WO2006095777A1 - 転がり軸受、カムシャフト装置、及び、カムシャフト支持装置 - Google Patents
転がり軸受、カムシャフト装置、及び、カムシャフト支持装置 Download PDFInfo
- Publication number
- WO2006095777A1 WO2006095777A1 PCT/JP2006/304486 JP2006304486W WO2006095777A1 WO 2006095777 A1 WO2006095777 A1 WO 2006095777A1 JP 2006304486 W JP2006304486 W JP 2006304486W WO 2006095777 A1 WO2006095777 A1 WO 2006095777A1
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- WO
- WIPO (PCT)
- Prior art keywords
- camshaft
- rolling bearing
- shaft
- rolling
- outer ring
- Prior art date
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
- F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L2001/0476—Camshaft bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2810/00—Arrangements solving specific problems in relation with valve gears
- F01L2810/02—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/18—Camshafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/80—Labyrinth sealings
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49229—Prime mover or fluid pump making
- Y10T29/49293—Camshaft making
Definitions
- the present invention relates to a rolling bearing, a camshaft device using the same, and a camshaft support device that supports a camshaft for opening and closing an intake / exhaust valve of an engine.
- An engine used in a vehicle such as an automobile has a cam shaft for opening and closing an air supply / exhaust valve.
- This camshaft is a shaft body in which a plurality of cams are arranged in the axial direction, and is arranged in a valve operating chamber surrounded by a cylinder head and a head cover of the engine.
- the camshaft is rotatably supported with respect to the cylinder head by a camshaft support device having a plurality of sliding bearings arranged at predetermined intervals in the axial direction.
- the sliding bearing of this camshaft support device may have a relatively high frictional resistance and increase the rotational torque when the engine speed is low, which is one of the factors that reduce the fuel efficiency of the engine. It was. Therefore, there is a structure in which a force shaft is supported by a rolling bearing as shown in Japanese Utility Model Publication Nos. 6-8704 and 4-12102 which improve the fuel efficiency of the engine. As a result, the frictional resistance is reduced, and an attempt is made to reduce the rotational torque.
- the rolling bearing of the conventional camshaft support device has been lubricated with lubricating oil circulating in the engine.
- This lubricating oil circulating in the engine contains foreign materials such as power sludge from combustion gas and wear powder generated by metal friction inside the engine.
- the rolling bearing is lubricated by the lubricating oil containing such foreign matter, the foreign matter enters the rolling bearing, causing vibration and noise, and causing abnormal wear, thereby causing the camshaft support device to The problem of reducing lifespan was attracted.
- an object of the present invention is to provide a camshaft support device capable of suppressing the occurrence of vibration and noise and a reduction in life even when a rolling bearing is used to reduce torque.
- Another object of the present invention is to provide a rolling bearing capable of supplying oil to the raceway without affecting the rolling of the rolling element, and a camshaft device using the rolling bearing.
- the rolling bearing of the present invention has a groove formed on the outer peripheral surface of the outer ring, and penetrates from the groove to a surface of the inner peripheral surface of the outer ring that does not contact the rolling element. It is characterized by the fact that the refueling hole is formed.
- the lubricating oil supplied in the groove formed on the outer peripheral surface of the outer ring can be supplied to the inner peripheral surface of the outer ring through the oil supply hole passing through the outer ring.
- the lubrication hole is open on the surface that does not come into contact with the rolling element, so it does not affect the rolling of the rolling element.
- Lubricating oil is supplied to the surface that does not come into contact with the rolling elements, that is, the portion other than the raceway surface.
- the lubricating oil flows along the inner peripheral surface of the outer ring toward the raceway surface and can be supplied to the raceway surface.
- the rolling bearing of the present invention includes a circumferential groove on the outer circumferential surface of the outer ring, and a circumferential groove. An axial groove opening from the inside to the side surface of the outer ring is formed.
- the lubricating oil supplied into the circumferential groove on the outer peripheral surface of the outer ring can be supplied to the side surface of the outer ring through the axial groove. Then, the lubricating oil supplied to the side surface of the outer ring flows around the side surface of the outer ring and the inner peripheral surface of the outer ring, and oil supply to the raceway surface becomes possible.
- the circumferential groove is formed at an axial center portion on the outer peripheral surface of the outer ring, and the axial groove extends in a straight line through both side surfaces of the outer ring. It is preferably formed on both sides in the axial direction of the direction groove. As a result, the lubricating oil can be evenly supplied to both sides of the rolling bearing in the axial direction. This is effective when the environments on the left and right sides of the rolling bearing are the same (for example, the shape of the peripheral members).
