JP2010084531A - Oil feeder for camshaft - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To feed oil to a phase variable mechanism without largely decreasing oil pressure from a head-side oil path formed in a bearing member, with no adverse effect on a rolling bearing. <P>SOLUTION: A camshaft 1 is supported by a bearing member 20 through the rolling bearing 50. Each of ends in an axial direction of a retainer 52 of the rolling bearing 40 has annular ends 71, 72 for sealing in the axial direction. The annular ends 71, 72 respectively have ring-like outer annular grooves 73, 76 formed at their outer circumferential surfaces, and ring-like inner annular grooves 74, 77 formed at their inner circumferential surfaces. Each of annular ends 71, 72 has communicating hole 75(78) formed to communicate the outer annular groove 73(74) with the inner annular groove 74(77). An oil path 61 on advance head side communicates with the outer annular groove 73, and an oil path 65 on an advance camshaft side communicates with the inner annular groove 74. An oil path 62 on a retard head side communicates with the outer annular groove 76, and an oil path 66 on a retard camshaft side communicates with the inner annular groove 77. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a camshaft oiling device.

  Many engines, particularly automobile engines, change the phase of the opening / closing timing of intake valves or exhaust valves. For this phase change, a hydraulic phase variable mechanism is provided at one end of the camshaft of the intake valve or exhaust valve, and by changing the hydraulic supply mode to this phase variable mechanism, the camshaft relative to the crankshaft is changed. Some change the phase. In general, oil supply to the hydraulic phase variable mechanism is performed from the head side oil passage in the bearing member that supports the cam shaft through the oil passage in the cam shaft.

  In Patent Document 1, when a cam shaft is rotatably supported via a roller bearing, which is a kind of rolling bearing, with respect to a bearing member provided in a cylinder head, one end side in the axial direction of a roller bearing retainer is disclosed. A side oil passage is formed on the side, and the head side oil passage formed in the bearing member and the cam shaft side oil passage formed in the cam shaft are communicated with each other through the side oil passage. Is disclosed. Patent Document 1 also discloses that a seal portion that seals the lateral oil passage is formed at the axial end portion of the roller bearing retainer. Patent Document 2 discloses that when the cam shaft is supported by a slide bearing, the head side oil passage and the cam shaft side oil passage communicate with each other via a sliding surface between the cam shaft and the slide bearing. Has been.

JP 2008-101714 A JP 9-250310 A

  By the way, when the camshaft is supported by a rolling bearing, the rolling bearing itself has a very weak hydraulic pressure holding function. For this reason, the head side oil passage and the camshaft side oil passage are communicated using the space in the rolling bearing. This is a hydraulic leak, that is, a decrease in the hydraulic pressure supplied to the phase variable mechanism, which is practically impossible to employ. In addition, if a large amount of oil flows into the rolling bearing, the rolling resistance increases, which is not preferable. Furthermore, as described in Patent Document 1, forming a lateral oil passage on the side of one end side in the axial direction of the cage of the roller bearing may increase the axial length of the portion related to the roller bearing. Also, the oil pressure in the side oil passage causes the roller bearing to receive an axial force and cause adverse effects such as being likely to cause problems in maintaining the axial positioning with high accuracy.

  The present invention has been made in view of the above circumstances, and its object is to provide a head-side oil passage formed in the bearing member when the camshaft is supported by the bearing member of the cylinder head via the rolling bearing. Another object of the present invention is to provide a camshaft oiling device that can supply the oil pressure from the shaft to the phase variable mechanism without greatly reducing the oil pressure, and that does not adversely affect the rolling bearing itself.

In order to achieve the above object, the following first solution is adopted in the present invention. That is, as described in claim 1 in the claims,
A cam shaft provided with a hydraulic phase variable mechanism at one end is rotatably supported by a bearing member of a cylinder head, and a cam shaft side formed on the cam shaft from a head side oil passage formed on the bearing member In a camshaft lubrication device that lubricates the phase variable mechanism via an oil passage,
An adjacent bearing member located next to the phase variable mechanism among the bearing members supports the camshaft via a rolling bearing,
The rolling bearing has a large number of rollers and a cage that holds the large number of rollers at predetermined intervals in the circumferential direction,
An annular end portion that performs an axial seal is formed at each axial end portion of the cage,
An annular outer annular groove is formed on the outer peripheral surface of each annular end, and an annular inner annular groove is formed on the inner peripheral surface of each annular end.
In each of the annular ends, a communication hole that connects the outer annular groove and the inner annular groove is formed,
An advance angle head side oil passage is communicated with the outer annular groove portion of one of the annular end portions, and an advance angle cam shaft side oil is communicated with the inner annular groove portion of the one annular end portion. The road is connected,
A retard head side oil passage is communicated with the outer annular groove portion of the other annular end portion among the annular end portions, and a retard cam shaft side oil is communicated with the inner annular groove portion of the other annular end portion. The road is in communication,
It is like that.

