JP2008038846A - Internal combustion engine lubrication structure - Google Patents

Abstract

In an oil supply structure having a conveyance path for supplying lubricating oil to the camshafts for intake and exhaust, a capacity of an oil pump serving as a conveyance source of the lubricating oil can be reduced.
A conveying path is provided in an inner space of a cylinder head cover 3L (3R) downstream of an oil supply path 33L (33R) for sending the lubricating oil in a lubricating oil reservoir 4 of the internal combustion engine to the cylinder head 2L (2R). It has been. Lubricating oil discharge ports 41 a and 42 a are provided at a plurality of locations in the transport direction of the transport path 36. The number of discharge ports 41a and 42a installed is the same as the number of groups when any number of cam lobes 13a and 14a provided on the camshafts 13 and 14 are divided into one group, and the discharge ports 41a and 42a. Lubricating oil is supplied across the plurality of cam lobes 13a, 14a, each included in a corresponding group.
[Selection] Figure 12

Description

  The present invention relates to an oil supply structure having a conveyance path for supplying lubricating oil to a camshaft side for intake and exhaust of a multi-cylinder internal combustion engine.

  Generally, in an internal combustion engine, lubricating oil in an oil pan is sucked up by an oil pump and supplied to a valve operating mechanism disposed on the cylinder head side.

  As the oil supply structure of this valve operating mechanism, there are an oil supply path for sending the lubricating oil in the oil pan to the cylinder head side, and a conveyance path connected downstream of the oil supply path for conveying the lubricating oil to the camshaft side. Have.

  This transport path is, for example, a shower pipe attached to the inner surface of the cylinder head cover. Lubricating oil is respectively supplied from a discharge port formed of through holes provided at several places in the longitudinal direction toward a plurality of cam lobes provided on the camshaft. Some have come to be sprayed (for example, see Patent Document 1).

Conventionally, lubricating oil is sprayed from one of the discharge ports provided at a plurality of locations in the transport direction of the transport path to each of the plurality of cam lobes provided on the camshaft.
JP-A-8-28235

  In the above-described conventional example, the number of discharge ports on the conveyance path is set equal to the number of cam lobes provided on the camshaft. Since it is necessary to increase the number of oil pumps, the oil pressure loss for sending the lubricating oil from the oil pan of the internal combustion engine to the end of the conveying path will increase, and the capacity of the oil pump as the lubricating oil conveying source will be increased. Need to be done.

  For this reason, there is room for improvement, such as the equipment cost of the oil supply structure and the burden on the internal combustion engine accompanying the drive of the oil pump.

  By the way, in addition to the conveyance path on the camshaft side, a conveyance path for supplying lubricating oil to the hydraulic lash adjuster provided in the valve operating mechanism is installed in parallel with the conveyance path on the camshaft side. In this case, since the amount of the lubricating oil transported increases, the oil pump tends to require a large capacity.

  The present invention makes it possible to reduce the capacity of an oil pump serving as a lubricating oil conveying source in an oil supply structure having a conveying path for supplying lubricating oil to the intake / exhaust camshaft side of an internal combustion engine. It is aimed.

  The present invention relates to an oil supply structure having a conveying path for supplying lubricating oil to the intake / exhaust camshaft side of a multi-cylinder internal combustion engine, and the conveying path supplies the lubricating oil in the lubricating oil reservoir of the internal combustion engine. It is provided in the cylinder head cover inner space downstream of the oil supply passage to be sent to the cylinder head side, and lubricating oil discharge ports are provided at a plurality of locations in the lubricating oil conveyance direction. The lubricating oil is supplied across the plurality of cam lobes included in the corresponding group, the number of which is equal to the number of the groups when the arbitrary number of all the cam lobes included in the group is divided into one group. It is characterized by.

  According to this configuration, it is possible to reduce the number of installed lubricating oil discharge ports as compared with the conventional example, so that the lubricating oil is sent from the lubricating oil reservoir of the internal combustion engine to the end of the conveyance path. The hydraulic pressure loss is smaller than in the conventional example.

  As a result, it is possible to reduce the capacity of the oil pump serving as the lubricating oil conveyance source, which is advantageous in reducing the facility cost of the oil supply structure and the burden on the internal combustion engine accompanying the driving of the oil pump.