- the circumferential groove is formed in an axial center portion on the outer peripheral surface of the outer ring, and the axial grooves are located on both sides in the axial direction of the circumferential groove and are positioned in the circumferential direction. It is preferable that they are formed in a shifted manner. According to this, it becomes effective when the ease of flow of the lubricating oil differs between the left and right due to the difference in environment between the left and right sides of the rolling bearing.
- the axial groove is formed to be inclined with respect to a straight line parallel to the central axis on the outer peripheral surface of the outer ring. According to this, it is possible to make it easy for the lubricating oil supplied into the circumferential groove to wrap around the side surface of the outer ring.
- the camshaft device of the present invention includes the rolling bearing, a shaft that is rotatably supported by the rolling bearing, and a shaft that is separate from the shaft and has a through hole.
- the rolling bearing is characterized in that it has a race ring made of a single ring and is attached to the shaft as an outer fitting shape.
- the rolling bearing can be attached by moving the shaft from the end of the shaft to a predetermined position before the cam is attached to the shaft. did Therefore, no joints are formed on the raceway surface where the raceway ring of the rolling bearing needs to be divided. If the raceway has a split structure and there is a joint on the raceway surface, vibration and noise will be generated when the rolling elements pass through the joint, reducing the bearing life. Further, the cam can be mounted at a predetermined position by moving the end force of the shaft as the shaft is inserted.
- the camshaft support device of the present invention is disposed in a valve operating chamber surrounded by an engine cylinder head and a head cover, and rotatably supports the camshaft with respect to the cylinder head. And a plurality of rolling bearings filled with grease, and shielding means for shielding engine oil from entering the rolling bearings.
- the shielding means since the shielding means is provided, the lubricating oil of the engine can be prevented from entering the pair of rolling bearings. As a result, while the foreign matter such as carbon sludge contained in the engine lubricating oil is prevented from entering the rolling bearing, the rolling bearings are filled with grease sealed inside. Can be reliably lubricated.
- the plurality of rolling bearings support only both ends of the camshaft.
- the configuration of the cylinder head and the like around the camshaft can be simplified compared to the case where the camshaft is supported by a larger number of bearings. Further, since the cam shaft is not supported by a bearing other than the rolling bearing, the rotational torque of the cam shaft can be further reduced as compared with the case where the cam shaft is supported by a larger number of bearings.
- the shielding means is formed in at least one of the cylinder head and the head cover, and the engine oil enters the valve operating chamber by partitioning the valve chamber.
- the shield plate is a shield plate in which the bearing chamber in which the plurality of rolling bearings are disposed is formed in the valve train chamber.
- the shielding plate for forming the bearing chamber is provided on at least one of the cylinder head and the cylinder cover, a member for shielding lubricating oil is separately assembled.
- the plurality of rolling bearings can be easily shielded from engine lubricating oil without penetration.
- the camshaft support device of the present invention is disposed outside the valve operating chamber surrounded by the cylinder head and the head cover of the engine, and the cylinder head or the head cover force is protruded at both ends of the valve operating chamber. And a pair of rolling bearings that are attached to both ends of the camshaft passing through the shaft and rotatably support the camshaft with respect to the cylinder head.
- the pair of rolling bearings are arranged outside the valve operating chamber, so that engine lubricating oil does not flow into the inside thereof. Accordingly, it is possible to prevent foreign matters contained in the engine lubricating oil from entering the rolling bearings.
- At least one of the pair of rolling bearings is a ball bearing.
- an axial load acting on the camshaft can be supported by the ball bearing.
- FIG. 1 is a partially sectional side view showing a camshaft device according to a first embodiment of the present invention.
- FIG. 2 is a cross-sectional view showing a first embodiment of a rolling bearing.
- FIG. 3 is a side view showing a second embodiment of the rolling bearing.
- FIG. 4 is an enlarged view of a part of the outer peripheral edge of the outer ring viewed from the axial direction.
- FIG. 5 is a side view showing a third embodiment of the rolling bearing.
- FIG. 6 is a side view showing a rolling bearing according to a fourth embodiment.
- FIG. 7 is a side view showing a fifth embodiment of a rolling bearing.
- FIG. 8 is a partial cross-sectional side view showing a second embodiment of the camshaft device.
- FIG. 9 is a cross-sectional view of the upper part of a 4-cycle engine in which the camshaft support device according to the first embodiment of the present invention is incorporated.
