifter 28. When the pressurization of fuel by the pump plunger 26 is started, the pump load F1 acts along the center line of the pump plunger 26, and the reaction force F2 of the pump load F1 acts at point C, as shown in the figure. However, since they are offset from each other, the lifter 28 tilts in the counterclockwise direction as shown. Furthermore, the camshaft 20
A pressing load F3 that urges the lifter 28 to one side in the horizontal direction acts along the rotation direction ω of. As a result, the lifter 28 strongly presses against the inner peripheral surface of the guide hole 41 of the lifter guide 23 in two radial directions indicated by A and B in the figure. The upper part of the lifter 28 contacts the A part, and the lower part of the lifter 28 contacts the B part.
Since the pressing load F3 is applied, the surface pressure becomes higher than that at the portion B, that is, the highest surface pressure is generated in the circumferential direction. FIG. 6 shows the distribution of the surface pressure along the circumferential direction of the lifter 28. The spread in the radial direction shows the magnitude of the surface pressure, but as shown in the figure, the surface pressure is generated. There are only two points, A and B, along the surface of rotation of the cam lobe 21, and the surface pressure is 0 in a region other than this, for example, in the direction orthogonal to the surface of rotation. The point A'in the figure is the maximum surface pressure generation point.

The first embodiment shown in FIGS. 3 and 4 mainly considers the lubrication in the above-mentioned section A.
As shown in FIG. 5, a pair of oil supply holes 51, which are the outlets of the lubricating oil passage 43, are formed on both sides of the portion A, which is a high surface pressure region, so as to sandwich it. More specifically, the point where the surface pressure of the A portion becomes 0 (point D) has a circular opening so as to be included in the opening diameter, and the direction along the radius line r of the guide hole 41. Is formed in. These two oil supply holes 51 are formed at the same height position in the axial direction of the guide hole 41, and particularly when the lifter 28 is at the bottom dead center position as shown in FIG. The tip end opening of the oil supply hole 51 is arranged at a height position where it is partially opened.
Specifically, a chamfered portion 52 formed of a tapered surface is formed on the upper edge of the side wall portion 28a of the lifter 28, and when the lifter 28 is at the bottom dead center position, the vertical surface of the side wall portion 28a and this chamfered portion. The height position of the oil supply hole 51 is set such that a boundary line 53 with the oil supply hole 52 is at a position intersecting with the tip end opening of the oil supply hole 51, for example, a position passing through the center of the tip end opening. As shown in FIG. 3, a plurality of communication holes 54 are formed through the bottom wall portion 28b of the lifter 28.

In the above-mentioned structure, the lubricating oil pressurized by the oil pump (not shown) of the internal combustion engine is constantly discharged from the oil supply hole 51, mainly between the lifter 28 and the guide hole 41. It is supplied to the clearance 55. Figure 4
As shown in FIG. 3, since the lubricating oil is supplied from the pair of oil supply holes 51 to both sides of the A part, which is a high surface pressure region, the vicinity of the A part can be surely lubricated, and the oil supply hole 51 is not Since it is not opened in the, it does not cause an increase in the surface pressure. When the lifter 28 reaches the bottom dead center position, the upper portion of the oil supply hole 51 is partially opened as shown in FIG. Therefore, although some of the lubricating oil flows through the clearance 55, some of the lubricating oil flows over the side wall portion 28a from the chamfered portion 52 and flows into the inside of the lifter 28, as shown by the arrow. As a result, the contact portion between the lower end 26a of the pump plunger 26 and the bottom wall portion 28b of the lifter 28, the return spring 42, and the like are lubricated. Further, the lubricating oil inside the lifter 28 drips downward through the communication hole 54, whereby
The contact portion between the camshaft 20 and the lifter 28 is lubricated. Since only part of the oil supply hole 51 is opened even at the bottom dead center position of the lifter 28, the lubricating oil passage 4
The decrease in hydraulic pressure on the 3 side is relatively small, and has little effect on the lubricating performance of other sliding parts. That is, it is possible to surely lubricate each part including the inside of the lifter 28 while suppressing the hydraulic pressure fluctuation in the entire lubrication system. Further, in the above-described embodiment, since the oil supply hole 51 is opened and closed via the chamfered portion 52, the oil supply hole 51 can be opened and closed without excessively shortening the axial length of the side wall portion 28a, and the lifter 28 is opened. The opening and closing of the oil supply hole 51 by the lifter 28 can be realized without impairing the stable reciprocating movement of

