CN110159385B - Engine valve timing and lift simultaneous variable device and control method thereof - Google Patents
Engine valve timing and lift simultaneous variable device and control method thereof Download PDFInfo
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- CN110159385B CN110159385B CN201910561262.8A CN201910561262A CN110159385B CN 110159385 B CN110159385 B CN 110159385B CN 201910561262 A CN201910561262 A CN 201910561262A CN 110159385 B CN110159385 B CN 110159385B
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- pushing mechanism
- engine
- valve
- lift
- chute
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0021—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
The invention discloses a device for simultaneously changing the valve timing and the lift of an engine, which comprises: an intake valve; the return spring is sleeved on the valve rod; one end of the return spring is abutted against the limiting baffle plate, and the other end is abutted against the engine shell; the pushing mechanism is fixedly arranged in the engine shell, and the installation direction of the pushing mechanism is vertical to the valve rod; the pushing ring is fixedly connected with the movable end of the pushing mechanism, and a first sliding groove is formed in the pushing ring; a hydraulic lifter fixedly mounted within the engine housing; one end of the rocker arm is hinged with the hydraulic tappet, and one side of the other end of the rocker arm is abutted against the end part of the valve rod; a second chute is arranged in the rocker arm; wherein an included angle is formed between the axis of the first chute and the axis of the second chute; a cam driven by an engine crankshaft; the pin shafts are arranged in the first chute and the second chute in a matching way and are contacted with the cam. The invention also provides a control method of the engine valve timing and lift simultaneous variable device.
Description
Technical Field
The invention belongs to the technical field of automobile engines, and particularly relates to a device for simultaneously changing the valve timing and lift of an engine and a control method thereof.
Background
The valve timing mechanism is used for opening and closing the air inlet and outlet valves at regular time according to the requirements of working cycle and ignition sequence carried out in each cylinder of the engine, so that fresh charge (the gasoline engine is combustible mixed gas and the diesel engine is air) timely enters the cylinder, and waste gas is timely discharged from the cylinder. The more fresh charge is drawn into the cylinder, the more power the engine may deliver. The higher the charge coefficient, the more mass of fresh air or combustible mixture that enters the cylinder, the more heat is evolved when the combustible mixture is combusted, and the more power is generated by the engine. For a working volume engine, the charge coefficient is related to the pressure and temperature in the cylinder at the end of intake. The higher the pressure and the lower the temperature, the greater the mass of gas in the volume and therefore the higher the charge coefficient. The pressure of the gas in the cylinder is reduced when the air inlet system is used for resisting the air flow, and the temperature of the gas is increased when the air inlet is finished due to the fact that the high-temperature waste gas remained in the cylinder in the previous cycle and the high-temperature parts such as the combustion chamber, the piston top and the valve are used for heating the fresh gas entering the cylinder, so that the mass of the fresh gas actually filled into the cylinder is always smaller than that of the fresh gas filled with the working volume of the cylinder in the air inlet state.
The conventional engine has a fixed mechanical structure, so that the valve timing of the engine is fixed, and the valve timing cannot be changed during the operation of the engine. However, the engine speed is influential on the flow of intake and exhaust gases and the engine combustion process. When the rotating speed is high, the air inlet flow speed is high, and the inertia energy is high, so that the air inlet valve is hoped to be opened earlier and closed later, and more mixed gas or air is fed as much as possible; on the contrary, when the engine speed is lower, the air inlet flow speed is low, the inertia energy is also small, if the air inlet valve is opened too early, the piston is in the upward exhaust at the moment, so that fresh air is easily extruded out of the cylinder, the air inlet is reduced, and the engine work tends to be unstable. At low speeds, it is therefore desirable that the engine intake valve be opened slightly later. Therefore, when the engine speed is different, the valve timing requirements are different. Therefore, in order to meet the requirements of each intake valve on timing and lift at different rotational speeds, the economy and the dynamic property of the engine are improved, and a variable valve timing lift device is required.
