JP2018178798A - Valve drive mechanism of internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve drive mechanism using oil pressure of a four-cycle internal combustion engine, having a simple structure and high reliability, and capable of being manufactured in a small-sized manner at low cost.SOLUTION: A valve drive mechanism of an internal combustion engine comprises output means, displacement oil pressure supply means and rotation transmission means. The displacement oil pressure supply means includes a displacement pump and a rotary joint. The displacement pump is provided with a reference profile and a cam profile inside a tubular cam. Hydraulic relay paths between a plurality of vanes or plungers and the respective pumps are provided in a rotor, the plurality of vanes or plungers sliding on an inner peripheral surface of the cam. The rotary joint is provided with a circumferential endless groove on an outer peripheral surface of the rotor or an inner peripheral surface of a rotor housing.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a valve drive mechanism of a four-stroke internal combustion engine that operates gas exchange valves hydraulically.

In a multi-cylinder internal combustion engine, a plurality of hydraulic supply members (hydraulic pumps etc.) operated by a drive cam driven by power from a crankshaft are radially arranged, and the cam is shared to simplify the structure and reduce the number of parts. There is an exhaust valve drive system for internal combustion engine (patent document 1) that reduces manufacturing cost and improves reliability, and a two-stroke internal combustion engine can be provided with a drive cam on a crankshaft, but in a four-stroke engine In the vane pump, the radial arrangement has a problem that the number of hydraulic circuits is restricted.
In a 4-cycle engine, a drive cam is provided coaxially to the crank, and a hydraulic drive system is provided to open and close the valve according to the rotation of the drive cam. There is a four-stroke engine (Patent Document 2) which can close the valve at any timing by connecting the output side oil passage to both the input side oil passage and the low pressure oil passage. The common cam that operates the valve makes it a simple structure, but it can close the valve at any timing but does not become equal acceleration movement, so it is difficult to suppress the closing impact of the valve, and when the control valve is a spool type, the movement of the spool High speed operation is difficult due to the problem of responsiveness due to the impact and the reciprocation of three positions.
The cam of the exhaust valve operates the pumping piston through the rocker arm member to operate the piston with the generated hydraulic pressure to open and close the intake valve, and the piston is controlled by the solenoid to close at an arbitrary timing, opening the passage There is a multi-cylinder internal combustion engine (Patent Document 3) that has a cushioning effect due to a change in area. The cam is common with the exhaust valve, the hydraulic path is short, and the cylinder head can be unitized. Necessary for each intake valve, it can be closed at any timing by control, but the valve closing speed becomes faster by the above control, and it is difficult to sufficiently suppress the seating impact at high rotational speed by cushioning with cushioning mechanism It is.

A gas exchange valve is operated by a slave cylinder hydraulically connected to a master cylinder having a cam provided on a camshaft and a plurality of vanes, and the amount of hydraulic fluid supplied is controlled by an actuating member of a control device. There is a device for hydraulically controlling a gas exchange valve of an engine (US Pat. No. 5,648,015), which arranges a control ring with a worm thread to surround the stator for pressure buildup and volume control. , Can control the amount by worm.
Since vanes are provided on the stator and hydraulic passages are provided substantially radially from the master cylinder, there is a problem that the number of hydraulic circuits is limited, the connection distance with the gas exchange valve becomes long, and the control device becomes complicated in each hydraulic passage. Hydraulic pressure adjustment mechanism is required.
The first cam and the second cam synchronized with the engine rotation, the first tappet and the second tappet sliding in the cylinder following the cam, and the pressure receiving portion of the cylinder hydraulic pressure chamber whose pressure changes as the tappet moves back and forth. A piston for pressing the valve according to the hydraulic pressure, and a phase adjusting means for changing the phase of the cam according to the operating condition, and the valve is opened in response to the first cam. There is a valve drive mechanism (patent document 5) of an internal combustion engine which closes the valve in response to the cam.
It is necessary for each valve controlled by the valve drive mechanism including the first cam and the second cam, etc., and there is a problem that the apparatus is complicated and the manufacturing cost becomes high.

There is a valve drive mechanism that uses a push rod such as OHV of the prior art, there are problems such as abnormal valve clearance due to thermal expansion of the push rod and difficulty in speeding up due to reciprocation, etc. Therefore, there is no concern about buckling like push rods, and because it transmits a compressive stress by hydraulic pressure, it has a lubricating function, and since the specific gravity of hydraulic oil is smaller than that of metallic push rods, inertia is small and it can cope with high speed rotation. There is an advantage.
According to the present invention, in a four-cycle internal combustion engine hydraulically operating gas exchange valves, a tubular cam provided with a cam profile on its inner circumferential surface, and a vane or plunger radially rotating while sliding on the inner circumferential surface of the cam A positive displacement pump comprising a rotor, a rotary joint (claim 1) provided on the rotor, a direction control valve (claim 2), phase control means (claim 3) for pivoting the cam, and a second By the positive displacement pump (claim 4), the problems of the above-mentioned document can be solved and the stepless opening / closing control of the gas exchange valve of the internal combustion engine can be performed with a simple structure. It is possible to add the lash adjuster function by the hydraulic pump function by the

Japanese Patent Application Laid-Open No. 63-1706 JP, 2013-133722, A JP, 2005-201259, A Japanese Patent Publication No. 2010-513767 Japanese Patent Application Laid-Open No. 55-096314

A displacement pump is driven by a cam mechanism driven by an internal combustion engine, and the hydraulic pressure generated by the displacement pump periodically operates a valve cylinder, and the valve cylinder opens and closes one or more gas exchange valves. In a reciprocating engine, there is a problem that switching of the hydraulic circuit accompanied by control is necessary to perform valve operation once per two rotations of the crankshaft when the cam is rotated by the crankshaft.
If a hydraulic passage is provided directly in the housing of the positive displacement pump, the hydraulic passage is arranged radially, and there is a problem that the installation of the hydraulic circuit is restricted in the vane pump and the plunger pump in structure.

  The first aspect of the present invention comprises a positive displacement pump driven by a four-stroke internal combustion engine, wherein the hydraulic pressure generated by the positive displacement pump causes the valve cylinder to periodically operate, and the valve cylinder comprises one or more gas exchange valves. A valve drive mechanism of an internal combustion engine comprising an output means, a positive displacement hydraulic pressure supply means, and a rotational transmission means in a reciprocating engine which is operated to open and close, wherein the output means comprises the valve cylinder, a crankshaft, and the crankshaft And at least one piston interlocking with the cylinder, and the rotational transmission means is provided on a drive wheel provided on the crankshaft and a rotor of the positive displacement pump whose effective diameter is twice that of the drive wheel. A driven wheel, the positive displacement hydraulic supply means comprising the positive displacement pump and a rotary joint, wherein the positive displacement pump is provided with a reference profile inside a tubular cam A cam profile is provided, and a plurality of vanes or plungers sliding on an inner circumferential surface of the cam is provided on the rotor, and the rotor includes a hydraulic relay passage for transferring each hydraulic pressure generated by the plurality of vanes or plungers. The rotary joint is provided on the outer peripheral surface of the rotor or the inner peripheral surface of the rotor housing with circumferential endless grooves corresponding to the respective hydraulic relay passages, and the circumferential endless grooves communicate with the valve cylinder in the hydraulic passage. It is a valve drive mechanism of an internal combustion engine.

  A second aspect of the present invention is characterized in that the positive displacement hydraulic pressure supply means comprises the positive displacement pump and a directional control valve instead of the rotary joint, and the positive displacement pump is provided with a reference profile inside the tubular cam. At least two cam profiles are provided at equal intervals in the circumferential direction, and the direction control valve is provided with circumferential end grooves corresponding to the respective hydraulic relay paths in the outer peripheral surface of the rotor or the inner peripheral surface of the rotor housing The valve drive mechanism of an internal combustion engine according to claim 1, wherein the valve cylinder communicates with the circumferential end groove in a hydraulic pressure passage.

  According to a third aspect of the present invention, there is provided a phase control means comprising an actuator for rotating the cam about the rotation shaft of the rotor and control means for the actuator, and the actuator controls the actuator according to the operating condition of the internal combustion engine. The valve drive mechanism for an internal combustion engine according to claim 1 or 2, wherein the cam is rotated to control the valve opening timing of the gas exchange valve.

  According to a fourth aspect of the present invention, in the axial direction of the rotor, two positive displacement pumps comprising the cam and the vane or the plunger are provided, and at least one positive displacement pump is provided with the phase control means. The cams of the one or more positive displacement pumps have at least one cam profile, and the substantially same phase hydraulic pressure generated by the vanes or the plungers of the respective positive displacement pumps communicate with the hydraulic relay passage, and the hydraulic relays 4. The valve drive mechanism for an internal combustion engine according to claim 3, wherein an air-to-oil converter is provided in the passage, and the cam is rotated by the phase control means according to the operating condition of the internal combustion engine to perform opening / closing adjustment of the gas exchange valve. It is.

According to the first aspect of the present invention, the positive displacement pump driven by the four-stroke internal combustion engine comprises a rotor, a tubular cam, and vanes or plungers provided on the rotary shaft of the rotor. In the simple structure in which the hydraulic circuit of the above can be arranged, the reliability of the hydraulic supply means is high, and there is an effect that it can be manufactured compactly and inexpensively.
Since the generated hydraulic pressure is supplied to the corresponding valve cylinder by the deceleration of the drive wheel provided on the crankshaft and the driven vehicle provided on the positive displacement pump to the corresponding valve cylinder, the switching means of the hydraulic circuit becomes unnecessary. .
The hydraulic joint can be provided at an arbitrary angle by the rotary joint consisting of circumferential endless grooves provided on the outer peripheral surface of the rotor or the inner peripheral surface of the rotor housing, thereby eliminating the problem of radial arrangement which becomes a restriction of the hydraulic circuit. it can.
Furthermore, by providing the oil pressure regeneration means, the oil pressure by the cell not contributing to the operation of the valve cylinder can be used, so it can be used as power steering, CVT, or oil pressure of the phase control means of claim 3 or 4 of the present invention. effective.
By providing the hydraulic pressure correction means in the hydraulic circuit of the valve cylinder, it is possible to add a lash adjuster function that automatically eliminates the valve clearance.