According to the above solution, the adjacent bearing member adjacent to the phase varying mechanism among the bearing members receives an external force in a direction intersecting the axial direction due to a tension from a chain or a timing belt wound around the phase varying mechanism. Therefore, the rotational resistance is particularly increased. However, the rotational resistance can be greatly reduced by supporting the camshaft with the adjacent bearing member with the rolling bearing. Further, the advance hydraulic pressure and the retard hydraulic pressure are individually supplied to the phase variable mechanism through a pair of annular ends that are axially separated from each other. This is also preferable for preventing interference. Furthermore, since the advance oil passage and the retard oil passage are formed by effectively using the cage, the structure can be simplified as a whole. Of course, since the space in the rolling bearing is not used as the hydraulic pressure supply path to the phase variable mechanism, a large amount of oil does not flow into the rolling bearing and its rotational resistance does not increase. It becomes. Furthermore, it is not necessary to separately form an extra space for oil passage formation on the side of the rolling bearing.
The

A preferred mode based on the first solution is as set forth in claim 2 and subsequent claims. That is,
Each annular end portion has the same diameter in the axially outer portion and the inner portion across the communication hole,
In the inner portion, an oil passage is formed for supplying oil toward the roller in communication with the communication hole.
(Corresponding to claim 2). In this case, an appropriate amount of lubricating oil can be supplied to the rollers through the oil passage formed in the inner portion.

  Each of the annular ends is configured such that the outer shape of the inner portion is set smaller than the outer portion in the axial direction across the communication hole (corresponding to claim 3). In this case, an appropriate amount of lubricating oil can be supplied to the rollers through the outer peripheral surface of the inner portion. In particular, lubricating oil can be supplied from the entire circumference of the inner portion toward the roller.

  The adjacent bearing member is formed with a drain oil passage facing the lower portion of the rolling bearing (corresponding to claim 4). In this case, it is preferable to reliably prevent a situation in which a large amount of oil stays in the rolling bearing and to prevent a situation in which the rotational resistance of the rolling bearing increases.

A large diameter portion is formed at a position corresponding to the roller of the cam shaft,
Each of the annular ends sandwiches the large diameter portion from the axial direction.
(Corresponding to claim 5). In this case, the cage itself, that is, the roller, can be reliably restricted from being displaced in the axial direction relative to the camshaft by using the cage itself.

Each of the annular end portions has an outer portion having a larger diameter than the inner portion with the communication hole interposed therebetween,
The outer portions having the large diameter sandwich the adjacent bearing member from the axial direction.
(Corresponding to claim 6). In this case, the cage itself, that is, the roller, can be reliably restricted from being displaced in the axial direction relative to the camshaft by using the cage itself.

The cage is made of synthetic resin;
An annular advance head-side annular groove continuous with the advance angle head-side oil passage is formed on the inner peripheral surface of the adjacent bearing member, and an annular delay connected with the retard angle head-side oil passage is formed. A corner head side annular groove is formed,
An annular advance cam shaft side annular groove continuous with the advance cam shaft side oil passage is formed on an outer peripheral surface of the cam shaft, and an annular advance connecting with the retard cam shaft side oil passage is formed. A retard camshaft-side annular groove is formed,
An annular outer lip portion individually extending into each head-side annular groove portion is formed on each peripheral edge portion of each outer annular groove portion,
An annular inner lip portion extending into each camshaft side annular groove portion is formed on each peripheral edge portion of each inner annular groove portion.
(Corresponding to claim 7). In this case, when the hydraulic pressure is supplied, each lip portion expands by elastic deformation in the corresponding head-side annular groove portion and camshaft-side annular groove portion, and the head-side oil passage of each communication hole formed in the cage. And the sealing performance with respect to the camshaft side oil passage can be enhanced.