Disclosure of Invention
The invention provides a device for simultaneously changing the valve timing and the lift of an engine, which aims to overcome the defect that the existing engine cannot simultaneously change the opening time and the lift of an intake valve.
The invention provides a control method of an engine valve timing and lift simultaneous variable device, which aims to control the extension length of a pushing mechanism according to the engine speed so as to change the opening time of an intake valve and the lift of the intake valve.
The technical scheme provided by the invention is as follows:
an engine valve timing and lift simultaneous variable device comprising:
the air inlet valve comprises a valve head part and a valve rod which are fixedly connected;
wherein the valve stem is movable through and into an engine housing;
the return spring is sleeved on the valve rod;
wherein, the end part of the valve rod is provided with a limit baffle along the circumferential direction of the valve rod; one end of the return spring is abutted against the limiting baffle plate, and the other end of the return spring is abutted against the engine shell;
a pushing mechanism fixedly installed in the engine housing, and an installation direction of the pushing mechanism is perpendicular to the valve stem;
the pushing ring is fixedly connected with the movable end of the pushing mechanism, and a first sliding groove is formed in the pushing ring;
a hydraulic lifter fixedly mounted within the engine housing;
one end of the rocker arm is hinged with the hydraulic tappet, and one side of the other end of the rocker arm is abutted against the end part of the valve rod; a second chute is arranged in the rocker arm;
wherein an included angle is formed between the axis of the first chute and the axis of the second chute;
a cam driven by an engine crankshaft;
wherein the intake valve and the cam are respectively positioned at two sides of the second chute;
the pin shafts are arranged in the first sliding groove and the second sliding groove in a matching mode and are abutted against the cam;
the pin shaft can reciprocate along the first sliding groove under the extrusion of the cam, and the pin shaft can reciprocate along the second sliding groove under the pushing of the pushing ring.
Preferably, the second chute is arc-shaped, the cam is arranged on the concave side of the second chute, and the intake valve is arranged on the convex side of the second chute.
Preferably, the engine valve timing and lift simultaneous variable device further comprises;
one end of the first buffer spring is fixedly connected to the pin shaft, and the other end of the first buffer spring is fixedly connected to one end of the second chute; and
and one end of the second buffer spring is fixedly connected to the pin shaft, and the other end of the second buffer spring is fixedly connected to the other end of the second chute.
Preferably, the pushing mechanism and the hydraulic tappet are respectively installed close to two ends of the second chute.
Preferably, the pushing mechanism has four locking positions, and the relationship between the extending lengths of the pushing mechanism corresponding to the four locking positions is that:
L 1 ＜L 2 ＜L 3 ＜L 4 ；
wherein L is 1 The extension length of the pushing mechanism corresponding to the first locking position is set; l (L) 2 The extension length of the pushing mechanism corresponding to the second locking position; l (L) 3 The extension length of the pushing mechanism corresponding to the third locking position; l (L) 4 Is the extension length of the pushing mechanism corresponding to the fourth locking position.
Preferably, one end of the rocker arm is fixedly connected with a first hinge part, and the hydraulic tappet is provided with a second hinge part;
the first hinge part is a sphere, and the second hinge part is internally provided with a spherical cavity; the first hinge part is free to rotate within the second hinge part.
An engine valve timing and lift simultaneous variable device comprising:
the two air inlet valves comprise valve heads and valve rods which are fixedly connected;
wherein the valve stem is movable through and into an engine housing;
the two return springs are respectively sleeved on the two valve rods;
wherein, the end part of the valve rod is provided with a limit baffle along the circumferential direction of the valve rod; one end of the return spring is abutted against the limiting baffle plate, and the other end of the return spring is abutted against the engine shell;
a pushing mechanism fixedly installed in the engine housing, and an installation direction of the pushing mechanism is perpendicular to the valve stem;
the two pushing rings are fixedly connected with the movable end of the pushing mechanism, and a first sliding groove is formed in each pushing ring;
two hydraulic lifters fixedly mounted within the engine housing;
the two rocker arms are symmetrically arranged on two sides of the pushing mechanism and are respectively close to the two pushing rings; one end of each rocker arm is hinged with each hydraulic tappet, and one side of the other end of each rocker arm is abutted against the end parts of the two valve rods; a second chute is arranged in the rocker arm;
wherein an included angle is formed between the axis of the first chute and the axis of the second chute;
a cam driven by an engine crankshaft;
wherein the intake valve and the cam are respectively positioned at two sides of the second chute;
the pin shafts are arranged in the first sliding groove and the second sliding groove in a matching mode and are abutted against the cam;
the pin shaft can reciprocate along the first sliding groove under the extrusion of the cam, and the pin shaft can reciprocate along the second sliding groove under the pushing of the pushing ring.