According to a second aspect of the present invention, the positive displacement hydraulic supply means comprises the positive displacement pump and a directional control valve, and the positive displacement pump comprises a reference profile and at least two cams inside the tubular cam. Since the profiles are provided equidistantly in the circumferential direction, the cam can be shared to arrange more hydraulic circuits than in claim 1 and there is an effect that it can be manufactured with a simple structure with high reliability, small size and low cost.
The directional control valve is provided with a circumferential end groove corresponding to the hydraulic pressure generated in the cam profile on the outer peripheral surface of the rotor or the inner peripheral surface of the rotor housing, and the rotor housing is provided with the same phase as the cam profiles. Since a hydraulic passage communicating with the valve cylinder is provided at a position communicating with the circumferential end groove on the inner circumferential surface, the directional control valve which does not require electrical control allows a plurality of valve cylinders to be hydraulically operated by one cell. The valve drive mechanism of the internal combustion engine has a simple structure, has high reliability, and is small and inexpensive.
By communicating the hydraulic circuit of the valve cylinder with the oil tank of the hydraulic pressure auxiliary means by the directional control valve at the end of the valve opening operation, there is an effect that a reliable lash adjuster function can be obtained.

  An actuator for rotating the cam about the rotation axis of the rotor according to claim 3 of the present invention and a phase control means provided with control means for the actuator are provided, and the operating condition of the internal combustion engine causes the actuator to Since the cam is rotated to control the phase of hydraulic pressure generation, the valve drive mechanism of an internal combustion engine capable of controlling the valve opening timing of the valve with a simple configuration is provided, which has an effect of high reliability, small size and low cost.

A fourth aspect of the present invention is that in the axial direction of the rotor, a second positive displacement pump is provided, one or both positive displacement pumps are provided with the phase control means, and the same phase generated by each positive displacement pump is provided. The valve control mechanism is capable of adjusting the opening / closing timing and / or the opening / closing amount of the gas exchange valve in a configuration in which oil pressure is communicated with the oil pressure relay passage and one empty oil converter is provided in each of the oil pressure relay passages. It has the effect of high reliability, small size and low cost with simple configuration.
Since the opening and closing control of the gas exchange valve corresponding to the operating condition of the internal combustion engine can be steplessly adjusted with high responsiveness by performing phase control of hydraulic pressure generation by rotating the cam with the actuator, the internal combustion engine There is an effect that the performance can be greatly improved.

FIG. 1 is an explanatory view of a configuration concept of a valve drive mechanism of an internal combustion engine provided with a positive displacement type hydraulic pressure supplying means comprising a positive displacement pump using a tubular cam and a rotary joint according to Embodiment 1 (corresponding to claim 1). The upper view of the positive displacement hydraulic pressure supply means of the first embodiment (FIG. 1) is a full sectional view, the lower view is a cross sectional view of each part of the main body, and a peripheral hydraulic circuit diagram. It is explanatory drawing of the construction concept of the valve drive mechanism of the gas exchange valve of intake and exhaust of 1 cylinder internal combustion engine which makes a positive displacement pump a plunger pump of implementation 2 (corresponding to claim 1). The upper view of the internal combustion engine according to the first embodiment and the second embodiment is a characteristic diagram of the lift amount of the valve during the entire stroke, and the lower diagram is an operation explanatory diagram according to the sectional view of the positive displacement pump of each phase of the valve operation stroke. It is structure explanatory drawing of the valve drive mechanism of the inlet valve of 4 cylinder internal combustion engine of Example 3 (corresponding to Claim 1). It is an arrangement perspective view of volume type oil pressure supply means of a valve drive mechanism of an intake valve of a 4 cylinder internal-combustion engine of the 3rd embodiment (Drawing 5) of the 3rd embodiment (Drawing 5), and a elements on larger scale of vane section section. It is explanatory drawing of the structural concept of the valve drive mechanism of 2 cylinder internal combustion engine with which the hydraulic pressure which generate | occur | produces with the vane pump of Example 4 (corresponding to claim 2) is supplied to each valve cylinder via a direction control valve. The middle view of the positive displacement hydraulic pressure supply means of the fourth embodiment (FIG. 7) is a full sectional view, the upper view is a positive displacement pump portion, the lower view is a cross sectional view of the rotary joint and each directional control valve, and a peripheral hydraulic circuit diagram. is there. It is a perspective view of the rotary joint and the directional control valve which consist of the circumferential direction groove | channel provided in the rotor of the positive displacement hydraulic pressure supply means of the said Example 4 (FIG. 8), and each hydraulic passage connection part. The upper view of the fourth embodiment is a valve lift characteristic view of the exhaust valve, and E10 (-30) is an operation explanatory view according to a sectional view of the positive displacement pump and the directional control valve of each phase of the valve lift characteristic view. It is explanatory drawing of the construction concept of the valve drive mechanism of 4 cylinder internal combustion engine with which the hydraulic pressure which generate | occur | produces Example 5 (corresponding to 2nd aspect) is supplied to each valve cylinder via a direction control valve. 11 is a full sectional view of the positive displacement hydraulic pressure supply means having a hydraulic passage arranged on one side according to the fifth embodiment (FIG. 11), the upper view is a pump portion, and the lower view is a cross sectional view of a rotary joint portion and each direction control valve portion. is there. The valve drive mechanism of Example 6 (corresponding to claim 2), which is an arrangement perspective view of the displacement type hydraulic pressure supply means for the exhaust and intake of an 8-cylinder internal combustion engine, and a sectional view of the displacement type pump portion in arrow view G. It is explanatory drawing of the construction concept of the valve drive mechanism of 6 cylinder internal combustion engine by positive displacement type hydraulic pressure supply means provided with three cam profiles of Example 7 (corresponding to claim 2). The upper view is a full sectional view of the positive displacement type hydraulic pressure supplying means of the seventh embodiment (FIG. 14) in which hydraulic pipes are provided on three sides, and a sectional view of a pump portion, a rotary joint portion and each direction control valve portion It is. It is explanatory drawing of the construction concept of the valve drive mechanism of 2 cylinder internal combustion engine by the positive displacement type hydraulic pressure supply means provided with the phase control means by an actuator of Example 8 (corresponding to claim 3). The upper view is a full sectional view, and the lower view is a sectional view of a pump portion and a peripheral hydraulic circuit diagram of the positive displacement type hydraulic pressure supplying means having a rotary cylinder according to a ninth embodiment (corresponding to claim 3). It is explanatory drawing of the structural concept of the valve drive mechanism of 3 cylinder internal combustion engine which adjusts the phase of two sets of vane pumps with a motor by Example 10 (corresponding to claim 4), and carries out opening / closing control of an inlet valve. The upper view of the tenth embodiment (FIG. 18) is a hydraulic characteristic view of the cam, the second cam and the valve cylinder, and the lower view is an operation explanatory view according to a schematic view of the positive displacement pump in each phase. It is control operation explanatory drawing by the valve lift characteristic figure of each cam phase control and each control pattern (1)-(3) of the valve drive mechanism of the internal combustion engine of the said Example 10 (FIG. 18, 19). FIG. 32 is a configuration diagram of a valve drive mechanism of a four-cylinder internal combustion engine according to Embodiment 11 (corresponding to claim 4) by means of phase control means and positive displacement hydraulic pressure supply means having two cam profiles. 21 is a full sectional view of a positive displacement hydraulic pressure supplying means provided with phase control means with two rotary cylinders, a sectional view of each pump portion, and a peripheral hydraulic circuit diagram according to Embodiment 11 (FIG. 21). FIG. It is structure explanatory drawing of the control system of the valve drive mechanism of the internal combustion engine of the mobile by the displacement type hydraulic pressure supply means provided with 2 sets of plunger pumps of Example 12 (corresponding to claim 4). FIG. 24 is a control flowchart of a valve drive mechanism of an internal combustion engine of the twelfth embodiment (FIG. 23), and valve opening control explanatory views by valve lift characteristic diagrams of control subroutines.

Each Example (Examples 1-12) of this invention is described below according to the said drawing (FIGS. 1-24).
In the following description, although the positive displacement pump is described with priority given to the embodiment of the vane pump having a simple structure, the vane pump of each embodiment can be replaced by a plunger pump capable of supporting high hydraulic pressure.
In each embodiment, the hydraulic pressure of the cell that does not contribute to the operation of the valve cylinder may be a hydraulic regenerative pump or a free space of air.

FIG. 1 is an explanatory view of a structural concept of a valve drive mechanism of an internal combustion engine having a positive displacement type hydraulic pressure supply means comprising a positive displacement pump using a tubular cam and a rotary joint according to the first embodiment (corresponding to claim 1). is there.
FIG. 1 is provided with a positive displacement pump driven by a four-stroke internal combustion engine 1, and the hydraulic pressure generated by the positive displacement pump causes the valve cylinder 41 (-1, -2) to periodically operate to In a reciprocating engine in which -1, -2) operates to open and close one gas exchange valve 45 (-1, -2), an internal combustion engine comprising output means 4, positive hydraulic pressure supply means 7, and rotational transmission means 6 1, the output unit 4 includes the valve cylinder 41 (−1, −2), a crankshaft 49, two pistons (not shown) interlocking with the crankshaft 49, and a cylinder 46 (not shown). -1, -2), and the rotational transmission means 6 is provided on the drive wheel 62 provided on the crankshaft 49 and the rotor 72 of the positive displacement pump whose effective diameter is twice that of the drive wheel 62. A driven wheel 61, and the volume type The pressure supply means 7 comprises the positive displacement pump and the rotary joint 76, the positive displacement pump providing a reference profile 710 and one cam profile 711 inside the tubular cam 71, the cam 71 The rotor 72 is provided with four vanes 73 sliding on the inner circumferential surface thereof, and the rotor 72 is provided with hydraulic relay paths 721 and 722 for transferring the hydraulic pressure generated by the four vanes, and the rotary joint 76 is provided on the outer peripheral surface of the rotor 72 or the inner peripheral surface of the rotor housing with a circumferential endless groove (not shown) corresponding to the hydraulic relay passages 721 and 722, and the valve cylinders 41 (-1, -2) It is explanatory drawing of the structural concept of the valve drive mechanism of the internal combustion engine 1 connected by the circumferential direction endless groove and hydraulic path 78 (-1, -2).
The hydraulic pressure auxiliary means 8 includes respective hydraulic pressure passages 88 (-1, -2) communicating with the hydraulic pressure passages 78 (-1, -2), and the hydraulic pressure passages 88 (-1, -2) are check valves. It communicates with the oil tank 80 via 83 (-1, -2).

