The present invention relates to techniques of an oil feed member for feeding lubricant to lubrication portions of valve gears for opening and closing intake and exhaust valves of an engine, and a lubricant feed mechanism for an engine provided with the same.
Conventionally, there have been publicly known techniques of an oil feed member for feeding lubricant to lubrication portions of valve gears for opening and closing intake and exhaust valves of an engine, and a lubricant feed mechanism for an engine provided with the same, as described in, for example, Patent Literature 1.
Patent Literature 1 describes an oil feed member (shower pipe) mounted on a cylinder cover of a cylinder head of an engine. The oil feed member is provided with an oil feed port for receiving lubricant to be fed to the oil feed port, and a plurality of discharge ports for discharging lubricant. To the oil feed member, lubricant guided by an oil passage such as an oil gallery of the cylinder head is fed.
In such a configuration, the lubricant fed from the oil passage such as the oil gallery through the oil feed port is discharged from the oil feed member through the plurality of discharge ports, so that the lubricant can be fed to lubrication portions (cams of camshaft) of valve gears disposed below the oil feed member.
However, in the technique described in Patent Literature 1, when the lubricant is fed to the oil feed member by the oil passage such as the oil gallery of the cylinder head, the closer to the oil feed port the discharge port is, more excessively the lubricant is fed. That is, there is a disadvantage that the lubricant is excessively fed from the oil feed member to the lubrication portions of the valve gears.
Patent Literature 1: JP 2008-38846 A
The present invention has been made in view of the above circumstances, and the problem to be solved is to provide an oil feed member capable of preventing lubricant from being excessively fed from an oil feed member to lubrication portions of valve gears, and a lubricant feed mechanism for an engine provided with the same.
The problem to be solved by the present invention is described above, and solutions for solving this problem are described as follows.
An oil feed member of the present invention is an oil feed member for feeding lubricant to lubrication portions of valve gears for opening and closing intake and exhaust valves of an engine, the oil feed member including: a pair of panel members laid over each other; and an oil passage formed by recessing laid surfaces of the pair of panel members, wherein the oil passage includes a downstream oil passage formed on a downstream side, and an upstream oil passage formed on an upstream side and having a smaller lubricant flow area than that of the downstream oil passage.
In the oil feed member of the present invention, the upstream oil passage includes a bent part that is bent to give pressure loss to the lubricant.
In the oil feed member of the present invention, the bent part includes an acute angle bent part that is bent at an acute angle.
In the oil feed member of the present invention, the oil feed member further includes: an oil feed port formed in an upstream end portion of the oil passage, for receiving the lubricant to be fed to the oil passage; a plurality of discharge ports for discharging the lubricant to the lubrication portions from above, the plurality of discharge ports being formed in downstream end portions of the oil passage; a plurality of derived oil passages for guiding, to the respective plurality of discharge ports, the lubricant from the downstream oil passage, the plurality of derived oil passages being branched from the downstream oil passage, wherein the plurality of derived oil passages are formed such that a derived oil passage having a shorter lubricant circulation channel from the oil feed port to a derived part has a longer lubricant circulation channel in the derived oil passage.
In the oil feed member of the present invention, the plurality of derived oil passages have a smaller lubricant flow area than a lubricant flow area of the downstream oil passage.
The oil feed member of the present invention is mounted on a head cover of a cylinder head of the engine, and doubles as a baffle plate for partitioning an oil separator chamber for separating oil from blow-by gas.
In the oil feed member of the present invention, the downstream oil passage, the plurality of derived oil passages, and the plurality of discharge ports are provided on each of the intake valve side and the exhaust valve side.
In the oil feed member of the present invention, the oil passage includes distribution oil passages for distributing and guiding, to the respective downstream oil passages on each of the intake valve side and the exhaust valve side, the lubricant from the upstream oil passage.
In the oil feed member of the present invention, the pair of panel members are formed of resin.
A lubricant feed mechanism for an engine of the present invention includes the oil feed member according to any one of claims 1 to 9.
As advantageous effects of the present invention, the following advantageous effects are exerted.
In the oil feed member of the present invention, the lubricant can be prevented from being excessively fed from the oil feed member to the lubrication portions of the valve gears.