Preferably, the pushing mechanism has four locking positions, and the relationship between the extending lengths of the pushing mechanism corresponding to the four locking positions is that:
L 1 ＜L 2 ＜L 3 ＜L 4 ；
wherein L is 1 The extension length of the pushing mechanism corresponding to the first locking position is set; l (L) 2 The extension length of the pushing mechanism corresponding to the second locking position; l (L) 3 The extension length of the pushing mechanism corresponding to the third locking position; l (L) 4 Is the extension length of the pushing mechanism corresponding to the fourth locking position.
A control method of a variable device for simultaneously controlling the valve timing and the lift of an engine, which controls the extension length of a pushing mechanism according to the rotating speed of the engine, and changes the opening time and the lift of an intake valve.
Preferably, the control method of the engine valve timing and lift simultaneous variable device includes:
when n is less than 1000r/m, controlling the pushing mechanism to lock at a first locking position;
when n is more than or equal to 1000 and less than 3500r/m, controlling the pushing mechanism to lock at a second locking position;
when n is more than 3500 and less than 6000r/m, controlling the pushing mechanism to lock at a third locking position;
when n is more than or equal to 6000r/m, controlling the lock pushing mechanism to lock at a fourth locking position;
wherein n is the engine speed; when the pushing mechanism is locked at the fourth lock position, the intake valve opening time is earliest and the intake valve lift is maximized.
The beneficial effects of the invention are as follows:
(1) The device for simultaneously changing the valve timing and the lift of the engine is integrally designed in the engine shell cover, has compact structure, can introduce high-pressure oil into the additionally arranged control reversing valve by additionally arranging the oil way from the main oil way of the cylinder cover in the engine shell cover, changes the positioning extension and shortening of the pushing cylinder of the hydraulic cylinder by switching the on oil way of the reversing valve, and has low reconstruction cost for the engine body and convenient and reliable control.
(2) Compared with the condition that most of the prior variable valve timing and lift technologies can only work at two positions, the variable valve timing and lift device for the engine can better adapt to the working conditions of high and low speed of the engine, improve the heat efficiency and improve the fuel economy.
(3) The control method of the engine valve timing and lift simultaneous variable device provided by the invention can monitor the engine speed in real time, and high-pressure oil is introduced along with the change of the speed to change the position of the pin shaft so as to change the opening time and the lift of the air inlet valve.
(4) According to the control method of the engine valve timing and lift simultaneous variable device, provided by the invention, the lift of the intake valve is increased simultaneously under the condition that the opening time of the intake valve is advanced, the change rule meets the use requirement of the working condition of the engine, the charging efficiency can be improved, the fuel oil is fully combusted, and the power performance requirement of the engine is met.
Drawings
FIG. 1 is a schematic view showing the general structure of an engine valve timing and lift simultaneous variable device according to the present invention.
Fig. 2 is a schematic structural view of a connection between a rocker arm and a hydraulic tappet according to the present invention.
Fig. 3 is a schematic structural view of a pushing mechanism according to the present invention.
Fig. 4 is a schematic view of the pushing mechanism according to the present invention in the first locking position.
Fig. 5 is a schematic view of the pushing mechanism according to the present invention in the second locking position.
Fig. 6 is a schematic view of the pushing mechanism according to the present invention in a third locking position.