- FIG. 10 is a sectional view taken along line II-II in FIG.
- FIG. 11 is a cross-sectional view of an upper part of a 4-cycle engine in which a camshaft support device according to a second embodiment of the present invention is incorporated.
- the present invention will be described in a camshaft device in which a shaft 1 having a cam 2 is rotatable as shown in FIG.
- This camshaft device operates an intake / exhaust valve of an automobile engine.
- the entire camshaft device will be described.
- This camshaft device is accommodated in a housing H (cylinder head) that also serves as an aluminum blotter.
- the camshaft device is separated from the straight shaft 1 and is attached to the shaft 1 in an external fitting manner.
- a plurality of rolling bearings 3 which rotatably support the shaft 1.
- a cam 2 and a rolling bearing 3 are disposed on the shaft 1 at predetermined positions in the axial direction of the shaft 1.
- one rolling bearing 3 is provided between a pair of cams 2 that form a pair.
- the rolling bearing 3 is attached to the shaft 1 as an outer fitting shape and rotatably supports the shaft 1, and is a deep groove ball bearing. As shown in FIG. 2, the rolling bearing 3 has an inner ring 4 and an outer ring 5 provided radially outward of the inner ring 4, and a raceway surface (railway groove) 6 of the inner ring 4 and A rolling element consisting of a plurality of balls 7 is interposed between the raceway surface (track groove) 12 of the outer ring 5. These balls 7 are held by a cage 13.
- the inner ring 4 is externally fitted and fixed to the outer peripheral surface la of the shaft 1, and the outer ring 5 is fitted to the housing interior surface of the housing H, and the rolling bearing 3 is fixed.
- FIG. 8 is a partial cross-sectional side view showing another embodiment of the camshaft device.
- the rolling bearing 3 provided in this device has an inner ring raceway surface 6 of the rolling bearing 3 formed on the outer peripheral surface la of the camshaft 1. That is, the inner ring 4 in the camshaft device of FIG. 1 is omitted, and the camshaft 1 is the inner ring.
- the number of parts can be reduced and the load capacity can be increased.
- FIG. 2 is a cross-sectional view showing a first embodiment of the rolling bearing 3.
- the rolling bearing 3 has a circumferential groove 31 (hereinafter referred to as a circumferential groove 31) formed on the outer circumferential surface 5 a of the outer ring 5, and penetrates from the circumferential groove 31 to the inner circumferential surface 5 b of the outer ring 5.
- the oil supply hole 33 is formed,
- the circumferential groove 31 is a concave groove that does not penetrate the outer ring 5 in the radial direction, and is formed continuously in the circumferential direction.
- the oil supply hole 33 is formed so as to open on a surface of the inner peripheral surface 5b of the outer ring 5 that does not contact the balls 7 as rolling elements. More specifically, the oil supply hole 33 is a surface other than the raceway surface 12 formed with a predetermined radius of curvature on the inner peripheral surface 5b of the outer ring 5, that is, on the axial side of the raceway surface 12 and at the center.
- the straight non-orbital surface 34 opens in a direction parallel to the axis C. Thereby, the oil supply hole 33 does not affect the rolling of the ball 7.
- At least one oil supply hole 33 may be formed, but it is preferable to provide a plurality of oil supply holes at equal intervals in the circumferential direction in order to supply oil to a plurality of locations simultaneously.
- the oil supply hole 33 opens at a position including the bottom surface of the circumferential groove 31 having a rectangular cross section. In FIG. 2, the oil supply hole 33 opens at a corner between the bottom surface and the side surface of the circumferential groove 31. .
- the lubricating oil tends to stay in the corners, but such lubricating oil can be supplied to the oil supply hole 33, and the retention of the lubricating oil can be prevented.
- the circumferential groove 31 is formed in the axial central portion on the outer peripheral surface 5a of the outer ring 5, and the oil supply hole 33 is radially inward while exerting a force in the axial direction from the circumferential groove 31. It is formed as a straight line extending to Although not shown, the circumferential groove 31 is formed on the axial edge (side) of the outer peripheral surface 5a, and the oil supply hole 33 is moved from the circumferential groove 31 to the axial center (axial center). It should be formed as a straight line extending inward in the radial direction toward the raceway surface 12).
- the lubricating oil is supplied into the circumferential groove 31 of the outer ring 5 of the rolling bearing 3 through the lubricating oil hole 35 formed in the housing H. It is supplied to the non-track surface 34 of the inner peripheral surface 5 b of the outer ring 5 through the oil supply hole 33. Then, the lubricating oil supplied to the non-track surface 34 part flows to the track surface 12 side along the inner peripheral surface 5b of the outer ring 5, and oil supply to the track surface 12 becomes possible.