In the oil feed member of the present invention, it is possible to equalize the amounts of the lubricant discharged from the plurality of discharge ports.
In the oil feed member of the present invention, it is possible to reduce the number of components.
In the oil feed member of the present invention, it is possible to feed the lubricant to the lubrication portions on the intake valve and the exhaust valve with a simple configuration.
In the oil feed member of the present invention, it is possible to reduce weight.
In the lubricant feed mechanism for an engine of the present invention, the lubricant can be prevented from being excessively fed from the oil feed member to the lubrication portions of the valve gears.
Hereinafter, the up-down direction, the right-left direction, and the front-back direction are defined in accordance with the arrows illustrated in the drawings.
First, a configuration of an engine 1 provided with a lubricant feed mechanism according to an embodiment of the present invention will be described with reference to
The engine 1 according to this embodiment is an inline 4-cylinder double overhead camshaft (DOHC) 16-valve gasoline engine. In the engine 1, a structure of an intake side and a structure of an exhaust side are substantially the same. In the following, for convenience of description, the structure of the exhaust side (structure of the left illustrated in
The engine 1 mainly includes a cylinder head 10, a cylinder head cover 20, valve gear 30, a cam cap 40, and an oil feed member 100.
The cylinder head 10 serves as a main structural body of the engine 1 together with a cylinder block (not illustrated). The cylinder head 10 is fixed to an upper surface of the cylinder block. The cylinder head 10 mainly includes cylinder-head-side bearings 11 and an oil gallery 12.
The cylinder-head-side bearings 11 rotatably support an exhaust-side camshaft 34A, which will be described later, from below. The cylinder-head-side bearings 11 are each formed on the left part of the cylinder head 10 so as to be recessed in a semicircular shape with the upper side open in front view.
The oil gallery 12 is an oil passage for feeding lubricant to respective parts of the engine 1 (for example, lubrication portions of the engine 1, and hydraulic apparatuses such as lash adjusters 33 described later). The oil gallery 12 is formed so as to pass through a left sidewall of the cylinder head 10 in the front-back direction.
The cylinder head cover 20 covers an upper part of the cylinder head 10. The cylinder head cover 20 is formed in a cup shape with the lower side open. The cylinder head cover 20 is placed on the upper part of the cylinder head 10, and appropriately fixed by bolts or the like. Inside the cylinder head cover 20, a baffle plate (oil feed member 100 described later in this embodiment) is mounted, and an oil separator chamber 21 is partitioned. The oil separator chamber 21 can accumulate blow-by gas, and enables the blow-by gas to flow back to an intake system after oil dropping is performed.
The valve gear 30 is a component for opening and closing an exhaust port (not illustrated) of the engine 1 at predetermined timing. The valve gear 30 mainly includes exhaust valves 31A, rocker arms 32, the lash adjusters 33, and the exhaust-side camshaft 34A.
Each of the exhaust valves 31A opens and closes the exhaust port (not illustrated) of the engine 1. The exhaust valve 31A is disposed such that the longitudinal direction is directed to the substantially up-down direction. A lower end of the exhaust valve 31A extends up to the exhaust port. A middle portion in the up-down direction of the exhaust valve 31A is slidably inserted into the cylinder head 10.
Each of the rocker arms 32 is a component for openably driving the exhaust valve 31A. One end of the rocker arm 32 abuts on an upper end of the exhaust valve 31A from above. The rocker arm 32 is provided with a rotatable roller 35 with an axis in the front-back direction as the center.
Each of the lash adjusters 33 is a component for adjusting a valve clearance. The lash adjuster 33 abuts on the other end of the rocker arm 32 from below.
Although illustration is omitted, two exhaust valves 31A are provided for one cylinder so as to be arranged in the front-back direction. That is, in this embodiment, a total of eight exhaust valves 31A are provided. Additionally, a total of eight rocker arms 32, a total of eight rollers 35, and a total of eight lash adjusters 33 are provided so as to correspond to the total of the eight exhaust valves 31A.