FIG. 7 is a schematic view of the pushing mechanism in a fourth locking position according to the present invention
Fig. 8 is a schematic diagram of a control method of an engine valve timing and lift simultaneous variable device according to the present invention.
Fig. 9 is a schematic view of a valve timing and lift simultaneous variable device of a double intake valve according to the present invention.
Detailed Description
The present invention is described in further detail below with reference to the drawings to enable those skilled in the art to practice the invention by referring to the description.
As shown in fig. 1, the present invention provides an engine valve timing and lift simultaneous variable device, mainly comprising: engine housing 100, intake valve 110, return spring 120, push mechanism 130, hydraulic lifter 140, rocker arm 150, pin 160, and cam 170.
The intake valve 110 is arranged vertically, the intake valve 110 comprising a valve head 111 and a valve stem 112, wherein the valve stem 112 is movable through the engine housing 100 and extends into the engine housing 100. The return spring 120 is sleeved on the valve rod 112; the upper end of the valve stem 112 is provided with a limit stopper 112a in the circumferential direction of the valve stem 112. The return spring 120 has an upper end abutting against the limit stopper 112a and a lower end abutting against the inner wall of the engine case 100.
The pushing mechanism 130 is fixedly installed at the left side of the inside of the engine housing 100, and the pushing mechanism 130 is horizontally disposed, i.e., the installation direction of the pushing mechanism 130 is perpendicular to the axial direction of the valve stem 112. The movable end of the pushing mechanism 130 is integrated with a pushing ring 131, and a first chute 131a is arranged in the pushing ring 131. The first chute 131a is a waist-shaped chute, and an axial direction of the first chute 131a is a vertical direction.
The hydraulic lifter 140 is fixedly installed on the right side of the inside of the engine housing 100. The right end of the rocker arm 150 is hinged with the hydraulic tappet 140, and the lower side of the left end of the rocker arm 150 is abutted against the upper end of the valve stem 120; and a second runner 151 is provided in the rocker arm. The first chute 131a and the second chute 151 are disposed to intersect, and an included angle is formed between an axis of the first chute 131a and an axis of the second chute 151.
The pin shaft 160 is arranged in the first chute 131a and the second chute 151 in a matching way; the upper side of the pin 160 is provided with a cam 170, the cam 170 is driven by a crankshaft of the engine through a belt or a chain, and the cam 170 is in contact with the pin 160. Wherein the pin 160 can reciprocate along the first chute 131a under the pressing of the cam 170, and the pin 160 can reciprocate along the second chute 151 under the pushing of the push ring 131.
In the present embodiment, the second chute 151 is arc-shaped, the cam 170 is provided on the concave side (upper side) of the second chute 151, and the intake valve 110 is provided on the convex side (lower side) of the second chute 151. A first buffer spring 153 and a second buffer spring 154 are respectively provided in the second sliding groove 151 of the rocker arm 150 at both sides of the pin 160. Wherein, the left end of the first buffer spring 153 is connected to the right side of the pin 160, and the right end is connected to the right end of the second chute 151; the left end of the second buffer spring 154 is connected to the left end of the second chute 151, and the right end is connected to the left side of the pin 160.
As shown in fig. 2, the rocker arm 150 is connected to the hydraulic jack in the following manner: the right end of the rocker arm is fixedly connected with a first hinge part 152, and the first hinge part 152 is a sphere; the hydraulic tappet 140 is provided with a second hinge part 141, and a spherical cavity is arranged in the second hinge part 141; wherein the first hinge part 152 is matingly disposed in the second interface part 141 and is freely rotatable within the second hinge part 141.