- FIG. 3 is a side view showing a second embodiment of the rolling bearing 3.
- the rolling bearing 3 includes a circumferential groove 31 (hereinafter referred to as a circumferential groove 31) on the outer circumferential surface 5a of the outer ring 5, and an axial groove 32 that opens from the circumferential groove 31 to the side surface 5c of the outer ring 5. (Hereinafter referred to as an axial groove 32).
- the circumferential groove 31 is a concave groove that does not penetrate the outer ring 5 in the radial direction. It is formed continuously.
- the circumferential groove 31 is formed in the central portion in the axial direction on the outer peripheral surface 5 a of the outer ring 5. That is, the circumferential groove 31 is formed on a virtual center line that is continuous in the circumferential direction that bisects the outer circumferential surface 5a of the outer ring 5 in the axial direction.
- the axial groove 32 is formed so as to penetrate the both side surfaces 5c of the outer ring 5 linearly across the circumferential groove 31. That is, the axial grooves 32 are formed side by side on both sides (left and right sides) of the circumferential groove 31. The axial grooves 32 on both sides are linear in the axial direction with the circumferential groove 31 in between. It is formed as a continuous groove. Further, at least one axial groove 32 may be formed in the circumferential direction, but it is preferable to form a plurality of strips at equal intervals in the circumferential direction as shown in FIG.
- FIG. 4 is a view of a part of the outer peripheral edge of the outer ring 5 as seen from the axial direction.
- the axial groove 32 and the circumferential groove 31 are formed with the same depth. According to this embodiment, since the axial grooves 32 are formed symmetrically with respect to the circumferential groove 31, the lubricating oil can be evenly supplied from both sides in the axial direction.
- FIG. 5 is a side view showing a third embodiment of the rolling bearing 3.
- a circumferential groove 31 and an axial groove 32 are formed on the outer circumferential surface 5 a of the outer ring 5, as in the second embodiment.
- the circumferential groove 31 is formed in the axially central portion on the outer circumferential surface 5 a of the outer ring 5.
- the axial grooves 32 are formed on both axial sides (left and right sides) of the circumferential groove 31, respectively. However, the left and right axial grooves 32 are displaced from each other in the circumferential direction (with different phases). Is formed. Therefore, this axial groove 32 does not linearly penetrate both side surfaces 5c of the outer ring 5, unlike the second embodiment (FIG. 3).
- At least one axial groove 32 may be formed in the circumferential direction on both sides of the circumferential groove 31, but it is preferable that a plurality of axial grooves 32 be formed at equal intervals in the circumferential direction as shown in FIG. .
- Other configurations are the same as those of the second embodiment. According to the third embodiment, this is effective when the flowability of the lubricating oil differs between the left and right due to the difference in the shape of the housing H on the left and right sides of the rolling bearing 3.
- FIG. 6 is a side view showing a fourth embodiment of the rolling bearing 3.
- FIG. 7 is a side view showing a fifth embodiment of the rolling bearing 3. Similar to the second embodiment, these rolling bearings 3 are formed with a circumferential groove 31 and an axial groove 32 on the outer circumferential surface 5a of the outer ring 5 to form a circumferential direction.
- the direction groove 31 is formed at the axially central portion on the outer peripheral surface 5 a of the outer ring 5.
- the axial groove 32 is formed on the outer peripheral surface 5a of the outer ring 5 so as to incline at a predetermined inclination angle ⁇ with respect to a straight line parallel to the central axis C of the rolling bearing 3 (hereinafter referred to as a reference line e). Yes.
- both axial grooves 32 adjacent to each other with the circumferential groove 31 interposed therebetween are formed in directions in which the respective center lines intersect with each other.
- the axial grooves 32 adjacent to each other with the circumferential groove 31 interposed therebetween are formed so that the center lines are parallel to each other.
- the lubricating oil can move downward in the axial groove 32 by its own weight.
- the left and right axial grooves 32 are arranged side by side with the circumferential groove 31 interposed therebetween.
- a plurality of axial grooves 32 having different angles ⁇ may be formed in the circumferential direction.