The function of the valve drive mechanism of the internal combustion engine 1 of FIG. 1 is that in the positive displacement pump comprising the cam 71, the rotor 72 and the vane 73 of the positive displacement hydraulic pressure supply means 7, the hydraulic pressure generated by the cam profile 711 is hydraulic relay The gas is supplied to the respective valve cylinders 41 (-1, -2) through the passages 721, 722, the rotary joint 76, and the hydraulic passages 78-1, 78-2, and the gas exchange valves 45 (-1,- When the valve 2) is opened and a negative pressure is generated due to a hydraulic pressure leak or the like, oil is supplied from the oil tank 80 of the hydraulic pressure auxiliary means 8 by the negative pressure.
The rotation of the rotor 72 is decelerated to a half of the rotational speed of the crankshaft 49 of the output means 4 by the rotational transmission means 6, so that it corresponds to the intake stroke or exhaust stroke of the four-stroke internal combustion engine 1. Open the valve.
The valve opening control based on the installation angle θ1 of the cam profile 711 and the installation angle θ2 of the vane 73 of the valve drive hydraulic pressure will be described with reference to FIG.
The hydraulic pressure which does not contribute to the valve drive is communicated to the oil tank 80 of the hydraulic auxiliary means 8 through the hydraulic relay passage 726 and the rotary joint 76, and the hydraulic pressure is always released to the atmospheric pressure.

FIG. 2 is a full sectional view of the upper part of the positive displacement hydraulic pressure supply means of the first embodiment (FIG. 1), the lower part is a sectional view of each part of the main body, and a peripheral hydraulic circuit diagram. It is.
The positive displacement hydraulic pressure supply means 7 of FIG. 2 includes the positive displacement pump cam 71, the rotor 72, and the vane 73, and the rotary joint 76, and the positive displacement pump is disposed inside the tubular cam 71. A reference profile 710 centered on the rotation axis of the rotor 72 and a cam profile 711 are provided, and the rotor 72 is provided with four vanes 73 sliding on the inner circumferential surface of the cam 71, the rotor 72 being And hydraulic relay paths 721, 722, and 726 for transferring the respective hydraulic pressures generated by the four vanes 73, and the rotary joint 76 has a circumferential endless groove 768-3 in the outer peripheral surface of the rotor and the inside of the rotor housing. The circumferential endless groove 768 (-1, -2) is provided on the circumferential surface, and the circumferential endless groove 768 (-1, -2) is not shown corresponding to the respective hydraulic relay paths 721, 722 and the respective hydraulic pressure. valve Supplying hydraulic pressure to the cylinder each hydraulic passage 78 (-1, -2) to second communication.
The circumferential endless groove 768-3 communicates with the hydraulic relay passage 726 communicating with the cells other than the cell 738 (-1, -2) which operates the valve and the hydraulic passage 79a communicating with the hydraulic regenerating means 9.
The hydraulic pressure auxiliary means 8a is provided with a throttle valve 81 and a check valve 82 in parallel with the check valve 83a.
The hydraulic pressure passage 79a is in communication with the upstream side of the relief valve 94 of the hydraulic pressure regenerating means 9 provided with the hydraulic pressure passages 98 and 99 of the regenerative hydraulic pressure.

The action of the positive displacement hydraulic supply means 7 of FIG. 2 is the same as that of FIG. 1 in the action of generating hydraulic pressure, and in the positive displacement pump comprising the cam 71, the rotor 72 and the vane 73 A hydraulic pressure generated by reducing the volume of (-1. 2.) passes through the hydraulic relay paths 721 and 722 and is provided on the inner peripheral surface of the rotor 72 which is the rotary joint 76, in the circumferential direction endless groove 768 (-1 , -2) and through hydraulic pressure passages 78-1 and 78-2 to respective valve cylinders 41 (-1, -2) not shown, and cyclically the gas exchange valve 45 (-1, -2). -2) Open the valve.
When a negative pressure is generated by a leak of hydraulic pressure or the like by the hydraulic pressure auxiliary means 8a, oil is replenished from the oil tank 80a of the hydraulic pressure auxiliary means by the negative pressure to prevent generation of air bubbles due to cavitation in the oil. Leak-down where a portion of the valve is returned to the oil tank 80a by the throttle valve 81 and the check valve 82 provides a lash adjuster function that eliminates the valve clearance automatically.
The hydraulic pressure generated by reducing the volume of the cells other than the cell 738 (-1. 2. 2) by the cam profile 711 passes through the hydraulic relay passage 726, the circumferential endless groove 768-3, and the hydraulic passage 79a. The hydraulic pressure can be supplied upstream of the relief valve 94 of the hydraulic pressure regenerating means 9 and hydraulic pressure can be supplied by the hydraulic pressure passages 98, 99.
The pressure of the regenerative oil pressure is controlled by the relief valve 94, and the check valves 93 and 94 have a backflow preventing action and an action for preventing the generation of air bubbles due to the negative pressure in the oil.

FIG. 3 is an explanatory view of a configuration concept of a valve drive mechanism of an intake and exhaust gas exchange valve of a one-cylinder internal combustion engine in which a positive displacement pump is a plunger pump according to the second embodiment (corresponding to claim 1).
FIG. 3 is provided with a positive displacement pump driven by a four-stroke internal combustion engine 1p, and the hydraulic pressure generated by the positive displacement pump causes the valve cylinders 411 and 412 to operate periodically, and one of the valve cylinders 411 and 412 is provided. A reciprocating engine for opening and closing gas exchange valves 451 and 452, which is a valve drive mechanism of an internal combustion engine comprising an output means 4p, a positive displacement hydraulic pressure supply means 7p, and a rotary transmission means 6p, said output means 4p being A valve cylinder 411, 412, a crankshaft 49p, a piston 47 interlocking with the crankshaft 49p, and a cylinder 46, and the rotational transmission means 6p includes a drive wheel 62p provided on the crankshaft 49p. And a driven wheel 61p provided on a rotor 72p of the positive displacement pump whose effective diameter is twice that of the driving wheel, and the positive displacement oil pressure supplying means 7p The displacement pump includes the positive displacement pump and a rotary joint 76p, and the positive displacement pump is provided with a reference profile 710p and one cam profile 711p inside a tubular cam 71p, and the inner circumferential surface of the cam 71p is slid Two moving plungers 74 (-1, -2) are provided on the rotor 72p, and the rotor 72p is a hydraulic relay path for transferring each oil pressure generated by the two plungers 74 (-1, -2) 721p, 722p, the rotary joint 76p is provided with a circumferential endless groove (not shown) corresponding to the hydraulic relay paths 721p, 722p on the outer peripheral surface of the rotor 72p or the inner peripheral surface of the rotor housing; Reference numeral 412 is an explanatory view of a structural concept of a valve drive mechanism of an internal combustion engine which is communicated with the circumferential endless grooves at hydraulic passages 781 and 782.

The function of the valve drive mechanism of the internal combustion engine 1p of FIG. 3 is that in the positive displacement pump comprising the cam 71p, the rotor 72p and the vane 73p of the positive displacement hydraulic pressure supply means 7p, the hydraulic pressure generated by the cam profile 711p is hydraulic relay Gas is supplied to the respective valve cylinders 411 and 412 through the passages 721p and 722p, the rotary joint 76p, and the hydraulic passages 781 and 782, and the gas exchange valves 451 and 452 are periodically opened to cause negative pressure due to hydraulic pressure leakage etc. In the case where the above occurs, oil is replenished from the oil tank of the hydraulic pressure auxiliary means 8p by the negative pressure.
By providing a cooler (not shown) on the side of the valve cylinders 411 and 412 of the hydraulic pressure passages 781 and 782, it is possible to prevent the temperature rise and deterioration of the oil.
The rotation of the rotor 72p is reduced by a half of the rotational speed of the crankshaft 49p of the output means 4p by the rotation transmission means 6, so that the rotor 72p corresponds to the intake stroke or exhaust stroke of the four-stroke internal combustion engine 1p. Open the valve.
The valve opening control based on the installation angle θ5 of the cam profile 711p and the installation angle θ6 of the plunger 74 (-1, -2) of the valve driving hydraulic pressure will be described with reference to FIG.

FIG. 4 is a characteristic diagram of the lift amount of the valve in the entire stroke of the internal combustion engine of the first embodiment and the second embodiment, and the lower diagram is an operation explanation by the sectional view of the positive displacement pump of each phase of valve operation stroke. FIG.
The upper diagram in FIG. 4 is a characteristic diagram of the lift amount of the valve of the first embodiment by the vane pump and the valve of the four cycles of the second embodiment by the plunger pump. The valve lift (A1, A2) of the first embodiment has two cylinders. Since it is the gas exchange valve 45 (-1, -2) of the intake (or exhaust) of the internal combustion engine 1, the valve lifts A1 and A2 have a phase difference of two strokes (360 °) of the crank angle. The valve lifts (P1 and P2) are the exhaust and intake gas exchange valves 451 and 452 of the one-cylinder internal combustion engine 1p, so the valve lifts P1 and P2 have a phase difference of two strokes (360 °) of the crank angle. .
As shown in the lower diagrams (A1) and (P1), by making the cam profiles 711 and 771p symmetrical, the rising behavior and the falling behavior of each valve lift characteristic diagram in the above figure become the same, and further, the rising behavior and The descending behavior is a parabola in the upside-down direction with the central portion of the valve stroke H as a boundary, but may be a sine curve or a simple S-shaped curve in a low speed internal combustion engine.
By making the circumferential cross-sectional shapes of the respective cam profiles 711 and 711p into shapes corresponding to the respective valve lift characteristic charts, the valve behavior becomes equal acceleration, and vibration and seating impact can be reduced, so that high speed operation can be made smooth.
In the first embodiment, since the reduction ratio of the rotary transmission means 6 is one half, the valve cylinder is moved over the entire stroke to suppress the moving speed of the valve.
(1)
θ1 = θ2
Since each stroke by the crankshaft is 180 °,
(2)
2 (θ1 + θ2) = 180 °
And substituting (Equation 1) into (Equation 2),
It becomes θ1 = θ2 = 45 °.
Also in the second embodiment, the reduction ratio of the rotary transmission means 6p is one half, so the valve cylinder is moved over the entire stroke (180 °) in order to suppress the moving speed of the valve.
(Number 3)
2θ5 = 180 °
Since the phase difference between the valve cylinders of the exhaust stroke and the intake stroke is one stroke (180 °),
(Number 4)
2θ6 = 180 °
Therefore, θ6 = 90 °.