The exhaust-side camshaft 34A is a component for openably driving the exhaust valves 31A by rocking the rocker arms 32 at predetermined timing. The exhaust-side camshaft 34A is placed on the cylinder-head-side bearings 11 of the cylinder head 10 in a state where the longitudinal direction is directed to the front-back direction. The exhaust-side camshaft 34A mainly includes the cams 36.
Each of the cams 36 is a part formed in a plate shape in which a distance from the rotation center (center of the exhaust-side camshaft 34A) to an outer periphery is not constant. The cam 36 is disposed at a position corresponding to each cylinder in the front-back direction. The cam 36 abuts on the roller 35 of the rocker arm 32 from above. In this embodiment, a total of eight cams 36 are provided, and abut on the respective corresponding rollers 35 from above.
The cam cap 40 is a component that is fixed to the upper part of the cylinder head 10, and holds the exhaust-side camshaft 34A between the cam cap 40 and the cylinder head 10. The cam cap 40 is formed in a substantially rectangular parallelpiped shape in which the longitudinal direction is directed to the right-left direction. The cam cap 40 mainly includes cam-cap-side bearings 41.
The cam-cap-side bearings 41 rotatably support the exhaust-side camshaft 34A from above. The cam-cap-side bearings 41 are each formed on the left part of the cam cap 40 so as to be recessed in a semicircular shape with the lower side open in front view. The cam-cap-side bearing 41 is formed at such a position as to face the cylinder-head-side bearing 11 of the cylinder head 10, and rotatably supports the exhaust-side camshaft 34A together with the cylinder-head-side bearing 11.
The oil feed member 100 is a member for feeding, to predetermined lubrication portions (cams 36 of the exhaust-side camshaft 34A in this embodiment), lubricant fed from the oil gallery 12 through a predetermined oil passage. The oil feed member 100 is mounted on the inside of the cylinder head cover 20.
A configuration of the oil feed member 100 will be later described in detail.
Although specific description is omitted, the engine 1 having the above configuration includes a valve gear 30 (on the intake side) for opening and closing an intake port (not illustrated) of the engine 1 at predetermined timing, as the structure of the intake side (structure of the right illustrated in
Hereinafter, the configuration of the oil feed member 100 will be described with reference to
The oil feed member 100 illustrated in
As illustrated in
As illustrated in
The oil feed member 100 mainly includes openings 101, an oil feed passage 102, an oil feed port 103, and discharge ports 104.
The openings 101 illustrated in
The oil feed passage 102 illustrated in
The introduction oil passages 130 each are an oil passage formed on the most upstream side in the oil feed passage 102. As illustrated in
The flow area of the introduction oil passage 130 is formed so as to be substantially the same as the flow area of the distribution oil passage 140 and the derived oil passages 160, which will be described later. Additionally, the flow area of the introduction oil passage 130 is formed so as to be smaller than the flow area of the basis oil passages 150 described later as illustrated in
The introduction oil passage 130 is disposed at a left front part of the oil feed member 100 such that the longitudinal direction is generally directed to the front-back direction. A front end of the introduction oil passage 130 is disposed in the vicinity of a left front end of the oil feed member 100. A back end of the introduction oil passage 130 is disposed at a substantially central part of the oil feed member 100.
The distribution oil passage 140 is an oil passage formed on a downstream side with respect to the introduction oil passage 130 in the oil feed passage 102. As illustrated in
The distribution oil passage 140 is disposed at a substantially central part in the front-back direction of the oil feed member 100 such that the longitudinal direction is directed to the right-left direction. A left end of the distribution oil passage 140 is disposed in the vicinity of a left end of the oil feed member 100. A right end of the distribution oil passage 140 is disposed in the vicinity of a right end of the oil feed member 100. A substantially central part in the longitudinal direction of the distribution oil passage 140 is connected to the back end of the introduction oil passage 130. Thus, the distribution oil passage 140 communicates with the introduction oil passage 130.
The basis oil passages 150 each are an oil passage formed on a downstream side with respect to the distribution oil passage 140 in the oil feed passage 102. The respective basis oil passages 150 are formed on the left (exhaust valve 31A side) and the right (intake valve 31B side) of the oil feed member 100. Herein, the configurations of the right and left basis oil passages 150 are substantially symmetric in the right-left direction, as illustrated in
The configurations of the right and left basis oil passages 150 are substantially symmetric in the right-left direction in this embodiment, but may be asymmetrical in the right-left direction.