  Preferably, the transport path is a shower pipe having a discharge port formed of a hole penetrating in a radial direction in a peripheral wall at a plurality of locations in the transport direction, and is supported by the inner surface of the cylinder head cover.

  If the transport path is configured with a shower pipe as in this configuration, for example, even when the transport path made of a shower pipe has a complicated bent shape, it can be relatively easily processed into a desired shape by bending it. Thus, the degree of freedom of design is expanded.

  Preferably, the discharge port is opened in such a direction that the lubricant is sprayed directly between the cam lobes of each group.

  According to this configuration, the lubricating oil discharged from the discharge port bounces off at the cam lobe or cam journal of the camshaft and scatters over a wide area to supply the lubricating oil to a place where it is difficult to reach. Will also be possible.

  Preferably, a conveyance path for supplying lubricating oil to the hydraulic lash adjuster side provided in the valve mechanism of the internal combustion engine is provided in parallel with the conveyance path on the camshaft side downstream of the oil supply path.

  In this configuration, when a two-system conveying path is installed on the cylinder head side, that is, the camshaft side and the lash adjuster side, it is required to increase the capacity of the oil pump as a lubricating oil conveyance source. However, even in such a case, it is advantageous that an oil pump having a relatively small capacity can be used as compared with the conventional example.

  According to the present invention, the number of discharge ports installed in the camshaft side conveyance path is made as small as possible from the number of cam lobes provided in the camshaft. The hydraulic pressure loss for sending the lubricating oil to the end can be reduced as compared with the conventional example, and the capacity of the oil pump serving as the lubricating oil conveyance source can be reduced. This is advantageous in reducing the facility cost of the oil supply structure and the burden on the internal combustion engine accompanying the drive of the oil pump.

  Hereinafter, an embodiment of the present invention will be described with reference to FIGS. First, FIG. 1 to FIG. 12 show an embodiment of the present invention.

  Prior to description of an oil supply structure for an internal combustion engine according to the present invention, a schematic configuration of an internal combustion engine to which the oil supply structure is applied will be described with reference to FIGS. 1 and 2.

  1 and 2 show a schematic configuration of an internal combustion engine (also referred to as an engine) mounted on a vehicle such as an automobile. The internal combustion engine here is, for example, a V-type six-cylinder DOHC gasoline engine.

  In the figure, 1 is a cylinder block, 2L and 2R are cylinder heads, 3L and 3R are cylinder head covers, and 4 is an oil pan (lubricating oil reservoir).

  The illustrated internal combustion engine includes six combustion chambers 6 defined by six cylinder bores of a cylinder block 1, two cylinder heads 2L and 2R, and six pistons 5, and air introduced from an intake system and an intake port 2a. A predetermined ratio of air-fuel mixture consisting of fuel injected from the fuel injection valves 7A and 7B is supplied, and this air-fuel mixture is ignited by the spark plug 8 and burned, whereby the crankshaft is connected from the piston 5 through the connecting rod 9. 10 is rotated. The exhaust gas after combustion is discharged from the exhaust port 2b to the exhaust system.

  The cylinder block 1 has two banks 1L and 1R on the left and right. The cylinder heads 2L and 2R are mounted and fixed on the upper portions of the banks 1L and 1R, respectively, and an oil pan 4 is attached to the lower portion of the cylinder block 1. Yes.

  The two cylinder heads 2L and 2R are respectively provided with an intake valve 11 for opening and closing the intake port 2a and an exhaust valve 12 for opening and closing the exhaust port 2b.

  An intake camshaft 13 that opens and closes the intake valve 11 and an exhaust camshaft 14 that opens and closes the exhaust valve 12 are mounted on camshaft housings 15L and 15R that are separate from the cylinder heads 2L and 2R. The camshafts 13 and 14 are rotatably supported by bolting the cam caps 16 to the camshaft housings 15L and 15R.

  The intake side camshaft 13 and the exhaust side camshaft 14 are rotationally driven by the crankshaft 10 via a timing chain (or timing belt) (not shown).

