JP2008291764A - High pressure fuel pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a high pressure fuel pump improved in lubricity of a cam/roller contact part or the like without using oil jet. <P>SOLUTION: The high pressure fuel pump 1 is provided with a plunger 23, a compression chamber 22, a lifter 51, and a helical compression spring 27. The plunger 23 is inserted to a cylinder 21 for reciprocating sliding, and the compression chamber 22 is partitioned by the cylinder 21 and the plunger 23. The lifter 51 is arranged in a lifter guide 52 for reciprocating sliding, and the helical compression spring 27 presses the lifter 51 to the outer peripheral surface side of the cam 111. The high pressure fuel pump 1 is provided with an oil pathway R1 and a plate 61. The oil pathway R1 is used for discharging the lubricating oil in an oil chamber 54 surrounded by the lifter 51 and the lifter guide 52 to the outside accompanying the reciprocation of the lifter 51 by rotation of the cam 111. An inclined surface 61b is formed on the plate 61, and the inclined surface 61b guides the lubricating oil discharged from the oil pathway R1 to the cam/roller contact part P1 between the cam 111 and the roller 53 which is brought into contact with the outer peripheral surface of the cam 111. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a high-pressure fuel pump that supplies high-pressure fuel to an injector (fuel injection valve) in an internal combustion engine such as an in-cylinder direct injection engine.

  In-cylinder direct injection engines mounted on automobiles and the like, fuel injection must be performed with the fuel pressure higher than the pressure in the combustion chamber. Therefore, the fuel sent from the fuel tank is added by a high-pressure fuel pump. The pressure is supplied to the injector.

  As a fuel supply system for a direct injection type in-cylinder engine, for example, a feed pump that feeds fuel from a fuel tank, a high-pressure fuel pump that pressurizes the fuel sent by the feed pump, and a fuel that is pressurized by the high-pressure fuel pump There is known one that includes a delivery pipe for storing the fuel and an injector arranged for each cylinder of the engine. The high-pressure fuel stored in the delivery pipe by the valve opening control of each injector is directly injected from the injector into the fuel chamber.

  As a high-pressure fuel pump used in such a fuel supply system, for example, a plunger inserted in a cylinder so as to be reciprocally slidable, a pressurizing chamber defined by the cylinder and the plunger, a lifter guide Some of them include a lifter connected to a plunger and a compression coil spring that presses the lifter toward the outer peripheral surface of the cam. When the cam nose is retracted from the lifter as the cam rotates, the plunger moves to increase the volume of the pressurizing chamber (intake stroke), and the cam nose of the cam pushes the lifter, and the plunger moves accordingly. In this structure, the fuel is pressurized and supplied to the delivery pipe or the like by repeating the process of reducing the volume of the pressurizing chamber (pressurizing process).

By the way, in the high-pressure fuel pump having the structure as described above, the outer peripheral surface of the cam is in contact with the bottom surface of the lifter or the outer peripheral surface of the roller rotatably supported by the lifter. It is desirable to lubricate by supplying lubricating oil (oil) to the bottom surface or the contact portion with the outer peripheral surface of the roller. For this reason, conventionally, in order to improve the lubricity at the contact portion, an oil jet that injects the lubricant oil toward the contact portion is provided to actively supply the lubricant. As shown in FIG. 1, measures are taken such as providing a hole in the bottom surface of the lifter and supplying lubricating oil inside the lifter through the hole.
JP 2003-269296 A

  However, the conventional measures described above for the high-pressure fuel pump have the following problems.

  First, an oil jet is separately required as a measure for providing an oil jet. Along with this, a lubricating oil supply path to the oil jet must be secured. However, disposing the lubricating oil supply path in the cylinder head having a complicated shape increases the labor of processing and its design is difficult. In addition, depending on the installation location of the oil jet, the lubricating oil supply path from the hydraulic pressure source becomes long, and the hydraulic pressure decreases greatly. For this reason, in order to inject lubricating oil to the contact portion (cam / lifter contact portion or cam / roller contact portion) by an oil jet, the hydraulic pressure of the hydraulic source must be set high.

  Next, as a countermeasure for providing a hole on the bottom surface of the lifter, in the case of a configuration in which the roller is supported by the lifter, the lubricating oil is not directly supplied to the outer peripheral surface of the roller other than the contact portion. become. Therefore, the lubricity is inferior compared with the case where the contact portion is directly lubricated. Further, as the roller rotates, there is a risk that the lubricating oil adhering to the centrifugal force will be splashed away.

  The present invention has been made in view of such problems, and an object thereof is to provide a high-pressure fuel pump capable of improving the lubricity of the contact portion without using an oil jet. .

  In the present invention, means for solving the above-described problems are configured as follows. That is, the present invention is a high-pressure fuel pump, a plunger inserted in a cylinder so as to be reciprocally slidable, a pressure chamber defined by the cylinder and the plunger, and reciprocally slid in a lifter guide A lifter arranged in a possible manner and a compression coil spring that presses the lifter toward the outer peripheral surface of the cam. The plunger moves reciprocally as the cam rotates, and the plunger By reciprocating, the fuel suction into the pressurizing chamber and the pressurization / discharge of the fuel in the pressurizing chamber are repeated.

  In such a high-pressure fuel pump, an oil passage for discharging the lubricating oil in the space surrounded by the lifter and the lifter guide to the outside along with the reciprocation of the lifter by the rotation of the cam, The lubricating oil discharged from the oil passage is provided with guide means for guiding the lubricating oil to a contact portion between the cam and a member in contact with the outer peripheral surface of the cam.

  Here, examples of the member in contact with the outer peripheral surface of the cam include a lifter and a roller rotatably supported by the lifter. In other words, the present invention can be applied to a high pressure fuel pump having a so-called direct hitting lifter structure in which the cam and the lifter are in contact, and also to a high pressure fuel pump having a so-called roller lifter structure in which the cam and the roller are in contact. Is possible.

  According to the above configuration, when the plunger moves in the direction in which the volume of the pressurizing chamber contracts due to the rotation of the cam (pressurization stroke), the space surrounded by the lifter and the lifter guide as the lifter moves. As a result, the lubricating oil in the space is discharged to the outside through the oil passage. Thus, the lubricating oil is forcibly discharged through the oil passage by the pump action accompanying the reciprocating motion of the lifter.

  Since the lubricating oil discharged through the oil passage is guided by the guide means to the contact portion between the cam and the member in contact with the outer peripheral surface of the cam, the contact portion can be directly lubricated. In addition, since the lubricating oil is positively fed to the contact portion by utilizing the pump action accompanying the reciprocating motion of the lifter, the lubricating oil has a certain momentum rather than just flowing down along the guide means. In the state, and in a state where the direction is restricted to some extent by the guide means, the light is discharged toward the contact portion. Thereby, lubricating oil can be supplied to the contact part sufficiently and efficiently. Accordingly, the lubricity at the contact portion can be improved without using an oil jet, and friction can be reduced.