The above description is for the case where the reduction ratio of the rotary transmission means 6 and 6p is one half, but when the reduction ratio is one quarter, the angles θ1, θ2, θ5 and θ6 can be reduced to one half. .
The following embodiment mainly describes the embodiment using a vane pump, but in each embodiment, the vane pump and the plunger pump can be selected, the lubrication is important, or the vane pump is advantageous when utilizing the regenerative oil pressure, A plunger pump is suitable for high pressure hydraulics.
In both the vane pump and the plunger pump, centrifugal force is generated when the rotor rotates at high speed, but an elastic body (spring) is provided to urge the sliding surface of the cam when rotating at low speed to ensure a substantially sealed state. Although an air release circuit or the like for back pressure treatment may be required in some cases, since the method is the same as that of the conventional vane pump, the illustration and the description of the operation will be omitted.

FIG. 5 is a configuration explanatory view of a valve drive mechanism of an intake valve of a four-cylinder internal combustion engine according to a third embodiment (corresponding to claim 1).
As shown in FIG. 5, in a valve drive mechanism of an intake valve of a four-cylinder internal combustion engine, the valve drive mechanism of an internal combustion engine 1b comprising an output means 4b, a positive displacement hydraulic pressure supply means 7b and a rotational transmission means 6b. The positive displacement hydraulic supply means 7b comprises the positive displacement pump and the rotary joint 76b, and the positive displacement pump is provided inside the tubular cam 71b with a reference profile 710b centered on the rotation axis of the rotor 72b. It has a simple structure in which one cam profile 711b is provided, and eight vanes 73b sliding on the inner peripheral surface of the cam are provided on the rotor 72b.
The simple structure can share one cam profile 711b of the cam 71b to arrange four sets of hydraulic circuits, so that there is an effect that the hydraulic supply means 7b has high reliability and can be manufactured compactly at low cost.
Since the hydraulic pressure generated by the decelerating rotation of the drive wheel provided on the crankshaft 49b and the half speed rotation by the driven vehicle provided on the positive displacement pump is supplied to the corresponding valve cylinder, the switching means of the hydraulic circuit becomes unnecessary. .
Further, by providing the oil pressure regeneration means 9b, the oil pressure by the cell which does not contribute to the operation of the valve cylinder can be used, so that it can be used as power steering, CVT, or oil pressure of phase control means of claim 3 or 4 of the present invention. When the hydraulic pressure is not required, the directional control valve 96 can be operated to suppress the occurrence of power loss due to the drive of the regenerative hydraulic pump.
The configuration and operation of the hydraulic pressure correction means 8b are the same as those of the second embodiment, and there is an effect that a lash adjuster function can be added to automatically eliminate the valve clearance.

FIG. 6 is an arrangement perspective view of a positive displacement hydraulic pressure supply means and a partially enlarged view of the vane section of the valve drive mechanism of the intake valve of the four-cylinder internal combustion engine of the third embodiment (FIG. 5).
Since hydraulic piping can be provided at any angle by means of a rotary joint composed of a circumferential endless groove (not shown) provided on the outer peripheral surface of the rotor 72b or the inner peripheral surface of the rotor housing, as shown in FIG. The problem of the restriction of radial arrangement can be solved.
A positive displacement hydraulic pressure supply means 7b is provided in parallel with the crankshaft 49b, and piping of the valve cylinder 411 (-1 to 4) and the positive displacement hydraulic pressure supply means 7b becomes easy, and the respective hydraulic pressure passages 781 (b1 to b4) intersect Because it can be arranged without, it is possible to unify by piping block.
The exhaust valve mechanism (not shown) may be provided with the positive displacement hydraulic pressure supply means 7b or may be another valve mechanism.

FIG. 7 is an explanatory view of a structural concept of a valve drive mechanism of a two-cylinder internal combustion engine in which the hydraulic pressure generated by the vane pump of the fourth embodiment (corresponding to claim 2) is supplied to each valve cylinder via a direction control valve.
The positive displacement hydraulic pressure supply means 7e of FIG. 7 includes the positive displacement pump and a directional control valve 77 (-1, -2) instead of the rotary joint, and the positive displacement pump includes the tubular cam 71e. The reference profile 710e and the two cam profiles 711e are provided at equal intervals in the circumferential direction on the inner side, and the directional control valve 77 (-1, -2) is the outer peripheral surface of the rotor 72e or the inner periphery of the rotor housing A circumferential end groove (not shown) corresponding to the hydraulic relay paths 721e and 722e is provided on the surface, and each of the valve cylinders 411 (e1, e2) and 412 (e1, e2) 2. The valve drive mechanism for an internal combustion engine according to claim 1, wherein the valve drive mechanism is in communication with e1, e2), 782 (e1, e2).
The rotary transmission means 6e, the rotary joint 76e, and the hydraulic pressure regenerating means 9e have the same configuration as that of the first embodiment (FIGS. 1 and 2).

The function of the positive displacement hydraulic pressure supply means 7e of the valve drive mechanism of the internal combustion engine 1e of FIG. 7 is the same as that of the first embodiment, in the rotor 72e rotating at a half rotation speed of the crankshaft 49e by the rotational transmission means 6e. A vane 73e with an included angle of θ2e (= θ2) is provided, and the oil pressure passing through the hydraulic relay passage 721e generated twice at equal intervals in one rotation of the rotor 72e by two cam profiles 711e is obtained by the direction control valve 77-1. The switching is performed in synchronization with the rotation of the rotor 72e, and the exhaust valve cylinders 412 (e1, e2) are alternately operated.
By setting the phase difference (θ2e + θ3e) of the pump to 90 ° of the rotor rotation angle similarly to the phase difference (θ6) of the hydraulic pump described in the second embodiment, the hydraulic pressure passing through the hydraulic relay passage 722e generated by the cam profile 711e Are switched in synchronization with the rotation of the rotor 72e by the directional control valve 77-2 to alternately operate the valve cylinders 411 (e1, e2) of the intake valve.
The rotary joint 76e and the hydraulic pressure regenerating means 9e have the same functions as those of the first embodiment (FIGS. 1 and 2), and therefore the description thereof is omitted.

FIG. 8 is a full sectional view of the middle section of the positive displacement hydraulic pressure supply means of the fourth embodiment (FIG. 7), the upper view is a positive displacement pump section, and the lower section is a sectional view of the rotary joint and each direction control valve It is a hydraulic circuit diagram.
In FIG. 8, the displacement type hydraulic pressure supply means 7 e shown in the middle view of FIG. 8 is a vane pump which is the displacement type pump shown in the upper view, and direction control valve 77 (−1, 2), wherein the positive displacement pump is provided with a reference profile 710e and two cam profiles 711e at equal intervals in the circumferential direction inside the tubular cam 71e, and the direction control shown in the lower figure and the lower figure right The valve 77 (-1, -2) is provided with two circumferential end grooves 778 (e1a, e2a) equal in number to the cam profile 711e on the outer peripheral surface of the rotor 72e, and the two cam profiles 711e and The valve cylinders 411 (e1, e2) and 412 (e1) of FIG. 7 are positioned in communication with the circumferential end groove 778 (e1a, e2a) on the inner peripheral surface of the rotor housing 702e in the same phase. The hydraulic pressure passages 781 (e1, e2) and 782 (e1, e2) communicating with e2) are provided, and each valve operating hydraulic pressure generated by the four vanes 73e is the direction control valve 77 (-1, -2) The valve drive mechanism of the internal combustion engine 1e sequentially supplies the hydraulic pressure to the plurality of corresponding valve cylinders 411 (e1, e2) and 412 (e1, e2).

The operation of the positive displacement hydraulic pressure supply means 7e of FIG. 8 is, as shown in the sectional view of the positive displacement pump portion in the upper figure, the half rotation speed of the crankshaft 49e as described in FIG. 7 of the fourth embodiment. The respective cells 738 (e1 and e2) are configured by providing two sets of vanes 73e with an included angle of θ2e provided to the rotor 72e that rotates at the same time, and the cells 738 (e1 and e2) have the two cam profiles 711 (the Each hydraulic pressure generated by e1, e2) is supplied to each hydraulic relay path 721e, 722e.
Therefore, the hydraulic pressure generated twice at equal intervals every rotation of the rotor 72e is supplied to the hydraulic relay paths 721e and 722e, and the supplied hydraulic pressure corresponds to the hydraulic relay paths 721e and 722e shown in the middle view. It is supplied to the circumferential direction end groove 778 (e1a, e2a).
The hydraulic pressure supplied to the circumferential end grooves 778 (e1a, e2a) shown in the lower drawing and the lower right in the lower drawing correspond to the hydraulic passages 782e1, 781e1 corresponding to the hydraulic generation phase of the cam 711e1 as the rotor 72e rotates. Since the hydraulic circuit is alternately switched to the hydraulic passages 782e2 and 781e2 corresponding to the hydraulic pressure generation phase of the cam 711e2, the exhaust valve cylinders 412 (e1, e2) provided in the cylinders 46 (e1, e2) are alternately switched. The hydraulic pressure is alternately supplied, and the valve opening operation is alternately performed at equal intervals.
The hydraulic pressure passing through the hydraulic relay passage 722e generated by the cam profile 711 (e1, e2) is switched in synchronization with the rotation of the rotor 72e by the directional control valve 77-2 to switch the valve cylinder 411 (e1, e2) of the intake valve. Operate alternately.
By setting the rotor phase difference (θ2e + θ3e) of the pump to 90 °, each intake valve cylinder 411 (e1, e2, with a 180 ° retarded angle between the operation of each exhaust valve cylinder 412 (e1, e2) and crank phase). Activate e2).
In the middle and lower figures, as shown in the lower right of the figure, a circumferential limit groove 778 (e1 b, e2 b) is provided in the remaining circumferential portion of the circumferential limit groove 778 (e1 a, e2 a). The end groove 778 (e1 b, e2 b) is communicated with the oil tank 80 e of the hydraulic auxiliary means 8 e via the hydraulic passage 79 e2, the circumferential endless groove 768 e2 and the hydraulic relay passage 725, except during hydraulic operation (gas exchange valve closed In the case of a valve), by releasing the hydraulic pressure to atmospheric pressure, a reliable gas exchange valve can be seated, so that there is an effect that a reliable lash adjuster function can be added.
The hydraulic pressure which does not contribute to the operation of the valve cylinder generated in the cells between the cells 738 (e1 and e2) is supplied to the hydraulic pressure regenerating means 9e via the hydraulic pressure passage 726e, the circumferential endless groove 768e1 and the hydraulic pressure passage 79e1. Accordingly, there is an effect that it can be used as power steering, CVT, or hydraulic pressure of the phase control means of claim 3 or 4 of the present invention.