  Two intake valves 11 and two exhaust valves 12 are arranged for each cylinder, and one intake side camshaft 13 and one exhaust side camshaft 14 are used as a set, and each cylinder head 2L, 2R. Each intake-side camshaft 13 and each exhaust-side camshaft 14 are provided with six cam lobes 13a, 14a, respectively, and each of the cam lobes 13a, 14a drives the intake valve 11 and the exhaust valve 12. It is like that.

  Rocker arms 17... Are arranged between the cam lobes 13 a and 14 a of the camshafts 13 and 14 and the valves 11 and 12.

  Note that the center of the intake camshaft 13 is offset from the center axis of the intake valve 11, and the center of the exhaust camshaft 14 is offset from the center axis of the exhaust valve 12. The rocker arms 17 are tilted by the cam lobes 13 a and 14 a of the camshafts 13 and 14, and the valves 11 and 12 are pressed by the rocker arms 17.

  The rocker arm 17 is an end pivot type, and a roller (reference numeral omitted) on which the cam lobes 13a and 14a of the camshafts 13 and 14 abut is rotatably provided at the center in the longitudinal direction. .

  Further, lash adjusters 18... Are arranged in order to ensure that the valve clearance between the cam lobes 13a, 14a of the cam shafts 13, 14 and the rollers of the rocker arms 17 is always an appropriate value.

  As shown in FIG. 3, the lash adjuster 18 has a generally known hydraulic type, and its body 18a is attached in a state where it is embedded in appropriate positions of the cylinder heads 2L and 2R. The external projecting end of the plunger 18b slidably accommodated in the body 18a is in contact with the position serving as the tilting fulcrum of the rocker arm 17, that is, one end in the longitudinal direction.

  The above-described intake valve 11, exhaust valve 12, intake side camshaft 13, exhaust side camshaft 14, rocker arm 17, lash adjuster 18 and the like are referred to as a valve operating mechanism.

  This valve operating mechanism is concealed from the outside by cylinder head covers 3L, 3R attached to the upper parts of the two cylinder heads 2L, 2R.

  In the internal combustion engine exemplified in this embodiment, hydraulic variable valve timing mechanisms (VVT) 21 and 22 are attached to the intake camshaft 13 and the exhaust camshaft 14.

  The variable valve timing mechanisms 21 and 22 control the valve timing (opening and closing) of the intake valve 11 and the exhaust valve 12 by continuously varying the phases of the intake camshaft 13 and the exhaust camshaft 14 as necessary. Is.

  These variable valve timing mechanisms 21 and 22 are of a type generally called a known vane actuator, for example, and have an advance hydraulic chamber and a retard hydraulic chamber, although not shown in detail. The intake side camshaft 13 is driven to the advance side or the retard side by controlling the hydraulic pressure supply to one of the hydraulic chambers with an oil control valve (OCV) 23.

  Next, an oil supply structure for the internal combustion engine configured as described above will be described.

  In the above-described internal combustion engine, as shown in FIGS. 1 and 2, the lubricating oil in the oil pan 4 provided at the bottom of the cylinder block 1 is sucked up by an oil pump (OP) 25 and filtered by an oil filter (OF) 26. Then, the oil is supplied to the cylinder block 1 through an oil supply passage 31 called a main oil hole or a main gallery, and two through two oil supply passages 32L, 32R, 33L, and 33R. The cylinder heads 2L and 2R are individually supplied.

  The oil pump 25 is rotationally driven by the crankshaft 10 via an appropriate belt not shown.

  The cylinder block-side oil supply passage 31 conveys the lubricating oil in the lateral direction (cylinder arrangement direction) inside the cylinder block 1 and performs lubrication of the crankshaft journal portion and in-cylinder lubrication by an oil jet. The lubricating oil that has lubricated and cooled each part in the cylinder block 1 is returned to the oil pan 4.

  On the other hand, the two cylinder head side oil supply passages 32L, 32R, 33L, 33R are lubricated in a diagonally vertical direction (a direction inclined at a predetermined angle with respect to the cylinder longitudinal direction) from the cylinder block 1 to the two cylinder heads 2L, 2R. Oil is conveyed to lubricate each part constituting the valve operating mechanism, and the advance side hydraulic chamber and the retard side hydraulic chamber of the variable valve timing mechanisms 21, 22 through the oil control valves 23. The hydraulic pressure is supplied to (omitted) and then returned to the oil pan 4.