  Here, the oil passage can be provided between the lifter and the lifter guide, and as a specific configuration thereof, for example, a recess formed in at least one of the lifter and the lifter guide can be used. .

  Further, as a specific configuration of the guide means, for example, it can be provided on the downstream side of the lubricating oil discharge direction of the oil passage, and can be an inclined surface inclined with respect to the lubricating oil discharge direction. It is preferable to set the inclination angle of the inclined surface to an angle that can guide the lubricating oil discharged from the oil passage to the contact portion.

  The inclined surface can be formed on a part of the lifter guide or a member provided integrally with the lifter guide. Further, when the high-pressure fuel pump has a roller lifter configuration, the inclined surface can be formed as a member for preventing rotation of the lifter supporting the roller around the axis.

  Here, when the high-pressure fuel pump has a roller lifter structure, it is preferable to provide second guide means for guiding the lubricating oil discharged from the oil passage toward the bearing portion of the roller. As a specific configuration of the second guide means, for example, a second inclined surface provided on the downstream side in the lubricating oil discharge direction of the oil passage and inclined with respect to the lubricating oil discharge direction can be used. In this case, it is preferable that the inclination angle of the second inclined surface is set to an angle that can guide the lubricating oil discharged from the oil passage to the bearing portion of the roller.

  According to the above configuration, the lubricating oil can be supplied not only to the contact portion between the cam and the roller but also to the bearing portion of the roller. As a result, the bearing portion of the roller can be directly lubricated, which is effective. Further, since the lubricating oil is positively fed to the contact portion between the cam and the roller and the bearing portion of the roller by utilizing the pump action accompanying the reciprocating motion of the lifter, the lubricating oil flows along the second guide means. Rather than simply flowing down, it is released toward the contact portion between the cam and the roller and the bearing portion of the roller with a certain degree of momentum and with a certain degree of direction being restricted by the second guide means. The Thus, the lubricating oil can be sufficiently and efficiently supplied to the contact portion between the cam and the roller and the bearing portion of the roller. Therefore, the lubricity of the contact portion between the cam and the roller and the bearing portion of the roller can be improved without using an oil jet, and friction can be reduced.

  Then, the inclined surface and the second inclined surface are prevented from rotating around a part of the lifter guide, a member provided integrally with the lifter guide, or the axis of the lifter supporting the roller. It is possible to form in the member for. The second inclined surface is preferably set at a different inclination angle and a different height position with respect to the inclined surface.

  According to the present invention, when the plunger moves in a direction in which the volume of the pressurizing chamber contracts due to the rotation of the cam, the pressure in the space surrounded by the lifter and the lifter guide increases with the movement of the lifter. As a result, the lubricating oil in the space is discharged to the outside through the oil passage. Thus, the lubricating oil is forcibly discharged through the oil passage by the pump action accompanying the reciprocating motion of the lifter.

  Since the lubricating oil discharged through the oil passage is guided by the guide means to the contact portion between the cam and the member in contact with the outer peripheral surface of the cam, the contact portion can be directly lubricated. In addition, since the lubricating oil is positively fed to the contact portion by utilizing the pump action accompanying the reciprocating motion of the lifter, the lubricating oil has a certain momentum rather than just flowing down along the guide means. In the state, and in a state where the direction is restricted to some extent by the guide means, the light is discharged toward the contact portion. Thereby, lubricating oil can be supplied to the contact part sufficiently and efficiently. Accordingly, the lubricity at the contact portion can be improved without using an oil jet, and friction can be reduced.

  The best mode for carrying out the present invention will be described with reference to the accompanying drawings.

  Below, the case where this invention is applied to the high pressure fuel pump used for the cylinder direct injection type multi-cylinder (for example, 6 cylinders) gasoline engine mounted in a motor vehicle is demonstrated.

-Fuel supply device 100-
Before describing the specific configuration of the high-pressure fuel pump, the schematic configuration of the fuel supply apparatus 100 to which the high-pressure pump is applied will be described with reference to FIG.

  A fuel supply apparatus 100 illustrated in FIG. 1 includes a feed pump 102 that feeds fuel from a fuel tank 101, and pressurizes the fuel fed by the feed pump 102 to inject the injectors 4, 4,. And a high-pressure fuel pump 1 that discharges toward

  The high-pressure fuel pump 1 includes a cylinder 21, a plunger 23, a pressurizing chamber 22, and an electromagnetic spill valve 30.

  The plunger 23 is driven by the rotation of a cam 111 attached to the intake camshaft 110 of the engine, and reciprocates in the cylinder 21. By the reciprocating movement of the plunger 23, the volume of the pressurizing chamber 22 is enlarged or reduced. In this embodiment, three cam peaks (cam noses) 112, 112, 112 are formed in the cam 111 with an angular interval of 120 ° around the rotation axis of the intake camshaft 110. The plunger 23 is pushed up by the three cam noses 112, 112, 112, and the plunger 23 moves in the cylinder 21.

  In this embodiment, since the engine is a 6-cylinder type, during each cycle of the engine, that is, while the crankshaft rotates twice, each of the injectors 4 provided for each cylinder once, for a total of 6 times. Fuel injection will be performed. In addition, for each cycle of the engine, the intake camshaft 110 rotates once, and the discharge operation from the high-pressure fuel pump 1 is performed three times.

  The pressurizing chamber 22 is partitioned by a plunger 23 and a cylinder 21. The pressurizing chamber 22 communicates with the feed pump 102 via the low pressure fuel pipe 104. The pressurizing chamber 22 communicates with a delivery pipe (pressure accumulating vessel) 106 through a high-pressure fuel pipe 105.

  Six injectors 4, 4,... Are connected to the delivery pipe. The delivery pipe 106 is provided with a fuel pressure sensor 161 that detects the fuel pressure (actual fuel pressure) inside the pipe. A return pipe 172 is connected to the delivery pipe 106 via a relief valve 171.

  The relief valve 171 opens when the fuel pressure in the delivery pipe 106 exceeds a predetermined pressure (for example, 13 MPa). By opening the relief valve 171, a part of the fuel stored in the delivery pipe 106 is returned to the fuel tank 101 via the return pipe 172. Thereby, an excessive increase in the fuel pressure in the delivery pipe 106 is prevented.

  Further, the return pipe 172 and the high-pressure fuel pump 1 are connected by a fuel discharge pipe 108 (shown by a broken line in FIG. 1), and the fuel leaked from the gap between the plunger 23 and the cylinder 21 of the high-pressure fuel pump 1 is sealed. The fuel is stored in the fuel storage chamber 6 at the top of the unit 5 and then returned to the fuel discharge pipe 108 connected to the fuel storage chamber 6.

  The low pressure fuel pipe 104 is provided with a filter 141 and a pressure regulator 142. The pressure regulator 142 returns the fuel in the low-pressure fuel pipe 104 to the fuel tank 101 when the fuel pressure in the low-pressure fuel pipe 104 exceeds a predetermined pressure (for example, 0.4 MPa). The fuel pressure is maintained below a predetermined pressure.

