JP2010190082A - High pressure pump driving structure for internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a high pressure pump driving structure for an internal combustion engine in which a high pressure pump having an input part to be operated in the axial direction is mounted on a cover member covering a valve gear including a cam shaft, and a pump driving rocker arm is provided between the pump cam of the cam shaft and the input member of the high pressure pump for rocking following the pump cam, for efficiently transmitting driving force from the pump cam to the high pressure pump while eliminating the need for specially strengthening the pump driving rocker arm itself and the support of the pump driving rocker arm. <P>SOLUTION: An abutting portion of the pump driving rocker arm 60 on the pump cam 58 and an abutting portion of the pump driving rocker arm 60 on the input part 62 are arranged in parallel to the operating axis of the input part 62 on the same side relative to a plane PL passing through the rocking center of the pump driving rocker arm 60. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  According to the present invention, a high pressure pump having an input portion that operates in an axial direction is attached to a cover member that covers a valve operating device including a camshaft, and a pump cam provided on the camshaft and an input portion of the high pressure pump In particular, the present invention relates to an internal combustion engine in which a rocker arm for driving a pump that swings following the pump cam is interposed, and more particularly, to an improvement in a structure for driving a high-pressure pump.

  A fuel pump drive structure in which a fuel pump attached to a cover member covering a valve gear including a camshaft is driven by a rocker arm for driving a pump driven by a pump cam provided on the camshaft. Is known from US Pat.

JP 2005-325705 A

  However, in the one disclosed in Patent Document 1 described above, a roller that is in rolling contact with the pump cam is pivotally supported at one end of a rocker arm for driving the pump having an oscillation fulcrum at an intermediate portion, and is in rolling contact with the input portion of the fuel pump. A roller is pivotally supported on the other end of the pump drive rocker arm, and the pump drive rocker arm is provided with a force point and an action point with the rocking center interposed therebetween. For this reason, the direction in which the pump cam swings and drives the pump drive rocker arm and the direction in which the pump drive rocker arm drives the fuel pump input section in the axial direction are opposite to each other. Is not efficient. In particular, a large force is required to drive the high-pressure pump, and it is necessary to efficiently transmit the driving force from the pump cam to the input portion of the high-pressure pump through the pump driving rocker arm. In addition, when the rocker arm for driving the pump is configured so that the force point and the action point are provided with the rocking center sandwiched between them, the force applied from the pump cam to one end of the rocker arm for driving the pump and the pump from the high pressure pump When the drive reaction force acting on the other end of the drive rocker arm is in the same direction, it is necessary to firmly support the pump drive rocker arm itself and the pump drive rocker arm.

  The present invention has been made in view of such circumstances, and efficiently transmits a driving force from a pump cam to a high-pressure pump, and specially strengthens the support of the pump driving rocker arm itself and the pump driving rocker arm. An object of the present invention is to provide a high-pressure pump drive structure in an internal combustion engine that eliminates the need for the internal combustion engine.

  In order to achieve the above object, according to the present invention, a high pressure pump having an input portion that operates in an axial direction is attached to a cover member that covers a valve operating device including a camshaft, and a cam for a pump provided on the camshaft. And an input portion of the high-pressure pump, an internal combustion engine in which a pump drive rocker arm that swings following the pump cam is interposed, and the pump drive rocker arm contacts the pump cam. The contact portion and the contact portion of the pump drive rocker arm with the input portion are arranged on the same side with respect to a plane passing through the swing center of the pump drive rocker arm in parallel with the operation axis of the input portion. This is a first feature.

  According to the present invention, in addition to the configuration of the first feature, a contact portion of the pump driving rocker arm with the pump cam is connected to the input portion of the pump driving rocker arm in a direction perpendicular to the plane. A second feature is that the pump is disposed between the contact portion and the rocking center of the rocker arm for driving the pump.

  Furthermore, in addition to the configuration of the first or second feature, the present invention provides the pump shaft of the camshaft and the rocker arm for driving the pump on the projection onto the plane orthogonal to the axis of the camshaft. A third feature is that a straight line connecting the contact portion with the cam is set in a direction substantially along the operation axis of the input portion.