Next, FIG. 7 shows a second embodiment in which the forming directions of the pair of oil supply holes 51 are changed. In this embodiment, as shown in the drawing, each oil supply hole 51 is inwardly directed toward the radial line r of the guide hole 41 passing through the opening center of the oil supply hole 51 so that the oil supply holes 51 are directed to the high surface pressure region, that is, the A portion. It is formed with an inclination. It is to be noted that each of the oil supply holes 51 is opened at a position including a point (point D) where the surface pressure becomes 0, as in the above-described embodiment. Since the oil supply hole 51 is inclined in this manner, the lubricating oil supplied to the clearance 55 between the guide hole 41 and the lifter 28 is guided toward the high surface pressure region, and the high surface pressure is obtained. The area, that is, the portion A, is more positively lubricated.

Next, FIG. 8 shows a third embodiment in which, in addition to the upper oil supply hole 51 arranged in the A section as described above, the lower oil supply hole 56 is added to the B section described above. There is. Like the upper oil supply hole 51, the lower oil supply hole 56 is composed of a pair of oil supply holes 56 symmetrically arranged with the portion B interposed therebetween.
Moreover, it is opened at a position where the surface pressure at the B portion becomes zero.
Then, with respect to the axial direction of the guide hole 41, the lifter 28
Is located at the top dead center position, the front end opening of each oil supply hole 56 is arranged at a height position that is partially opened by the lower edge of the lifter 28.

Therefore, in this structure, the pair of oil supply holes 56 is also provided in the B portion, which is the high surface pressure region having the next highest surface pressure after the A portion.
Ensures reliable lubrication, and can prevent localized wear and seizure. Further, when the lifter 28 reaches the top dead center position, a part of the oil supply hole 56 is opened and the cam lobe 21
Lubricating oil is sprayed toward. Therefore, Cam Rob 2
It is possible to lubricate between 1 and the lifter 28 more reliably. At this time, since only part of the oil supply hole 56 is opened, the decrease in hydraulic pressure is small.

[Brief description of drawings]

FIG. 1 is a structural explanatory view of a high-pressure fuel pump according to the present invention.

FIG. 2 is an explanatory diagram of an entire fuel system in which this high-pressure fuel pump is used.

FIG. 3 is a cross-sectional view of the essential parts showing the first embodiment of the present invention.

4 is a cross-sectional view taken along the line EE of FIG.

FIG. 5 is an explanatory diagram showing the relationship between the behavior of the lifter and the force when the pump is operating.

FIG. 6 is an explanatory diagram showing a surface pressure distribution between a lifter and a guide hole.

FIG. 7 is a sectional view similar to FIG. 4, showing a second embodiment.

FIG. 8 is a sectional view similar to FIG. 3 showing a third embodiment.

[Explanation of symbols]

1 ... High-pressure fuel pump 20 ... Camshaft 21 ... Kamlob 23 ... Lifter guide 26 ... Pump Plunger 28 ... Lifter 41 ... Guide hole 51, 56 ... Refueling hole 52 ... Chamfer

Claims (9)