  Further, a pulsation damper 107 is provided in the low pressure fuel pipe 104, and the pulsation damper 107 suppresses fuel pressure pulsation in the low pressure fuel pipe 104 when the high pressure fuel pump 1 is operated. . Further, the high pressure fuel pipe 105 is provided with a check valve 151 for preventing the fuel discharged from the high pressure fuel pump 1 from flowing backward.

  The high-pressure fuel pump 1 is provided with an electromagnetic spill valve 30 for communicating or blocking between the low-pressure fuel pipe 104 and the pressurizing chamber 22. The electromagnetic spill valve 30 includes an electromagnetic solenoid 31 and opens and closes by controlling energization of the electromagnetic solenoid 31.

  Next, the opening / closing operation of the electromagnetic spill valve 30 will be described with reference to FIG.

  First, when the energization of the electromagnetic solenoid 31 is stopped, the electromagnetic spill valve 30 is opened by the elastic force of the compression coil spring 37, and the low pressure fuel pipe 104 and the pressurizing chamber 22 are in communication with each other. In this state, when the cam 111 rotates together with the intake camshaft 110 and the plunger 23 moves in the direction in which the volume of the pressurizing chamber 22 increases (in the direction in which the plunger 23 descends in FIG. 1) (intake stroke). The fuel delivered from the feed pump 102 is sucked into the pressurizing chamber 22 through the low-pressure fuel pipe 104.

  On the other hand, when the cam 111 rotates together with the intake camshaft 110 and the plunger 23 moves in the direction in which the volume of the pressurizing chamber 22 contracts (the direction in which the plunger 23 rises in FIG. 1) (pressurization stroke), electromagnetic When the electromagnetic spill valve 30 is closed against the elastic force of the compression coil spring 37 by energizing the solenoid 31, the low-pressure fuel pipe 104 and the pressurizing chamber 22 are disconnected, and the fuel pressure in the pressurizing chamber 22 is blocked. When the valve reaches a predetermined value, the check valve 40 is opened, and high-pressure fuel is discharged toward the delivery pipe 106 through the high-pressure fuel pipe 105.

  The fuel discharge amount in the high-pressure fuel pump 1 is adjusted by controlling the closing period of the electromagnetic spill valve 30 in the pressurization stroke. That is, if the closing time of the electromagnetic spill valve 30 is advanced and the closing period is lengthened, the fuel discharge amount increases. If the closing start time of the electromagnetic spill valve 30 is delayed and the closing period is shortened, the fuel discharge amount decreases. To come. In this manner, the fuel pressure in the delivery pipe 106 is controlled by adjusting the fuel discharge amount of the high-pressure fuel pump 1.

  Here, the pump duty DT which is a control amount for controlling the fuel discharge amount of the high-pressure fuel pump 1 (the valve closing start timing of the electromagnetic spill valve 30) will be described. This pump duty DT varies between 0% and 100%, and is a value related to the cam angle of the cam 111 of the intake camshaft 110 corresponding to the valve closing period of the electromagnetic spill valve 30.

  Specifically, with respect to the cam angle of the cam 111, as shown in FIG. 2, the cam angle (maximum cam angle) corresponding to the maximum valve closing period of the electromagnetic spill valve 30 is θ0, and the target fuel pressure in the maximum valve closing period is set. If the cam angle (target cam angle) corresponding to is θ, the pump duty DT is expressed as a ratio of the target cam angle θ to the maximum cam angle θ0 (DT = θ / θ0). Accordingly, the pump duty DT becomes closer to 100% as the closing period (closing timing) of the target electromagnetic spill valve 30 approaches the maximum closing period, and the target closing period approaches “0”. The value is closer to 0%.

  And as the pump duty DT approaches 100%, the valve closing start timing of the electromagnetic spill valve 30 adjusted based on the pump duty DT is advanced, and the valve closing period of the electromagnetic spill valve 30 becomes longer. As a result, the fuel discharge amount of the high-pressure fuel pump 1 increases and the actual fuel pressure increases. Further, as the pump duty DT approaches 0%, the valve closing start timing of the electromagnetic spill valve 30 adjusted based on the pump duty DT is delayed, and the valve closing period of the electromagnetic spill valve 30 is shortened. As a result, the fuel discharge amount of the high-pressure fuel pump 1 is reduced and the actual fuel pressure is lowered. The details of the procedure for calculating the pump duty DT are omitted here.

-Specific configuration of high-pressure fuel pump 1-
Next, a specific configuration of the high-pressure fuel pump 1 will be described with reference to FIG.

  The high-pressure fuel pump 1 illustrated in FIG. 3 is a plunger type pump, and includes a pump unit 20 provided in the housing 10, an electromagnetic spill valve 30, and a check valve 40.

  The pump unit 20 includes a cylinder 21, a pressurizing chamber 22, a plunger 23, and a lifter 51. The cylinder 21 is formed at the center of the housing 10, and a pressurizing chamber 22 is formed on the tip side (the upper end side in FIG. 3). The plunger 23 is a substantially cylindrical member, and is inserted into the cylinder 21 so as to be slidable in the axial direction (the vertical direction here).

  The lifter 51 is a bottomed and cylindrical member, and the base end (lower end) of the plunger 23, the retainer 26, the compression coil spring 27, and the like are accommodated therein. A lower portion of the lifter 51 is a roller support portion 51b, and a roller 53 that is rotatable about an axis extending parallel to the axis of the intake camshaft 110 is supported by the roller support portion 51b. . The lower end of the roller 53 can come into contact with the outer peripheral surface of the cam 111. Thus, the lifter 51 is configured as a so-called roller lifter. The roller 53 can be supported by a rotating shaft 53a fixed to the roller support portion 51b via, for example, a large number of rollers (for example, see FIG. 9). In this embodiment, lubricating oil is supplied to a contact portion (cam / roller contact portion) P1 between the outer peripheral surface of the cam 111 and the outer peripheral surface of the roller 53 to improve the lubricity in the cam / roller contact portion P1. I try to let them. A configuration for supplying lubricating oil to the cam / roller contact portion P1 will be described later.

  The lifter guide 52 has a cylindrical space, and the lifter 51 is accommodated in the space so as to be slidable in the axial direction. The lifter guide 52 is formed, for example, in a cylindrical shape, and is provided integrally with the cam carrier on the cam carrier that supports the intake camshaft 110. A pin for preventing the lifter 51 from rotating about the axis is attached to the lifter guide 52. The pin is a rod-like member and is integrally supported by the lifter guide 52 (see FIG. 5 and the like).

  A retainer 26 is integrally attached to the proximal end portion of the plunger 23. A spring seat member 52 a is fitted on the upper portion of the lifter guide 52. A compression coil spring 27 is sandwiched between the lower surface of the spring seat member 52 a and the retainer 26. By the elastic force of the compression coil spring 27, an urging force in a direction of pushing down the plunger 23 (a direction in which the volume of the pressurizing chamber 22 is expanded) is applied, and the roller 53 supported by the lifter 51 is directed toward the cam 111. Is pressed.

