WO2011086815A1 - 可変動弁装置付エンジン - Google Patents
可変動弁装置付エンジン Download PDFInfo
- Publication number
- WO2011086815A1 WO2011086815A1 PCT/JP2010/072885 JP2010072885W WO2011086815A1 WO 2011086815 A1 WO2011086815 A1 WO 2011086815A1 JP 2010072885 W JP2010072885 W JP 2010072885W WO 2011086815 A1 WO2011086815 A1 WO 2011086815A1
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- WIPO (PCT)
- Prior art keywords
- cam phase
- cylinder head
- oil
- cam
- engine
- Prior art date
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Classifications
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- 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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
- F01L1/143—Tappets; Push rods for use with overhead camshafts
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- 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
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
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- 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
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- 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
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0223—Variable control of the intake valves only
- F02D13/0234—Variable control of the intake valves only changing the valve timing only
- F02D13/0238—Variable control of the intake valves only changing the valve timing only by shifting the phase, i.e. the opening periods of the valves are constant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0257—Independent control of two or more intake or exhaust valves respectively, i.e. one of two intake valves remains closed or is opened partially while the other is fully opened
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
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- 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
- F01L2001/0471—Assembled camshafts
- F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
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- 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
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- 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
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
- F01L2001/34433—Location oil control valves
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- 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
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
- F01L2001/34483—Phaser return springs
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- 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
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L2001/34486—Location and number of the means for changing the angular relationship
- F01L2001/34489—Two phasers on one camshaft
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- 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
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates to an engine provided with a cam phase variable mechanism capable of changing a cam phase.
- an engine equipped with a variable cam phase mechanism has increased as a variable valve operating device that changes the valve opening / closing timing (cam phase). Furthermore, a technique has been developed in which the cam phase variable mechanism is employed in an engine having a plurality of valves in one cylinder, and the opening / closing timing of only a part of the plurality of valves is changed according to the operating state of the engine.
- the camshaft used for such a valve gear of an engine is assembled by fitting a separate cam crest to a shaft member so as to be rotatable.
- the cam phase variable mechanism uses a hydraulically driven actuator such as a vane actuator, and is arranged at the end of the camshaft. By changing the phase between the shaft member and the cam crest, a plurality of valves are provided. Among them, it is possible to make a split variable in which the phases of some valves and other valves are variable (see Patent Document 1).
- the camshaft is generally housed in the cylinder head of the engine.
- the cylinder head has a structure in which the entire upper part is opened for assembly and maintenance of a valve operating device such as a camshaft.
- a cylinder head cover is detachably fixed to the upper part of the cylinder head by a bolt, and has a structure that covers the opening of the cylinder head.
- variable valve phase mechanism When the variable valve phase mechanism is provided in the valve operating apparatus as in Patent Document 1, the axial dimension of the entire variable valve mechanism is increased as compared with a conventional engine that does not include the variable cam phase mechanism. End up. Therefore, it is necessary to newly prepare a cylinder head that accommodates the valve operating device in the axial direction in order to accommodate the cam phase variable mechanism.
- An object of the present invention is to provide an engine with a variable valve operating device having a structure capable of providing a cam phase variable mechanism while suppressing the size of a cylinder head.
- the invention according to claim 1 is provided on a camshaft that is driven to rotate by transmission of power from a crankshaft to one end side, and is provided on the camshaft with respect to the crankshaft.
- the cam phase variable mechanism is provided on the other end side opposite to the one end side of the camshaft, and is located outside the cylinder head.
- the cover member is arranged and fixed to the cylinder head, and covers at least the lower part of the cam phase varying mechanism.
- the cam phase variable mechanism is a hydraulic actuator, and a control valve for controlling supply / discharge of hydraulic oil to / from the cam phase variable mechanism is fixed to the cover member.
- the cylinder head and the cover member are open at the top, and the cover member is formed so that the opening surface of the upper portion is flush with the opening surface of the cylinder head. And a cylinder head cover that covers the cover and the opening of the cover member together.
- the cover member is provided with detecting means for detecting the phase of the cam variably controlled by the cam phase varying mechanism.
- the drain oil passage of the control valve is opened in the cylinder head.
- an oil passage that connects the space in the cover and the space in the cylinder head is formed in the partition wall that separates the space in the cover member and the space in the cylinder head.
- the cam phase variable mechanism has a cylindrical outer shape and is arranged coaxially with the cam shaft, and the inner wall of the cover member is formed in an arc shape along the outer periphery of the cam phase variable mechanism. I did it.
- the inner wall of the cover member is provided with introducing means for guiding the hydraulic oil in the storage portion to the oil passage by rotation of the cam phase variable mechanism.
- the cover member is open at the top and the space in the cover member is formed in a semi-cylindrical shape, covering the lower half of the cam phase variable mechanism, and the cylinder head cover is formed of the cam phase variable mechanism.
- An inner wall was formed in an arc shape along the outer periphery so as to cover the upper part of the cover member.
- the cover member is formed separately from the cylinder head and is fixed to the cylinder head.
- the cam phase variable mechanism is provided at both ends of the camshaft, and the camshaft is rotatably supported by a plurality of bearings provided in the cylinder head, and is provided at both ends.
- the oil passages for introducing the hydraulic oil to the two cam phase variable mechanisms are formed in the cylinder head and the camshaft, respectively, and the oil passages in the cylinder head and the camshaft are provided at different bearing portions.
- an oil passage for introducing hydraulic oil to one of the two cam phase variable mechanisms has an annular oil groove on the outer peripheral surface of the camshaft.
- the oil passage for introducing the hydraulic oil into the other second cam phase variable mechanism is provided with an annular oil groove on the inner peripheral surface of the bearing portion.
- the engine is provided with a plurality of intake valves in one cylinder, and the first cam phase varying mechanism varies the phases of the plurality of intake valves as a whole, and the second cam phase varying mechanism. Changed the phase of some of the intake valves.