  According to the first feature of the present invention, the pump drive rocker arm is in contact with the pump cam with respect to a plane passing through the swing center of the pump drive rocker arm parallel to the operation axis of the input unit. Since the point of action and the point of action, which is the abutment part of the pump drive rocker arm to the input part of the high pressure pump, are arranged on the same side, the pump drive rocker arm is not enlarged, and the pump cam is used for pump drive. The force applied to the rocker arm is transmitted from the pump drive rocker arm to the high-pressure pump without being reversed, and the drive force can be efficiently transmitted by bringing the drive force point and the action point close to each other. In addition, bending of the rocker arm for driving the pump can be suppressed, and the support of the rocker arm for driving the pump and the rocker arm for driving the pump is particularly strong. It is not required to be in.

  According to the second feature of the present invention, the pump drive rocker arm is input to the input portion of the pump drive rocker arm in a direction perpendicular to the plane passing through the swing center of the pump drive rocker arm parallel to the operation axis of the input portion of the high pressure pump. Since the abutment portion of the pump drive rocker arm to the pump cam is disposed between the abutment portion and the swing center of the pump drive rocker arm, the pump drive rocker arm can be shortened, Thereby, the weight of the rocker arm for driving the pump can be reduced and the bending of the rocker arm for driving the pump can be suppressed.

  Further, according to the third aspect of the present invention, the straight line connecting the axis of the camshaft and the abutting portion of the pump drive rocker arm to the pump cam is on a projection view on a plane perpendicular to the axis of the camshaft. Therefore, when the high-pressure pump is driven by the pump drive rocker arm, the input line is prevented from tilting from the operating direction and increasing the sliding resistance. .

1 is a plan view of an engine body according to Embodiment 1. FIG. FIG. 2 is a sectional view taken along line 2-2 of FIG. FIG. 3 is a sectional view taken along line 3-3 in FIG. 2. FIG. 4 is a view taken along line 4-4 in FIG. 2. FIG. 5 is a sectional view taken along line 5-5 of FIG. FIG. 6 is a sectional view taken along line 6-6 of FIG. It is a figure which shows the operating state of the high pressure pump and the rocker arm for driving the pump.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  The first embodiment of the present invention will be described with reference to FIGS. 1 to 7. First, in FIGS. 1 and 2, the engine body 11 has a pair of right bank BR and left bank BL that are mutually V-shaped. In the right bank BR arranged on the right side when the vehicle is mounted, the first to fourth cylinders C1 to C4 are arranged side by side in the cylinder arrangement direction 15, and are mounted when the vehicle is mounted. In the left bank BL arranged on the left side, the fifth to eighth cylinders C5 to C8 are arranged side by side in the cylinder arrangement direction 15. Moreover, the first and fourth cylinders C1 and C4 of the right bank BR and the sixth and seventh cylinders C6 and C7 of the left bank BL can be deactivated.

  Referring also to FIG. 2, the left bank BR includes a cylinder block 12L, a cylinder head 13L coupled to the upper portion of the cylinder block 12L, and a head cover 14L as a cover member coupled to the cylinder head 13L. The head cover 14LR is formed in a box shape having a substantially rectangular side wall 14a and a ceiling wall 14b connected to the side wall 14a.

  The cylinder block 12L is formed with cylinder bores 16 for the fifth to eighth cylinders C5, C6, C7, and C8 arranged in the cylinder arrangement direction 15, and is slidably fitted into the cylinder bores 16. Combustion chambers 18 are formed between the cylinder block 12L and the cylinder head 13L for each of the cylinders C5 to C8.