  Here, when the cam 111 rotates together with the intake camshaft 110, the cam nose 112 of the cam 111 applies an upward pressing force to the roller 53 of the lifter 51, so that the lifter 51 and the plunger 23 are raised while the compression coil is moved. The spring 27 is compressed to reduce the volume of the pressurizing chamber 22. On the other hand, when the cam nose 112 moves away from the roller 53 of the lifter 51, the lifter 51 and the plunger 23 are lowered by the urging force of the compression coil spring 27 to increase the volume of the pressurizing chamber 22.

  The electromagnetic spill valve 30 is disposed to face the pressurizing chamber 22. The electromagnetic spill valve 30 includes an electromagnetic solenoid 31, a bobbin 32, a core 33, an armature 34, a poppet valve 35, and a seat body 36. The electromagnetic solenoid 31 includes a coil wound around the bobbin 32 in a ring shape, and a core 33 is fitted and fixed in the central through hole of the bobbin 32. A portion of the armature 34 is fixed to one end of the poppet valve 35, and a part of the armature 34 is disposed coaxially with the core 33 so as to enter the central through hole of the bobbin 32. Concave portions are formed on the opposing surfaces of the core 33 and the armature 34, and a compression coil spring 37 is housed in a compressed state between the concave portions. The armature 34 is urged toward the pressurizing chamber 22 by the elastic force of the compression coil spring 37. The poppet valve 35 is slidably inserted into a through hole in the sheet body 36. A disc-shaped valve body 35 a is formed at the lower end of the poppet valve 35.

  In the above configuration, when the electromagnetic solenoid 31 is not energized, the valve body 35a is separated from the seat portion 36a of the seat body 36 by the elastic force of the compression coil spring 37, and the electromagnetic spill valve 30 is opened. On the other hand, when the electromagnetic solenoid 31 is energized by supplying power to the terminal 38, a magnetic circuit is formed by the support member 39 that supports the core 33, the armature 34, and the electromagnetic spill valve 30 as a whole. On the contrary, the armature 34 moves to the core 33 side. As a result, the poppet valve 35 moves to the side opposite to the pressurizing chamber 22, the valve body 35a comes into contact with the seat portion 36a of the seat body 36, and the electromagnetic spill valve 30 is closed (shown in FIG. 3). Status).

  On the other hand, when the electromagnetic spill valve 30 is in the open state, fuel can flow between the plurality of supply passages 36 b formed in the seat body 36 and the pressurizing chamber 22.

  A low pressure fuel passage 11 is formed in the housing 10 so as to communicate with the supply passage 36b. When the plunger 23 descends with the electromagnetic spill valve 30 open, the low pressure fuel pumped from the fuel tank 101 by the operation of the feed pump 102 is filtered, the pressure regulator 142, the low pressure fuel passage 11, and The air is sucked into the pressurizing chamber 22 through the supply passage 36b.

  The pressurizing chamber 22 formed on the tip side of the cylinder 21 is formed with a larger diameter than the inner peripheral surface of the cylinder 21. The plunger 23 enters the pressurizing chamber 22 before the closing timing of the electromagnetic spill valve 30, and the plunger 23 reaches the top dead center after the electromagnetic spill valve 30 is closed. In addition, a gap is formed between the inner peripheral surface of the pressurizing chamber 22 and the outer peripheral surface of the plunger 23 in a state where the distal end portion of the plunger 23 has entered the pressurizing chamber 22. A high pressure fuel passage 12 is formed in the housing 10, and the pressurizing chamber 22 communicates with the check valve 40 through the high pressure fuel passage 12.

  The check valve 40 includes a casing 41 connected to the high-pressure fuel passage 12, a seat body 42 and a spring base body 45 disposed in the casing 41, and a valve body (valve) facing the seat body 42 so as to be able to contact and separate. Body) 43 and a compression coil spring 44 that urges the valve body 43 toward a contact position with respect to the seat body 42. The check valve 40 is connected to the high-pressure fuel pipe 105. When the pressure of fuel pumped from the pressurizing chamber 22 through the high pressure fuel passage 12 exceeds a predetermined value, the valve body 43 separates from the seat body 42 against the urging force of the compression coil spring 44. Moved to position. As a result, the check valve 40 is opened, and the high pressure fuel pumped from the high pressure fuel passage 12 is supplied to the delivery pipe 106 via the high pressure fuel pipe 105.

-Characteristic part of embodiment (supply of lubricating oil to cam / roller contact part)-
Next, a characteristic part of this embodiment, that is, a configuration for supplying lubricating oil to the cam / roller contact portion P1 in the high-pressure fuel pump 1 will be described. In this embodiment, for example, without providing an oil jet that injects lubricating oil toward the cam / roller contact portion P1, lubricating oil is supplied to the cam / roller contact portion P1, and the cam / roller contact portion is supplied. The lubricity in P1 is improved.

  Here, a gap is provided between the lifter 51 and the lifter guide 52, but the gap is narrow except for a pair of flat portions 51a and 51a (see FIG. 5 and the like) described later. For this reason, although it is possible to send the lubricating oil to the cam / roller contact portion P1 through the narrow gap, the amount is small. Therefore, in this embodiment, a configuration including an oil passage for sending the lubricating oil to the cam / roller contact portion P1 and a guide means for guiding the lubricating oil from the oil passage to the cam / roller contact portion P1. Adopted. This specific configuration will be described below with reference to three examples.

(First embodiment)
First, a first embodiment will be described with reference to FIGS. 4 is a view showing a main part of the high-pressure fuel pump according to the first embodiment, FIG. 5 is a view as viewed from an arrow A in FIG. 4, and FIG. 6 is a view as viewed from an arrow B in FIG. In FIG. 6, the cam 111 is omitted.

  The lifter 51 of the high-pressure fuel pump 1 is formed with a pair of flat surface portions (two-surface width portions) 51a and 51a extending in parallel with each other along the axial direction. The pair of flat portions 51a and 51a are provided symmetrically with an angular interval of 180 ° around the axis of the lifter 51, and the outer shape of the lifter 51 is not circular when viewed from the axial direction, but a pair of flat portions 51a and 51a. It has a substantially oval shape that is recessed inward by 51a.

  The pair of flat portions 51a, 51a of the lifter 51 are provided to form an oil passage for sending to the cam / roller contact portion P1 and to prevent the pin 55 from rotating around the axis of the lifter 51. ing. The assembling property of the lifter 51 is improved by providing the pair of plane portions 51a and 51a symmetrically. A pin 55 is in contact with one of the pair of flat portions 51a and 51a. Due to the engagement between the one flat portion 51a and the pin 55, rotation of the lifter 51 around the axis is prevented. Note that the rotation of the lifter 51 around the axis may be prevented by means other than the pin 55. Also, the outer shape of the lifter 51 may be a shape other than those described above.

  The gap between the lifter 51 and the lifter guide 52 is larger in the pair of flat portions 51a and 51a than in the other portions, and the lubricating oil can be sent to the cam / roller contact portion P1 through this gap. It is possible. Therefore, the gap between the lifter 51 and the lifter guide 52 by the pair of flat portions 51a and 51a can be used as an oil passage for sending the lubricating oil to the cam / roller contact portion P1.