  According to the present invention, the rolling shaft bearing is used to reduce the rotational resistance of the camshaft, and the hydraulic pressures for advance and retard from the head side oil passage are made to interfere with each other without greatly decreasing. Without being supplied to the phase variable mechanism. Further, it is preferable for shortening the axial length of the portion where the rolling bearing is disposed as much as possible, and the rolling bearing is not adversely affected by the hydraulic pressure supplied to the phase variable mechanism.

  Hereinafter, an embodiment of the present invention will be described by taking as an example a case where it is applied as a camshaft oiling device for an automobile engine. In FIG. 1, reference numeral 1 denotes a camshaft, which is used for driving an exhaust valve in the embodiment. The cam shaft 1 is rotatably supported by the cylinder head 10, and a cam shaft supporting bearing member provided on the cylinder head 10 is indicated by reference numeral 20. Note that a plurality of cam shaft support bearing members are provided at intervals in the axial direction of the cam shaft 1, but only the bearing member 20 provided on one end side of the cam shaft 1 is shown in FIG. The bearing member 20 is an adjacent bearing member.

  A phase variable mechanism 30 is assembled on one end side of the cam shaft 1. As shown in FIG. 2, the phase variable mechanism 30 roughly includes an outer member 31 and an inner member 32. The outer member 31 has a large number of teeth 35 on its outer peripheral surface. A chain or timing belt driven by a crankshaft (not shown) is wound around (engaged with) the tooth portion 35, and the crankshaft and the outer member 31 are always rotated integrally.

  The inner member 32 is fixed in contact with one end of the cam shaft 1 from the axial direction, and is always rotated integrally with the cam shaft 1. In the embodiment, the inner member 32 is fixed to the camshaft 1 by bolts 33 while being aligned by a positioning pin (not shown). As shown in FIG. 2, a plurality of recesses 36 are formed on the inner peripheral surface of the outer member 31 at intervals in the circumferential direction. A convex portion 37 that protrudes into the concave portion 36 is formed on the outer peripheral surface of the inner member 32. Within each recess 36, an advance working chamber 38 and a retard working chamber 39 are defined by a projecting portion 37. In FIG. 2, when the hydraulic pressure is supplied to the advance working chamber 38 in a state where the phase variable mechanism 30 rotates clockwise (the hydraulic pressure is discharged from the retard working chamber 39), the inner member 32 becomes the outer member 31. 2, the cam shaft 1 is advanced relative to the crankshaft. Conversely, when hydraulic pressure is supplied to the retarding working chamber 39 (hydraulic discharge from the advance working chamber 38), the inner member 32 is rotated relative to the outer member 31 counterclockwise in FIG. The shaft 1 is retarded with respect to the crankshaft.

The inner member 32 is urged in the advance direction with respect to the outer member 31 by a coil spring 34 as urging means. That is, when the hydraulic pressure is supplied to the advance working chamber 38, the advance is made while being assisted by the urging force of the coil spring 34,
When the hydraulic pressure is supplied to the retarding working chamber 39, the retarding is performed while resisting the urging force of the coil spring 34. The outer member 31 is restricted from relative displacement in the axial direction with respect to the inner member 32. In FIG. 1, an advance angle internal oil passage continuously connected to the advance angle working chamber 38 formed in the phase variable mechanism 30 (in the inner member 32 in the embodiment) is indicated by reference numeral 41, and is used for the retard angle. A retarding internal oil passage that is always connected to the working chamber 39 is indicated by reference numeral 42.

  As shown in FIG. 3 in particular, the bearing member 20 includes a lower holding portion 21 formed in the cylinder head 10 and a cap member 23 fixed to the cylinder head 10 by bolts 22. The camshaft 1 is rotatably supported via a rolling bearing 50 in a state of being sandwiched between the lower holding portion 21 and the cap member 23 from the vertical direction. As known, the rolling bearing 50 includes an outer ring 51, a cage 52, and a large number of needle-shaped rollers (rollers) 53. The cage 52 has a cylindrical shape, and a large number of storage spaces are formed at intervals in the circumferential direction. A roller 53 is stored and held in each of the storage spaces (see also FIG. 6). ). With such a retainer 53, the rollers 53 are positioned in the axial direction and the circumferential intervals between the rollers 53 are secured. The rolling bearing 50 has a half structure and is assembled to the cam shaft 1 from the radially outer side.