As illustrated in
The basis oil passage 150 is disposed in the vicinity of the left end of the oil feed member 100 such that the longitudinal direction is directed to the right-left direction. A front end of the basis oil passage 150 is disposed in the vicinity of a front end of the oil feed member 100. A back end of the basis oil passage 150 is disposed in the vicinity of a back end of the oil feed member 100. A part slightly behind from a central part in the longitudinal direction of the basis oil passage 150 is connected to the left end of the distribution oil passage 140. Thus, the basis oil passage 150 communicates with the introduction oil passage 130.
The derived oil passages 160 each are an oil passage formed on a downstream side (most downstream side) with respect to the basis oil passage 150 in the oil feed passage 102. Similarly to the basis oil passage 150, the derived oil passages 160 are formed on the left (exhaust valve 31A side) and the right (intake valve 31B side) of the oil feed member 100. Herein, the configurations of the right and left derived oil passages 160 are substantially symmetric in the right-left direction, as illustrated in
The configurations of the right and left derived oil passages 160 are substantially symmetric in the right-left direction in this embodiment, but may be asymmetrical in the right-left direction.
As illustrated in
A plurality of (seven in this embodiment) the derived oil passages 160 are provided so as to be branched from the basis oil passage 150. Hereinafter, the seven derived oil passages 160 are referred to as a first derived oil passage 161, a second derived oil passage 162, a third derived oil passage 163, a fourth derived oil passage 164, a fifth derived oil passage 165, sixth derived oil passage 166, and a seventh derived oil passage 167 in order from the back side.
The first derived oil passage 161 illustrated in
The second derived oil passage 162 illustrated in
The third derived oil passage 163 illustrated in
The fourth derived oil passage 164 illustrated in
The fifth derived oil passage 165 illustrated in
The sixth derived oil passage 166 illustrated in
The seventh derived oil passage 167 illustrated in
The oil feed port 103 illustrated in
The discharge ports 104 illustrated in
As illustrated in
A remaining discharge port 104 in the eight discharge ports 104 is formed at such a position as to overlap with the front end of the basis oil passage 150 in plan view. Thus, lubricant guided to the front side of the basis oil passages 150 is discharged from the discharge port 104 to the outside (downward) of the oil feed member 100 at the front end. Thus, the front end of the basis oil passage 150 becomes a downstream end portion of the oil feed passage 102.
The eight discharge ports 104 are disposed so as to correspond to the eight cams 36 of the exhaust-side camshaft 34A. Thus, the eight discharge ports 104 can feed the discharged lubricant to the eight cams 36. In this embodiment, the eight discharge ports 104 are disposed at such positions as to overlap with the respective eight cams 36 in plan view (not illustrated).
As illustrated in
In the oil feed passage 102 configured as described above, the lubricant from the oil feed port 103 is guided to the introduction oil passage 130, the distribution oil passage 140, the basis oil passage 150, the plurality of derived oil passages 160 (the first derived oil passage 161, the second derived oil passage 162, the third derived oil passage 163, the fourth derived oil passage 164, the fifth derived oil passage 165, the sixth derived oil passage 166, and the seventh derived oil passage 167) in order. Then, the lubricant fed to the left ends of the plurality of derived oil passages 160 and the front end of the basis oil passage 150 is discharged downward through the respective discharge ports 104. Thus, as illustrated in
Hereinafter, configurations of the lengths of the plurality of derived oil passages 160 (circulation channels of lubricant) will be described in detail.
As described above, the second derived oil passage 162 is formed so as to be longer than the first derived oil passage 161. Additionally, the third derived oil passage 163 is formed so as to be longer than the second derived oil passage 162. Herein, the first derived oil passage 161, the second derived oil passage 162, and the third derived oil passage 163 are disposed from the back side to the front side toward a connection part of the basis oil passage 150 and the distribution oil passage 140 in order. Thus, the first derived oil passage 161, the second derived oil passage 162, and the third derived oil passage 163 are formed such that a derived oil passage disposed nearer a connection part of the distribution oil passage 140 and the basis oil passage 150 (eventually, the oil feed port 103) has a longer lubricant circulation channel.