  Here, since the pin 55 is in contact with the one flat portion 51a on the pin 55 side, the presence of the pin 55 prevents the lubricating oil from being sent to the cam / roller contact portion P1. For this reason, the gap between the lifter 51 and the lifter guide 52 by the one flat portion 51a on the pin 55 side does not function as an oil passage. Therefore, the gap between the lifter 51 and the lifter guide 52 by the other flat portion 51a on the side opposite to the pin 55 is made to function as an oil passage (hereinafter referred to as oil passage R1).

  The supply of the lubricating oil to the cam / roller contact portion P1 through the oil passage R1 is performed when the lifter 51 is raised, specifically, as follows.

  The oil passage R1 communicates with a space (hereinafter referred to as an oil chamber) 54 surrounded by the inner surfaces of the lifter 51, the lifter guide 52, and the spring seat member 52a. Lubricating oil is supplied to the oil chamber 54 from, for example, an engine oil pump, and is supplied to the oil chamber 54 through an oil passage (oil hole) formed in a cam carrier supporting the intake camshaft 110, the lifter guide 52, and the like. It is possible to supply the lubricating oil. Note that the lubricating oil pumped up from the oil bath or the like by the cam 111 may be supplied to the oil chamber 54 by sucking the lubricating oil through the oil passage R1 when the lifter 51 is lowered. The oil chamber 54 may be filled with lubricating oil, but not only lubricating oil but also air may be mixed.

  When the plunger 23 moves in the direction in which the volume of the pressurizing chamber 22 contracts due to the rotation of the cam 111 (pressurization stroke), the lifter 51 rises. As the lifter 51 rises, the pressure in the oil chamber 54 increases, and as a result, the lubricating oil in the oil chamber 54 is forced to flow out into the gap between the lifter 51 and the lifter guide 52. At this time, the lubricating oil is discharged to the outside through the oil passage R1.

  On the other hand, when the plunger 23 moves in the direction in which the volume of the pressurizing chamber 22 increases due to the rotation of the cam 111 (suction stroke), the lifter 51 descends and the volume of the oil chamber 54 increases. As a result, the pressure in the oil chamber 54 decreases, and the lubricating oil is sucked into the oil chamber 54. At this time, the lubricating oil flows into the oil chamber 54 from the oil passage, the oil passage R1, and the like.

  In this manner, the lubricating oil is forcibly discharged through the oil passage R1 by the pump action accompanying the reciprocating movement of the lifter 51 up and down. The lubricating oil discharged from the oil passage R1 is guided to the cam / roller contact portion P1 by the plate 61. The plate 61 is a plate-like member having an inclined surface 61 b and is attached to the lower surface of the lifter guide 52 by bolts 62. The plate 61 functions as a guide means for guiding the lubricating oil from the oil passage R1 to the cam / roller contact portion P1. In FIG. 3, the plate 61 is omitted.

  The plate 61 is provided on the downstream side in the lubricating oil discharge direction of the oil passage R1, in this case, below the other flat portion 51a of the pair of flat portions 51a and 51a. When viewed from the axial direction of the lifter 51, the plate 61 has a tip 61 a extending from the inner surface of the lifter guide 52 toward the lifter 51. The tip portion 61a is provided so as to overlap a part or all of the oil passage R1, and the discharge direction of the lubricating oil discharged through the oil passage R1 is changed by the tip portion 61a. Here, the tip portion 61a overlaps the entire oil passage R1. The portion of the tip 61a closest to the lifter 51 extends along a direction orthogonal to the axial direction of the lifter 51 and the rotational axis of the roller 53, and is provided so as not to interfere with the cam 111 and the like.

  Further, the upper surface (surface on the oil passage R1 side) of the tip portion 61a is not perpendicular to the lubricating oil discharge direction of the oil passage R1 (in this case, with respect to the axial direction of the lifter 51), and is not predetermined. The inclined surface 61b is inclined at an angle. The inclination angle and height position of the inclined surface 61b are set to such an inclination angle and height position that the lubricating oil discharged from the oil passage R1 can be guided to the cam / roller contact portion P1.

  According to the high pressure fuel pump 1 as described above, when the lifter 51 is lifted, the discharge direction of the lubricating oil discharged through the oil passage R1 is such that the inclined surface 61b of the front end portion 61a of the plate 61 causes the cam / roller contact portion P1. Will be changed towards. Thus, since the lubricating oil is guided toward the cam / roller contact portion P1, the cam / roller contact portion P1 can be directly lubricated. Further, since the lubricating oil is positively fed to the cam / roller contact portion P1 by utilizing the pump action accompanying the reciprocating movement of the lifter 51 up and down, the lubricating oil simply flows down the inclined surface 61b of the plate 61. It is discharged toward the cam / roller contact portion P1 with a certain degree of momentum, but with a certain degree of direction regulated by the plate 61. As a result, the lubricating oil can be supplied to the cam / roller contact portion P1 sufficiently and efficiently. Therefore, the lubricity in the cam / roller contact portion P1 can be improved without using an oil jet, and friction can be reduced.

  Next, a modification of the first embodiment will be described.

  (1) The high pressure fuel pump 1 may have a so-called direct hitting type lifter in which the cam 111 and the lifter 51 are in contact with each other. In this case, it is possible to supply lubricating oil to the contact portion (cam / lifter contact portion) between the outer peripheral surface of the cam 111 and the bottom surface of the lifter 51 via the oil passage R1 as described above. In the case of this direct hitting type lifter, it is not particularly necessary to prevent the lifter 51 from rotating by the pin 55 or the like.

  (2) The oil passage R1 for sending the lubricating oil to the cam / roller contact portion P1 is not limited to the one using the flat portion 51a provided in the lifter 51. That is, if the outer shape of the lifter 51 is recessed from the circular shape inward when viewed from the axial direction, the recess (notch portion) can be used as the oil passage R1. Alternatively, a recess (notch) that is recessed outward may be provided on the inner periphery of the lifter guide 52 instead of the outer periphery of the lifter 51, and the recess may be used as the oil passage R1. Furthermore, you may provide a recessed part in both the outer periphery of the lifter 51, and the inner periphery of the lifter guide 52, and may utilize those recessed parts as oil path R1. Note that the opening area of the oil passage R1 has been obtained through experiments, simulation calculations, and the like in consideration of the pressure rise in the oil chamber 54 as the lifter 51 rises, the amount of lubricant discharged from the oil chamber 54, and the like. It is sufficient to make a decision.

  (3) The guide means for guiding the lubricating oil to the cam / roller contact portion P1 may be other than the inclined surface 61b formed on the plate 61 described above. For example, the lower portion of the lifter guide 52 may be processed to provide a protrusion having an inclined surface similar to that of the plate 61 described above, and the inclined surface may function as a guide means. Moreover, you may employ | adopt the inclined surface 56d (refer FIG. 10, FIG. 11) of the pin 56 of 3rd Example mentioned later as a guide means. The inclination angle and height position of the inclined surface are determined by experiments, simulation calculations, etc. in consideration of the amount of lubricating oil discharged from the oil chamber 54 and the positional relationship between the inclined surface and the cam / roller contact portion P1. It can be determined empirically.