  An intake port 19 for each of the cylinders C5 to C8 is provided on one side surface (left side surface in FIG. 2) of the cylinder head 13L, and each other side surface (right side surface in FIG. 2) is provided on each other side surface of the cylinder head 13L. Exhaust ports 20 for each of the cylinders C5 to C8 are provided. Moreover, in the cylinder head 13L, a pair of intake valves 21, 21... For each of the cylinders C5 to C8 is disposed so as to be openable and closable so as to switch communication / blockage between the combustion chambers 18 and the intake ports 19. A pair of exhaust valves 22, 22... For each of the cylinders C5 to C8 is disposed so as to be openable and closable so as to switch communication between the combustion chamber 18 and the exhaust port 20. Is energized in the valve closing direction by a valve spring 23 that is contracted between the cylinder head 13L, and each valve 22 is energized in a valve closing direction by a valve spring 24 that is contracted between the cylinder head 13L. Be energized by. Further, a spark plug 25, whose tip is exposed at the center of the combustion chamber 18, is screwed into the cylinder head 13L for each of the cylinders C5 to C8. The cylinder head 13L has an annular shape between the head cover 14L and the cylinder head 13L. The plug cylinders 27 penetrating the head cover 14L with the sealing members 26 are interposed so as to insert the spark plugs 25.

  Further, the cylinder head 13L is provided with injectors 106 for directly injecting fuel together with compressed air into the combustion chambers 18 for each of the fifth to eighth cylinders C5 to C8, and these injectors 106 are common. Connected to the fuel rail 107.

  Between the cylinder head 13L and the head cover 14L, an intake side valve device 28 for opening and closing the intake valves 21 and an exhaust side valve device 29 for opening and closing the exhaust valves 22 are accommodated.

  The intake side valve device 28 always opens and closes the intake valves 21 and the exhaust valves 22 for the fifth cylinder C5 and the eighth cylinder C8, but operates the engine at a low speed for the sixth cylinder C6 and the seventh cylinder C7. The intake valve 21... And the exhaust valve 22... Are sometimes closed so as to be in a cylinder deactivation state, and the configuration of the intake side valve device 28 in the eighth cylinder C4 is shown in FIG. This will be described below with reference to FIG.

  An intake side camshaft 31 having an axis parallel to the cylinder arrangement direction 15 is rotatably supported on the head cover 14L, and an intake side rocker shaft 32 having an axis parallel to the intake side camshaft 31 is supported. Rotational power decelerated with a 1/2 reduction ratio is transmitted to the intake camshaft 31 from a crankshaft (not shown).

  The intake side camshaft 31 includes a pair of low speed cams 33, 34, a single high speed cam 35, and the high speed cam 35 sandwiched between one low speed cam 33 and the other low speed cam. 34 and a decompression cam 36 disposed at a position between the high speed cam 35 and the high speed cam 35.

  On the other hand, the upper side of the first, second, third and fourth sub rocker arms 38, 39, 40, 41 is supported on the intake side rocker shaft 32 so as to be swingable, and below the sub rocker arms 38-41. The first and second rocker arms 43, 44 have one end pivotably supported by the cylinder head 13L via hydraulic tappets 45 and the other end abutting against the stem ends 21a of the intake valves 21. Is placed.

  The first to fourth sub rocker arms 38 to 41 have the first and third sub rocker arms 38 and 40 directly above the first and second rocker arms 43 and 44, and the second sub rocker arm 39 to the first and third rocker arms 38, 40, the fourth sub rocker arm 41 and the second sub rocker arm 39 are sandwiched between the fourth sub rocker arm 41 and the second sub rocker arm 39 so as to be swingably supported on the intake side rocker shaft 32. The sub rocker arms 38 and 41 are rotatably supported by rollers 46 and 47 that are in rolling contact with the low speed cams 33 and 34, and the second sub rocker arm 39 is rotatably supported by a roller 48 that is in rolling contact with the high speed cam 35. . The first and third sub-rocker arms 38 and 40 are provided with slipper portions 53 and 54 that contact rollers 51 and 52 that are pivotally supported by intermediate portions of the first and second rocker arms 43 and 44, respectively.

  Accordingly, when the first and third sub-rocker arms 38 and 40 swing around the axis of the intake-side rocker shaft 32, the first and second rocker arms 43 are pressed by the rollers 51 and 52 being pressed by the second slipper portions 53 and 54. 44 swing around the hydraulic tappets 45 as a fulcrum, and the intake valves 21 are driven to open and close.