As described above, the fourth derived oil passage 164 is formed so as to be longer than the fifth derived oil passage 165. Additionally, the fifth derived oil passage 165 is formed so as to be longer than the sixth derived oil passage 166. Additionally, the sixth derived oil passage 166 is formed so as to be longer than the seventh derived oil passage 167. Herein, the seventh derived oil passage 167, the sixth derived oil passage 166, the fifth derived oil passage 165, and the fourth derived oil passage 164 are disposed from the front side to the back side toward the connection part of the basis oil passage 150 and the distribution oil passage 140 in order. Thus, the seventh derived oil passage 167, the sixth derived oil passage 166, the fifth derived oil passage 165, and the fourth derived oil passage 164 are formed such that a derived oil passage disposed nearer the oil feed port 103 has a longer lubricant circulation channel.
Also in a case where all the derived oil passages (the first derived oil passage 161, the second derived oil passage 162 and the third derived oil passage 163, and the fourth derived oil passage 164, the fifth derived oil passage 165, the sixth derived oil passage 166 and the seventh derived oil passage 167) are compared, the derived oil passages are formed such that a derived oil passage disposed nearer the connection part of the distribution oil passage 140 and the basis oil passage 150 (eventually, the oil feed port 103) has a longer lubricant circulation channel.
Herein, pressure loss is caused in lubricant circulated forward and backward from the connection part of the basis oil passage 150 and the distribution oil passage 140. That is, the pressure loss of lubricant increases as getting farther away from the connection part of the basis oil passage 150 with the distribution oil passage 140, and therefore it is considered that an amount of distributed lubricant of a derived oil passage disposed far from the connection part is less than an amount of distributed lubricant of a derived oil passage near the connection part.
However, in this embodiment, the first derived oil passage 161, the second derived oil passage 162, and the third derived oil passage 163 are formed such that the derived oil passage disposed nearer the oil feed port 103 has the longer lubricant circulation channel. Additionally, the seventh derived oil passage 167, the sixth derived oil passage 166, the fifth derived oil passage 165, and the fourth derived oil passage 164 are formed such that the derived oil passage nearer the oil feed port 103 has the longer lubricant circulation channel. Therefore, it is possible to reduce an influence on the basis oil passage 150 by pressure loss.
Specifically, for example, the long length (lubricant circulation channel) of the third derived oil passage 163 whose pressure loss of lubricant distributed from the basis oil passages 150 is small is secured, so that the pressure loss of lubricant circulated in the third derived oil passage 163 is increased. On the other hand, the length (lubricant circulation channel) of the first derived oil passage 161 whose pressure loss of lubricant distributed from the basis oil passages 150 is large is shortened, so that the pressure loss of lubricant circulated in the first derived oil passage 161 is reduced.
It is considered that the pressure loss of the discharge port 104 disposed farthest (in the eight discharge ports 104) from the connection part of the basis oil passages 150 with the distribution oil passage 140 is significantly large, and therefore the discharge port 104 disposed farthest is provided with no derived oil passage (discharge port 104 is directly provided in the basis oil passage 150).
With such a configuration, it is possible to equalize the amounts of lubricant discharged from the discharge ports 104 provided in the plurality of derived oil passages 160 (the first derived oil passage 161, the second derived oil passage 162, the third derived oil passage 163, the fourth derived oil passage 164, the fifth derived oil passage 165, the sixth derived oil passage 166, and the seventh derived oil passage 167), and the discharge port 104 provided in the front end of the basis oil passages 150.
Hereinafter, a configuration of a shape of the introduction oil passage 130 will be described in detail with reference to
The introduction oil passage 130 is disposed such that the longitudinal direction is generally directed to the front-back direction, and formed in a shape appropriately bent by a plurality of bent parts. The introduction oil passage 130 includes an introduction first oil passage 131, an introduction second oil passage 132, an introduction third oil passage 133, and an introduction fourth oil passage 134. Additionally, the plurality of bent parts include a first bent part 131a, a second bent part 132a, and a third bent part 133a.