As shown in fig. 3 to 7, the pushing mechanism 130 adopts a double-acting hydraulic cylinder, which is composed of a fixed cylinder 130a, a piston 130b and a pushing cylinder 130c, wherein a pushing ring 131 is integrated on the right side of the pushing cylinder 130 c. The fixed cylinder 130a and the pushing cylinder 130c have hydraulic chambers inside, respectively, and the length of the hydraulic chamber of the fixed cylinder 130a is greater than that of the hydraulic chamber of the pushing cylinder 130 c. The left and right ends of the piston rod 130B are respectively positioned in the hydraulic cavity of the fixed cylinder 130a and the hydraulic cavity of the pushing cylinder 130c, and the left and right ends of the hydraulic cavity of the fixed cylinder 130a are respectively provided with an oil through port A and an oil through port B; an oil port C and an oil port D are provided at both left and right ends of the hydraulic chamber of the push cylinder 130C, respectively. The high-pressure oil is led into the additionally arranged control reversing valve through additionally arranging an oil way in the engine cylinder cover from the main oil way of the cylinder cover, and the positioning extension and shortening of the pushing cylinder of the hydraulic cylinder are changed by switching the switching-on oil way of the reversing valve. The pushing mechanism 130 has four locking positions, and the relationship of the extending lengths of the pushing mechanism corresponding to the four locking positions is:
L 1 ＜L 2 ＜L 3 ＜L 4 ；
wherein L is 1 The extension length of the pushing mechanism corresponding to the first locking position is set;L 2 the extension length of the pushing mechanism corresponding to the second locking position; l (L) 3 The extension length of the pushing mechanism corresponding to the third locking position; l (L) 4 Is the extension length of the pushing mechanism corresponding to the fourth locking position.
As shown in fig. 4, when the pushing mechanism 130 is in the first locking position, the left end of the piston rod 130b abuts against the left end of the hydraulic chamber of the fixed cylinder 130 a; and the right end of the piston rod 130b abuts against the right end of the hydraulic chamber of the push cylinder 130c, at which time the piston rod extends by a length L 1 。
As shown in fig. 5, when the pushing mechanism 130 is in the second locking position, the left end of the piston rod 130b abuts against the left end of the hydraulic chamber of the fixed cylinder 130 a; and the right end of the piston rod 130b abuts against the left end of the hydraulic chamber of the push cylinder 130c, at which time the piston rod extends by a length L 2 。
As shown in fig. 6, when the pushing mechanism 130 is in the third locking position, the left end of the piston rod 130b abuts against the right end of the hydraulic chamber of the fixed cylinder 130 a; and the right end of the piston rod 130b abuts against the right end of the hydraulic chamber of the push cylinder 130c, at which time the piston rod extends by a length L 3 。
As shown in fig. 7, when the pushing mechanism 130 is in the fourth locking position, the left end of the piston rod 130b abuts against the right end of the hydraulic chamber of the fixed cylinder 130 a; and the right end of the piston rod 130b abuts against the left end of the hydraulic chamber of the push cylinder 130c, at which time the piston rod extends by a length L 4 。
In this embodiment, the cam 170 rotates in a clockwise direction, and the cam 170 presses the pin 160 by rotating. The pin 160 is moved up and down within the push ring 131 and drives the rocker arm 150 to rotate about the hydraulic lifter 140. Since the intake valve 110 is pressed against the engine housing 100 by the return spring 120, when the rocker arm 150 is depressed, the return spring 120 is compressed, and when the intake process is completed, the rocker arm 150 is lifted, and the return spring 120 is extended to drive the intake valve 110 to move so that the intake valve 110 is closed. Meanwhile, by controlling the extension length of the pushing mechanism 130, the position of the pin 160 in the horizontal direction is changed, so that the contact time of the pin 160 and the small end (the end far from the axis of the cam) of the cam 170 is changed, namely the opening time of the engine valve is changed; while the distance the rocker arm 150 is depressed can be changed, i.e., the valve lift can be changed.