- the bearing portion in which the oil passage for introducing the hydraulic oil to the second cam phase variable mechanism is formed has the oil passage for introducing the hydraulic oil to the first cam phase variable mechanism.
- the inner diameter was made larger than the bearing part.
- the cam phase varying mechanism is provided outside the cylinder head and is disposed in the cover member.
- the cam phase variable mechanism does not need to be housed in the cylinder head, so that it is possible to realize an engine with a variable valve operating device provided with the cam phase variable mechanism while suppressing the size of the cylinder head. Therefore, it is possible to reduce the size of the cylinder head processing equipment, and to make the shape of the cylinder head substantially the same as that of the engine not equipped with the cam phase variable mechanism. Can be suppressed.
- the cam hole into which the camshaft is inserted can be pierced and machined in the manufacture of the cylinder head, the machining can be facilitated and the accuracy of the cam hole can be improved to reduce the friction when the camshaft rotates.
- the cam phase variable mechanism is a hydraulic actuator and the hydraulic oil supply passage to the cam phase variable mechanism is via a sliding surface between the bearing portion formed by machining the cam hole and the cam shaft.
- the actuator since the actuator is stored in a partitioned space, a large amount of lubricating oil in the cylinder head is not agitated by the rotation of the actuator, so that the agitation resistance does not increase and the lubricating oil becomes mist and mixes with blow-by. Does not adversely affect oil consumption.
- the control valve for controlling the supply and discharge of the hydraulic oil to and from the cam phase variable mechanism that is a hydraulic actuator is fixed to the cover member.
- these processing can be concentrated on a cover member that is relatively smaller than the cylinder head, and the processing cost can be reduced.
- the control valve is disposed in the vicinity of the actuator, a reliable variable response can be obtained.
- the cylinder head cover covers the opening of the cylinder head and the opening of the cover member together, the number of parts can be reduced. Furthermore, since the cylinder head cover mounting surface is disposed on the same surface of the cylinder head and the cover member, it is possible to ensure sealing performance on the cylinder head cover mounting surface.
- the detection means for detecting the phase of the cam that is variably controlled by the cam phase variable mechanism is disposed on the cover member, so that the component required when the cam phase variable mechanism is provided.
- the processing of the attachment portion is concentrated on the cover member, and the processing cost can be reduced.
- variable cam phase mechanism since the variable cam phase mechanism is housed in the cover member, even if the hydraulic fluid leaks from the variable cam phase mechanism, the hydraulic fluid to the outside Outflow can be prevented. And since the oil passage which connects the space in the cover member and the space in the cylinder head is formed in the partition wall, the hydraulic oil leaking into the cover member is discharged into the space in the cylinder head, and in the cover member Storage of hydraulic oil can be suppressed. Therefore, when the cam phase variable mechanism is operated, friction due to agitation of the hydraulic oil in the cover member can be reduced, and variable responsiveness by the cam phase variable mechanism can be improved.
- variable valve gear engine of claim 7 of the present invention since the inner wall of the cover member is formed in an arc shape along the outer shape of the cam phase variable mechanism, the hydraulic oil is stored in the cover member. In this case, the hydraulic oil in the cover member is smoothly agitated when the cam phase variable mechanism is rotated, and an increase in friction can be suppressed. In addition, since the aeration can be suppressed by smooth agitation of the hydraulic oil, when the hydraulic oil in the cover member is recovered and reused as the hydraulic oil of the cam phase variable mechanism, the hydraulic pressure by the aeration is reduced. The decrease is suppressed, and the decrease in the operation response of the cam phase variable mechanism can be prevented. Moreover, since it forms in circular arc shape, the shape of a cover member can be made small and a compact design is attained.
- the operating oil in the cover member stirred by the rotation of the cam phase variable mechanism is guided to the oil passage by the introducing means. Can be discharged smoothly. Therefore, the storage of the hydraulic oil can be quickly eliminated, and the stirring resistance of the hydraulic oil can be quickly reduced.
- the entire circumference of the cam phase variable mechanism can be covered with a relatively small gap inside by combining the cylinder head cover and the storage portion. Therefore, it is possible to store the cam phase variable mechanism housing in which the overall size is suppressed with a simple configuration and the amount of hydraulic oil stored is suppressed.
- the storage portion of the cam phase variable mechanism is separate from the cylinder head, the dimensions of the engine and the cylinder head that do not require the cam phase variable mechanism are increased. It can be shared at the location of the part.
- the oil passage for introducing the hydraulic oil to the first cam phase variable mechanism includes an annular oil groove on the outer peripheral surface of the rotating camshaft. Since the oil passage for introducing the hydraulic oil to the cam phase variable mechanism 2 has an annular oil groove on the inner peripheral surface of the fixed bearing portion, the oil passage supplied to the oil groove to the first cam phase variable mechanism The oil in the annular oil groove on the outer peripheral surface of the camshaft is also dragged and rotated at the opening of the camshaft, so that the oil flow is fast relative to the opening, and the oil groove to the second cam phase variable mechanism The oil in the annular oil groove on the inner peripheral surface of the bearing portion is rotated by being dragged only on the rotating cam shaft surface side at the opening portion of the oil passage supplied to the oil passage, and the oil flow is delayed with respect to the opening portion.
- a part of the intake valves by the second cam phase variable mechanism rather than the variable of the whole phases of the plurality of intake valves by the first cam phase variable mechanism.
- the phase can be varied with priority. Therefore, for example, even when the amount of hydraulic oil supplied from the oil pump decreases at a low speed and a low load of the engine, so-called split variable of the intake valve by the second cam phase variable mechanism can be performed quickly and can be performed quickly.
- the optimum cam timing can be changed without delay, so that fuel efficiency can be improved while maintaining high drivability.
- the bearing portion in which the oil passage for introducing the hydraulic oil to the second cam phase variable mechanism is formed is connected to the first cam phase variable mechanism. Since the inner diameter is larger than the bearing portion in which the oil passage for introducing the oil is formed, the peripheral speed of the hydraulic oil in the oil groove is increased, and the oil pressure in the vicinity of the opening of the oil passage is unlikely to increase.