  In the bearing member 20, an advance angle head side oil passage 61 and a retard angle head side oil passage 62 are formed as head side oil passages. Further, an advance cam shaft side oil passage 65 and a retard angle cam shaft side oil passage 66 are formed in the cam shaft 1. The advance cam shaft side oil passage 65 is always in communication with the advance angle internal oil passage 41 in the phase variable mechanism 30. Similarly, the retarded camshaft side oil passage 66 is always in communication with the retarded internal oil passage 42 in the phase variable mechanism 30.

  The head side oil passages 61 and 62 and the camshaft side oil passages 65 and 66 are communicated with each other via a cage 52 of the rolling bearing 50, and this point will be described with reference to FIGS. To do. First, the axial end portions of the cage 52 are formed as annular annular end portions 71 and 72 so as to come into contact with the inner peripheral surface of the outer ring 51 and the outer peripheral surface of the cam shaft 1. In contrast, it is sealed from the axial direction.

  An annular outer annular groove 73 centering on the camshaft 1 is formed on the outer peripheral surface of one annular end 71. An annular inner annular groove 74 centering on the camshaft 1 is formed on the inner peripheral surface of the annular end 71. Further, the annular end portion 71 is formed with a plurality of communication holes 75 for communicating the inner and outer annular groove portions 73 and 74 (see FIG. 4).

  Similarly, an annular outer annular groove 76 centering on the camshaft 1 is formed on the outer peripheral surface of the other annular end 72. An annular inner annular groove 77 centering on the cam shaft 1 is formed on the inner peripheral surface of the annular end 72. Further, the annular end portion 72 is formed with a plurality of communication holes 78 for communicating the inner and outer annular groove portions 76 and 77 (see FIG. 4).

  The outer ring 51 of the rolling bearing 50 is assembled in the bearing member 20 and is substantially integrated with the bearing member 20 (can be regarded as the same component as the bearing member 20). The outer ring 51 has flange portions 51a and 51b that clamp the retainer 52 from the axial direction. The outer ring 51 is formed with an opening 81 as an oil passage that is always in communication with the outer annular groove 73 and the head-side oil passage 61, and at the same time with respect to the outer annular groove 76 and the head-side oil passage 62. An opening 82 is formed as a communicating oil passage.

  The inner annular groove 74 is always in communication with the camshaft side oil passage 65, and the inner annular groove 77 is in continuous communication with the camshaft side oil passage 66.

  As shown in FIG. 5, the outer end portions 71a and 72a and the inner portions 71b and 72b sandwiching the communication hole 75 or 76 have the same diameter. That is, both the outer portions 71a and 72a and the inner portions 71b and 72b are set so as to exhibit an axial sealing function. In order to supply the lubricating oil to the rollers 53, the outer peripheral surfaces of the inner portions 71b and 72b of the respective annular end portions 71 and 72 are directed to the rollers from the outer annular groove portions 73 or 76, for example, as shown in FIG. The oil passages 85 and 86 extending in this manner are formed in the form of, for example, notches. A plurality of the oil passages 85 and 86 are formed at intervals in the circumferential direction of the cage 52. The oil passage 85.86 can be formed in an appropriate format, for example, in the form of a hole that opens to the side surfaces of the communication holes 75 and 78. The oil passages 85 and 86 may be inclined toward the rotation direction of the camshaft 1 (for example, in FIG. 6, when the rotation direction of the camshaft 1 is downward in the drawing, the oil passages 85 and 86 If 86 is inclined so as to gradually move upward as it goes to roller 53, the flow of oil toward roller 53 can be promoted (if the oil flow is not promoted, the inclination is set in the reverse direction). Good).

  1 and 3, the bearing member 20 is formed with a drain oil passage 24 opened on the upper surface of the lower holding portion 21. The drain oil passage 24 extends downward and opens to the outside (valve chamber) from the side surface of the bearing member 20. An oil escape hole 51a communicating with the drain oil passage 24 is formed at the bottom of the outer ring 51 of the rolling bearing 50 (see FIG. 3).