FIG. 9 is a perspective view of a rotary joint and directional control valves including circumferential grooves provided on the rotor of the positive displacement hydraulic pressure supply means of the fourth embodiment (FIG. 8) and hydraulic passage connection parts.
The rotor 72e of the positive displacement hydraulic pressure supply means 7e is a directional control valve 77 comprising a pump portion provided with vanes 73e and a circumferential end groove 778 (e1a, e1b) communicating with the hydraulic passage 782 (e1, e2). 1 and a directional control valve 77-2 comprising a circumferential end groove 778 (e2a, e2b) communicating with the hydraulic pressure passage 781 (e1, e2) and comprising a circumferential endless groove 768e1 communicating with the hydraulic pressure passage 79e1. The rotary joint 76e1 and the rolling joint 76e2 of the same structure are provided.
Since the pump unit and the directional control valve are provided in the rotor 72e, the gas exchange valve of the four-stroke internal combustion engine can be operated with a simple configuration that does not require electrical control, so it is inexpensive and highly reliable. There is an effect that can cope with high speed rotation.

FIG. 10 is a valve lift characteristic diagram of the exhaust valve in the upper view of the fourth embodiment, and E10 (〜3030) is an operation explanation by a sectional view of the positive displacement pump and direction control valve of each phase of the valve lift characteristic diagram. FIG.
The upper diagram (E) of FIG. 10 is a characteristic diagram of the valve lift of the exhaust valve cylinder 412 (e1, e2) of the two-cylinder four-stroke internal combustion engine 1e of the fourth embodiment (FIG. 7). The vertical axis is the valve lift amount (h).
Similarly to the first embodiment (FIG. 4), the rotational transmission means 6e sets θ1e = θ2e = 45 °, and the hydraulic pressure generated in the cell 738e5 formed by the vanes 73e provided on the rotor 72e passes through the hydraulic relay path 721e. And is supplied to one of the exhaust valve cylinders 412 (e1, e2) through the hydraulic passage 782 e1 or hydraulic passage 782 e2 by switching the hydraulic circuit. Since the valve lift operation is performed, as shown in the upper figure (E). The valve cylinders 412 (e1, e2) alternately perform valve lift operations.

The operation of the positive displacement pump of FIG. 10 and the three-position rotary sliding directional control valve 77-1 will be described below.
As shown in (E10), when the hydraulic pressure is not generated in the cell 738e5, switching of the hydraulic circuit of the directional control valve 77-1 is performed in both valve cylinders 412 (e1, e2) as shown in (E10a). In the standby mode, the hydraulic pressure becomes atmospheric pressure by communicating with the oil tank of the hydraulic auxiliary means (not shown) via the hydraulic relay path 725, so that the lash adjuster function can be added.
As shown in (E20), when the rotor 72e rotates and the cell profile 738e5 generates oil pressure by the cam profile 711e1, as shown in (E20a), the direction control valve 77-1 supplies the oil pressure to the oil pressure passage 782e1. Then, the valve cylinder 412e1 is operated, and the hydraulic pressure of the waiting hydraulic passage 782e2 continues the atmospheric pressure.
As shown in (E30), when the rotor 72e is further rotated and the oil pressure of the cell 738e6 is generated by the cam profile 711e2, both hydraulic circuits of the hydraulic passage 782 (e1, e2) are replaced to operate the valve cylinder 412e2. .
The intake valve cylinder 411 (e1, e2) is similarly operated by delaying the phase of the cell 738e6 hydraulically driving the intake valve cylinder 411 (e1, e2) to the exhaust cell 738e5 by 90 ° as a rotor angle. it can.

FIG. 11 is an explanatory view of a structural concept of a valve drive mechanism of a four-cylinder internal combustion engine in which the hydraulic pressure generated in the fifth embodiment (corresponding to claim 2) is supplied to each valve cylinder via a direction control valve.
Embodiment 5 of FIG. 11 adds the hydraulic pump circuit in which the vanes of the pump portion of the positive displacement hydraulic pressure supply means 7e of the above-mentioned Embodiment 4 (FIG. 7) and the hydraulic relay path are phase shifted 180 degrees. An exhaust and intake valve drive mechanism of a four-cylinder internal combustion engine 1c provided with four directional control valves 77 (c1 to c4) corresponding to a circuit.

FIG. 12 is a full sectional view of the positive displacement hydraulic pressure supply means arranged on one side surface of the hydraulic passage according to the fifth embodiment (FIG. 11), the upper view is a pump portion, and the lower view is a rotary joint portion and each direction control valve portion. FIG.
The positive displacement hydraulic pressure supply means 7c of the fifth embodiment of FIG. 12 is the same as the vane 73e and the hydraulic relay paths 721e and 722e of the pump section sectional view (upper view) of the positive displacement hydraulic pressure supply means 7e of the fourth embodiment (FIG. 8). A hydraulic pump circuit phase-shifted by 180 ° is added, a direction control valve 77 (c1 to c4) corresponding to the added hydraulic pump circuit is provided, and each valve cylinder corresponding to the direction control valve 77 (c1 to c4) By providing the communicating hydraulic passages 781 (c1 to c4) and 782 (c1 to c4) on one (downward) side surface, the hydraulic piping of the positive displacement hydraulic pressure supplying means 7c can be blocked in the shortest distance.
In the cross-sectional view of the rotor 72c in FIG. 12 (left in the lower figure), the regenerative hydraulic pressure is supplied from the 79c1 to the hydraulic regenerating means 9c through the hydraulic relay passage 726c and the circumferential endless groove 768c1 of the rotary joint 76c.
The operation of the direction control valve 77c1 corresponding to the hydraulic relay passage 721c will be described below (in the lower diagram) and (in the lower diagram right).
The hydraulic pressure of the valve cylinder 412c1 is supplied to the hydraulic passage 782c1 through the hydraulic relay passage 721c and the circumferential end groove 778c1a (in the lower diagram), and the oil is discharged through the hydraulic passage 79c2 when the valve cylinder 412c1 is at rest. A circumferential end groove 778c1b communicating with the tank 80c communicates with the hydraulic pressure passage 782c1 to obtain a lash adjuster effect.
The hydraulic oil pressure of the valve cylinder 412c4 whose phase is 180 ° different from that of the valve cylinder 412c1 (in the lower drawing) from the valve cylinder 412c1 (in the lower drawing) is supplied to the hydraulic passage 782c4 through the hydraulic relay passage 721c and the circumferential end groove 778c1c. When the valve cylinder 412c4 is at rest, the circumferential end groove 778c1d communicating with the oil tank 80c via the hydraulic pressure passage 79c2 is communicated with the hydraulic pressure passage 782c4 to obtain a lash adjuster effect.
The circumferential end groove 778c1b and the circumferential end groove 778c1d communicate with each other by a groove provided parallel to the axis of the rotor 72c, and the other directional control valves 77 (c2 to c4) have the same configuration as that described above.

FIG. 13 shows a valve drive mechanism according to a sixth embodiment (corresponding to claim 2), including an arrangement perspective view of a displacement type hydraulic pressure supply means for the exhaust and intake of an 8-cylinder internal combustion engine and a cross section of the displacement type pump portion in arrow view G. FIG.
As shown by the arrow G, four of the pump section sectional view (FIG. 12 (upper view)) of the positive displacement hydraulic pressure supply means 7c of the exhaust and intake valve drive mechanism of the four-cylinder internal combustion engine of the fifth embodiment. The hydraulic relay paths (721c to 724c) are also provided at positions shifted in phase by 45 °, and as shown in FIG. 13, positive and negative hydraulic pressure supply means 7s of the exhaust and intake valve drive mechanisms of the eight cylinder internal combustion engine 1s are provided on both sides. Provided in the valley of the V-type cylinder block.
Example 6 of FIG. 13 can operate 16 gas exchange valves (not shown) of exhaust and intake of eight cylinders with two cam profiles 711s, so the integration of the movable parts of the valve drive mechanism makes it compact and has a small number of parts. The structure is small and simple, and an inexpensive and reliable valve drive mechanism can be obtained.
As shown in the arrow view G, the two cam profiles 711 s can be disposed in the horizontal direction, and each hydraulic passage communicating with the valve cylinder (not shown) can be disposed on both sides in the horizontal direction of the volumetric hydraulic supply means 7 s. It is easy to block piping at the shortest distance, and there is an effect that the valve drive mechanism of the internal combustion engine 1s can be manufactured inexpensively at a small space.

FIG. 14 is an explanatory view of a structural concept of a valve drive mechanism of a six-cylinder internal combustion engine according to a seventh embodiment (corresponding to claim 2) of positive displacement hydraulic pressure supplying means having three cam profiles.
The positive displacement hydraulic pressure supply means 7d of FIG. 14 includes a positive displacement pump and directional control valves 77 (d1 to d4) instead of the rotary joint, and the positive displacement pump is disposed inside the tubular cam 71d. A reference profile and three cam profiles 711d are provided at equal intervals in the circumferential direction, and the directional control valve 77 (d1 to d4) corresponds to the hydraulic relay passage on the outer peripheral surface of the rotor or the inner peripheral surface of the rotor housing The circumferential end grooves (not shown) are provided, and the intake and exhaust valve cylinders 411 (d1 to d6) and 412 (d1 to d6) are respectively provided with the circumferential end grooves and the hydraulic passages 781 (d1 to d6), 782 ( It is a valve drive mechanism of internal combustion engine 1d of Claim 1 communicated by d1-d6).