- the lubricating oil is supplied into the circumferential groove 31 from the hole 35 formed in the housing H, and this lubricating oil is supplied to the shaft. It is supplied to the both axial sides 5c, 5c of the outer ring 5 through the direction groove 32. Then, the lubricating oil supplied to the side surface 5c of the outer ring 5 flows around the side surface 5c of the outer ring 5 and the inner peripheral surface 5b of the outer ring 5, and oil supply to the track portion becomes possible.
- the bearing ring of the rolling bearing 3 of each embodiment is not a divided structure, but is formed of a ring-shaped integrated body (one-piece structure). That is, in FIG. 1, the inner ring 4 and the outer ring 5 are each made of an annular integral member, and in FIG. 8, the outer ring 5 also has an annular integral member force. This prevents seams from appearing on the raceway surface.
- the rolling bearing 3 is attached to a predetermined position in the axial direction of the shaft 1 (rolling bearing mounting portion 15) with the shaft 1 at the end of the shaft 1 also inserted into the shaft 1 and moved axially along the shaft 1. It is done.
- this camshaft device has an assembly structure in which the shaft 1 and the cam 2 are produced as separate bodies and the forces are also assembled to form a camshaft. That is, the shaft 1 is a linear member, and the cam 2 is formed with a through-hole 10 for fitting to the shaft 1. As a result, the cam 2 also has an external force applied to the end of the shaft 1. It can be moved in the axial direction along the shaft 1 and attached to a predetermined position in the axial direction of the shaft 1 (force mounting portion 14).
- the shaft 1, the cam 2, and the rolling bearing 3 can be configured as one cam shaft unit, and the one configured in advance as this unit can be assembled to the housing H.
- a shaft member 26 is attached to one end (left side) of the shaft 1, and the shaft member 26 is fixed so as to be concentric with the shaft 1.
- a pulley 9 for rotating the shaft 1 and a cylindrical roller bearing 11 that supports the vicinity of the pulley 9 are attached to the shaft member 26.
- a large radial belt load acts on the pulley 9, but the shaft member 26 and the shaft 1 can be stably supported by using the cylindrical roller bearing 11 having a large load capacity.
- the oil supply hole 33, the circumferential groove 31, and the axial groove 32 are formed in the outer ring of the cylindrical roller bearing 11 in the same manner.
- the cam 2 attached to the shaft 1 will be further described.
- the cam 2 may be configured to rotate integrally with the shaft 1 using a key member (not shown) or the like, but in the through hole 10 of the cam 2, It is preferable to fit the shaft 1 with a tightening margin and fix it! Therefore, the cam 2 may be attached to the shaft 1 by shrink fitting, for example. As a result, the cam 2 can be easily and firmly attached, no additional fixing member is required, and the number of parts can be reduced.
- the shaft 1 will be further described.
- the shaft 1 is configured as a straight line that allows the cam 2 and the rolling bearing 3 to be attached to predetermined positions by moving the cam 2 and the rolling bearing 3 in the axial direction from the end side. . That is, in order to move the cam 2 and the rolling bearing 3 axially to the predetermined positions of the end force of the shaft 1, the cam mounting portion 14 and the rolling bearing mounting portion 15 have the same outer diameter, and these
- the shaft 1 is configured so as to have a circular cross section having a maximum outer diameter in the portion.
- the raceway surface 6 is formed on the rolling bearing mounting portion 15, and the outer diameter of the rolling bearing mounting portion 15 is the diameter at the shoulder.
- the shaft 1 has the same diameter over the entire length and has a circular section that is uniform in the axial direction. The surface becomes straight (that is, there is no step on the outer circumferential surface la over the entire length).
- all the cam mounting portions 14 and all the rolling bearing mounting portions 15 having the same outer diameter are set to the maximum diameter, and the other portions are set to have a slightly smaller diameter. It can also be a straight line with small steps.
- the lubricating oil can be effectively supplied to the bearing raceway portion, and a camshaft device including the rolling bearing 3 having excellent lubrication performance can be obtained.
- the camshaft unit including the shaft 1, the cam 2, and the rolling bearing 3 can prevent the oil from running out and can function smoothly.
- the rolling bearing 3 supporting the shaft 1 in the vicinity of the cam 2 as a deep groove ball bearing, the following operational effects can be obtained.
- a plurality of cams 2 are provided on the shaft 1, and a load is applied to the cams 2 during the operation of the supply / exhaust valve of the engine, causing periodic waviness (vibration) on the shaft 1.
- the displacement due to the undulation of the shaft 1 can be released by the raceway surface having a curved surface and the ball 7 in contact with the raceway surface.