As shown in FIG. 8, the invention also provides a control method of the engine valve timing and lift simultaneous variable device, wherein the engine speed threshold value related in the control method is obtained according to different engine models, displacement, maximum speed and other experimental calibration, and the calibration process is obtained by online calibration of the bench with better indexes such as air inlet efficiency, maximum power and the like. As prior art, no description will be given here. The control method comprises the following steps:
working condition I, engine speed n 1 High-pressure oil is injected into the oil port B and the oil port C simultaneously, the oil port A and the oil port D are connected with a low-pressure oil return port, so that the pushing mechanism 130 is locked at a first locking position (as shown in fig. 4), the extension distance of the pushing mechanism 130 is shortest, the pin shaft 160 is positioned at the lowest position (farthest from the hydraulic tappet 140) in the second sliding groove 151, under the action of the cam 170, the pin shaft 160 drives the rocker arm 150 to reciprocate up and down, and accordingly the intake valve 110 is driven to open and close, and due to the relative positions of the pin shaft 160 and the cam 170, the opening time of the intake valve 110 is latest and the valve lift is smallest.
Working condition two, engine speed n 2 High-pressure oil is injected into the oil port B and the oil port D simultaneously, the oil port A and the oil port C are connected with a low-pressure oil return port, so that the control pushing mechanism 130 is locked at a second locking position (shown in fig. 5), the extending distance of a hydraulic cylinder is short, the pin shaft 160 is positioned at a lower position of the second sliding groove 151, the pin shaft 160 drives the rocker arm 150 to move up and down under the action of the cam 170, and accordingly the intake valve 110 is driven to be opened and closed, and due to the relative positions of the pin shaft 160 and the cam 170, the opening time of the intake valve 110 is advanced and the valve lift is improved compared with the first working condition.
Working condition three, engine speed n 3 High-pressure oil is injected into the oil port A and the oil port C at the same time, and the oil port B and the oil port D are connected with a low-pressure oil return port; the control pushing mechanism 130 is locked at the third locking position (as shown in fig. 6), the pin 160 is located at the higher position of the second chute 151, and the pin 160 drives the rocker arm 150 to move up and down under the action of the cam 170, therebyThe intake valve 110 is driven to open and close, and the opening time of the intake valve 110 is advanced and the valve lift is improved compared with the second working condition due to the relative positions of the pin shaft 160 and the cam 170.
Working condition four, engine speed n 4 High-pressure oil is injected into the oil port A and the oil port D simultaneously, the oil port B and the oil port C are connected with a low-pressure oil return port, so that the control pushing mechanism 130 is locked at a fourth locking position (shown in fig. 7), the extending distance of a hydraulic cylinder is longest, the pin shaft 160 is positioned at the highest position of the second sliding groove 151 (closest to the hydraulic tappet 140), at the moment, under the action of the cam 170, the pin shaft 160 drives the rocker arm 150 to move up and down, and then drives the intake valve 110 to open and close, and the relative positions of the pin shaft 160 and the cam 170 enable the opening time of the intake valve 110 to be earliest and the valve lift to be largest.
The relation of the engine speeds corresponding to the first working condition, the second working condition, the third working condition and the fourth working condition is as follows:
n 1 ＜n 2 ＜n 3 ＜n 4 。
in this embodiment, the specific control method of the engine valve timing and lift simultaneous variable device includes:
firstly, acquiring the real-time rotating speed n of an engine through a rotating speed sensor;
when n is less than 1000r/m, injecting high-pressure oil into the oil through holes B and C, wherein the oil through holes A and D are connected with low-pressure oil return holes;
when n is more than or equal to 1000 and less than 3500r/m, injecting high-pressure oil into the oil through holes B and D, and connecting the oil through holes A and C with low-pressure oil return holes;
when n is more than 3500 and less than 6000r/m, injecting high-pressure oil into the oil through holes A and C, and connecting the oil through holes B and D with low-pressure oil return holes;
when n is more than or equal to 6000r/m, high-pressure oil is injected into the oil through holes A and D, and the oil through holes B and C are connected with low-pressure oil return holes.