(Second embodiment)
Next, a second embodiment will be described with reference to FIGS. FIG. 7 is a view showing a main part of the high-pressure fuel pump according to the second embodiment, and corresponds to FIG. 5 in the first embodiment. FIG. 8 is a perspective view showing the plate of FIG.

  The second embodiment is an improvement of the first embodiment. In the high-pressure fuel pump 1, the configuration of the oil passage R1 for sending the lubricating oil to the cam / roller contact portion P1 is the same as that of the first embodiment. As in the case of the first embodiment, the lubricating oil from the oil passage R1 is supplied not only to the cam / roller contact portion P1 but also to the bearing portion P2 (see FIG. 9) inside the roller 53. It is different from the case of. Here, different points will be mainly described, and the same components (see FIGS. 3 to 6) as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted.

  In order to guide the lubricating oil from the oil passage R1 to the cam / roller contact portion P1, the plate 61 is used in the first embodiment (see FIGS. 4 to 6). In order to guide the lubricant oil to the cam / roller contact portion P1 and the bearing portion P2 of the roller 53, a plate 63 as shown in FIGS. 7 and 8 is used.

  The plate 63 of this example has a configuration in which a protrusion is added to the plate 61 of the first embodiment. Specifically, the plate 63 is a plate-like member having a protrusion 63 b and is attached to the lower surface of the lifter guide 52 by a bolt 62. The plate 63 is provided below the oil passage R1, in other words, below the other flat portion 51a of the pair of flat portions (two-surface width portions) 51a, 51a of the lifter 51. When viewed from the axial direction of the lifter 51, the plate 63 has a leading end 63 a extending from the inner surface of the lifter guide 52 toward the lifter 51. The leading end 63a is provided so as to overlap a part or all of the oil passage R1, and the discharge direction of the lubricating oil discharged through the oil passage R1 is changed by the tip 63a. Here, the tip end portion 63a overlaps the entire oil passage R1. The portion of the tip end portion 63 a closest to the lifter 51 extends along a direction (hereinafter referred to as a width direction) orthogonal to the axial direction of the lifter 51 and the rotational axis direction of the roller 53.

  Further, a protrusion 63b protruding upward is formed at the center in the width direction of the tip 63a of the plate 63. Therefore, the front end portion 63a of the plate 63 is raised higher in the center portion 63c in the width direction where the protrusion 63b is provided than the both end portions 63d and 63d in the width direction. The upper surface (surface on the oil passage R1 side) of the central portion 63c is an inclined surface 63e that is not perpendicular to the axial direction of the lifter 51 but is inclined at a predetermined angle, and the both ends 63d and 63d are The upper surface is the same inclined surfaces 63f and 63f. The inclination angle and height position of the inclined surface 63e are set to such an inclination angle and height position that the lubricating oil discharged from the oil passage R1 can be guided to the bearing portion P2 of the roller 53. The inclination angles and height positions of the inclined surfaces 63f and 63f are set to inclination angles and height positions that can guide the lubricating oil discharged from the oil passage R1 to the cam / roller contact portion P1. Here, the inclined surface 63e and the inclined surfaces 63f and 63f are made to have different inclination angles and height positions, so that the lubricating oil discharged from the oil passage R1 is made to be a bearing portion of the cam / roller contact portion P1 and the roller 53. It branches to P2 and is supplied. Note that the lubricating oil discharged from the oil passage R1 may be branched by changing the inclination angle or height position of the inclined surface 63e and the inclined surfaces 63f, 63f.

  According to the high pressure fuel pump 1 as described above, since the protrusion 63b is provided on the plate 63, the discharge direction of the lubricating oil discharged through the oil passage R1 is branched by the protrusion 63b when the lifter 51 is raised. . At both ends 63d and 63d in the width direction without the protrusion 63b, the direction of lubricant discharge is changed toward the cam / roller contact portion P1 by the inclined surfaces 63f and 63f of the ends 63d and 63d. Thus, since the lubricating oil is guided toward the cam / roller contact portion P1, the cam / roller contact portion P1 can be directly lubricated.

  Further, in the central portion 63c in the width direction where the protrusion 63b is provided, the discharge direction of the lubricating oil is changed toward the bearing portion P2 of the roller 53 by the inclined surface 63e of the central portion 63c. Thereby, since the lubricating oil is guided toward the bearing portion P2 of the roller 53, the lubricating oil can be supplied also to the bearing portion P2 of the roller 53.

  Specifically, as shown in FIG. 9, the roller 53 is supported by a rotating shaft 53 a fixed to the roller support portion 51 b of the lifter 51 via a large number of rollers 53 b, 53 b,. The bearing portion P2 of the roller 53 can be directly lubricated, which is effective. In this case, as shown in FIG. 9, in order to prevent the roller 53b from dropping off and the roller 53 from shifting in the rotational axis direction, the lower portion of the roller support portion 51b is extended downward in the lifter 51. It is desirable to provide the extending portion 51c. The extending portion 51c is provided below the pair of flat portions 51a and 51a of the lifter 51, respectively. Therefore, it is necessary to arrange the plate 63 so as not to interfere with the extending portion 51c. Further, in order to prevent the lubricating oil supplied to the bearing portion P2 of the roller 53 from being blocked by the extending portion 51c, as shown in FIG. 9, a slit 51d smaller than the size of the roller 53b is formed in the extending portion 51c. It is preferable to provide it. FIG. 9 shows a case where five slits 51d are provided. If it carries out like this, falling off of the roller 53b can be prevented by the extension part 51c, and lubricating oil can be supplied to the bearing part P2 of the roller 53 from the slit 51d.

  Further, the lubricating oil is positively fed to the cam / roller contact portion P1 and the bearing portion P2 of the roller 53 by utilizing the pump action associated with the reciprocating movement of the lifter 51 up and down. The cam / roller contact portion P1 in a state where the plate 63 has a certain degree of momentum and is restricted (squeezed) to some extent by the plate 63, not just flowing down the inclined surfaces 63e, 63f, 63f. And discharged toward the bearing portion P2 of the roller 53. Accordingly, the lubricating oil can be supplied sufficiently and efficiently to the cam / roller contact portion P1 and the bearing portion P2 of the roller 53. Therefore, the lubricity of the cam / roller contact portion P1 and the bearing portion P2 of the roller 53 can be improved without using an oil jet, and friction can be reduced.

  Next, a modification of the second embodiment will be described.

  As modifications of the second embodiment, the same modifications as those of the first embodiment can be mentioned, but other modifications can be given as follows.