- the axial load acting on the shaft 1 can be received by the rolling bearing 3, and the axial displacement of the shaft 1 can be regulated.
- shaft device of the present invention is not limited to the illustrated form, and may be of other forms within the scope of the present invention.
- FIGS. 1 and 8 eight cams 2 are provided, and the rolling bearing 3 is provided.
- the force which is set to 4 are not limited to this and can be changed.
- FIG. 9 is a cross-sectional view of the upper part of the 4-cycle engine in which the camshaft support device according to the first embodiment of the present invention is incorporated.
- the camshaft support device 51 is arranged in a valve operating chamber E surrounded by a cylinder head 52 at the top of the four-cycle engine and a head cover 53 covering the top of the cylinder head 52.
- the camshaft support device 51 rotatably supports a camshaft 54 that opens and closes a supply / exhaust valve (not shown) provided in the cylinder head 52.
- the camshaft 54 protrudes to the outside of the head cover 53 through a hole P communicating with the inside and outside of the valve operating chamber E formed in the cylinder head 52 and the head cover 53.
- a toothed pulley 54a for rotating the camshaft 54 in synchronism with a crankshaft (not shown) is attached to the tip protruding outward.
- the camshaft 54 includes a shaft main body 54b, a plurality of cams 54c for operating a valve operating mechanism for opening and closing a supply / exhaust valve (not shown), and a cylindrical shape for positioning the axial interval between the cams 54c.
- a plurality of spacers 54d The camshaft 54 is configured by press-fitting a cam 54c and a spacer 54d to the shaft body 54b in a predetermined arrangement.
- the camshaft support device 51 includes a first rolling bearing 55 attached to one end on the pulley 54a side of the camshaft 54, a second rolling bearing 56 attached to the other end, and a valve And a shielding plate S forming a bearing chamber E1 in which the first and second rolling bearings are arranged in the valve chamber E by partitioning the chamber E.
- the first and second rolling bearings 55 and 56 support the camshaft 54 so as to be rotatable with respect to the cylinder head 52 at both ends of the camshaft 54.
- the first rolling bearing 55 includes an inner ring 55a, an outer ring 55b, and a plurality of cylindrical rollers 55c disposed between the inner and outer rings, and grease is sealed between the inner and outer rings 55a and 55b by a seal.
- a grease-filled cylindrical roller bearing is configured.
- a shaft body 54b of the camshaft 54 is inserted in a press-fit state on the inner peripheral side of the inner ring 55a of the first rolling bearing 55.
- the first rolling bearing 55 is positioned at a predetermined position on one end side of the camshaft 54 by a spacer 54d.
- the first rolling bearing 55 is fixed to the cylinder head 52 side with the outer peripheral surface of the outer ring 55b sandwiched between the bracket 52b formed on the cylinder head 52 and the cap 52c.
- the second rolling bearing 56 includes an inner ring 56a, an outer ring 56b, and a plurality of rollers disposed between the inner and outer rings. And a ball bearing of a grease-filled type in which grease is sealed between the inner and outer rings 56a and 56b with a seal.
- a shaft body 54b of the camshaft 54 is inserted in a press-fit state on the inner peripheral side of the inner ring 56a of the second rolling bearing 56.
- the first rolling bearing 55 is positioned at a predetermined position on the other end side of the camshaft 54 by a spacer 54d.
- the second rolling bearing 56 is fixed to the cylinder head 52 side with its outer peripheral surface held between a bracket 52d formed on the cylinder head 52 and a cap 52e.
- the camshaft 54 is supported only at both ends by the first and second rolling bearings 55 and 56, for example, when the camshaft 54 is supported by a larger number of bearings.
- the configuration of the cylinder head 52 and the like around the camshaft 54 can be simplified as compared with the above. Furthermore, since the rotational torque of the bearing is reduced as compared with the case where the camshaft 54 is supported by a larger number of bearings, it is advantageous in reducing the camshaft 54 torque.
- the shielding plate S has an upper shielding plate S1 formed inside the head cover 53 and a lower shielding plate S2 formed on the cylinder head 52.
- FIG. 10 is a cross-sectional view taken along line II-II in FIG. As shown in the figure, the upper and lower shielding plates Sl, S2 cover the upper surface of the cylinder head 52. When the head cover 53 is attached to the cylinder head 52, the end surfaces of the upper and lower shielding plates S1, S2 are aligned. Has been.
- the upper and lower shielding plates Sl, S2 are formed with semicircular cutouts Sla, S2a, respectively.