FIG. 15 is a full sectional view of the positive hydraulic pressure supply means of the seventh embodiment (FIG. 14) in which hydraulic pipes are provided on three sides, and a pump section, a rotary joint, and each direction control valve. It is sectional drawing of a part.
The positive displacement hydraulic pressure supply means 7d shown in FIG. 15 includes a positive displacement pump comprising a cam 71d, a rotor 72d, and a vane 73d, and directional control valves 77 (d1 to d4) instead of the rotary joint. In the pump, a reference profile 710d and three cam profiles 711 (d1 to d3) are provided at equal intervals in the circumferential direction inside the tubular cam 71d, and the directional control valve 77 (d1 to d4) is the rotor The circumferential end grooves 778d1a to 778d4a corresponding to the hydraulic relay paths 721d to 724d are provided on the outer peripheral surface of 72d, and the valve cylinders 411 (d1 to d6) and 412 (d1 to d6) are the circumferential end grooves 778d1a. The valve drive mechanism of an internal combustion engine according to claim 1, which communicates with 〜778d4a at hydraulic pressure passages 781 (d1 to d6) and 782 (d1 to d6).

The action of the positive displacement hydraulic pressure supply means 7d of FIG. 15 is that, as shown in the left cross section of the pump section in FIG. The rotor housing 702d is supplied to the circumferential end grooves 778d1a to 778d4a of the valve 77 (d1 to d4), and corresponds to the phase of the cam profile 711 (d1 to d3) as shown in the directional control valve 77d3 in the right of the drawing. The hydraulic passages 782 (d4, d5, d6) are provided on three side surfaces of the same phase at the same phase, and the circumferential end groove 778d3a sequentially corresponds to the hydraulic passages 782 (d4, d5, d5, d5) of the valve cylinder by the rotation of the rotor 72d. Supply hydraulic pressure in communication with d6).
The circumferential endless groove 768d1 on the left in the figure below is a rotary joint 76d communicating with the hydraulic pressure regenerating means 9d (not shown) and the circumferential endless groove 768d2 in the whole cross sectional view with the oil tank 80d of the hydraulic pressure assisting means 8d (not shown).
The circumferential end grooves 778d1a to 778d4a provided in the remaining circumferential direction of the circumferential end grooves 778d1a to 778d4a communicate with the circumferential endless groove 768d2 via the hydraulic relay passage 725d, and the fourth embodiment (FIG. The lash adjuster function is obtained as described in.

FIG. 16 is an explanatory view of a structural concept of a valve drive mechanism of a two-cylinder internal combustion engine by means of a positive displacement hydraulic pressure supplying means provided with phase control means by an actuator according to an eighth embodiment (corresponding to claim 3).
FIG. 16 is provided with a phase control means 5 provided with an actuator 51 for rotating the cam 71f around the rotation axis of the rotor 72f, and a control means 55 of the actuator 51, and depending on the operating condition of the internal combustion engine 1f. The valve drive mechanism of an internal combustion engine 1f according to claim 1 or 2, wherein the cam 71f is rotated by an actuator 51 to adjust and control the valve opening timing of the gas exchange valve 41 (f1, f2).

The function of the positive displacement hydraulic pressure supply means 7f in FIG. 16 is that, in the positive displacement pump comprising the cam 71f, the rotor 72f, and the vane 73f, the valve cylinder 41 (f1, f2) is rotated by rotating the cam 71f with the actuator 51. The phase advance or phase retard is generated at the hydraulic pressure generation timing supplied to the) to adjust the timing of gas exchange, and control the amount of gas exchange and / or the rate of gas exchange.
The control is performed by operating the actuator 51 by the control means 55 controlled by the ECU (not shown) according to the operating condition of the internal combustion engine 1 f.
The functions of the hydraulic field means 8f and the hydraulic pressure regenerating means 9f are omitted because they are the same as those of the above embodiment.

FIG. 17 is a full sectional view of the displacement type hydraulic pressure supplying means having a rotary cylinder according to a ninth embodiment (corresponding to claim 3), and a lower view is a sectional view of a pump portion and a peripheral hydraulic circuit diagram.
FIG. 17 shows a phase control means 5g comprising a rotary cylinder 511, which is a mechanical actuator for rotating the cam 71g about the rotation axis of the rotor 72g, and a control valve 551, which is control means for the actuator. The internal combustion engine according to claim 1 or 2, wherein the cam 71g is rotated by the rotary cylinder 511, which is the actuator, according to the operating condition of the internal combustion engine (not shown) to control the valve opening timing of the gas exchange valve (not shown). It is a valve drive mechanism.
The rotary cylinder 511 has a cam 71g rotatably provided in a space formed by the side housing 701g, the cam housing 703, and the rotor housing 702g as shown in the entire cross sectional view (upper view), and the cross section of the pump portion As shown in the figure (left in the figure below), the rotor housing 702g which rotates the inside of the cam housing 703 is disposed alternately with a plurality of projecting blades (vanes) which contact the sliding surface on the other side substantially sealingly. The hydraulic passages 58g1 and 58g2 are alternately communicated with the spaces between the projecting blades, which can be circumferentially formed, to form a rotary cylinder 511.

The action of the positive displacement hydraulic pressure supply means 7g of FIG. 17 controls the hydraulic pressure generated by the hydraulic pressure regeneration means 9g by the control valve 551, and supplies it to the rotary cylinder 511 via the hydraulic pressure passages 58g1 and 58g2. By changing the cam phase, the operating timing of the valve cylinder is adjusted.
The positive displacement hydraulic pressure supply means 7g is obtained by adding the phase control means 5g to the positive displacement hydraulic pressure supply means 7 of the first embodiment (FIG. 2), and the explanation of the operation other than the phase control will be omitted.
The control valve 95 provided in the hydraulic pressure regenerating means 9g can reduce the rotational load when the hydraulic pressure regeneration is not required.

FIG. 18 is an explanatory view of a conceptual configuration of a valve drive mechanism of a three-cylinder internal combustion engine which adjusts the phases of two sets of vane pumps by a motor and controls opening and closing of an intake valve.
18 (corresponding to claim 3) shows a servomotor 515 (-1, -2) which is an electric actuator for rotating the cam 71 (p1, p2) about the rotation axis of the rotor 72p, and the actuator A phase control means 5p comprising a controller 556 as control means is provided, and the cam 71 (p1, p2) is rotated by the actuator according to the operating condition of the internal combustion engine 1p, and the gas exchange valve 45 (p1 to p1) is provided. The valve drive mechanism of an internal combustion engine according to claim 1 or 2, wherein adjustment control of the valve opening timing of p3) is performed.
In FIG. 18 (corresponding to claim 4), the positive displacement pump and the second positive displacement pump are provided in the axial direction of the rotor 72p, and at least one of the positive displacement pumps is provided with the phase control means 5p. The hydraulic relay paths 721p, 722p and 723p communicate the hydraulic pressure generated by the vanes of substantially the same phase of the positive displacement pump, and one air-to-oil converter 729 (-1, -2) is connected to each of the hydraulic relay paths. , -3), and both the cams 71 (p1, p2) are rotated by the phase control means 5p according to the operating condition of the internal combustion engine 1p, and the gas exchange valve 45 (p1 to p3) is opened. The valve drive mechanism for an internal combustion engine according to claim 3, wherein adjustment control of timing and opening degree is performed.

The action of the positive displacement hydraulic pressure supply means 7p of FIG. 18 is to rotate the worm 516 (-1, 2) by the servomotor 515 (-1, 2) which is the actuator of the phase control means 5p, and the cam 71 (p1). , P2) by rotating the worm gear 517 (-1, -2) provided on the outer circumference of the cam 71 (p1, p2) to control the phase of hydraulic pressure generation.
The servomotor, which is an actuator, may be a stepping motor or the like.
The gas exchange valve 45 is controlled by adjusting and controlling the operation of the valve cylinder 411 (p1 to p3) according to the hydraulic synthesis (the synthesis method will be described in FIG. 19) of the generated hydraulic pressure of the two positive displacement pumps of substantially the same phase. Adjustment control of the valve opening timing and the opening degree of p1 to p3) is performed.
Since cavitation occurs when a negative pressure is generated by hydraulic synthesis, both hydraulic pressure generation amounts and the capacities of the air-to-oil converters 729 (-1, -2, -3) are made equal.
The prevention of the negative pressure will be described with reference to FIG.

FIG. 19 is a hydraulic characteristic diagram of the cam, the second cam, and the valve cylinder in the upper diagram of the tenth embodiment (FIG. 18), and the lower diagram is an operation explanation by the schematic diagram of the positive displacement pump in each phase. FIG.
In the upper diagram (Fig. 3) of Fig. 19, the horizontal axis is the crank angle, and the vertical axis is the characteristic of hydraulic pressure generation amount (valve lift amount). Oil pressure generation of cams 71p1 and 71p2 of two positive displacement pumps with thick line part The oil pressure generation amount of the positive displacement hydraulic pressure supply means 7p by the amount and the combination of the two, the painted portion in the thick line is a net oil pressure which is a hydraulic positive pressure portion, and the remaining portion in the thick line is the empty It is an oil pressure amount that does not contribute to the net oil pressure due to the oil pressure absorbing action of oil converter 729 (-1, -2, -3).
The oil pressure generation timing is adjusted by adjusting the phase of the cam 71 (p1, p2) by the phase control means 5p, and the valve exchange timing and / or degree of opening of the gas exchange valve are adjusted by the functions described in FIG. Perform adjustment control.

The operation of the positive displacement hydraulic pressure supply means 7p of FIG. 19 will be described below in accordance with the operation explanatory diagrams (p1 to p5) of the cells 781 (pa1 and pa2).
In (p1), no hydraulic pressure is generated by the cam 71 (p1, p2), and the hydraulic pressure is at atmospheric pressure by the lash adjuster function (not shown). It becomes.
In (p2), the hydraulic pressure generated by the cam 71p1 flows in while biasing the spring of the air-to-oil converter 729-1, and the hydraulic pressure generation amount and the flow-in amount coincide with each other. Since the amount of oil at 1 is at the maximum value, positive hydraulic pressure does not occur yet.
Between (p2) and (p3) including (p3), the oil amount of the air-to-oil converter 729-1 does not increase at the maximum value, so the generated oil amount of the cam 71p2 is all positive. It becomes a hydraulic pressure, and at (p3) it becomes the maximum of the positive hydraulic pressure.
Between (p3) and (p4) including (p4), the oil amount of the air-oil converter 729-1 is at the maximum value, and the oil amount of the cam 71p2 does not change. The decrease in hydraulic pressure reduces the positive hydraulic pressure, and the positive hydraulic pressure disappears at (p4).
Between (p4) and (p5) including (p5), the positive pressure disappears in (p4), and the oil pressure of the cam 71p2 decreases, and the air pressure decreases, and the air pressure decreases. The amount of water in the converter 729-1 is reduced to a minimum value.
The curved part of the thick line is the above-mentioned transfer curve for mitigating the impact set by the cam profile 711 (p1, p2), and the adjacent cells 738pb and 738pc also have the same transfer curve as shown by the two-dot chain line. Become.