[Claims] 1. A pump plunger that is driven up and down to pressurize fuel, and a bottomed cylindrical shape that is provided so as to face the lower end of the pump plunger and that is vertically slidably fitted in a lifter guide. And a cam that abuts on the bottom surface of the lifter and rotates so as to move the lifter up and down, in a sliding surface between the lifter guide and the lifter. An oil supply hole for supplying lubricating oil is formed on the inner wall surface of the lifter guide.When the lifter is at the bottom dead center, a part of the oil supply hole is released from the upper edge of the lifter and the remaining part is left. An oil supply device for a high-pressure fuel pump, which is provided at a height position where it is covered by the outer peripheral surface of the lifter. 2. The chamfered portion is provided on the upper edge of the lifter, and a part of the oil supply hole is opened through the chamfered portion at the bottom dead center. The high-pressure fuel pump described in 1. 3. A pump plunger that is driven up and down to pressurize fuel, and a bottomed cylindrical shape that is provided so as to face the lower end of the pump plunger and that is vertically slidably fitted in a lifter guide. And a cam that abuts on the bottom surface of the lifter and rotates so as to move the lifter up and down, in a sliding surface between the lifter guide and the lifter. An oil supply hole for supplying lubricating oil is formed in the inner wall surface of the lifter guide.When the lifter is at the top dead center, a part of the oil supply hole is released from the lower edge of the lifter and the remaining part is left. An oil supply device for a high-pressure fuel pump, which is provided at a height position where it is covered by the outer peripheral surface of the lifter. 4. A pump plunger that is driven up and down to pressurize fuel, and a bottomed cylindrical shape that is provided so as to face a lower end of the pump plunger and that is vertically slidably fitted in a lifter guide. And a cam that abuts on the bottom surface of the lifter and rotates so as to move the lifter up and down, in a sliding surface between the lifter guide and the lifter. An upper oil supply hole for supplying lubricating oil and a lower oil supply opening are formed respectively on the inner wall surface of the lifter guide, and the upper oil supply hole is partially formed when the lifter is at the bottom dead center. It is opened from the upper edge of the lifter and is provided at a height position where the rest is covered by the outer peripheral surface of the lifter, and the lower oil supply hole is partially opened from the lower edge of the lifter when the lifter is at the top dead center. With Part refueling apparatus of the high pressure fuel pump, characterized in that provided at a height position covered by the lifter outer peripheral surface. 5. The lower oil supply hole in the circumferential direction of the lifter guide is located on the side where the cam lobe initially contacts the lifter bottom surface along the cam rotation direction, and the upper oil supply hole is the same as the lower oil supply hole. Is located on the opposite side, and the refueling device for the high-pressure fuel pump according to claim 4, wherein 6. The oil supply hole is opened in a position adjacent to a high surface pressure area at an intersection of a cam rotating surface and an inner wall surface of the lifter guide in a circumferential direction of the lifter guide. The high-pressure fuel pump according to any one of claims 1 to 5, characterized in that. 7. The oil supply hole is composed of a pair of oil supply holes which are arranged symmetrically with respect to the radial line of the lifter guide and which are located at the same height.
The high-pressure fuel pump according to any one of to 6. 8. A radius of the lifter guide located on both sides of the high surface pressure area, which is an intersection of the cam rotation surface and the inner wall surface of the lifter guide, and passing through the respective opening centers. The high-pressure fuel pump according to any one of claims 1 to 7, wherein the high-pressure fuel pump is formed so as to be inclined inward with respect to a line so as to be directed toward the high surface pressure region side. 9. A pump plunger that is driven up and down to pressurize fuel, and a bottomed cylindrical shape that is provided so as to face the lower end of the pump plunger and that is vertically slidably fitted in a lifter guide. And a cam that abuts on the bottom surface of the lifter and rotates so as to move the lifter up and down, in a sliding surface between the lifter guide and the lifter. An oil supply hole for supplying lubricating oil is formed on the inner wall surface of the lifter guide, and this oil supply hole is a high surface pressure area at the intersection of the cam rotation surface and the lifter guide inner wall surface in the circumferential direction of the lifter guide. A fuel supply device for a high-pressure fuel pump, characterized in that the fuel supply device is opened at a position adjacent to and avoiding the above.