- the cutout portions Sla, S2 a form a hole S3 that is combined with each other to allow the camshaft 54 to pass through when the end surfaces of the upper and lower shielding plates Sl, S2 are made to coincide with each other.
- the diameter of the hole S3 is set so as to be a gap of about V ⁇ that the engine lubricating oil cannot easily pass through with respect to the outer diameter of the camshaft 54 !.
- such a shielding plate S partitions the both ends in the longitudinal direction inside the valve train chamber E, whereby the bearing chamber E1 in which the first and second rolling bearings 55, 56 are arranged.
- a cam chamber E2 in which a cam 54c and a valve mechanism (not shown) are arranged is formed in the valve chamber E.
- Engine lubrication oil is supplied to lubricate the cam 54c and the valve mechanism (not shown).
- the shielding oil S prevents the engine lubricating oil from easily entering.
- the shielding plate S constitutes a shielding means that shields the ingress of engine lubricating oil into the first and second rolling bearings 55 and 56.
- the first and second rolling bearings 55 and 56 shield the engine lubricating oil in the valve operating chamber E from the first and second rolling bearings 55 and 56. Since the plate S is provided, engine lubricating oil can be prevented from flowing into the first and second rolling bearings 55 and 56. Therefore, it is possible to prevent foreign matters such as carbon sludge contained in the engine lubricating oil from entering the first and second rolling bearings 55 and 56 and to prevent the first and second rolling bearings 55 and 56 from entering.
- the rolling bearings 55 and 56 are reliably lubricated by the grease enclosed therein.
- the cylinder head 52 and the head cover 53 are provided with the shielding plate S, it is possible to easily perform the first operation without particularly incorporating a member for shielding engine lubricating oil. And the second rolling bearings 55 and 56 can be shielded from engine lubricating oil.
- first and second rolling bearings 55 and 56 only the both ends of the camshaft 54 are supported by the first and second rolling bearings 55 and 56.
- a sliding bearing or the like may be disposed between the plurality of cams 54c.
- FIG. 11 is a cross-sectional view of the upper part of a four-cycle engine in which the camshaft support device according to the second embodiment of the present invention is incorporated.
- the main difference between the present embodiment and the first embodiment is that the first and second rolling bearings 55 and 56 are arranged outside the valve operating chamber E, and pass through the valve operating chamber E to the cylinder head. 52 and cam with both ends protruding from the head cover 53 The point that both ends of the shaft 54 are supported, the shielding plate S is formed on the cylinder head 52 and the head cover 53, and the point is that a ball bearing is used for the first rolling bearing 55. . Since other points are the same as those in the first embodiment, description thereof is omitted.
- holes! 3 , Q communicating with the inside and outside of the valve chamber E are formed on the engine longitudinal side surfaces of the cylinder head 52 and the head cover 53.
- the camshaft 54 is arranged through the valve chamber E in such a manner that both ends project from the cylinder head 52 and the head cover 53 by passing through these holes! 3 and Q.
- the first and second rolling bearings 55 and 56 supporting the camshaft 54 have outer peripheries by the brackets 52b and 52d formed on the outer casing E of the cylinder head 52 and the caps 52c and 52e, respectively. It is clamped and fixed to the cylinder head 52 side.
- the first and second rolling bearings 55 and 56 are disposed outside the valve operating chamber E.
- the ambient temperature can be kept lower. Therefore, grease having a lower viscosity can be sealed, and the rotational torque of the camshaft 54 can be further reduced.
- the degree of freedom of the seal material and grease filling form of these rolling bearings 55 and 56 is increased.
- the axial load acting on the camshaft 54 during engine operation can be supported by the ball bearing.
- the both ends of the camshaft 54 are supported.
- a plurality of cams 54c are provided as necessary.
- a sliding bearing or the like may be arranged between them. Note that the present invention is not limited to the above-described embodiment.
- the force shielding plate S formed on the cylinder head 52 and the head cover 53 so that the bearing chamber E1 is provided at both ends of the valve train chamber E is constituted by a separate member.
- the rolling bearing may be covered with a box and shielded from lubricating oil.
- a shielding plate S may be provided on both sides of the rolling bearing to provide a bearing chamber.
- the camshaft 54 uses a force camshaft in which the cam 54c, the shaft body 54b, and the spacer 54d are assembled, and a force shaft in which the shaft is integrally formed. You can also.
- the first and second rolling S bearings that support the camshaft 54 are formed using a rolling bearing having inner and outer rings, and a track is formed on the outer peripheral surface of the camshaft 54, thereby eliminating the inner rings. It may be a rolling bearing.