- the so-called intake valve split variable is performed by the second cam phase variable mechanism, the variable split of the intake valve can be performed quickly with priority, and high drivability and fuel consumption performance are maintained.
- the degree of freedom in design can be increased, and the strength reliability can be improved. Further, it is possible to balance the variable responsiveness of the cam phase variable mechanisms provided at both ends of the camshaft.
- the top view which shows the structure in the cylinder head in the engine with a variable valve apparatus of this embodiment.
- Sectional drawing which shows the structure of an intake camshaft.
- the rear view of the engine which shows the attachment state of an actuator cover and a cylinder head cover.
- the perspective view which shows the outer side shape of an actuator cover.
- the perspective view which shows the inner side shape of an actuator cover.
- Sectional drawing which shows the shape of the weir of an actuator cover.
- Sectional drawing which shows the structure of an intake camshaft and its support part.
- Explanatory drawing which shows the peripheral speed of the hydraulic fluid in an oil groove at the time of providing an oil groove in the camshaft side.
- Explanatory drawing which shows the circumferential speed of the hydraulic fluid in an oil groove at the time of providing an oil groove in the cylinder head side.
- Sectional drawing of the groove width direction which shows the circumferential speed of the hydraulic fluid in an oil groove at the time of providing an oil groove in the camshaft side.
- Sectional drawing of the groove width direction which shows the circumferential speed of the hydraulic fluid in an oil groove at the time of providing an oil groove in the cylinder head side.
- FIG. 1 is a top view showing a structure in a cylinder head 2 of an engine with a variable valve operating apparatus (hereinafter simply referred to as an engine 1) of the present embodiment.
- FIG. 2 is a cross-sectional view showing the structure of the intake camshaft 4.
- the engine 1 of this embodiment is an in-line three-cylinder engine having a DOHC valve operating mechanism.
- cam sprockets 5 and 6 are connected to an exhaust camshaft 3 and an intake camshaft 4 (corresponding to the camshaft of the present application), which are rotatably supported inside the cylinder head 2, respectively.
- These cam sprockets 5 and 6 are connected to a crankshaft (not shown) via a chain 7.
- One cylinder 8 of the engine 1 is provided with two intake valves 9 and 10 and two exhaust valves (not shown).
- the two intake valves 9, 10 are driven by first intake cams 11 and second intake cams 12 that are alternately arranged on the intake camshaft 4. Specifically, of the two intake valves, the first intake valve 9 is driven by the first intake cam 11, and the second intake valve 10 is driven by the second intake cam 12.
- the two exhaust valves are driven by an exhaust cam 13 fixed to the exhaust camshaft 3.
- the intake camshaft 4 has a double structure including a hollow outer camshaft 21 and an inner camshaft 22 inserted into the outer camshaft 21.
- the outer cam shaft 21 and the inner cam shaft 22 are arranged concentrically with a slight gap, and are rotatably supported by a plurality of bearing portions 23a to 23e formed in the cylinder head 2 of the engine 1. .
- the first intake cam 11 is fixed to the outer cam shaft 21.
- a second intake cam 12 (corresponding to the valve drive cam of the present application) is supported on the outer cam shaft 21 so as to be rotatable.
- the second intake cam 12 includes a substantially cylindrical support portion 12 a into which the outer cam shaft 21 is inserted, and a cam peak portion 12 b that protrudes from the outer periphery of the support portion 12 a and drives the second intake valve 10. .
- the second intake cam 12 and the inner cam shaft 22 are connected by a pin-like member 24.
- the pin-shaped member 24 passes through the support portion 12a of the second intake cam 12, the outer cam shaft 21, and the inner cam shaft 22, and is inserted into a hole provided in the inner cam shaft 22 with almost no gap.
- a long hole 25 through which the pin-like member 24 passes is formed in the outer cam shaft 21 so as to extend in the circumferential direction. Therefore, the first intake cam 11 is driven by the rotation of the outer cam shaft 21, and the second intake cam 12 is driven by the rotation of the inner shaft 22.
- the intake camshaft 4 is provided with a first cam phase variable mechanism 30 and a second cam phase variable mechanism 31.
- a known vane type hydraulic actuator is used for the first cam phase variable mechanism 30 and the second cam phase variable mechanism 31.
- the vane hydraulic actuator is configured such that a vane rotor is rotatably provided in a cylindrical housing (cover), and varies the rotation angle of the vane with respect to the housing according to the supply of hydraulic oil into the housing. It has a function.
- a first cam phase variable mechanism 30 is provided at the front end of the intake camshaft 4. Specifically, the cam sprocket 6 is fixed to the housing of the first cam phase varying mechanism 30, and the front end portion of the outer cam shaft 21 is fixed to the vane rotor of the first cam phase varying mechanism 30.
- a second cam phase variable mechanism 31 is provided at the rear end of the intake camshaft 4. Specifically, the rear end portion of the outer cam shaft 21 is fixed to the housing 31 a of the second cam phase varying mechanism 31, and the second intake cam 12 is attached to the vane rotor of the second cam phase varying mechanism 31. The inner camshaft 22 to be connected is fixed.
- the first cam phase varying mechanism 30 has a function of varying the rotation angle of the outer cam shaft 21 with respect to the cam sprocket 6, while the second cam phase varying mechanism 31 is an inner cam shaft 22 with respect to the outer cam shaft 21.
- the variable mechanism 31 has a split variable function that varies the opening / closing timing of the second intake valve 10 with respect to the opening / closing timing of the first intake valve 9.
- the cylinder head 2 includes a first cam sensor 32 that detects the actual rotation angle of the outer cam shaft 21 and a first OCV (oil control valve) that controls the intake and discharge of hydraulic oil to and from the first cam phase variable mechanism 30. 33 is fixed.
- the first OCV 33 is disposed at a position close to the first cam phase varying mechanism 30 and is formed to extend in the vertical direction from the oil pump (not shown) fixed to the cylinder block of the engine 1 to the cylinder head 2. Hydraulic oil is supplied through the oil passage 34.