FIG. 20 is a control operation explanatory view of each cam phase control and the valve lift characteristic chart of each control pattern (1) to (3) of the valve drive mechanism of the internal combustion engine of the tenth embodiment (FIGS. 18 and 19). .
FIG. 20 is a characteristic diagram of the crank angle on the horizontal axis and the lift amount of the valve on the vertical axis. The phase control means 5p adjusts the phase of the cam 71 (p1, p2) to adjust the hydraulic pressure generation timing, The valve cylinder is operated by controlling the generation timing and generation amount of the hydraulic pressure of the hydraulic pressure supply means 7p, and adjustment control of the opening timing and / or the opening degree of the gas exchange valve is performed.
As shown in FIG. 19 (upper stage), the valve opening control is performed by adjusting the phase of the cam 71p2 and the valve closing control is performed by adjusting the phase of the cam 71p1, and as a result of this adjustment, the oil pressure of each cell 738pa2 and cell 738pa1 changes.
As shown in FIG. 19 (lower stage), the hydraulic components of the cells 738pa2 and 738pa1 act as the valve-opening component of 71p2 and the valve-closing component of 71p1, and according to the synthesis result of each hydraulic component, the gas exchange valve 45p1 Open / close control can be performed.
According to the synthesis result, the movement curve is maintained even if the phase is changed by the phase control means 5p, so that the valve drive mechanism capable of coping with the quiet and stable high speed rotation can be achieved by the acceleration / deceleration relaxation effect.
By the above control, in the case of the control pattern (1), the phase of the cam 71 (p1, p2) can be adjusted in the same direction, and the opening / closing timing of the gas exchange valve 45p1 can be controlled, and in the case of the control pattern (2) The phase of the cam 71 (p1, p2) is adjusted in the reverse direction to control the opening / closing amount of the gas exchange valve 45p1. In the case of control pattern (3), only the phase of the cam 71p1 is adjusted Atkinson cycle control can be performed by controlling the closing timing of the replacement valve 45p1.
When only Atkinson cycle control of control pattern (3) is intended, the phase adjustment of the cam 71p2 is unnecessary, so the servomotor 515-2 which is an electrical actuator can be omitted.

FIG. 21 is a block diagram of a valve drive mechanism of a four-cylinder internal combustion engine according to Embodiment 11 (corresponding to claim 4) by means of phase control means and positive displacement hydraulic pressure supply means having two cam profiles.
In FIG. 21, a positive displacement pump and a second positive displacement pump are provided in the axial direction of the rotor 72t, and both positive displacement pumps are provided with the phase control means 5t, and substantially the same phase of each positive displacement pump is provided. The hydraulic pressure generated by the vane 73 (t1, t2) is communicated with the hydraulic relay paths 721t, 722t, and each of the hydraulic relay paths 721t, 722t is provided with one air-to-oil converter 729 (t1, t2). According to the operating condition of the internal combustion engine 1t, both the cams 71 are rotated by the phase control means 5t, and adjustment control of the valve opening timing and the opening degree of the gas exchange valve 451 (t1 to t4) is performed. 3 is a valve drive mechanism of the internal combustion engine 1t described in 3;

The function of the positive displacement hydraulic pressure supply means 7t in FIG. 21 is that the hydraulic pressure generated by the hydraulic pressure regeneration means 9t is supplied to the respective actuators 51 (t1, t2) via the respective control valves 551 (t1, t2). Thus, the phase of the cam 71 (t1, t2) is adjusted.
The hydraulic pressure generated by the two positive displacement pumps provided with the two cam profiles 711 (t1, t2) is controlled by the direction control valve 77 (t1, t2) provided in the hydraulic relay paths 721t, 722t. Since the valve cylinder 411 (t1 to t4) corresponding to the rotational phase of 72t is supplied, adjustment control of the valve opening timing and the opening degree of the gas exchange valve 451 (t1 to t4) can be performed.
The actions of the two cam profiles and the directional control valve 77 (t1, t2) are the same as those of the fourth to seventh embodiments, and the actions of the air-hydraulic converter 729 (t1, t2) are the same as those of the tenth embodiment. I omit explanation.

FIG. 22 is a full sectional view of a positive displacement type hydraulic pressure supplying means provided with phase control means with two rotary cylinders, a sectional view of each pump portion, and a peripheral hydraulic circuit diagram according to Embodiment 11 (FIG. 21). . The displacement type hydraulic pressure supply means 7t of FIG. 22 is provided with a second displacement type pump of the same configuration as the displacement type pump on the left of the figure below and in the axial direction of the rotor 72t. The hydraulic pressure regenerating means is provided with a control valve 551 (t1, t2) which is control means 5t, and a rotary cylinder 511 (t1, t2) consisting of a cam 71 (t1, t2) and a cam housing 703 (t1, t2). Adjustment control of the valve opening timing and the opening degree of the gas exchange valve 451 (t1 to t4) is performed by the hydraulic pressure generated at 9 t.
The configuration and operation of the rotary cylinder 511 (t1, t2) overlap with the description of the ninth embodiment, so the description will be omitted.
When the circumferential direction end groove 778 of the directional control valve 77 interferes with a plurality of cam profiles 711, the interference is prevented by dividing the directional control valve 77 in the axial direction of the rotor 72 as in the ninth embodiment. it can.

FIG. 23 is a configuration explanatory view of a control system of a valve drive mechanism of an internal combustion engine of a moving body by a displacement type hydraulic pressure supplying means provided with two sets of plunger pumps of the twelfth embodiment (corresponding to claim 4).
FIG. 23 shows that the plunger pump consisting of three plungers which is a positive displacement pump and the second positive displacement pump are provided in the axial direction of the rotor 72k, and both positive displacement pumps are provided with phase control means 5k. The hydraulic pressure generated by the plungers of substantially the same phase of each of the positive displacement pumps is communicated through a hydraulic relay path (not shown), and both cams 71 (K1, k2) are controlled by the phase control means 5k according to the operating condition of the internal combustion engine 1k FIG. 8 is a configuration explanatory view of a control system of a valve drive mechanism of an internal combustion engine 1k that performs adjustment control of the valve opening timing and the opening degree of the gas exchange valve by rotating
The ECU 12, which is an electronic control unit such as a valve drive mechanism of the internal combustion engine 1k, includes a CPU (central processing unit), a storage element including RAM and ROM, an input port, an output port, and a DC power source. For the connection of the entry output port, relay devices (such as amplifiers) are not shown.
As described in the above embodiment, the hydraulic sequence control which is mechanical control is automatically performed by the rotation of the rotor 72k, and in the electric control system of FIG. Control.

The function of the control system is to operate a valve cylinder (not shown) by a hydraulic pressure supplied from a positive displacement hydraulic pressure supply means 7k having two sets of plunger pumps which are valve drive mechanisms of an internal combustion engine 1k to operate a gas exchange valve. Open the valve.
The control valves 55 (k1, k2) of the phase control means 5k are controlled by the output of the ECU 12 based on the input information of the accelerator opening sensor 17 etc. to operate the actuators 51 (k1, k2). The phase of the cam 71 (k1, k2) is adjusted, the opening timing and opening degree of the gas exchange valve (not shown) opened by the valve cylinder are controlled, and the internal combustion engine 1k is operated according to the operating condition. .

FIG. 24 is a control flow chart of a valve drive mechanism of an internal combustion engine of the twelfth embodiment (FIG. 23) and a valve open control explanatory view by valve lift characteristic diagrams of control subroutines.
The valve drive mechanism of the internal combustion engine 1k is controlled by the input / output information etc. shown in FIG. 23, and in particular the control judgment such as acceleration or deceleration is performed by the accelerator opening sensor 17 or the brake opening sensor 18 by the accelerator pedal or brake pedal operation. The driver's intention and the driving situation of the internal combustion engine 1k are analyzed, judged, predicted, and the respective driving subroutines are executed according to the control flowchart of FIG.

First, the ECU 12 determines whether the driving command is ON (step S601).
Here, if it is determined that the operation command is not ON, after executing the control stop subroutine (step S612), the process returns to START of this processing routine at RETURN.
On the other hand, if it is determined that the operation command is ON, it is then determined whether the warm-up operation is in progress (step S602).
Here, if it is determined that the warm-up operation is not being performed, it is determined whether the throttle MAX is set after the normal setting subroutine (step S604) is executed.
On the other hand, when it is determined that the warm-up operation is being performed, the warm-up setting subroutine (step S603) is executed to determine whether the throttle is the MAX (step S605).
Specifically, in the warm-up setting subroutine, adjustment control such as securing the combustibility is performed as shown in the characteristic diagram A (right figure) in accordance with the temperature of the combustion chamber of the internal combustion engine 1k, the supply condition of lubricating oil, etc. .
Here, if it is determined that the throttle is the maximum, the full load operation subroutine (step S606) is executed, and the process returns to the step S601.
Specifically, in the full load operation subroutine, as shown in the characteristic diagram A (right figure) due to operating conditions such as load and vehicle speed, temperature rise of the internal combustion engine 1k, etc., charging of intake air for output increase due to overlap etc. Adjust control of quantity etc.
On the other hand, if it is determined that the throttle is not MAX, it is determined whether the throttle is ON (step S607).
Here, if it is determined that the throttle is ON, the partial load operation subroutine (step S608) is executed, and the process returns to step S601.
Specifically, in the partial load operation subroutine, as shown in the characteristic diagram A (right figure) due to operating conditions such as load and vehicle speed, temperature rise of the internal combustion engine 1k, etc., intake efficiency is improved to improve output efficiency by Atkinson cycle control. Perform adjustment control such as filling efficiency.
On the other hand, if it is determined that the throttle is not ON, it is determined whether the brake pedal is ON (step S609).
Here, if it is determined that the brake pedal is ON, an engine brake control subroutine (step S610) is executed, and the process returns to step S601.
Specifically, in the engine brake control subroutine, the fuel supply is stopped as shown in the characteristic diagram A (right) according to the operating conditions such as load and vehicle speed, and the intake valve is adjusted to adjust the pumping loss of intake. Perform adjustment control.
On the other hand, when it is determined that the brake pedal is not ON, the idling control subroutine (step S611) is executed, and the process returns to step 601.
This control flowchart is repeatedly performed during operation of the internal combustion engine 1k.