The introduction first oil passage 131 linearly extends toward the left front side from the upstream end portion (a position overlapped with the oil feed port 103 in plan view) of the introduction oil passage 130. The first bent part 131a is disposed in the extending end of the introduction first oil passage 131. The extending direction of the introduction first oil passage 131 is changed (bent) from the left front side to the right back side at the first bent part 131a. The first bent part 131a is formed in a substantially V-shape in plan view. Herein, the pressure loss of the introduction oil passage 130 is adjusted by the bending angle (angle α illustrated in
The introduction second oil passage 132 linearly extends toward the right back side from the first bent part 131a. The second bent part 132a is disposed in the extending end of the introduction second oil passage 132. The extending direction of the introduction second oil passage 132 is changed (bent) from the right back side to the right behind at the second bent part 132a.
The introduction third oil passage 133 linearly extends toward the right behind from the second bent part 132a. The third bent part 133a is disposed in the extending end of the introduction third oil passage 133. The extending direction of the introduction third oil passage 133 is changed (bent) from the right behind to the right back side at the third bent part 133a. The third bent part 133a is formed in a substantially arcuate shape in plan view.
The introduction fourth oil passage 134 linearly extends toward the right back side from the third bent part 133a. The extending end of the introduction fourth oil passage 134 is connected to the distribution oil passage 140. Thus, the introduction fourth oil passage 134 is connected to the distribution oil passage 140 so as to form an angle (about 60 degrees in this embodiment) inclined to the longitudinal direction (the right-left direction) of the distribution oil passage 140 (refer to the angle β illustrated in
Thus, the introduction oil passage 130 includes the plurality of bent parts (the first bent part 131a, the second bent part 132a, and the third bent part 133a), and the extending direction is appropriately changed, and therefore it is possible to increase the length of the introduction oil passage 130. Accordingly, it is possible to increase the pressure loss of lubricant in the introduction oil passage 130.
In the introduction oil passage 130, the plurality of bent parts (the first bent part 131a, the second bent part 132a, and the third bent part 133a) can give pressure loss to lubricant, and adjust the pressure loss of the lubricant in the introduction oil passage 130. The first bent part 131a in the plurality of bent parts is set such that the bending angle is an acute angle. Consequently, it is possible to further increase the pressure loss of the lubricant in the introduction oil passage 130 (compared to a case where there is no bent part set such that a bending angle is an acute angle).
Thus, in the introduction oil passage 130, it is possible to adjust the pressure loss of the lubricant while increasing the pressure loss, and it is possible to prevent the amount of lubricant circulated in the oil feed passage 102 of the oil feed member 100 from becoming excessive. That is, the amount of the lubricant circulated in the oil feed passage 102 of the oil feed member 100 can be made to be a suitable amount. Therefore, even in a case where lubricant from the oil gallery 12 is continuously (not intermittently) fed to the oil feed member 100, the lubricant can be prevented from being excessively fed from the oil feed member 100 to the cams 36 of the exhaust-side camshaft 34A.
As described above, the flow area of the introduction oil passage 130 is formed to be smaller than the flow area of the basis oil passage 150. That is, while it is possible to suppress the amount of the lubricant circulated in the introduction oil passage 130 while securing a sufficient amount of lubricant in the basis oil passage 150 connected to the plurality of derived oil passages 160 (in which the discharge ports 104 are disposed). Therefore, even in a case where the lubricant from the oil gallery 12 is continuously (not intermittently) fed to the oil feed member 100, the lubricant can be prevented from being excessively fed from the oil feed member 100 to the cams 36 of the exhaust-side camshaft 34A.
As described above, the oil feed member 100 according to the embodiment of the present invention is the oil feed member for feeding lubricant to the lubrication portions of the valve gears 30 for opening and closing the intake valves 31B and the exhaust valves 31A of the engine 1, which includes: the upper panel member 110 and the lower panel member 120 (pair of panel members) laid over each other; and the oil feed passage 102 (oil passage) formed by recessing laid surfaces of the upper panel member 110 and the lower panel member 120 (pair of panel members), wherein the oil feed passage 102 (oil passage) includes the basis oil passages 150 (downstream oil passage) formed on the downstream side, and the introduction oil passage 130 (upstream oil passage) formed on the upstream side and having a smaller lubricant flow area than that of the basis oil passages 150 (downstream oil passage).