- the first cam sensor 32 is used for controlling the first OCV 33, that is, for controlling the operation of the first cam phase varying mechanism 30.
- the rear end of the intake camshaft 4 passes through the rear wall 2a of the cylinder head 2, and the second cam phase varying mechanism 31 is disposed outside the cylinder head 2.
- the rear wall 2a of the intake camshaft 4 is provided with a bearing portion 23e that supports the rear end portion of the intake camshaft 4.
- FIG. 3 is a rear view of the engine 1 showing how the actuator cover 40 and the cylinder head cover 41 are attached.
- FIG. 4 is a perspective view showing the outer shape of the actuator cover 40
- FIG. 5 is a perspective view showing the inner shape of the actuator cover 40.
- an actuator cover 40 (corresponding to a cover member of the present application) is fixed to the cylinder head 2 by bolts 42.
- the actuator cover 40 is fixed to the cylinder head 2 so as to cover the lower half of the second cam phase varying mechanism 31 whose outer shape is cylindrical, with a slight gap.
- the actuator cover 40 is open at the top, and is formed such that its upper surface 40a is flush with the upper surface 2b of the cylinder head 2 when fixed to the cylinder head 2.
- the cylinder head cover 41 covering the upper surface of the cylinder head 2 has a shape protruding rearward from the cylinder head 2 so as to also cover the upper surface of the actuator cover 40.
- a space 43 for accommodating the second cam phase varying mechanism 31 is formed by a part of the actuator cover 40 and the cylinder head cover 41.
- the contact surface 40b of the actuator cover 40 with the cylinder head 2 is formed with a seal groove 40c for storing a rubber seal for preventing oil leakage from the internal space 43.
- the actuator cover 40 includes a second OCV (corresponding to a control valve of the present application) 44 that controls the intake and discharge of hydraulic oil to and from the second cam phase variable mechanism 31, and the vane rotor of the second cam phase variable mechanism 31.
- a second cam sensor 45 (corresponding to the detection means of the present application) for detecting the rotation timing is attached.
- the second OCV 44 is supplied with hydraulic oil from a hydraulic oil passage (not shown) formed in the cylinder head 2 via an oil passage 40g formed in the actuator cover 40. Then, the second cam phase variable mechanism is formed from the second OCV 44 through the oil passage 40d formed in the actuator cover 40, the oil passage 71 formed in the cylinder head 2, and the oil passage 72 formed in the outer cam shaft 21. Hydraulic oil is supplied to 31. The drain of the second OCV 44 passes through the drain oil passage 40 h formed in the actuator cover 40 and the drain oil passage 2 d in the rear wall 2 a of the cylinder head 2 and is returned into the cylinder head 2.
- the second cam sensor 45 faces the part fixed to the vane rotor of the outer peripheral wall 31b of the second cam phase varying mechanism 31 and is fixed to the actuator cover 40, and detects the actual rotation angle of this part. Thus, the actual rotation angle of the inner camshaft 22 is detected.
- the actual cam angle difference between the outer cam shaft 21 and the inner cam shaft 22 is detected by the second cam sensor 45 based on the difference from the rotation angle of the outer cam shaft 21 detected by the first cam sensor 32.
- This actual rotation angle difference is used for the control of the second OCV 44, that is, the operation control of the second cam phase variable mechanism 31.
- the detection surface 45a of the second cam sensor 45 is located slightly above the lower end of the space 43 in the actuator cover 40. Thereby, even when, for example, iron powder is mixed in the space 43, it is difficult to accumulate in front of the detection surface 45a, and erroneous detection of the second cam sensor 45 can be suppressed.
- FIG. 6 is an explanatory diagram showing the position of the oil passage 50 of the cylinder head 2 and the position of the weir 52 provided in the actuator cover 40.
- An oil passage 50 is formed in the rear wall 2a of the cylinder head 2 to communicate the space 43 in the actuator cover 40 and the space 51 in the cylinder head.
- the oil passage 50 faces the gap between the inner peripheral wall 40 e of the actuator cover 40 and the outer peripheral wall 31 b of the second cam phase varying mechanism 31, and the second cam phase from the bottom.
- the variable mechanism 31 is disposed on the rotational direction side.
- the inner peripheral wall 40e of the actuator cover 40 is provided with a weir 52 (corresponding to the introducing means of the present application) protruding upward.
- the height of the weir 52 is set so as not to contact the outer peripheral wall 31 b of the rotating second cam phase varying mechanism 31.
- the weir 52 is provided so as to be inclined upward from the rear wall 40 f side toward the cylinder head 2, and the end 52 a on the cylinder head 2 side is set to be positioned above the opening of the oil passage 50. ing.
- FIG. 7 is a cross-sectional view showing the structure of the intake camshaft 4 and its support portion.
- the hydraulic fluid from the first OCV 33 to the first cam phase variable mechanism 30 is provided via an oil passage 61 formed in the cylinder head 2 and an oil passage 62 formed in the intake camshaft 4.
- the cam journal 63 which is the portion of the intake camshaft 4 supported by the bearing portion 23a, has an annular oil groove 64 formed on the outer peripheral surface thereof.
- the bearing portion 23a faces the oil groove 64.
- An oil passage 61 is open on the inner peripheral surface of the. As a result, the oil passages 61 and 62 always communicate with each other between the relatively rotating bearing portion 23a and the cam journal 63.
- hydraulic oil is supplied from the second OCV 34 to the second cam phase variable mechanism 31 through the oil passage 71 formed in the cylinder head 2 and the oil passage 72 formed in the outer camshaft 21. Is done.
- an annular oil groove 73 is formed on the inner peripheral surface of the bearing portion 23e, and a cam that is a portion of the intake camshaft 4 that faces the oil groove 73 and is supported by the bearing portion 23e.
- An oil passage 72 is opened on the outer peripheral surface of the journal 74.