  In the above configuration, the hydraulic pressure for advance from the head side oil passage 61 is the opening 81 formed in the outer ring 51, the outer annular groove 73, the communication hole 75, the inner annular groove 74, the camshaft side oil passage 65. , The oil is supplied to the advance working chamber 38 through the advance angle internal oil passage 41 in the phase varying mechanism 30 (the hydraulic pressure is discharged from the advance working chamber 38 through the reverse route).

  Further, the retarding hydraulic pressure from the head side oil passage 62 includes an opening 82 formed in the outer ring 51, an outer annular groove 76, a communication hole 78, an inner annular groove 77, a cam shaft side oil passage 66, and a phase variable. The oil is supplied to the retarding working chamber 39 via the retarding internal oil passage 42 in the mechanism 30 (the hydraulic pressure is discharged from the retarding working chamber 39 through the reverse path).

  As described above, the advance hydraulic pressure and the retard hydraulic pressure are individually supplied to the phase variable mechanism 30 via the annular end portions 71 and 72 of the cage 52 that are separated in the axial direction. Become. In addition, a large amount of oil is unnecessarily supplied toward the rollers 53 due to the sealing action of the annular end portions 71 and 72, or a large amount of oil leaks from the axially outer side of the cage 52. Is prevented. By the oil passages 85 and 86, a part of the advance hydraulic pressure or the retard hydraulic pressure is supplied toward the roller 53 by an appropriate amount, and the roller 53 is appropriately lubricated. Further, when excess oil is supplied to the roller 53 portion, it is quickly discharged through the drain oil passage 24 (preventing a situation in which the rolling resistance of the roller 53 increases due to a large amount of oil).

  Here, of the annular end portions 71 and 72 at each end portion of the cage 52, the annular end portion 71 positioned on the side far from the phase variable mechanism 30 is used for supplying the advance hydraulic pressure. That is, the urging force of the coil spring 34 in the phase variable mechanism 30 is set in the direction of assisting the advance angle as described above. For this reason, in order to promptly change the phase of the phase variable mechanism 30 in the retarding direction, the hydraulic pressure supply path for the retarding working chamber 39 is set so that the hydraulic pressure is supplied to the retarding working chamber 39 as quickly as possible. The length is shorter than the hydraulic pressure supply path for the advance working chamber 38. That is, a short hydraulic pressure supply path that passes through the annular end 72 on the side close to the phase variable mechanism 30 is selected for the retarding working chamber 39. Thereby, the response of the hydraulic pressure supply is made substantially the same at the advance angle and the retard angle.

  FIG. 7 shows a second embodiment of the present invention. The same components as those of the above-mentioned embodiment are denoted by the same reference numerals, and redundant description thereof is omitted (this is the case of the following third embodiment). The same applies to the following forms). In the present embodiment, in the embodiment of FIG. 1, the outer shape of the inner portions 71b and 72b is smaller than the outer shape of the outer portions 71a and 72a with the communication hole 75 or 78 as a boundary. It is. That is, the entire outer peripheral surfaces of the inner portions 71b and 72b are configured as the oil passages 85 and 86 for supplying the lubricating oil to the rollers 53 in the embodiment. In the case of this embodiment, it becomes possible to supply lubricating oil from the entire circumference of the cage 52 toward the roller 53 (uniform lubricating oil supply).

  FIG. 8 shows a third embodiment of the present invention. In the present embodiment, the cage 52 is entirely made of synthetic resin. In addition, an annular annular groove 91 centered on the cam shaft 1 is formed on the inner peripheral surface of the outer ring 51 (which can be regarded as the bearing member 20) so as to correspond to the annular ends 71 and 72, while the cam shaft An annular groove portion 92 centering on the camshaft 1 is also formed on the outer peripheral surface of 1. Then, annular lip portions 93 and 94 centering on the camshaft 1 projecting from the peripheral edge portion of the inner and outer annular groove portions 73 or 74 are formed on the outer peripheral surface side and the inner peripheral surface side of the annular end portions 71 and 72. It is. A pair of the lip portions 93 and 94 is provided at a small interval in the axial direction.