  The second and fourth sub rocker arms 39 and 41 are integrally provided with contact arm portions 39a and 41a extending upward from the portion supported by the intake side rocker shaft 32, respectively. Lost motion springs 55 are provided between 39a, 41a and the head cover 14L to bias the rollers 48, 47 pivotally supported by the second and fourth sub rocker arms 39, 41 toward the intake camshaft 31.

  On the other hand, the first to fourth sub rocker arms 38 to 41 are connected to the second sub rocker arm 39, and the third sub rocker arm 40 is connected to the fourth sub rocker arm 41. There is provided a connection switching mechanism (not shown) for switching between a state in which the first and third sub-rocker arms 38, 40 are not connected to any of the second and fourth sub-rocker arms 39, 41 by the action of hydraulic pressure. Thus, in a state where the third sub-rocker arm 40 is connected to the fourth sub-rocker arm 41 without connecting the first and third sub-rocker arms 38, 40 to the second sub-rocker arm 39, the first and third sub-rocker arms 38, 40 are connected. In response to the movement of the low speed cams 33 and 34, the intake valves 21 are opened / closed with characteristics corresponding to the cam profile of the low speed cams 33 and 34, and the first and third sub rocker arms 38 and 40 are moved. In the state of being connected to the second sub-rocker arm 39, both the intake valves 21... The first and third sub rocker arms 38 and 40 are driven to open and close with characteristics corresponding to 35 cam profiles, and the second and fourth sub rocker arms are driven. In a state where neither of 39 and 41 is connected, as the first sub-rocker arm 38 is driven by the low speed cam 34, one of the intake valves 21 is driven to open and close with characteristics corresponding to the cam profile of the low speed cam 33, As the third sub rocker arm 40 is driven by the decompression cam 36, the other intake valve 21 is opened at the decompression time.

  Referring to FIGS. 5 and 6 together, the intake camshaft 31 has journal portions 31a at portions corresponding to the cylinders C5 to C8, and the head cover 14 includes each journal portion. A plurality of bearing portions 14c arranged in the cylinder arrangement direction so as to rotatably support at least a half circumference of the outer circumference of 31a, in this embodiment 1, the entire circumference of the journal portion 31a ... are the side wall 14c and the ceiling wall of the head cover 14. 14b is integrally provided so as to be continuous with 14b. Further, a mounting boss 56 is integrally provided on the ceiling wall 14b of the head cover 14 at a position adjacent to one of the plurality of bearing portions 14c... In the direction along the axis of the intake camshaft 31, and the injector 106. A high pressure pump 57 for supplying fuel is attached to the mounting boss 56.

  In addition, the mounting boss 56 is a bearing portion 14c disposed in an intermediate portion along the cylinder arrangement direction 15 among the plurality of bearing portions 14c... In the first embodiment, between the seventh and eighth cylinders C7 and C8. The mounting boss 56 is provided integrally with the ceiling wall 14b of the head cover 14L at a position adjacent to the bearing portion 14c from the eighth cylinder C8 side. The mounting boss 56 determines the operating direction of the high-pressure pump 57 and the cylinder axis of the left bank BL. That is, it is integrally provided on the ceiling wall 14b of the head cover 14L in parallel with the axis of the cylinder bore 16.

  The intake camshaft 31 is provided with a pump cam 58 at a position corresponding to the high-pressure pump 57, and a roller 59 that is in rolling contact with the pump cam 58 is pivotally supported on the intake rocker shaft 32. The pump drive rocker arm 60 is supported so as to be swingable. Further, the pump driving rocker arm 60 is provided with an arm portion 60a extending toward the high pressure pump 57, and the roller 61 pivotally supported at the tip of the arm portion 60a is brought into rolling contact with the input portion 62 of the high pressure pump 57. To do. Therefore, in the high-pressure pump 57, when the pump driving rocker arm 60 swings according to the rotation of the intake camshaft 31, a driving force is applied from the pump driving rocker arm 60 to the input portion 62 of the high pressure pump 57. Therefore, it is driven in a direction parallel to the cylinder axis.