- the inner diameter of the bearing portion 23e in which the oil passage 71 to the second cam phase varying mechanism 31 is formed is the oil passage 61 to the first cam phase varying mechanism 30. It is formed larger than the inner diameter of the bearing portion 23a.
- the second cam phase varying mechanism 31 that varies the phase difference between the two intake valves 9 and 10 is provided on the rear outer side of the cylinder head 2.
- the second cam phase varying mechanism 31 is housed in an actuator cover 40 that is a separate component from the cylinder head 2.
- the engine 1 of this embodiment can make the front-and-rear dimension of the cylinder head 2 the same compared with the conventional engine without the 2nd cam phase variable mechanism 31.
- FIG. Therefore, it is possible to reduce the processing equipment of the cylinder head 2.
- the bearing portion 23e for supporting the rear end portion of the intake camshaft 4 is formed on the rear wall 2a of the cylinder head 2, other bearings of the intake camshaft 4 are produced when the cylinder head 2 is manufactured. It is possible to pierce and process from the rear side of the cylinder head 2 including the cam holes for the portions 23a to 23d. Therefore, it is possible to easily drill holes for the bearing portions 23a to 23e, improve the accuracy thereof, and reduce friction during rotation of the intake camshaft 4. Further, since the hydraulic oil path to the cam phase variable mechanism 31 passes through the sliding surface between the bearing portion 23e and the cam journal 74, the accuracy of the cam hole of the bearing portion 23e is improved, so that the sliding portion It is possible to reduce the leakage of hydraulic oil.
- the cylinder head cover 41 covers the opening of the cylinder head 2 and the opening of the actuator cover 40 together, the number of parts can be reduced. Furthermore, since the upper surface 40a of the actuator cover 40 and the upper surface 2a of the cylinder head 2 are the same surface, the lower surface of the cylinder head cover 41 is flush with this. Therefore, it is possible to ensure the sealing performance between the cylinder head cover 41, the cylinder head 2, and the actuator cover 40.
- the actuator cover 40 is fixed with a second OCV 44 for performing hydraulic oil supply / discharge control to the second cam phase variable mechanism 31. Therefore, the mounting process of the second OCV 44 can be performed not on the cylinder head 2 but on the actuator cover 40 which is a relatively small part, and work such as removing burrs and cleaning during processing can be easily performed at low cost. Can do.
- the second cam sensor 45 that detects the phase difference between the first intake cam 11 and the second intake cam 12 or simply the phase of the second intake cam 12 is also arranged in the actuator cover 40, the second When the cam phase variable mechanism 31 is provided, peripheral device attachment processing that is necessary is integrated into the actuator cover 40, and the processing cost can be reduced.
- the space 43 in the actuator cover 40 is composed of the space 51 in the cylinder head 2 and the rear wall 2a. It is another space separated by.
- the second cam phase variable mechanism 31, which is a hydraulic actuator may leak hydraulic oil due to its structure, but even if hydraulic oil leaks from the second cam phase variable mechanism 31, the actuator cover 40 may The outflow to the is prevented.
- the space for housing the second cam phase varying mechanism 31 and the space 51 in the cylinder head 2 are different spaces, the lubricant oil splashed in the space 51 in the cylinder head 2 is not covered by the actuator cover. Inflow into the space 43 in the 40 can be prevented.
- the drain of the second OCV 44 is not opened to the space 43 in the actuator cover 40 but to the space 51 in the cylinder head 2, the hydraulic oil in the actuator cover 40 is drained by the drain of the second OCV 44. Storage can be prevented.
- the friction due to the agitation of the hydraulic oil can be reduced when the second cam phase variable mechanism 31 rotates along with the rotation of the intake camshaft 4.
- the operation responsiveness of the second cam phase variable mechanism 31, that is, the variable responsiveness of the second intake valve 10 can be improved.
- the hydraulic oil is not sufficiently discharged from the actuator cover 40, for example. Even if the oil is stored, the hydraulic oil is smoothly agitated when the second cam phase variable mechanism 31 rotates, and an increase in friction can be suppressed. Further, since aeration can be suppressed by smooth agitation of the hydraulic oil, when the hydraulic oil in the actuator cover 40 is recovered and reused as hydraulic oil for the second cam phase variable mechanism 31 and the like. As a result, a decrease in operating hydraulic pressure due to aeration can be suppressed, and a decrease in operating responsiveness of the second cam phase variable mechanism 31 and the like can be prevented.
- a weir 52 is provided on the inner peripheral wall 40 e of the actuator cover 40, and the hydraulic oil in the actuator cover 40 that is agitated by the rotation of the second cam phase varying mechanism 31 by the weir 52 is an oil passage 50. Therefore, the hydraulic oil in the actuator cover 40 can be smoothly discharged from the oil passage 50. Therefore, the storage of the hydraulic oil can be quickly eliminated, and the stirring resistance of the hydraulic oil can be quickly reduced.
- the actuator cover 40 has a structure in which the lower half of the second cam phase varying mechanism 31 is accommodated and the upper half of the second cam phase varying mechanism 31 is covered by the cylinder head cover 41.
- the actuator cover 40 and the cylinder head cover 41 cover the entire circumference of the second cam phase variable mechanism 31 with a relatively small gap, the overall dimensions are reduced with a simple configuration, and the hydraulic oil is contained inside.
- the second cam phase variable mechanism 31 can be stored while suppressing the storage of the first cam phase.
- annular oil groove 64 is provided on the outer peripheral surface of the cam journal 63
- annular oil groove 73 is provided on the inner peripheral surface of the bearing portion 23e.
- FIG. 8 is an explanatory view showing the peripheral speed of hydraulic oil in the oil grooves 64 and 73.
- FIG. 8A shows a case where the oil groove 64 is provided on the camshaft (cam journal 63) side
- FIG. A case where an oil groove 73 is provided on the bearing portion 23e) side is shown.
- the peripheral speed is shown linearly for easy comparison.