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/885,149 US7707983B2 (en) | 2005-03-11 | 2006-03-08 | Rolling bearing, cam shaft assembly and cam shaft supporting apparatus |
EP06715406A EP1860338A4 (en) | 2005-03-11 | 2006-03-08 | BEARING BEARINGS, CAMSHAFT DEVICE, AND CAMSHAFT SUPPORT DEVICE |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005068866A JP4400484B2 (ja) | 2005-03-11 | 2005-03-11 | カムシャフト支持装置 |
JP2005-068864 | 2005-03-11 | ||
JP2005-068866 | 2005-03-11 | ||
JP2005068864A JP4929605B2 (ja) | 2005-03-11 | 2005-03-11 | 転がり軸受及びカムシャフト装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006095777A1 true WO2006095777A1 (ja) | 2006-09-14 |
Family
ID=36953371
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2006/304486 WO2006095777A1 (ja) | 2005-03-11 | 2006-03-08 | 転がり軸受、カムシャフト装置、及び、カムシャフト支持装置 |
Country Status (4)
Country | Link |
---|---|
US (1) | US7707983B2 (ja) |
EP (2) | EP1860338A4 (ja) |
KR (1) | KR20070116834A (ja) |
WO (1) | WO2006095777A1 (ja) |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007024092A1 (de) * | 2007-05-22 | 2008-11-27 | Mahle International Gmbh | Nockenwelle |
JP5145953B2 (ja) † | 2008-01-10 | 2013-02-20 | 株式会社ジェイテクト | カムシャフト装置 |
FR2928408B1 (fr) * | 2008-03-06 | 2011-08-26 | Peugeot Citroen Automobiles Sa | Procede de montage d'un arbre a cames. |
DE102009009665A1 (de) * | 2009-02-19 | 2010-08-26 | Mahle International Gmbh | Brennkraftmaschine mit wenigstens einer Nockenwelle |
US8166939B2 (en) * | 2009-03-05 | 2012-05-01 | GM Global Technology Operations LLC | Cam bearing surface of an engine cylinder head that includes an axially extending oil passage |
JP5598075B2 (ja) * | 2010-04-28 | 2014-10-01 | 株式会社ジェイテクト | 転がり軸受装置 |
DE102010024722A1 (de) | 2010-06-23 | 2011-12-29 | Mahle International Gmbh | Nockenwelle |
JP5741893B2 (ja) * | 2010-09-03 | 2015-07-01 | 株式会社ジェイテクト | カムシャフト装置 |
DE102011077563B4 (de) | 2011-06-15 | 2022-08-11 | Mahle International Gmbh | Brennkraftmaschine |
DE102012105230A1 (de) * | 2012-06-15 | 2013-12-19 | Thyssenkrupp Presta Teccenter Ag | Verfahren zur materialabtragenden Bearbeitung einer verstellbaren Nockenwelle sowie Anordnung zur Durchführung des Verfahrens |
US8931444B2 (en) * | 2012-11-20 | 2015-01-13 | Ford Global Technologies, Llc | Head packaging for cylinder deactivation |
DE102013207573A1 (de) * | 2013-04-25 | 2014-10-30 | Mahle International Gmbh | Lagerrahmen oder Zylinderkopfhaube |
DE102014104995A1 (de) * | 2014-04-08 | 2015-10-08 | Thyssenkrupp Presta Teccenter Ag | Modul mit vororientierter Nockenwelle |
US9951817B2 (en) * | 2014-12-04 | 2018-04-24 | United Technologies Corporation | Integral oil damper and jet for lubrication of bearings and seals |
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- 2006-03-08 WO PCT/JP2006/304486 patent/WO2006095777A1/ja active Application Filing
- 2006-03-08 EP EP11154485A patent/EP2317083B1/en not_active Expired - Fee Related
- 2006-03-08 KR KR1020077022163A patent/KR20070116834A/ko not_active Application Discontinuation
- 2006-03-08 US US11/885,149 patent/US7707983B2/en not_active Expired - Fee Related
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Also Published As
Publication number | Publication date |
---|---|
US7707983B2 (en) | 2010-05-04 |
EP2317083A1 (en) | 2011-05-04 |
US20080170816A1 (en) | 2008-07-17 |
KR20070116834A (ko) | 2007-12-11 |
EP1860338A4 (en) | 2010-12-29 |
EP1860338A1 (en) | 2007-11-28 |
EP2317083B1 (en) | 2012-10-24 |
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