In another embodiment, as shown in FIG. 9, a dual intake valve mechanism is employed. Comprising two inlet valves 110, 210; two return springs 120, 220 are correspondingly arranged; two hydraulic lifters 140, 240; two rocker arms 150, 250; buffer springs 153 and 154 are arranged in the corresponding rocker arm 150, and buffer springs 252 and 253 are arranged in the rocker arm 250; the air inlet valves and the rocker arms are in one-to-one correspondence, and the specific installation mode is the same as that of one air inlet valve. The two rocker arms cooperate with a set of pushing mechanisms 130, a pin 160 and a cam 170; the pushing mechanism 130 is arranged between the two rocker arms 150 and 250, one end of the pushing mechanism 130 is integrated with the two pushing rings 131 and 231, and the pin shaft 160 is simultaneously matched and arranged in the two pushing rings 131 and 231 and the sliding grooves in the rocker arms 150 and 250. The cam 170 is disposed between the two push rings 131 and 231 and contacts the pin 160 for pressing the pin 160.
Likewise, the pushing mechanism 130 employs a double-acting hydraulic cylinder, which can provide four different locking positions and can be locked at the corresponding positions.
The control method of the double-intake valve mechanism is the same as that of the single-intake valve mechanism, namely, the position of the pin shaft 160 is changed in real time according to the rotation speed of the engine, and the opening time and the lift of the intake valve are both improved along with the improvement of the rotation speed, so that the charging efficiency of the engine is improved, and the requirement on the dynamic property is met.
Although embodiments of the present invention have been disclosed above, it is not limited to the details and embodiments shown and described, it is well suited to various fields of use for which the invention would be readily apparent to those skilled in the art, and accordingly, the invention is not limited to the specific details and illustrations shown and described herein, without departing from the general concepts defined in the claims and their equivalents.
Claims (10)
1. An engine valve timing and lift simultaneous variable apparatus, comprising:
the air inlet valve comprises a valve head part and a valve rod which are fixedly connected;
wherein the valve stem is movable through and into an engine housing;
the return spring is sleeved on the valve rod;
wherein, the end part of the valve rod is provided with a limit baffle along the circumferential direction of the valve rod; one end of the return spring is abutted against the limiting baffle plate, and the other end of the return spring is abutted against the engine shell;
a pushing mechanism fixedly installed in the engine housing, and an installation direction of the pushing mechanism is perpendicular to the valve stem; the pushing mechanism adopts a double-acting hydraulic cylinder;
the pushing ring is fixedly connected with the movable end of the pushing mechanism, and a first sliding groove is formed in the pushing ring;
a hydraulic lifter fixedly mounted within the engine housing;
one end of the rocker arm is hinged with the hydraulic tappet, and one side of the other end of the rocker arm is abutted against the end part of the valve rod; a second chute is arranged in the rocker arm;
wherein an included angle is formed between the axis of the first chute and the axis of the second chute;
a cam driven by an engine crankshaft;
wherein the intake valve and the cam are respectively positioned at two sides of the second chute;
the pin shafts are arranged in the first sliding groove and the second sliding groove in a matching mode and are abutted against the cam;
the pin shaft can reciprocate along the first sliding groove under the extrusion of the cam, and the pin shaft can reciprocate along the second sliding groove under the pushing of the pushing ring.
2. The engine valve timing and lift simultaneous variable device according to claim 1, wherein the second runner is arc-shaped, the cam is provided on a concave side of the second runner, and the intake valve is provided on a convex side of the second runner.
3. The engine valve timing and lift simultaneous variable device according to claim 2, characterized by further comprising;
one end of the first buffer spring is fixedly connected to the pin shaft, and the other end of the first buffer spring is fixedly connected to one end of the second chute; and
and one end of the second buffer spring is fixedly connected to the pin shaft, and the other end of the second buffer spring is fixedly connected to the other end of the second chute.
4. The engine valve timing and lift simultaneous variable device according to claim 2 or 3, wherein the pushing mechanism and the hydraulic lifter are mounted near both ends of the second runner, respectively.
5. The engine valve timing and lift simultaneous variable apparatus according to claim 4, wherein the pushing mechanism has four lock positions, and the four lock positions correspond to the relationship of pushing mechanism extension lengths:
L 1 ＜L 2 ＜L 3 ＜L 4 ；
wherein L is 1 The extension length of the pushing mechanism corresponding to the first locking position is set; l (L) 2 The extension length of the pushing mechanism corresponding to the second locking position; l (L) 3 The extension length of the pushing mechanism corresponding to the third locking position; l (L) 4 Is the extension length of the pushing mechanism corresponding to the fourth locking position.