  That is, as shown in FIG. 7A, the roller 61 is in contact with the input unit 62 at a position spaced apart by a distance δA on the side opposite to the intake side rocker shaft 32 with respect to the operation axis C of the input unit 62. The input unit 62 is at the lowest position, and the roller 61 pushes up the input unit 62 while slidingly contacting the input unit 62 as the pump driving rocker arm 60 is rotated upward by the pump cam 58. 7B, the roller 61 is in contact with the input unit 62 at a position spaced by a distance δB toward the intake side rocker shaft 32 with respect to the operation axis C of the input unit 62. Is the highest position. Thus, the fuel oil discharged from the high-pressure pump 57 is supplied to the fuel rail 107 through the supply line 108.

  By the way, the distance δA between the abutting portion of the pump driving rocker arm 60 and the operation axis C when the input portion 62 is at the lowest position, and the input portion 62 are at the highest position. The distance δB between the contact portion of the pump driving rocker arm 60 to the input portion 62 and the operating axis C is set to be substantially equal to the input portion 62. The abutting portion to the input portion 62 is close to the operating axis of the input portion 62, and the input portion 62 is restrained from being inclined by the pressing force action from the pump driving rocker arm 60.

  Moreover, the contact portion of the pump drive rocker arm 60 with the pump cam 58, that is, the contact portion of the roller 59 with the pump cam 58, and the contact portion of the pump drive rocker arm 60 with the input portion 62, The abutting portion of the roller 61 with respect to the input portion 62 is parallel to the operating axis of the input portion 62 with respect to the plane PL passing through the swing center of the pump driving rocker arm 60, that is, the axis of the intake side rocker shaft 82. Arranged on the same side.

  Further, the arm portion 60a of the pump driving rocker arm 60 is pump-driven from the portion so as to bend toward the high-pressure pump 57 side from the portion supporting the roller 59 that is in rolling contact with the pump cam 58 in the pump driving rocker arm 60. It is provided integrally with the rocker arm 60, so that the length of the rocker arm 60 for driving the pump can be reduced and the weight can be reduced.

  Further, a contact portion of the pump drive rocker arm 60 with the pump cam 58 is a contact portion with the input portion 62 of the pump drive rocker arm 60 in a direction orthogonal to the plane PL, and the pump drive rocker arm. 60 is disposed between the rocking center (the axis of the intake rocker shaft 32).

  Further, on a projection view on a plane orthogonal to the axis of the intake camshaft 31, a straight line L connecting the axis of the intake camshaft 31 and the contact portion of the pump drive rocker arm 60 with the pump cam 58 is shown. As shown in FIG. 7, it is set in a direction substantially along the operation axis C of the input unit 62.

  Further, the lubricating oil of the high-pressure pump 57 is supplied with lubricating oil from the intake side rocker shaft 32. As shown in FIG. 6, the bearing 14c between the seventh and eighth cylinders C7 and C8 includes A lubricating oil passage 109 connecting the intake side rocker shaft 32 and the high pressure pump 57 is provided. Thus, the oil dripping from the lubrication part of the high-pressure pump 57 is used for lubrication of each part of the intake side valve operating device 28.

  Incidentally, the intake side camshaft 31 provided with the low speed cams 33, 34, high speed cam 35, decompression cam 36 and pump cam 58 is inserted into the head cover 141 from one end side thereof and the bearings. Are supported by the portions 14c, and the circular bearing holes 105 provided in the respective bearing portions 14c for inserting and supporting the journal portions 31a of the intake camshaft 31 and the journal portions 31a. Is set to a size that allows the low speed cams 33, 34,..., The high speed cam 35, the decompression cam 36, and the pump cam 58 to be inserted.