  (1) The guide means (second guide means) for guiding the lubricating oil to the bearing portion P2 of the roller 53 may be other than the inclined surface 63e formed on the protrusion 63b of the plate 63 described above. For example, the lower part of the lifter guide 52 may be processed to provide a protrusion having an inclined surface similar to the protrusion 63b of the plate 63 described above, and the inclined surface may function as the second guiding means. It should be noted that the size of the protrusion 63 of the plate 63, the inclination angle and height position of the inclined surface take into account the amount of lubricating oil discharged from the oil chamber 54, the positional relationship between the inclined surface and the bearing portion P2 of the roller 53, and the like. Then, it may be determined empirically by experiments and simulation calculations.

(Third embodiment)
Next, a third embodiment will be described with reference to FIGS. FIG. 10 is a view showing a main part of the high-pressure fuel pump of the third embodiment, and corresponds to FIG. 5 in the first embodiment. FIG. 11 is a perspective view showing the pin of FIG.

  The third embodiment is an improvement of the first embodiment, and in the high-pressure fuel pump 1, there is not only one oil passage for sending lubricating oil to the cam / roller contact portion P1 or the like. This is different from the case of the first embodiment. Here, different points will be mainly described, and the same components (see FIGS. 3 to 6) as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted.

  The oil passage for sending the lubricating oil to the cam / roller contact portion P1 in the high-pressure fuel pump 1 is only the oil passage R1 in the first embodiment (see FIGS. 4 to 6). In addition to the oil passage R1, an oil passage R2 as shown in FIGS. 10 and 11 is also provided. That is, in the first embodiment, since the gap between the lifter 51 and the lifter guide 52 by the one flat portion 51a on the pin 55 side of the lifter 51 cannot be used as an oil passage, the lubricating oil is used as the cam / roller contact portion. It was the structure which sent to P1 from one side. On the other hand, in this example, by using the pin 56 as shown in FIGS. 10 and 11, the gap between the lifter 51 and the lifter guide 52 by the one flat portion 51a on the pin 56 side is also the oil passage R2. It can be used as. Therefore, in this example, the lubricating oil is fed into the cam / roller contact portion P1 from both sides.

  Further, as the guiding means for guiding the lubricating oil from the oil passage R1 to the cam / roller contact portion P1, the same plate 61 as in the first embodiment is used (see FIGS. 4 to 6). On the other hand, in this example, the pin 56 is used as guide means for guiding the lubricating oil from the oil passage R2 to the cam / roller contact portion P1.

  The pin 56 of this example has a configuration in which a depression is added to the pin 55 of the first embodiment. Specifically, the pin 56 is a rod-shaped member having a recess 56 a and is integrally supported by the lifter guide 52.

  A recess 56 a that is recessed toward the lifter guide 52 side is formed in a portion of the pin 56 on the lifter 51 side. The recess 56 a is provided at the center of the pin 56 in the longitudinal direction. Accordingly, in the pin 56, the center portion 56b in the longitudinal direction with the depression 56a has a smaller amount of protrusion to the lifter 51 side than both end portions 56c and 56c in the longitudinal direction. The upper surface (surface on the oil passage R2 side) of the central portion 56b is an inclined surface 56d that is not perpendicular to the axial direction of the lifter 51 but is inclined at a predetermined angle. On the other hand, the upper surfaces of both end portions 56c, 56c are not inclined surfaces, and remain circular in cross section. The inclination angle and height position of the inclined surface 56d are set to such an inclination angle and height position that the lubricating oil discharged from the oil passage R2 can be guided to the cam / roller contact portion P1. In addition, it is preferable to set the inclination angle of the inclined surface 56d to be larger as the pin 56 is closer to the cam / roller contact portion P1, that is, as it is positioned below.

  In addition, of the pair of flat portions 51 a and 51 a of the lifter 51, both end portions 56 c and 56 c of the pin 56 are in contact with one flat portion 51 a. Due to the engagement between the one flat surface portion 51a and both end portions 56c and 56c of the pin 56, the rotation of the lifter 51 around the axis is prevented.

  Further, since the recess 56 a is provided, a gap is provided between the one flat portion 51 a of the lifter 51 and the central portion 56 b of the pin 56. Accordingly, since it is possible to discharge the lubricating oil to the cam / roller contact portion P1 through this gap, the oil passage through the gap between the lifter 51 and the lifter guide 52 by the one flat portion 51a on the pin 55 side. It becomes possible to function as R2.

  According to the high pressure fuel pump 1 as described above, when the lifter 51 is lifted, the discharge direction of the lubricating oil discharged through the oil passage R1 is such that the inclined surface 61b of the front end portion 61a of the plate 61 causes the cam / roller contact portion P1. Will be changed towards. Further, since the pin 56 is provided with a recess 56a, when the lifter 51 is raised, the discharge direction of the lubricating oil discharged through the oil passage R2 is changed to the cam / roller contact portion P1 by the inclined surface 56d of the pin 56. Will be changed. As a result, since the lubricating oil is guided from both sides toward the cam / roller contact portion P1, the cam / roller contact portion P1 can be directly lubricated. Further, since the lubricating oil is positively fed from both sides to the cam / roller contact portion P1 by utilizing the pump action accompanying the reciprocating movement of the lifter 51 up and down, the lubricating oil is applied to the inclined surface 61b of the plate 61 and The discharge is directed toward the cam / roller contact portion P1 with a certain amount of momentum, not just flowing down the inclined surface 56d of the pin 56, and with a certain direction regulated by the plate 61 and the pin 56. Is done. As a result, the lubricating oil can be sufficiently and efficiently supplied from both sides to the cam / roller contact portion P1. Therefore, the lubricity in the cam / roller contact portion P1 can be improved without using an oil jet, and friction can be reduced. In this case, since the lubricating oil is supplied to the cam / roller contact portion P1 not only from one side but from both sides, the lubricity in the cam / roller contact portion P1 is higher than that in the first and second embodiments. Can be further improved, and the friction can be further reduced.

  Next, a modification of the third embodiment will be described.

  As a modification of the third embodiment, the same modification as that of the first embodiment can be mentioned. However, the following modification can be given.

  (1) The guide means for guiding the lubricating oil from the oil passage R2 to the cam / roller contact portion P1 may be other than the inclined surface 56d formed on the pin 56 described above. For example, as shown in FIG. 12, a plate 61 provided below the oil passage R1 is also provided below the oil passage R2, and the inclined surface 61b of the plate 61 cams the lubricating oil from the oil passage R2. -It is possible to guide to the roller contact portion P1. In this case, it is not necessary to provide the inclined surface 56d in particular in the pin 56, but since it is necessary to allow the lubricating oil to pass therethrough, it is necessary to provide the recess 56a. The size of the recess 56a of the pin 56, the inclination angle and height position of the inclined surface take into account the amount of lubricating oil discharged from the oil chamber 54, the positional relationship between the inclined surface and the cam / roller contact portion P1, and the like. Then, it may be determined empirically by experiments and simulation calculations.

  Here, if the pin 56 is far from the cam / roller contact portion P1, that is, if the position of the pin 56 is upward, the directionality of the lubricating oil from the oil passage R2 guided by the inclined surface 56d of the pin 56. In this case, it is preferable to provide the plate 61 below the oil passage R2. The plate 61 below the oil passage R2 can be formed integrally with the plate 61 below the oil passage R1.