With such a configuration, the lubricant can be prevented from being excessively fed from the oil feed member 100 to the lubrication portions (the cams 36 of the intake-side camshaft 34B and the cams 36 of the exhaust-side camshaft 34A) of the valve gears 30.
In the oil feed member 100, the introduction oil passage 130 (upstream oil passage) includes the first bent part 131a, the second bent part 132a, and the third bent part 133a that are bent to give pressure loss to the lubricant.
With such a configuration, the lubricant can be prevented from being excessively fed from the oil feed member 100 to the lubrication portions (the cams 36 of the intake-side camshaft 34B and the cams 36 of the exhaust-side camshaft 34A) of the valve gears 30.
In the oil feed member 100, the bent part includes the acute angle bent part (first bent part 131a) that is bent at an acute angle.
With such a configuration, the lubricant can be prevented from being excessively fed from the oil feed member 100 to the lubrication portions (the cams 36 of the intake-side camshaft 34B and the cams 36 of the exhaust-side camshaft 34A) of the valve gears 30.
The oil feed member 100 further includes: the oil feed port 103 formed in an upstream end portion of the oil feed passage 102 (oil passage), for receiving the lubricant to be fed to the oil feed passage 102; the plurality of discharge ports 104 for discharging the lubricant to the lubrication portions from above, the plurality of discharge ports 104 being formed in downstream end portions of the oil feed passage 102 (oil passage); the plurality of derived oil passages 160 (the first derived oil passage 161, the second derived oil passage 162, the third derived oil passage 163, the fourth derived oil passage 164, the fifth derived oil passage 165, the sixth derived oil passage 166, and the seventh derived oil passage 167) for guiding, to the respective plurality of discharge ports 104, the lubricant from the basis oil passages 150 (downstream oil passage), the plurality of derived oil passages 160 being branched from the basis oil passages 150 (downstream oil passage), wherein the plurality of derived oil passages 160 are formed such that a derived oil passage having a shorter lubricant circulation channel from the oil feed port 103 to a derived part (connection part of the derived oil passage 160 and the basis oil passage 150) has a longer lubricant circulation channel in the derived oil passage.
With such a configuration, it is possible to equalize the amounts of the lubricant discharged from the plurality of discharge ports 104.
In the oil feed member 100, the plurality of derived oil passages 160 have a smaller lubricant flow area than that of the basis oil passages 150 (downstream oil passage).
With such a configuration, the lubricant can be prevented from being excessively fed from the oil feed member 100 to the lubrication portions (the cams 36 of the intake-side camshaft 34B and the cams 36 of the exhaust-side camshaft 34A) of the valve gears 30.
The oil feed member 100 is mounted on the cylinder head cover 20 of the cylinder head 10 of the engine 1, and doubles as a baffle plate for partitioning the oil separator chamber 21 for separating oil from blow-by gas.
With such a configuration, it is possible to reduce the number of components.
In the oil feed member 100, the basis oil passage 150 (downstream oil passage), the plurality of derived oil passages 160, and the plurality of discharge ports 104 are provided on each of the intake valve 31B side and the exhaust valve 31A side.
With such a configuration, the single member (the oil feed member 100) can feed the lubricant to the lubrication portions on the intake valve 31B side and the exhaust valve 31A side (the cams 36 of the intake-side camshaft 34B and the cams 36 of the exhaust-side camshaft 34A), and it is possible to reduce the number of components.
In the oil feed member 100, the oil feed passage 102 (oil passage) includes distribution oil passages 140 for distributing and guiding, to the respective basis oil passages 150 (downstream oil passages) on each of the intake valve 31B side and the exhaust valve 31A side, the lubricant from the introduction oil passage 130 (upstream oil passage).
With such a configuration, the distribution oil passage 140 enables the lubricant from the single oil passage (introduction oil passage 130) to be distributed and guided to the respective basis oil passages 150 on the intake valve 31B side and the exhaust valve 31A side, and therefore it is possible to feed the lubricant to the lubrication portions on the intake valve 31B side and the exhaust valve 31A side (the cams 36 of the intake-side camshaft 34B and the cams 36 of the exhaust-side camshaft 34A).