The embodiments 1 to 12 describe an example of the present invention, and the displacement type hydraulic pump of each embodiment is replaced with a vane pump by a plunger pump or vice versa.
The intake valve can be a vane pump, the exhaust valve can be a large vane pump or a plunger pump that is advantageous for high pressure, and it can be used in combination with a conventional cam system.
By means of the phase control means of the present invention, it is possible to selectively control the drive of the intake valve, such as adjusting the valve opening timing and the opening degree, and adjusting the exhaust valve such as the opening degree.
The examples 1 to 12 show an example of the present invention and do not limit the present invention, and those skilled in the art can make changes and improvements.

  Since the valve drive mechanism of the internal combustion engine according to the present invention utilizes hydraulic pressure, the function of lubrication and lash adjuster can be easily coped, and since the cam is shared, it has a simple structure with few components, reducing the size and weight of the internal combustion engine As it can, it is suitable for internal combustion engines mounted on moving bodies such as cars and ships.

DESCRIPTION OF SYMBOLS 1 internal combustion engine 4 output means 5 phase control means 6 rotation transmission means 7 positive displacement hydraulic pressure supply means 8 hydraulic pressure auxiliary means 9 hydraulic pressure regeneration means 12 ECU (electronic control device)
Reference Signs List 15 cam angle sensor 16 crank angle sensor 17 accelerator opening sensor 18 brake opening sensor 20 intake 21 intake passage 30 exhaust 31 exhaust passage 41 valve cylinder 42 valve piston 43 spring 45 gas exchange valve 46 cylinder 47 piston 48 connecting rod 49 crank shaft 51 Actuator 54 Check valve 55 Control means 58 Hydraulic pressure passage (discharge)
59 Hydraulic passage (return)
61 Follower Car 62 Drive Car 63 Transmission Medium 70 Housing 71 Cam 72 Rotor 73 Vane 74 Plunger 76 Revolving Joint 77 Direction Control Valve (Rotating Slide Type)
78 Hydraulic passage (valve drive)
79 hydraulic passage 80 oil tank 81 throttle valve 82, 83 check valve 88 hydraulic passage 92, 93 check valve 94 relief valve 95 control valve 96 direction control valve 98 hydraulic passage (discharge)
99 Hydraulic passage (return)
411 valve cylinder (intake)
412 valve cylinder (exhaust)
451 Gas Exchange Valve (Intake)
452 Gas Exchange Valve (Exhaust)
511 rotary cylinder 515 servo motor 516 worm 517 worm gear 551 control valve 556 controller 701 side housing 702 rotor housing 703 cam housing 704 intermediate housing 710 reference profile 711 cam profile 715 cam shift angle sensor 721 hydraulic relay path (first hydraulic pressure)
722 Hydraulic relay route (second hydraulic pressure)
723 Hydraulic relay route (third hydraulic pressure)
724 Hydraulic relay route (4th hydraulic pressure)
725 Hydraulic relay (atmospheric pressure)
726 Hydraulic relay passage 729 air-to-oil converter 738 cell 768 circumferential endless groove 778 circumferential endless groove 781 hydraulic passage (intake valve)
782 Hydraulic passage (exhaust valve)

The operation of the positive displacement hydraulic pressure supply means 7p of FIG. 19 will be described below in accordance with the operation explanatory diagrams (p1 to p5) of the cell 738 (pa1 and pa2).
In (p1), no hydraulic pressure is generated by the cam 71 (p1, p2), and the hydraulic pressure is at atmospheric pressure by the lash adjuster function (not shown). It becomes.
In (p2), the hydraulic pressure generated by the cam 71p1 flows in while biasing the spring of the air-to-oil converter 729-1, and the hydraulic pressure generation amount and the flow-in amount coincide with each other. Since the amount of oil at 1 is at the maximum value, positive hydraulic pressure does not occur yet.
Between (p2) and (p3) including (p3), the oil amount of the air-to-oil converter 729-1 does not increase at the maximum value, so the generated oil amount of the cam 71p2 is all positive. It becomes a hydraulic pressure, and at (p3) it becomes the maximum of the positive hydraulic pressure.
Between (p3) and (p4) including (p4), the oil amount of the air-oil converter 729-1 is at the maximum value, and the oil amount of the cam 71p2 does not change. The decrease in hydraulic pressure reduces the positive hydraulic pressure, and the positive hydraulic pressure disappears at (p4).
Between (p4) and (p5) including (p5), the positive pressure disappears in (p4), and the oil pressure of the cam 71p2 decreases, and the air pressure decreases, and the air pressure decreases. The amount of water in the converter 729-1 is reduced to a minimum value.
The curved part of the thick line is the above-mentioned transfer curve for mitigating the impact set by the cam profile 711 (p1, p2), and the adjacent cells 738pb and 738pc also have the same transfer curve as shown by the two-dot chain line. Become.

FIG. 20 is a control operation explanatory view of each cam phase control and the valve lift characteristic chart of each control pattern (1) to (3) of the valve drive mechanism of the internal combustion engine of the tenth embodiment (FIGS. 18 and 19). .
FIG. 20 is a characteristic diagram of the crank angle on the horizontal axis and the lift amount of the valve on the vertical axis. The phase control means 5p adjusts the phase of the cam 71 (p1, p2) to adjust the hydraulic pressure generation timing, The valve cylinder is operated by controlling the generation timing and generation amount of the hydraulic pressure of the hydraulic pressure supply means 7p, and adjustment control of the opening timing and / or the opening degree of the gas exchange valve is performed.
As shown in FIG. 20 (upper stage), the valve opening control is performed by adjusting the phase of the cam 71p2 and the valve closing control is performed by adjusting the phase of the cam 71p1, and as a result of this adjustment, the hydraulic pressures of the respective cells 738pa2 and 738pa1 change.
As shown in FIG. 20 (lower part), the hydraulic components of the cells 738pa2 and 738pa1 act as the valve-opening component of 71p2 and the valve-closing component of 71p1, and according to the synthesis result of each hydraulic component, the gas exchange valve 45p1 Open / close control can be performed.
According to the synthesis result, the movement curve is maintained even if the phase is changed by the phase control means 5p, so that the valve drive mechanism capable of coping with the quiet and stable high speed rotation can be achieved by the acceleration / deceleration relaxation effect.
By the above control, in the case of the control pattern (1), the phase of the cam 71 (p1, p2) can be adjusted in the same direction, and the opening / closing timing of the gas exchange valve 45p1 can be controlled, and in the case of the control pattern (2) The phase of the cam 71 (p1, p2) is adjusted in the reverse direction to control the opening / closing amount of the gas exchange valve 45p1. In the case of control pattern (3), only the phase of the cam 71p1 is adjusted Atkinson cycle control can be performed by controlling the closing timing of the replacement valve 45p1.
When only Atkinson cycle control of control pattern (3) is intended, the phase adjustment of the cam 71p2 is unnecessary, so the servomotor 515-2 which is an electrical actuator can be omitted.

Claims (4)

Reciprocating motion comprising a positive displacement pump driven by a four-stroke internal combustion engine, wherein the hydraulic pressure generated by the positive displacement pump causes the valve cylinder to periodically operate and the valve cylinder opens and closes one or more gas exchange valves. In the institution,
A valve drive mechanism for an internal combustion engine, comprising an output means, a positive displacement hydraulic pressure supply means, and a rotational transmission means, comprising:
The output means is
The valve cylinder, a crankshaft, at least one piston interlocking with the crankshaft, and a cylinder;
The rotational transmission means is
And a driven vehicle provided on the crankshaft, and a driven vehicle provided on a rotor of the positive displacement pump whose effective diameter is twice that of the driving vehicle.
The positive displacement hydraulic pressure supply means
And a rotary joint.
The displacement pump is
Inside the tubular cam, a reference profile and a cam profile are provided, and a plurality of vanes or plungers sliding on the inner circumferential surface of the cam are provided on the rotor.
The rotor comprises a hydraulic relay passage for transferring each hydraulic pressure generated by the plurality of vanes or plungers,
The rotary joint is provided with circumferential endless grooves corresponding to the respective hydraulic relay passages in the outer peripheral surface of the rotor or the inner peripheral surface of the rotor housing,
A valve drive mechanism of an internal combustion engine, wherein each circumferential endless groove communicates with the valve cylinder through a hydraulic passage. The positive displacement hydraulic pressure supply means
The displacement pump, and a directional control valve instead of the rotary joint;
The displacement pump is
Inside the tubular cam, a reference profile and at least two cam profiles are circumferentially equally spaced,
The directional control valve is provided with a circumferential end groove corresponding to each hydraulic relay passage on the outer peripheral surface of the rotor or the inner peripheral surface of the rotor housing,
The valve drive mechanism of an internal combustion engine according to claim 1, wherein the valve cylinder communicates with each of the circumferential end grooves at a hydraulic pressure passage. There is provided a phase control means provided with an actuator for rotating the cam about the rotation shaft of the rotor and control means for the actuator, and the cam is rotated by the actuator according to the operating condition of the internal combustion engine. The valve drive mechanism for an internal combustion engine according to claim 1 or 2, wherein adjustment control of the valve opening timing of the gas exchange valve is performed. The positive displacement pump and the second positive displacement pump are provided in the axial direction of the rotor, and at least one of the positive displacement pumps is provided with the phase control means.
Hydraulic pressure generated by vanes or plungers having substantially the same phase of each of the positive displacement pumps is communicated with the hydraulic relay passage, and one air-to-oil converter is provided in each of the hydraulic relay passages;
4. The control method according to claim 3, wherein at least one of the cams is rotated by the phase control means according to the operating condition of the internal combustion engine, and adjustment control of the valve opening timing and / or the opening degree of the gas exchange valve is performed. Valve drive mechanism for an internal combustion engine as described.

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