  Thus, the lubricating oil in the oil pan 4 is circulated and used inside the internal combustion engine.

  Here, the part to which the features of the present invention are applied will be described in detail.

  The two cylinder head side oil supply passages 32L, 32R serving as the first system are connected to the front end side of the cylinder block side oil supply passage 31, and a total of four variable valve timing mechanisms 21 provided in the left and right banks 1L, 1R. , 22, the lubricating oil is supplied to the oil control valve 23 of the variable valve timing mechanism 21 on the intake side in each of the banks 1L, 1R.

  In each bank 1L, 1R, each oil control valve 23 of the intake side variable valve timing mechanism 21 and each oil control valve 23 of the exhaust side variable valve timing mechanism 22 communicate with each other through relay paths 34L, 34R. The lubricating oil is sent from the oil control valve 23 on the intake side to the oil control valve 23 on the exhaust side through the relay paths 34L and 34R.

  The two cylinder head side oil supply passages 33L and 33R serving as the second system are connected to the rear end side of the cylinder block side oil supply passage 31, and are connected in parallel to each other downstream via joints 35L and 35R. Lubricating oil is supplied to the intake side camshaft 13 and the exhaust side camshaft 14 side and the lash adjuster 18 side provided in the two banks 1L and 1R, respectively, through the two systems of transport paths 36 and 37. .

  The joints 35L and 35R have, for example, a cylindrical shape. As shown in FIG. 10, the joint 35L, 35R is provided with a receiving passage 35a that is open at the lower end surface and extends upward along the center line. One discharge passage 35b that opens radially outward is provided near the opening, and two discharge passages 35c and 35d that open outward in the radial direction are provided at two positions near the back of the receiving passage 35a. It has been.

  The cylinder head-side oil supply passages 33L and 33R are connected to the lower openings of the receiving passages 35a and 35a of the joints 35L and 35R, respectively, in a state where they are inserted correspondingly.

  The camshaft side conveyance path 36 is a pair of shower pipes 41 and 42 disposed in the banks 1L and 1R.

  As shown in FIG. 11, one end side of the shower pipes 41 and 42 constituting the camshaft side conveying path 36 is at the back of the two discharge passages 35b, 35c and 35d in the joints 35L and 35R, that is, in the vertical direction. It is connected to the discharge passages 35c and 35d at two circumferential positions located on the upper side.

  The shower pipes 41 and 42 of the banks 1L and 1R are open at one end in the longitudinal direction and closed at the other end in the longitudinal direction (free end side), and radially around the peripheral walls at a plurality of locations in the longitudinal direction. Discharge ports 41a and 42a each having a penetrating hole are provided.

  The shower pipes 41 and 42 are bolted to the inner surfaces of the cylinder head covers 3L and 3R via a plurality of appropriate support members 46, and one shower pipe 41 is located above the intake side camshaft 13 or The other shower pipe 42 is arranged above the exhaust side camshaft 14.

  The shower pipes 41 and 42 are made of an appropriate metal material or resin material, and are appropriately bent as shown in FIGS.

  As described above, the camshaft side conveying path 36 has an open structure that releases the lubricating oil into the cylinder head cover inner space in the middle of the lubricating oil conveying direction.

  The lash adjuster side conveyance path 37 communicates, in each of the banks 1L and 1R, a single pipe 43 whose both ends in the longitudinal direction are open and a cylinder head passage 44 formed inside the cylinder heads 2L and 2R. It has a connected structure.

  One end side of the pipe 43, which is one component of the lash adjuster side conveyance path 37, is located near the opening, that is, in the vertical direction lower side of the two discharge passages 35b, 35c, 35d in the joints 35L, 35R. It is connected to a single discharge passage 35b.

  The pipe 43 is made of an appropriate metal material or resin material, and is appropriately bent as shown in FIGS.

  As shown in FIG. 2, the cylinder head inner passage 44 is provided, for example, in a substantially straight line in the lateral direction (cylinder arrangement direction) in the walls of the cylinder heads 2 </ b> L and 2 </ b> R. Is provided with an introduction portion 44a that opens toward the upper surface of the wall portion of the cylinder head 2L, 2R.