Additionally, the lubricant feed mechanism for the engine 1 according to the present invention includes the oil feed member 100.
With such a configuration, the lubricant can be prevented from being excessively fed from the oil feed member 100 to the lubrication portions (the cams 36 of the intake-side camshaft 34B and the cams 36 of the exhaust-side camshaft 34A) of the valve gears 30.
The engine 1 according to this embodiment is an inline 4-cylinder double overhead camshaft (DOHC) 16-valve gasoline engine, but an engine to which the present invention can be applied is not limited to this.
The introduction oil passage 130 according to this embodiment is an embodiment of the “upstream oil passage” according to the present invention. The configuration (shape, for example) of the “upstream oil passage” according to the present invention is not limited to the configuration of the introduction oil passage 130.
The first bent part 131a, the second bent part 132a, and the third bent part 133a according to this embodiment each are an embodiment of the “bent part” according to the present invention. The configuration of the “bent part” according to the present invention is not limited to the configurations of the first bent part 131a, and the like. For example, the “bent parts” according to the present invention may not be three, and one, two, four or more bent parts may be provided.
The first bent part 131a according to this embodiment is an embodiment of the “acute angle bent part” according to the present invention. The configuration of the “acute angle bent part” according to the present invention is not limited to the configuration of the first bent part 131a. The “acute angle bent part” according to the present invention may not be one, but two or more “acute angle bent parts” may be provided.
In the oil feed member 200, introduction oil passages 230 are formed in zigzag by continuously disposing bent parts bent at a substantially right angle in plan view. With such a configuration, pressure loss can be applied to lubricant, and the pressure loss of the lubricant in each introduction oil passage 230 can be increased, and therefore the lubricant can be prevented from being excessively fed from an oil feed member 200 to cams 36 of an exhaust-side camshaft 34A.
In
A material of the panel member (namely, the “pair of panel members” according to the present invention) for forming the “oil feed member” according to the present invention is not only metal, but can be also resin. Thus, in a case where resin is used as the material of the panel member for forming the “oil feed member” according to the present invention, it is possible to reduce the weight of the “oil feed member”.
Thus, in the oil feed member 100, the upper panel member 110 and the lower panel member 120 (pair of panel members) are formed of resin.
With such a configuration, the oil feed member 100 enables reduction in weight.
The present invention is applicable to an oil feed member for feeding lubricant to lubrication portions of valve gears for opening and closing intake and exhaust valves of an engine, and a lubricant feed mechanism for an engine provided with the same.
1: Engine
30: Valve gear
31A: Exhaust valve
31B: Intake valve
100: Oil feed member
102: Oil feed passage
110: Upper panel member
120: Lower panel member
130: Introduction oil passage
150: Basis oil passage
Number | Date | Country | Kind |
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2014-104836 | May 2014 | JP | national |
Filing Document | Filing Date | Country | Kind |
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PCT/JP2015/062848 | 4/28/2015 | WO | 00 |
Publishing Document | Publishing Date | Country | Kind |
---|---|---|---|
WO2015/178180 | 11/26/2015 | WO | A |
Number | Name | Date | Kind |
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20100095922 | Nakajima | Apr 2010 | A1 |
20140076266 | Honnikoppa | Mar 2014 | A1 |
20150260062 | Hikita et al. | Sep 2015 | A1 |
Number | Date | Country |
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35 20 876 | Sep 1986 | DE |
2008-38846 | Feb 2008 | JP |
WO 2014050716 | Apr 2014 | WO |
Entry |
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International Search Report (PCT/ISA/210) dated Jul. 28, 2015, by the Japanese Patent Office as the International Searching Authority for International Application No. PCT/JP2015/062848. |
Written Opinion (PCT/ISA/237) dated Jul. 28, 2015, by the Japanese Patent Office as the International Searching Authority for International Application No. PCT/JP2015/062848. |
Number | Date | Country | |
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20170044940 A1 | Feb 2017 | US |