  Thus, if the diameter of the journal portion 31a... And the bearing hole 105... Is reduced in order to reduce the size of the head cover 14l, the pump cam 58 is also formed smaller. Driven by the arm portion 60a of the pump drive rocker arm 6060 to be driven, the stroke required by the high pressure pump 57 is sufficiently set by setting the lever ratio of the pump drive rocker arm 6060 even if the pump cam 58 is small. Can be secured.

  2 and 3, the exhaust side valve operating device 29 in the eighth cylinder C8 is provided with a pair of low speed cams 63, 64 and a single high speed cam 65 and a bearing portion of the head cover 14L. 14c ... has an exhaust side camshaft 68 arranged in parallel with the intake side camshaft 31 so as to be rotatably supported, and an axis parallel to the exhaust side camshaft 68 to the bearing portion 14c ... The exhaust side rocker shaft 69 is supported, the first, second and third sub rocker arms 70, 71, 72 supported so as to be swingable by the exhaust side rocker shaft 69, and one end portion of the cylinder through the hydraulic tappet 75. The first and second rocker arms 76 and 77 are pivotally supported by the head 13 and the other end abuts against the stem ends 22a of the exhaust valves 22. The support structure of the exhaust camshaft 68 at 14c ... are the same as the support structure for the intake camshaft 31 in the bearing portion 14c ....

  Focusing on FIG. 1, a boss mounted on the ceiling wall 14b of the head cover 14R at a position adjacent to the bearing portion 14c of the cylinder head 14R from the fourth cylinder C4 side between the third and fourth cylinders C3 and C4 of the right bank BR. 56 is provided, and a high-pressure pump 57 that is driven in the same manner as the high-pressure pump 57 on the left bank BL side is attached to the mounting boss 56.

  Next, the operation of the first embodiment will be described. A plurality of head covers 14L, 14R covering one surface of the cylinder heads 13L of the engine body 11 are rotatably supported on the entire outer periphery of the intake camshaft 31. Are integrated with each other, and are positioned adjacent to one of the plurality of bearings 14c in the direction along the axis of the intake camshafts 31 in the first embodiment. The head cover 14L, at a position adjacent to the bearing portion 14c between the cylinders C7 and C8 from the eighth cylinder C8 side and at a position adjacent to the bearing portion 14c between the third and fourth cylinders C3 and C4 from the fourth cylinder C4 side. Since the high pressure pumps 57 are mounted on the mounting bosses 56, the ribs for reinforcement are unnecessary, and the thickness of the head covers 14L, 14R can be increased. Without it is possible to improve the mounting bosses 56 ... rigidity, it is possible to avoid the increase in weight of the engine body 11. Moreover, since the relative positional accuracy of the bearing portion 14c between the seventh and eighth cylinders C7 and C8 and the bearing portion 14c and the mounting bosses 56 between the third and fourth cylinders C3 and C4 can be maintained high, it is used for the pump. The relative positional accuracy of the cams 58 and the high-pressure pumps 57 can be increased.

  Moreover, in the first embodiment, the intake side camshafts 31 are inserted into the head holes 14L and 14R from one end thereof and inserted into and supported by the bearing holes 105 of the bearing portions 14c integrated with the head covers 14L and 14R. Therefore, the relative positions of the intake-side camshafts 31 and the high-pressure pumps 57 are compared with those in which the intake-side camshafts 31 are rotatably supported so as to be sandwiched between the divided bearing portions. Accuracy can be increased.

  The engine body 11 is provided with first to fourth cylinders C1 to C4 and fifth to eighth cylinders C5 to C8 arranged in a cylinder arrangement direction 15 parallel to the axial direction of the intake camshafts 31. , The mounting bosses 56... Of the plurality of bearings 14 c... Are disposed at the intermediate part along the cylinder arrangement direction 15. In this embodiment 1, the time between the seventh and eighth cylinders C 7 and C 8 is received. Since the head cover 14L and 14R are integrally provided adjacent to the portion 14c and the bearing portion 14c between the third and fourth cylinders C3 and C4, it is possible to prevent the engine body 11 from being enlarged in the cylinder arrangement direction 15. In addition, the high-pressure pump 57 may be damaged when an assembly operation for mounting the engine body 11 on a vehicle is performed or when an impact is applied to the engine body 11 from the vehicle side in a vehicle-mounted state. It is possible to prevent.