  As shown in FIGS. 2 and 3, several points in the longitudinal direction of the cylinder head passage 44 are communicated with oil holes 18c provided in individual bodies 18a of the lash adjuster 18, and the introduction portion The other end side (free end side) of the pipe 43 is connected to 44a.

  In this way, the lash adjuster-side conveyance path 37 has a structure that is completely sealed from the joints 35L and 35R to the inside of the lash adjuster 18, so that lubricating oil does not leak into the cylinder head cover in the middle of the conveyance direction. It has become.

  In this embodiment, the single pipe 43, which is a constituent element of the lash adjuster side conveyance path 37, is bent into a substantially “h” shape when viewed from the side, as shown in FIGS. It has become.

  This pipe 43 is formed by discharging the shower pipes 41 and 42 in a state where the pair of shower pipes 41 and 42 constituting the camshaft side conveyance path 36 is not attached to the cylinder heads 2L and 2R. It arrange | positions in the perpendicular direction lower side rather than the exits 41a and 42a.

  Specifically, in a state where the pair of shower pipes 41 and 42 are set in a horizontal posture without being attached to the cylinder heads 2L and 2R, the pipe 43 has an upstream region, that is, a region near the joints 35L and 35R. It is arranged below the pipes 41 and 42 in the vertical direction, and the middle part in the longitudinal direction is once raised up above the two shower pipes 41 and 42 in the vertical direction. It is bent so as to be arranged below the shower pipes 41 and 42 in the vertical direction.

  Next, the installation locations of the plurality of discharge ports 41a and 42a provided in the shower pipes 41 and 42 constituting the camshaft side conveyance path 36 will be described in detail.

  In short, as shown in FIG. 12, the number of outlets 41a and 42a installed is the same as the number of groups when any number of cam lobes 13a and 14a provided on the camshafts 13 and 14 is divided into one group. The discharge ports 41a and 42a are arranged so as to supply lubricating oil across the plurality of cam lobes 13a and 14a included in the corresponding group.

  Specifically, in the internal combustion engine in this embodiment, first, in the discharge ports 41a and 42a, the lubricating oil is sprayed directly toward the cam lobes 13a and 14a included in each group (for example, obliquely downward). It is open to.

  In consideration of the configuration in which the internal combustion engine in this embodiment has two intake valves 11 and two exhaust valves 12 per cylinder, the intake side camshaft 13 and the exhaust side camshaft 14 In FIG. 1, the two cam lobes 13a and 14a arranged adjacent to each other in the axial direction corresponding to the two intake valves 11 and the two exhaust valves 12 per cylinder are set as one group.

  In other words, both the number of outlets 41a of the shower pipe 41 for the intake side camshaft 13 and the number of outlets 42a of the shower pipe 42 for the exhaust side camshaft 14 are both set to one bank 1L (1R). ) Is the same as the number of cylinders.

  That is, the lubricating oil is directly sprayed across the two cam lobes 13a (14a) included in one group by one discharge port 41a (42a).

  By the way, the lubricating oil discharged from the discharge ports 41a, 42a spreads in a shower shape at an appropriate angle because of the relationship that the discharge pressure of the oil pump 25 is applied and the oil is discharged vigorously. As described above, the lubricating oil can be sprayed across the plurality of cam lobes 13a and 14a.

  Since the lubricant oil sprayed in this manner rebounds at the cam lobes 13a and 14a and cam journal portions (reference numerals omitted) of the camshafts 13 and 14 and scatters over a wide range to the periphery thereof, the lubricant oil reaches the end. Supply to difficult places is also possible.

  In short, as described above, the number of installation of the discharge ports 41a and 42a of the camshaft side conveyance path 36 installed in the cylinder heads 2L and 2R is reduced to half that of the conventional example. Effects and effects can be obtained.

  First, the loss of hydraulic pressure for sending the lubricating oil from the oil pan 4 of the internal combustion engine to the end of the camshaft side conveyance path 36 is smaller than that of the conventional example. This is advantageous in reducing the cost of the oil supply structure and the burden on the internal combustion engine accompanying the driving of the oil pump 25, such as the capacity of the oil pump 25 serving as a lubricant source being reduced. .