  The lip 93 extends into the annular groove 91 and is elastically deformed (enlarged and deformed) so as to expand in the axial direction when receiving hydraulic pressure from the head-side oil passage 61 to improve the sealing performance. Become. Similarly, the lip portion 94 extends into the annular groove portion 92 and is elastically deformed (expanded and deformed) so as to expand in the axial direction when receiving hydraulic pressure from the head-side oil passage 61, thereby providing a sealing property. Will increase. Further, when the hydraulic pressure is not supplied, the lip portions 93 and 94 are separated from the inner side surfaces of the annular groove portions 91 and 92 or lightly contacted, and the sliding resistance is reduced. In FIG. 8, the advance oil passage has been described as an example, but the configuration requirements corresponding to the annular groove portions 91 and 92 and the lip portions 93 and 94 are similarly formed in the retard oil passage. It is what has been.

  FIG. 9 shows a fourth embodiment of the present invention. In the present embodiment, the large-diameter portion 1 a is formed on the camshaft 1 at a position corresponding to the roller 53. The inner diameters of the annular end portions 71 and 72 of the cage 52 are set to be smaller than the outer diameter of the large diameter portion 1a, and the large diameter portion 1a is sandwiched from the axial direction by the pair of annular end portions 71 and 72. It is. According to the present embodiment, it is not necessary to position the retainer 52 in the axial direction by the outer ring 51, which is preferable for simplifying the outer ring 52. Further, since the opening positions of the communication holes 75 and 78 on the camshaft 1 side are shifted to the inner side in the radial direction with respect to the roller 53, a large amount of oil does not flow into the roller 53 unnecessarily. This is also preferable.

  FIG. 10 shows a fifth embodiment of the present invention. In the embodiment of FIG. 9, the axial end of the large-diameter portion 1a of the cam shaft 1 is gradually lowered toward the outer side in the axial direction. Accordingly, the inner peripheral surfaces of the annular end portions 71 and 72 of the cage 52 are also tapered surfaces.

  FIG. 11 shows a sixth embodiment of the present invention. In the present embodiment, of the annular ends 71 and 72 of the cage 52, the outer shape of the axially outer side portions 71a and 72a is made larger than the outer shape of the outer ring 51 with the communication hole 75 or 78 as a boundary. The outer side portions 71a and 72a sandwich the bearing member 20 from the axial direction. Further, the outer ring 51 is provided on the outer ring 51 in the embodiment shown in FIG. 5 or the like by setting the axially outer side end of the outer ring 51 to be located on the inner side in the axial direction with respect to the outer annular groove 73 or 76. The openings 81 and 82 as oil passages are not formed. That is, the openings of the head side oil passages 61 and 62 are extended so as to reach the inner surface side in the axial direction of the outer portion 71a (the extensions are indicated by reference numerals 61a and 62a), and directly from the extensions 61a and 62a. In particular, hydraulic pressure is supplied to the outer annular groove 73 or 76. Further, it is also preferable for reducing the sliding area between the outer ring 51 and the cage 53.

  Although the embodiment has been described above, the present invention is not limited to the embodiment, and can be appropriately changed within the scope described in the scope of claims. For example, the invention includes the following cases. . The phase variable mechanism 30 may be used for the intake valve (assembled to the intake valve camshaft). The urging direction by the coil spring 24 may be opposite to the embodiment. The head side oil passages 61 and 62 or the cam shaft side oil passages 65 and 66 are not limited to one, and a plurality of head side oil passages 61 and 62 may be provided at intervals in the circumferential direction of the cam shaft 1. Of course, the object of the present invention is not limited to what is explicitly stated, but also implicitly includes providing what is substantially preferred or expressed as an advantage.

1 is a side cross-sectional view showing a first embodiment of the present invention. FIG. 2 is a cross-sectional view corresponding to line X2-X2 in FIG. 1. FIG. 3 is a cross-sectional view corresponding to line X3-X3 in FIG. 1. X4-X4 line equivalent sectional drawing of FIG. The expanded sectional view of the rolling bearing part shown in FIG. The principal part top view which looked at the rolling bearing shown in FIG. 5 from the radial direction outer side. Sectional drawing which shows the 2nd Embodiment of this invention and respond | corresponds to FIG. Sectional drawing which shows the 3rd Embodiment of this invention and respond | corresponds to FIG. Sectional drawing which shows the 4th Embodiment of this invention and respond | corresponds to FIG. Sectional drawing which shows the 5th Embodiment of this invention and respond | corresponds to FIG. Sectional drawing which shows the 6th Embodiment of this invention and respond | corresponds to FIG.