- 8C is a sectional view in the groove width direction when the oil groove 64 is provided on the camshaft side
- FIG. 8D is a sectional view in the groove width direction when the oil groove 73 is provided on the cylinder head side. The velocity distribution in the groove is shown.
- the oil in the annular oil groove 73 provided on the inner peripheral surface of the bearing portion 23e is rotated on the camshaft side. Only the oil is dragged and rotated, and the flow of oil becomes slower with respect to the opening. As a result, a pressure difference near the opening of the supply oil passage to the oil groove 73 occurs, and the second cam phase variable mechanism 31 is closer to the second cam phase variable mechanism 31 than the vicinity of the opening of the oil passage to the first cam phase variable mechanism 30.
- the oil pressure is lower near the opening of the oil passage, and it becomes easier to supply hydraulic oil into the oil groove 73.
- the cam journal is located on the opposite side of the oil passage 71 in the vicinity of the opening.
- the hydraulic oil rotates due to viscosity as the cylinder 74 rotates (c in the figure), but the hydraulic oil is difficult to rotate in the vicinity of the groove wall and the peripheral speed is relatively low (d in the figure). Accordingly, the peripheral speed (d in the figure) of the hydraulic oil in the vicinity of the opening of the oil passage 71 of the oil groove 73 is relatively small.
- the hydraulic pressure differs because the peripheral speed of the hydraulic oil in the vicinity of the opening of the supply oil passage to the oil groove is different, and this hydraulic pressure difference is changed from the oil passages 61 and 71 formed in the bearing portions 23a and 23e to the oil groove 64, This affects the ease with which hydraulic oil can flow into 73. That is, as shown in FIGS. 8B and 8D, when the oil groove 73 is provided on the cylinder head 2 side, the hydraulic pressure in the vicinity of the opening of the supply oil passage is smaller and the hydraulic oil flows more easily. As shown, when the oil groove 64 is provided on the camshaft side, the hydraulic pressure in the vicinity of the opening of the supply oil passage is larger and the hydraulic oil does not easily flow.
- the hydraulic oil is supplied to the second cam phase variable mechanism 31 using an oil passage provided with an oil groove 73 on the cylinder head 2 side, an oil groove 64 is provided on the intake camshaft 4 side.
- the hydraulic oil is supplied in preference to the first cam phase variable mechanism 30 to which the hydraulic oil is supplied using the oil path, and the split variable operation responsiveness by the second cam phase variable mechanism 31 can be improved. it can.
- the bearing in which the oil passage to the second cam phase varying mechanism 31 is formed from the bearing portion 23a in which the oil passage to the first cam phase varying mechanism 30 is formed. Since the inner diameter of the portion 23 e is larger, the peripheral speed of the hydraulic oil in the oil groove 73, particularly its maximum value, becomes larger than the oil groove 64. Thus, even if the maximum peripheral speed increases, the peripheral speed of the hydraulic oil in the vicinity of the opening of the supply oil passage in the oil groove 73 is low, so the pressure is small and the hydraulic oil flows into the oil groove 73. It becomes easy. Therefore, it is possible to maintain a state in which the hydraulic oil is more easily supplied to the second cam phase variable mechanism 31 than the first cam phase variable mechanism 30.
- journal diameter can be designed to be large, and while maintaining high drivability and fuel efficiency, design flexibility can be increased and strength reliability can be improved. Also, by changing the oil groove arrangement of the cam journal, the oil pressure in the vicinity of the opening of the supply oil passage is adjusted, and the variable responsiveness of the first cam phase variable mechanism 30 and the second cam phase variable mechanism 31 is balanced. You can also
- hydraulic oil is supplied to both the first cam phase variable mechanism 30 and the second cam phase variable mechanism 31 via the oil passage 34 close to the first cam phase variable mechanism 30. Therefore, the oil path from the oil pump to the first cam phase variable mechanism 30 is shorter than the oil path from the oil pump to the second cam phase variable mechanism 31. Therefore, considering the overall distance of the oil passage, the pressure loss is greater in the oil passage to the second cam phase variable mechanism 31, but the configuration of the bearing portions 23a and 23e as described above causes the first By improving the supply performance of the hydraulic oil to the second cam phase variable mechanism 31, the disadvantage of the supply performance of the hydraulic oil can be eliminated.
- FIGS. 9A to 9D are cross-sectional views showing examples of arrangement of the oil passage 61 with respect to the oil groove 73 when the oil groove 73 is provided on the cylinder head (bearing portion 23e) side.
- the hydraulic oil in the oil groove 73 rotates while being dragged only on the cam journal 74 side, and the supply port of the oil passage 71 to the oil groove 73 is rotated. Since the speed of the hydraulic oil in the vicinity of the (opening) becomes slow, it becomes easy to supply the hydraulic oil from the oil passage 71 to the oil groove 73. Therefore, as shown in FIGS.
- FIG. 10 is a structural diagram showing the shape of a groove 53 which is another embodiment of the introducing means.
- the weir 52 is provided in the actuator cover 40 as an introduction means for introducing the hydraulic oil into the oil passage 50.
- a groove 53 may be provided instead of the weir 52 as shown in FIG.
- the groove 53 is inclined upward from the rear wall 40f side to the cylinder head 2 side, and the end 53a on the cylinder head 2 side faces the oil passage 50. Is set.
- the hydraulic oil in the actuator cover 40 that is agitated by the rotation of the second cam phase varying mechanism 31 is easily guided to the oil passage 50, and the hydraulic oil in the actuator cover 40 is supplied to the oil passage 50. Can be discharged smoothly.
- the cylinder head cover 41 is configured to cover the upper half of the second cam phase varying mechanism 31.
- the upper half of the second cam phase varying mechanism 31 is separated from the cylinder head cover 41.
- a covering member may be provided.
- the present invention can be applied to an engine that includes only the second cam phase variable mechanism 31. it can.
- the cam sprocket 6 may be fixed to the tip of the outer cam shaft 21.
- the second cam phase variable mechanism 31 is provided outside the rear side of the cylinder head 2 and is covered with the actuator cover 40, so that the longitudinal dimensions of the cylinder head 2 can be reduced. Can be suppressed.