  Further, in the case where the two systems of conveying paths 36 and 37 on the camshaft side and the lash adjuster side are installed on the cylinder heads 2L and 2R side as in this embodiment, an oil pump as a lubricating oil conveying source is provided. However, even in such a case, it is advantageous that the oil pump 25 having a relatively small capacity can be used as compared with the conventional example.

  Furthermore, in the above embodiment, the camshaft side conveyance path 36 is constituted by the shower pipes 41 and 42 and a part of the lash adjuster side conveyance path 37 is constituted by the pipe 43. Even in the case where the plate 37 has a complicated bent shape, it is preferable in that the degree of freedom in design is widened such that it is relatively easy to process the plate into a desired shape by bending.

  Hereinafter, other embodiments of the present invention will be described.

  (1) In the above embodiment, a V-type six-cylinder internal combustion engine is taken as an example, but the number of cylinders is particularly limited, such as a V-type eight-cylinder type, a V-type ten-cylinder type, a V-type twelve-cylinder type, and the like. In addition, the features of the present invention can be applied to an in-line multi-cylinder type internal combustion engine in the same manner as in the above embodiment.

  As an example, FIGS. 13 and 14 show other embodiments to which the features of the present invention are applied. In this embodiment, an in-line four-cylinder DOHC gasoline engine is taken as an example of the internal combustion engine.

  Simply speaking, the cylinder block 1 in this internal combustion engine has only one bank of the V-type six cylinders described in the above embodiment, and the one bank is increased by one cylinder from three cylinders to four cylinders. It has a configuration like this.

  The camshaft-side transport path 36 and the lash adjuster-side transport path 37 disposed in the single cylinder head 2 have basically the same configurations as those shown in FIGS.

  However, in this embodiment, since the internal combustion engine is an in-line four-cylinder DOHC gasoline engine, the number of cam lobes 13a, 14a of the intake side camshaft 13 and the exhaust side camshaft 14 is eight, so that the intake side And the number of lash adjusters 18 on the exhaust side is sixteen, a total of sixteen.

  The number of the outlets 41a and 42a of the shower pipes 41 and 42 in the camshaft side conveyance path 36 is set so that the two adjacent cam lobes 13a and 14a in the intake side camshaft 13 and the exhaust side camshaft 14 are grouped. As a thing, four discharge ports 41a and 42a of shower pipes 41 and 42 are provided.

  In the case of this embodiment, basically the same operations and effects as those of the above embodiment can be obtained.

  (2) In the said embodiment, the number of installation of the discharge outlets 41a and 42a of the shower pipes 41 and 42 is not specifically limited.

  For example, the number of the discharge ports 41a and 42a can be further reduced. However, the smaller the number of the discharge ports 41a and 42a, the more widely the lubricating oil discharged from one discharge port 41a and 42a is set to be dispersed. Is preferred. For reference, for example, if the discharge ports 41a and 42a have a shape that gradually increases in diameter from the inside to the outside, it is advantageous in spreading the lubricating oil over a wide range.

  (3) In the above embodiment, the discharge ports 41a and 42a of the shower pipes 41 and 42 are opened toward the camshafts 13 and 14, but the opening direction is not particularly limited. Alternatively, it may be directed upward from the horizontal direction.

  In this case, for example, as shown in FIG. 15, the lubricating oil discharged upward is collided with members such as the cylinder head covers 3L, 3R and bounced back, and the lubricating oil is applied to the camshafts 13, 14 to be lubricated. It is preferable to adopt a form in which the slag is dispersed. In this way, it is possible to approximate the dispersion of the lubricating oil as described in the above embodiment.

  (4) In the above embodiment, the configurations and shapes of the camshaft side conveyance path 36 and the lash adjuster side conveyance path 37 disposed in the cylinder heads 2L and 2R are not particularly limited, and are characteristic of the present invention. It is possible to change appropriately within the range including

  (5) In the above embodiment, the type and detailed configuration of the internal combustion engine are not particularly limited. For example, in the above embodiment, an example in which the valve operating mechanism is a rocker arm type is given. However, even when the valve operating mechanism is a direct acting type, the features of the present invention can be applied in the same manner as in the above embodiment.