  Further, the abutting portion of the pump driving rocker arm 60 to the pump cam 58 and the abutting portion of the pump driving rocker arm 60 to the input portion 62 are parallel to the operation axis of the input portion 62 and are connected to the pump driving rocker arm 60. Are arranged on the same side with respect to the plane PL passing through the oscillation center of the shaft, and therefore, the force point which is a contact portion of the pump drive rocker arm 60 with respect to the pump cam 58 and the high pressure pump 57 with respect to the plane PL. The operating point that is the contact portion of the pump driving rocker arm 60 to the input portion 62 is arranged on the same side, and the pump driving rocker arm 60 is not enlarged, and the pump cam 58 drives the pump. The force applied to the rocker arm 60 is transmitted from the pump driving rocker arm 60 to the high pressure pump 57 without being reversed, and the driving force point and the operating point are brought close to each other. By doing so, not only can the driving force be transmitted efficiently, but also the bending of the pump driving rocker arm 60 can be suppressed, and the pump driving rocker arm 60 itself and the pump driving rocker arm 60 can be supported. It is not necessary to be particularly strong.

  Further, the contact portion of the pump drive rocker arm 60 with the pump cam 58 is in contact with the input portion 62 of the pump drive rocker arm 60 in the direction perpendicular to the plane PL, and the pump drive rocker arm 60. The pump drive rocker arm 60 can be shortened, thereby reducing the weight of the pump drive rocker arm 60 and suppressing the bending of the pump drive rocker arm 60. be able to.

  Further, on a projection view on a plane orthogonal to the axis of the intake camshaft 31, a straight line L connecting the axis of the intake camshaft 31 and the contact portion of the pump drive rocker arm 60 with the pump cam 58 is shown. Since the input portion 62 is set in a direction substantially along the operation axis C, when the high-pressure pump 57 is driven by the pump drive rocker arm 60, the axis of the input portion 62 is inclined from the operation direction and the sliding resistance is increased. It is suppressed.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the present invention described in the claims. Is possible.

  For example, the present invention is applicable not only to a V-type multi-cylinder internal combustion engine but also to an in-line multi-cylinder internal combustion engine.

14L, 14R: Head cover 28 as a cover member ... Intake side valve device 31 as a valve operating device ... Intake side camshaft 57 as a camshaft ... High pressure pump 58 ... Pump cam 60... Rocker arm 62 for driving the pump 62... Input portion C... Operation axis L.

Claims (3)

  A high pressure pump (57) having an input portion (62) operating in the axial direction is attached to a cover member (14L, 14R) that covers the valve gear (28) including the camshaft (31), and the camshaft (31 The pump drive rocker arm (60) that swings in accordance with the pump cam (58) between the pump cam (58) provided on the high pressure pump (57) and the input portion (62) of the high pressure pump (57). In the internal combustion engine in which the pump drive rocker arm (60) is in contact with the pump cam (58) and the pump drive rocker arm (60) is connected to the input part (62). The contact portion is arranged on the same side with respect to a plane (PL) passing through the swing center of the pump drive rocker arm (60) in parallel with the operation axis of the input portion (62). To internal combustion engine It takes a high-pressure fuel pump drive structure.   The abutment portion of the pump drive rocker arm (60) with the pump cam (58) is connected to the input portion (62) of the pump drive rocker arm (60) in a direction perpendicular to the plane (PL). 2. The high-pressure pump drive structure for an internal combustion engine according to claim 1, wherein the high-pressure pump drive structure is disposed between the contact portion and a rocking center of the pump drive rocker arm (60).   On the projection onto the plane orthogonal to the axis of the camshaft (31), the axis of the camshaft (31) and the contact portion of the pump drive rocker arm (60) with the pump cam (58) The high-pressure pump drive structure in an internal combustion engine according to claim 1 or 2, wherein a straight line (L) connecting the two is set in a direction substantially along the operation axis (C) of the input section (62).

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