- the present invention is applied to an in-line three-cylinder engine having a DOHC type valve mechanism, but of course, it can be applied to an SOHC structure or an engine having a different number of cylinders.
Abstract
Description
請求項3に記載の発明では、シリンダヘッド及びカバー部材は上部が開口し、カバー部材は、上部の開口面がシリンダヘッドの開口面と同一平面上に位置するように形成され、シリンダヘッドの開口部とカバー部材の開口部とを合わせて覆うシリンダヘッドカバーを備えるようにした。
請求項5に記載の発明では、制御弁のドレーン油路がシリンダヘッド内に開放するようにした。
請求項7に記載の発明では、カム位相可変機構は、外形が円柱状でありカムシャフトと同軸に配置され、カバー部材の内壁が、カム位相可変機構の外周に沿って円弧状に形成されるようにした。
請求項9に記載の発明では、カバー部材は、上部が開放されてカバー部材内の空間が半円筒状に形成され、カム位相可変機構の下半分を覆い、シリンダヘッドカバーは、カム位相可変機構の外周に沿って円弧状に内壁が形成され、カバー部材の上部を覆うようにした。
請求項11に記載の発明では、カム位相可変機構は、カムシャフトの両端部に夫々備えられるとともに、カムシャフトがシリンダヘッドに複数設けられた軸受け部により回転可能に支持され、両端部に設けられた2個のカム位相可変機構へ作動油を導入する油路は、シリンダヘッド内及びカムシャフト内に夫々形成され、互いに異なる軸受け部においてシリンダヘッド内の油路とカムシャフト内との油路とが連通するように形成されるとともに、2個のカム位相可変機構のうち一方の第1のカム位相可変機構へ作動油を導入する油路はカムシャフトの外周面に円環状の油溝を備え、他方の第2のカム位相可変機構へ作動油を導入する油路は軸受け部の内周面に円環状の油溝を備えるようにした。
また、カム位相可変機構が油圧式のアクチュエータであるとともにカム位相可変機構への作動油の供給油路がカム穴の加工によって形成された軸受け部とカムシャフトとの摺動面を介している場合には、カム穴の加工精度が向上することで摺動面でのオイル漏れを減少させ、カム位相可変機構の作動応答性を向上させることができる。
図1は本実施形態の可変動弁装置付エンジン(以下、単にエンジン1という)のシリンダヘッド2内の構造を示す上面図である。図2は、吸気カムシャフト4の構造を示す断面図である。
図1及び3~5に示すように、シリンダヘッド2には、アクチュエータカバー40(本願のカバー部材に該当する)がボルト42によって固定されている。アクチュエータカバー40は、シリンダヘッド2に固定されることで、外形が円柱状である第2のカム位相可変機構31の下側半分を、若干隙間を持って覆うように形成されている。
アクチュエータカバー40には、第2のカム位相可変機構31への作動油の吸排を制御する第2のOCV(本願の制御弁に該当する)44と、第2のカム位相可変機構31のベーンロータの回転タイミングを検出する第2のカムセンサ45(本願の検出手段に該当する)が取り付けられている。
シリンダヘッド2の後壁2aには、アクチュエータカバー40内の空間43と、シリンダヘッド内の空間51とを連通する油路50が形成されている。図6に示すように、油路50は、アクチュエータカバー40の内周壁40eと第2のカム位相可変機構31の外周壁31bとの間の隙間に面して、最下部より第2のカム位相可変機構31の回転方向側に位置して配置されている。
図7に示すように、第1のOCV33から第1のカム位相可変機構30へは、シリンダヘッド2に形成された油路61、吸気カムシャフト4に形成された油路62を介して作動油が供給される。特に、軸受け部23aに支持される吸気カムシャフト4の部位であるカムジャーナル63には、その外周面に円環状に油溝64が形成されており、この油溝64に面して軸受け部23aの内周面に油路61が開口している。これにより、相対的に回転する軸受け部23aとカムジャーナル63との間で常に油路61、62が連通する構造となっている。
シリンダヘッド側に油溝73を設けた場合には、上記のように、油溝73内での作動油はカムジャーナル74側だけが引きずられて回転し、油溝73に対する油路71の供給口(開口部)付近の作動油の速度が遅くなるので、油路71から油溝73への作動油が供給し易くなる。よって、図9A~図9Dに示すように、油溝73への作動油の供給位置及び供給方向を自由に設定しても、作動油が供給不足され難くなり、油路71の配置等の設計自由度を高くすることが可能となる。
上記実施形態では、作動油を油路50に導入する導入手段としてアクチュエータカバー40内に堰52を設けたが、この堰52の代わりに図10に示すように溝53を設けてもよい。溝53は、堰52と同様に、後壁40f側からシリンダヘッド2側に向かって、上方に傾斜して設けられ、そのシリンダヘッド2側の端部53aが、油路50に面するように設定されている。
なお、以上の実施形態では、シリンダヘッドカバー41が第2のカム位相可変機構31の上半分を覆う構造となっているが、シリンダヘッドカバー41とは別に第2のカム位相可変機構31の上半分を覆う部材を設けてもよい。
2 シリンダヘッド
2d ドレーン油路
4 吸気カムシャフト
9 第1の吸気バルブ
10 第2の吸気バルブ
23a、23e 軸受け部
30 第1のカム位相可変機構
31 第2のカム位相可変機構
40 アクチュエータカバー(カバー部材)
40h ドレーン油路
41 シリンダヘッドカバー
44 第2のOCV(制御弁)
45 第2のカムセンサ(検出手段)
50 油路
52 堰(導入手段)
53 溝(導入手段)
64、73 油溝
Claims (13)
- 一端側にクランクシャフトからの動力が伝達されて回転駆動するカムシャフトに設けられ、前記クランクシャフトに対して前記カムシャフトに設けられるバルブ駆動用のカムの位相を可変するカム位相可変機構を備えた可変動弁装置付エンジンにおいて、
前記カム位相可変機構は、前記カムシャフトの前記一端側とは反対の他端側に設けられ、シリンダヘッドの外方に配置されるとともに、
前記シリンダヘッドに固定され、前記カム位相可変機構の少なくとも下部を覆うカバー部材を備えたことを特徴とする可変動弁装置付エンジン。 - 前記カム位相可変機構は、油圧式のアクチュエータであるとともに、