6. The engine valve timing and lift simultaneous variable device according to claim 5, wherein one end of the rocker arm is fixedly connected with a first hinge part, and the hydraulic tappet is provided with a second hinge part;
the first hinge part is a sphere, and the second hinge part is internally provided with a spherical cavity; the first hinge part is free to rotate within the second hinge part.
7. An engine valve timing and lift simultaneous variable apparatus, comprising:
the two air inlet valves comprise valve heads and valve rods which are fixedly connected;
wherein the valve stem is movable through and into an engine housing;
the two return springs are respectively sleeved on the two valve rods;
wherein, the end part of the valve rod is provided with a limit baffle along the circumferential direction of the valve rod; one end of the return spring is abutted against the limiting baffle plate, and the other end of the return spring is abutted against the engine shell;
a pushing mechanism fixedly installed in the engine housing, and an installation direction of the pushing mechanism is perpendicular to the valve stem; the pushing mechanism adopts a double-acting hydraulic cylinder;
the two pushing rings are fixedly connected with the movable end of the pushing mechanism, and a first sliding groove is formed in each pushing ring;
two hydraulic lifters fixedly mounted within the engine housing;
the two rocker arms are symmetrically arranged on two sides of the pushing mechanism and are respectively close to the two pushing rings; one end of each rocker arm is hinged with each hydraulic tappet, and one side of the other end of each rocker arm is abutted against the end parts of the two valve rods; a second chute is arranged in the rocker arm;
wherein an included angle is formed between the axis of the first chute and the axis of the second chute;
a cam driven by an engine crankshaft;
wherein the intake valve and the cam are respectively positioned at two sides of the second chute;
the pin shafts are arranged in the first sliding groove and the second sliding groove in a matching mode and are abutted against the cam;
the pin shaft can reciprocate along the first sliding groove under the extrusion of the cam, and the pin shaft can reciprocate along the second sliding groove under the pushing of the pushing ring.
8. The engine valve timing and lift simultaneous variable apparatus according to claim 7, wherein the pushing mechanism has four lock positions, and the four lock positions correspond to the relationship of pushing mechanism extension lengths:
L 1 ＜L 2 ＜L 3 ＜L 4 ；
wherein L is 1 The extension length of the pushing mechanism corresponding to the first locking position is set; l (L) 2 The extension length of the pushing mechanism corresponding to the second locking position; l (L) 3 The extension length of the pushing mechanism corresponding to the third locking position; l (L) 4 Is the extension length of the pushing mechanism corresponding to the fourth locking position.
9. A control method of an engine valve timing and lift simultaneous variable device according to any one of claims 1 to 8, characterized in that the opening timing of the intake valve and the lift of the intake valve are changed by controlling the length of extension of the pushing mechanism in accordance with the rotation speed of the engine.
10. The control method of the engine valve timing and lift simultaneous variable device according to claim 9, characterized by comprising:
when n is less than 1000r/m, controlling the pushing mechanism to lock at a first locking position;
when n is more than or equal to 1000 and less than 3500r/m, controlling the pushing mechanism to lock at a second locking position;
when n is more than 3500 and less than 6000r/m, controlling the pushing mechanism to lock at a third locking position;
when n is more than or equal to 6000r/m, controlling the lock pushing mechanism to lock at a fourth locking position;
wherein n is the engine speed; when the pushing mechanism is locked at the fourth lock position, the intake valve opening time is earliest and the intake valve lift is maximized.
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| CN201910561262.8A CN110159385B (en) | 2019-06-26 | 2019-06-26 | Engine valve timing and lift simultaneous variable device and control method thereof |
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| CN201910561262.8A CN110159385B (en) | 2019-06-26 | 2019-06-26 | Engine valve timing and lift simultaneous variable device and control method thereof |
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