  However, in the case of an internal combustion engine in which the valve mechanism is a direct acting type, a cam journal is formed adjacent to the valve lifter, and the cam lobe is generally lubricated with lubricating oil from the cam journal. Although it is considered necessary to make the passage 44 different from that of the above-described embodiment, the pipes 43 constituting the camshaft-side conveyance path 36 and the shower pipes 41 and 42 and the lash adjuster-side conveyance path 37 are described above. It can be basically the same as the embodiment.

It is sectional drawing which looked at one Embodiment of the internal combustion engine to which the characteristic of this invention was applied from the front end side. It is a perspective view which shows typically the oil supply structure of the internal combustion engine shown in FIG. It is a figure which expands and shows a part of valve operating mechanism in the one-side bank of FIG. FIG. 2 is a partially exploded perspective view showing the internal combustion engine shown in FIG. 1. 5 is a detailed plan view of the camshaft side conveyance path and the lash adjuster side conveyance path of FIG. 4 as viewed from above. FIG. FIG. 5 is a detailed plan view of the camshaft side conveyance path and the lash adjuster side conveyance path of FIG. 4 as viewed from below. It is the figure seen from the arrow (7) side in FIG. 5 and FIG. It is the figure seen from the arrow (8) side in FIG. 5 and FIG. It is the figure seen from the arrow (9) side in FIG. 5 and FIG. FIG. 6 is a cross-sectional view taken along line (10)-(10) in FIG. 5. It is an arrow view of the (11)-(11) line cross section of FIG. FIG. 12 schematically shows the relative positional relationship between the discharge port of the camshaft side conveyance path shown in FIGS. 5 to 11 and the cam lobe of the camshaft, as viewed from the side of the internal combustion engine. A cross-sectional view of another embodiment of the internal combustion engine to which the features of the present invention are applied is viewed from the front end side, and corresponds to FIG. It is a perspective view which shows typically the oil supply structure of the internal combustion engine shown in FIG. 13, and respond | corresponds to FIG. Still another embodiment of the present invention corresponds to FIG.

Explanation of symbols

1 Cylinder block 1L, 1R Cylinder block left and right banks 2L, 2R Cylinder head 3L, 3R Cylinder head cover
4 Oil pan (lubricating oil reservoir)
DESCRIPTION OF SYMBOLS 11 Intake valve 12 Exhaust valve 13 Intake side camshaft 13a Intake side camshaft cam lobe 14 Exhaust side camshaft 14a Exhaust side camshaft cam lobe 25 Oil pump (lubricant conveyance source)
33L, 33R Second system cylinder head side oil supply passages 35L, 35R Joint 36 Camshaft side conveyance passages 41, 42 Shower pipes 41a, 42a constituting camshaft side conveyance passages 36 Shower pipe discharge ports

Claims (4)

An oil supply structure having a conveyance path for supplying lubricating oil to a camshaft side for intake and exhaust of a multi-cylinder internal combustion engine,
The conveying path is provided in the cylinder head cover inner space downstream of the oil supply path for sending the lubricating oil in the lubricating oil reservoir of the internal combustion engine to the cylinder head side, and there are lubricating oil discharge ports at a plurality of locations in the lubricating oil conveying direction. Provided,
The number of discharge ports installed is the same as the number of groups when any number of cam lobes provided on the camshaft is divided into one group, and each of these discharge ports is included in a corresponding group. An oil supply structure for an internal combustion engine, characterized in that lubricating oil is supplied across the cam lobe.   2. The fuel supply structure for an internal combustion engine according to claim 1, wherein the transport path is a shower pipe having a discharge port formed of a hole penetrating in a radial direction in a plurality of peripheral walls in the transport direction, and is supported by an inner surface of a cylinder head cover. An oil supply structure for an internal combustion engine.   3. An oil supply structure for an internal combustion engine according to claim 1, wherein the discharge port is opened in such a direction that the lubricant is directly sprayed between the cam lobes of each group. Construction.   The oil supply structure for an internal combustion engine according to any one of claims 1 to 3, wherein a conveyance path for supplying lubricating oil to a hydraulic lash adjuster provided in a valve operating mechanism of the internal combustion engine is provided downstream of the oil supply path. An oil supply structure for an internal combustion engine, wherein the oil supply structure is provided in parallel with the conveyance path on the camshaft side.

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