前記カバー部材に、前記カム位相可変機構への作動油の給排を制御する制御弁が固定されたことを特徴とする請求項1に記載の可変動弁装置付エンジン。 - 前記シリンダヘッド及び前記カバー部材は上部が開口し、
前記カバー部材は、上部の開口面が前記シリンダヘッドの開口面と同一平面上に位置するように形成され、
前記シリンダヘッドの開口部と前記カバー部材の開口部とを合わせて覆うシリンダヘッドカバーを備えたことを特徴とする請求項1または2に記載の可変動弁装置付エンジン。 - 前記カム位相可変機構により可変制御されたカムの位相を検出する検出手段が、前記カバー部材に備えられたことを特徴とする請求項1~3のいずれかに記載の可変動弁装置付エンジン。
- 前記制御弁のドレーン油路は、前記シリンダヘッド内に開放されたことを特徴とする請求項2に記載の可変動弁装置付エンジン。
- 前記カバー部材内の空間と前記シリンダヘッド内の空間とを隔てる隔壁には、前記カバー内の空間と前記シリンダヘッド内の空間とを連通する油路が形成されていることを特徴とする請求項1~5のいずれかに記載の可変動弁装置付エンジン。
- 前記カム位相可変機構は、外形が円柱状であり前記カムシャフトと同軸に配置され、
前記カバー部材の内壁は、前記カム位相可変機構の外周に沿って円弧状に形成されたことを特徴とする請求項6に記載の可変動弁装置付エンジン。 - 前記カバー部材の内壁に、前記カム位相可変機構の回転によって前記収納部内の作動油を前記油路に導く導入手段が設けられたことを特徴とする請求項7に記載の可変動弁装置付エンジン。
- 前記カバー部材は、上部が開放されて前記カバー部材内の空間が半円筒状に形成され、前記カム位相可変機構の下半分を覆い、
前記シリンダヘッドカバーは、前記カム位相可変機構の外周に沿って円弧状に内壁が形成され、前記カバー部材の上部を覆うことを特徴とする請求項3に記載の可変動弁装置付エンジン。 - 前記カバー部材は、前記シリンダヘッドとは別体に形成され、前記シリンダヘッドに固定されていることを特徴とする請求項1~9のいずれかに記載の可変動弁装置付エンジン。
- 前記カム位相可変機構は、前記カムシャフトの両端部に夫々備えられるとともに、前記カムシャフトが前記シリンダヘッドに複数設けられた軸受け部により回転可能に支持され、
前記両端部に設けられた2個のカム位相可変機構へ作動油を導入する油路は、前記シリンダヘッド内及び前記カムシャフト内に夫々形成され、互いに異なる前記軸受け部において前記シリンダヘッド内の油路と前記カムシャフト内との油路とが連通するように形成されるとともに、
前記2個のカム位相可変機構のうち一方の第1のカム位相可変機構へ作動油を導入する油路は前記カムシャフトの外周面に円環状の油溝を備え、他方の第2のカム位相可変機構へ作動油を導入する油路は前記軸受け部の内周面に円環状の油溝を備えることを特徴とする請求項2に記載の可変動弁装置付エンジン。 - 前記エンジンは1つの気筒に複数の吸気バルブが備えられ、
前記第1のカム位相可変機構は前記複数の吸気バルブ全体の位相を可変するとともに、前記第2のカム位相可変機構は前記複数の吸気バルブのうち一部の吸気バルブの位相を可変させることを特徴とする請求項11に記載の可変動弁装置付エンジン。 - 前記第2のカム位相可変機構へ作動油を導入する油路が形成された軸受け部は、前記第1のカム位相可変機構へ作動油を導入する油路が形成された軸受け部より内径が大きく形成されていることを特徴とする請求項12に記載の可変動弁装置付エンジン。
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RU2012107419/06A RU2505684C2 (ru) | 2010-01-14 | 2010-12-20 | Двигатель с регулируемым клапанным механизмом |
BR112012004596A BR112012004596A2 (pt) | 2010-01-14 | 2010-12-20 | motor equipado com um conjunto de válvulas variável |
KR1020127005463A KR101271897B1 (ko) | 2010-01-14 | 2010-12-20 | 가변동 밸브 장치 부착 엔진 |
EP10843169.3A EP2525053B1 (en) | 2010-01-14 | 2010-12-20 | Engine with variable valve gear |
US13/393,047 US8607748B2 (en) | 2010-01-14 | 2010-12-20 | Engine equipped with variable valvetrain |
CN201080038699.0A CN102695851B (zh) | 2010-01-14 | 2010-12-20 | 带有可变气门装置的发动机 |
JP2011549891A JP5073106B2 (ja) | 2010-01-14 | 2010-12-20 | 可変動弁装置付エンジン |
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RU2693944C1 (ru) * | 2018-07-09 | 2019-07-08 | Публичное акционерное общество "АВТОВАЗ" | Двигатель внутреннего сгорания |
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JPWO2011086815A1 (ja) | 2013-05-16 |
CN102695851B (zh) | 2014-02-26 |
EP2525053A4 (en) | 2013-06-19 |
JP5073106B2 (ja) | 2012-11-14 |
RU2505684C2 (ru) | 2014-01-27 |
EP2525053B1 (en) | 2015-02-11 |
KR101271897B1 (ko) | 2013-06-05 |
KR20120039751A (ko) | 2012-04-25 |
US8607748B2 (en) | 2013-12-17 |
US20120152192A1 (en) | 2012-06-21 |
BR112012004596A2 (pt) | 2016-04-05 |
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