  On the other hand, if the pin 56 is close to the cam / roller contact portion P1, that is, if the position of the pin 56 is downward, the direction of the lubricating oil from the oil passage R2 guided by the inclined surface 56d of the pin 56 is increased. Variations are less likely to occur. In this case, for example, as shown in FIG. 13, the plate 61 below the oil passage R1 is omitted, and the pin 56 provided in the oil passage R2 is also provided in the oil passage R1, and the inclined surface of the pin 56 is provided. With 56d, it is possible to guide the lubricating oil from the oil passage R1 to the cam / roller contact portion P1.

  (2) The configuration of the second embodiment can be combined with the configuration of the third embodiment. In this way, the lubricating oil can be supplied to both the cam / roller contact portion P1 and the bearing portion P2 of the roller 53 (see FIG. 9) from both sides. It can be further improved. Here, when the guide means for guiding the lubricating oil from the oil passage R2 to the cam / roller contact portion P1 is the inclined surface 56d formed on the pin 56, the projection of the plate 63 described above is formed in the recess 56a of the pin 56. What is necessary is just to provide the protrusion etc. which have the inclined surface similar to 63b (refer FIG. 7, FIG. 8).

  (3) Either one of the lubricating oil from the oil passage R1 and the lubricating oil from the oil passage R2 may be guided to the cam / roller contact portion P1, and the other may be guided to the bearing portion P2 of the roller 53. .

  (4) There may be three or more oil passages for sending the lubricating oil. For example, three oil passages are provided, lubricant oil is supplied from two of the oil passages to the cam / roller contact portion P1, and the lubricant oil is supplied from the remaining oil passage to the bearing portion P2 of the roller 53. Is also possible.

-Other embodiments-
The embodiment of the present invention has been described above. However, the embodiment shown here is an example and can be variously modified.

  (1) In the above description, the lifter 51 is reciprocated by the rotation of the cam 111 attached to the intake camshaft 110. However, the lifter 51 is reciprocated by the rotation of the cam attached to the exhaust camshaft. Also good.

  (2) In the above, the lifter 51 is reciprocated by the cam 111 having the three cam noses 112, 112, 112. However, the lifter 51 is moved by the cam having the other number of cam noses (for example, two cam noses). It may be configured to reciprocate.

  (3) The case where the present invention is applied to an in-cylinder direct injection type 6-cylinder gasoline engine mounted on an automobile has been described above. The present invention is not limited to this, and can be applied to, for example, a gasoline engine having any number of cylinders such as an in-cylinder direct injection four-cylinder gasoline engine. Further, the present invention is not limited to a gasoline engine, but can be applied to other internal combustion engines such as a diesel engine. Furthermore, the engine to which the present invention is applicable is not limited to an automobile engine.

It is a figure which shows typically an example of the fuel supply apparatus to which the high-pressure fuel pump of this invention is applied. It is a figure for demonstrating the opening / closing operation | movement of an electromagnetic spill valve. It is a longitudinal cross-sectional view which shows an example of the high pressure fuel pump of this invention. It is a figure which shows the principal part of the high pressure fuel pump of 1st Example. It is A arrow directional view of FIG. FIG. 6 is a view taken in the direction of arrow B in FIG. 5. It is a figure which shows the principal part of the high pressure fuel pump of 2nd Example. It is a perspective view which shows the plate of FIG. It is a figure which shows the specific example of the roller supported by a lifter. It is a figure which shows the principal part of the high pressure fuel pump of 3rd Example. It is a perspective view which shows the pin of FIG. It is a figure which shows the principal part of the high pressure fuel pump of the modification of 3rd Example. It is a figure which shows the principal part of the high pressure fuel pump of the modification of 3rd Example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 High pressure fuel pump 21 Cylinder 22 Pressurization chamber 23 Plunger 27 Compression coil spring 30 Electromagnetic spill valve 51 Lifter 52 Lifter guide 53 Roller 61 Plate 61b Inclined surface 100 Fuel supply device 110 Intake camshaft 111 Cam P1 Cam / roller contact part R1 Through Oil passage

Claims (12)

A plunger inserted into the cylinder so as to be reciprocally slidable; a pressure chamber defined by the cylinder and the plunger; a lifter disposed within the lifter guide so as to be slidable back and forth; and the cam lifter A compression coil spring that presses against the outer peripheral surface side, the lifter moves with the rotation of the cam, and the plunger reciprocates. In a high-pressure fuel pump that repeatedly pressurizes and discharges fuel in the pressurizing chamber,
An oil passage for discharging the lubricating oil in the space enclosed by the lifter and the lifter guide to the outside as the lifter reciprocates due to rotation of the cam;
A high-pressure fuel pump comprising: guide means for guiding lubricating oil discharged from the oil passage to a contact portion between the cam and a member in contact with an outer peripheral surface of the cam.   The high-pressure fuel pump according to claim 1, wherein the oil passage is provided between a lifter and a lifter guide.   The high-pressure fuel pump according to claim 2, wherein the oil passage is configured as a recess formed in at least one of a lifter and a lifter guide.   The guide means is provided downstream of the oil passage in the lubricating oil discharge direction, and is at an angle that can guide the lubricating oil discharged from the oil passage to the contact portion with respect to the lubricating oil discharge direction. The high-pressure fuel pump according to any one of claims 1 to 3, wherein the high-pressure fuel pump is configured as an inclined inclined surface.   5. The high-pressure fuel pump according to claim 1, wherein the member in contact with the outer peripheral surface of the cam is the lifter.   5. The high-pressure fuel pump according to claim 1, wherein the member in contact with the outer peripheral surface of the cam is a roller rotatably supported by the lifter.   The high-pressure fuel according to any one of claims 4 to 6, wherein the inclined surface is formed on a part of the lifter guide or a member provided integrally with the lifter guide. pump.   The high-pressure fuel pump according to claim 6, wherein the inclined surface is formed on a member for preventing rotation around the axis of the lifter that supports the roller.   7. The high-pressure fuel pump according to claim 6, further comprising second guide means for guiding the lubricating oil discharged from the oil passage toward the bearing portion of the roller.   The second guide means is provided downstream of the oil passage in the lubricating oil discharge direction, and lubricates at an angle so that the lubricating oil discharged from the oil passage can be guided to the bearing portion of the roller. The high-pressure fuel pump according to claim 9, wherein the high-pressure fuel pump is configured as a second inclined surface inclined with respect to the oil discharge direction.   The inclined surface and the second inclined surface are a part of the lifter guide, a member provided integrally with the lifter guide, or for preventing rotation of the lifter supporting the roller around the axis. The high-pressure fuel pump according to claim 10, wherein the high-pressure fuel pump is formed on a member.   The high-pressure fuel pump according to claim 10 or 11, wherein at least one of an inclination angle and a height position of the second inclined surface is different from that of the inclined surface.

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