Explanation of symbols

1: Cam shaft 1a: Large diameter portion 10: Cylinder head 20: Bearing member 21: Lower holding portion 23: Cap member 24: Drain oil passage 30: Phase variable mechanism 31: Outer member 32: Inner member 36: Concave portion 37: Convex portion Portion 38: Advance angle working chamber 39: Delay angle work chamber 41: Advance angle internal oil passage 42: Delay angle internal oil passage 50: Rolling bearing 51: Outer ring 52: Cage 53: Roller 61: Head side oil Road (for advance)
62: Head side oil passage (for retarded angle)
65: Cam shaft side oil passage (for advance angle)
66: Cam shaft side oil passage (for retarded angle)
71, 72: annular end 73.76: outer annular groove 74, 77: inner annular groove 75, 77: communication hole 81, 82: opening 91, 92: annular groove 93.94: lip

Claims (7)

A cam shaft provided with a hydraulic phase variable mechanism at one end is rotatably supported by a bearing member of a cylinder head, and a cam shaft side formed on the cam shaft from a head side oil passage formed on the bearing member In a camshaft lubrication device that lubricates the phase variable mechanism via an oil passage,
An adjacent bearing member located next to the phase variable mechanism among the bearing members supports the camshaft via a rolling bearing,
The rolling bearing has a large number of rollers and a cage that holds the large number of rollers at predetermined intervals in the circumferential direction,
An annular end portion that performs an axial seal is formed at each axial end portion of the cage,
An annular outer annular groove is formed on the outer peripheral surface of each annular end, and an annular inner annular groove is formed on the inner peripheral surface of each annular end.
In each of the annular ends, a communication hole that connects the outer annular groove and the inner annular groove is formed,
An advance angle head side oil passage is communicated with the outer annular groove portion of one of the annular end portions, and an advance angle cam shaft side oil is communicated with the inner annular groove portion of the one annular end portion. The road is connected,
A retard angle head side oil passage is communicated with the outer annular groove portion of the other annular end portion among the annular end portions, and the retard angle cam shaft side oil is communicated with the inner annular groove portion of the other annular end portion. The road is in communication,
A camshaft oiling device characterized by that. In claim 1,
Each annular end portion has the same diameter in the axially outer portion and the inner portion across the communication hole,
In the inner portion, an oil passage is formed for supplying oil toward the roller in communication with the communication hole.
A camshaft oiling device characterized by that. In claim 1,
Each of the annular end portions has a camshaft oiling device in which the outer shape of the inner portion is set smaller than the outer portion in the axial direction across the communication hole. In any one of Claims 1 thru | or 3,
A camshaft oiling device, wherein a drain oil passage that faces a lower portion of the rolling bearing is formed in the adjacent bearing member. In any one of Claims 1 thru | or 4,
A large diameter portion is formed at a position corresponding to the roller of the cam shaft,
Each of the annular ends sandwiches the large diameter portion from the axial direction.
A camshaft oiling device characterized by that. In any one of Claims 1 thru | or 4,
Each of the annular end portions has an outer portion having a larger diameter than the inner portion with the communication hole interposed therebetween,
The outer portions having the large diameter sandwich the adjacent bearing member from the axial direction.
A camshaft oiling device characterized by that. In any one of Claims 1 thru | or 6,
The cage is made of synthetic resin;
An annular advance head-side annular groove continuous with the advance angle head-side oil passage is formed on the inner peripheral surface of the adjacent bearing member, and an annular delay connected with the retard angle head-side oil passage is formed. A corner head side annular groove is formed,
An annular advance cam shaft side annular groove continuous with the advance cam shaft side oil passage is formed on an outer peripheral surface of the cam shaft, and an annular advance connecting with the retard cam shaft side oil passage is formed. A retard camshaft-side annular groove is formed,
An annular outer lip portion individually extending into each head-side annular groove portion is formed on each peripheral edge portion of each outer annular groove portion,
An annular inner lip portion extending into each camshaft side annular groove portion is formed on each peripheral edge portion of each inner annular groove portion.
A camshaft oiling device characterized by that.

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