CN115013108A - Internal combustion engine hydraulic valve mechanism with variable opening times - Google Patents
Internal combustion engine hydraulic valve mechanism with variable opening times Download PDFInfo
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- CN115013108A CN115013108A CN202210852911.1A CN202210852911A CN115013108A CN 115013108 A CN115013108 A CN 115013108A CN 202210852911 A CN202210852911 A CN 202210852911A CN 115013108 A CN115013108 A CN 115013108A
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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
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
- F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
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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
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/40—Methods of operation thereof; Control of valve actuation, e.g. duration or lift
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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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Abstract
The invention discloses a hydraulic valve mechanism of an internal combustion engine with variable opening times, which mainly comprises a valve component, a hydraulic piston component, a first distribution cam driving system, a second distribution cam driving system, a control valve and a low-pressure system. The invention controls the working mode of the valve through the directional control valve or the combined control valve, can realize the working mode of single opening of the valve of the internal combustion engine in one working cycle, the working mode of secondary opening in one working cycle, the working mode of multiple opening in one working cycle and the working mode of non-opening, and realizes the mutual switching among the working modes of various valves. The internal combustion engine can be matched with various working modes such as a normal acting mode, a cylinder deactivation mode, an internal EGR mode and an exhaust braking mode, the problems of complex structure, high cost, poor consistency and the like in the prior art are solved, and the method has important significance for promoting energy conservation and emission reduction of the internal combustion engine and improving braking power of the internal combustion engine.
Description
Technical Field
The invention relates to a valve mechanism of an internal combustion engine, in particular to a hydraulic valve mechanism of the internal combustion engine, which realizes variable opening times in one working cycle.
Background
With the increasing severe energy environment crisis and the continuous development of the internal combustion engine technology, the single valve lift can not meet the working requirement of the internal combustion engine, and the seeking for realizing various valve motion laws becomes a new trend of the internal combustion engine valve mechanism development, wherein the valve multiple-opening technology has wide application prospect: the intake valve is opened for the second time in the exhaust stroke, so that part of high-temperature waste gas in the cylinder can flow back to the air inlet channel to participate in the next cycle of combustion, the integral exhaust temperature of the internal combustion engine under the working condition of low speed and small load is effectively improved, and the catalytic conversion efficiency of post-treatment is improved; the exhaust valve is opened for the second time in the intake stroke, and high-temperature waste gas in the exhaust passage is sucked back to the cylinder, so that the internal EGR function is realized, and the NOx emission can be effectively reduced; the exhaust valve is opened for the second time at the last stage of the compression stroke, and high-pressure gas compressed in the cylinder is released into the exhaust passage, so that the compression release type braking function is realized, and the braking power of the internal combustion engine is improved; the cylinder stopping function can be realized without opening the valve, part of cylinders stop working under the low-load working condition, the loads of other cylinders are increased, so that the cylinders work closer to a high-efficiency area, and the oil consumption of the internal combustion engine is reduced.
The existing valve multiple opening technology has various schemes, and can be divided into a camshaft type and a cam-free type according to a driving mode. The camshaft type valve driving mechanism is more typical of engine braking devices which can be provided, a braking piston is arranged on an exhaust valve, the exhaust valve can be opened at the end of a compression stroke by controlling the extension of the braking piston through an electromagnetic valve, and the switching of the exhaust valve from single opening to secondary opening is completed. The cam-free shaft type valve driving mechanism enables the valve motion law to have larger change space, but a high-frequency electromagnetic valve or a high-frequency electromagnet is adopted as a driving source of the valve, the response speed is difficult to adapt to the high rotating speed of an internal combustion engine, and the problems of poor consistency, high cost, high energy consumption, valve seating impact and the like exist.
Disclosure of Invention
The invention aims to overcome the defects in the prior art, and provides a hydraulic valve mechanism with variable opening times for an internal combustion engine, which can realize a single-opening working mode, a secondary-opening working mode, a multi-opening working mode and a non-opening working mode of a valve of the internal combustion engine in one working cycle, realize the mutual switching among multiple valve working modes, and can be matched with the internal combustion engine to realize multiple working modes such as a normal working mode, a cylinder deactivation mode, an internal EGR mode and an exhaust braking mode.
The technical scheme adopted by the invention is as follows:
the invention discloses a hydraulic valve mechanism of an internal combustion engine with variable opening times, which comprises a valve component, a hydraulic piston component, a first valve actuating cam driving system, a second valve actuating cam driving system, a direction control valve and a low-pressure system, wherein the valve component is connected with the hydraulic piston component;
the hydraulic piston assembly comprises a hydraulic piston and a piston sleeve, a piston cavity is arranged between the hydraulic piston and the piston sleeve, and the hydraulic piston drives the valve assembly to reciprocate;
the first valve cam driving system comprises a first cam, a first hydraulic tappet and a first tappet sleeve, a first tappet cavity is arranged between the first hydraulic tappet and the first tappet sleeve, and the first cam drives the first hydraulic tappet to reciprocate;
the second distribution cam driving system comprises a second cam, a second hydraulic tappet and a second tappet sleeve, a second tappet cavity is arranged between the second hydraulic tappet and the second tappet sleeve, and the second cam drives the second hydraulic tappet to reciprocate;
the directional control valve comprises a first directional control valve and a second directional control valve; the first direction control valve comprises a P oil port, an A oil port and a T oil port, the P oil port of the first direction control valve is communicated with the first tappet cavity, the A oil port of the first direction control valve is communicated with the piston cavity, and the T oil port of the first direction control valve is communicated with the low-pressure system;
the second directional control valve comprises a P oil port, an A oil port and a T oil port, the P oil port of the second directional control valve is communicated with the second tappet cavity, the A oil port of the second directional control valve is communicated with the piston cavity, and the T oil port of the second directional control valve is communicated with the low-pressure system;
the valve of the internal combustion engine can be in a single-opening working mode in one working cycle, a secondary-opening working mode in one working cycle, a multi-opening working mode in one working cycle and a non-opening working mode by controlling the communication between the oil port P and the oil port A or the communication between the oil port P and the oil port T of the first directional control valve and the communication between the oil port P and the oil port A or the communication between the oil port P and the oil port T of the second directional control valve; according to the functional requirements, the invention selects two or more than two valve working modes for use and realizes the mutual switching between the working modes.
Further, the valve positions of the first directional control valve or the second directional control valve respectively comprise a first valve position and a second valve position; the first valve position is that the oil port P is communicated with the oil port A; the second valve position is that the P hydraulic fluid port is communicated with the T hydraulic fluid port.
Furthermore, the first distribution cam driving system further comprises a first one-way valve, an oil inlet of the first one-way valve is communicated with the low-pressure system, and an oil outlet of the first one-way valve is communicated with the first tappet cavity; the second distribution cam driving system further comprises a second one-way valve, an oil inlet of the second one-way valve is communicated with the low-pressure system, and an oil outlet of the second one-way valve is communicated with the second tappet cavity.
Furthermore, the number of the hydraulic piston assemblies is one set or two or more sets, and the piston cavities of the two sets or more sets of hydraulic piston assemblies are communicated.
Furthermore, in the first and second air distribution cam driving systems, the cam directly drives a plane hydraulic tappet or a roller hydraulic tappet; the cam drives the hydraulic tappet to move through the roller rocker arm assembly or the tappet and push rod assembly.
In a second aspect, the invention discloses a hydraulic valve mechanism of an internal combustion engine with variable opening times, which comprises a valve component, a hydraulic piston component, a first distribution cam driving system, a second distribution cam driving system, a combined control valve and a low-pressure system, wherein the valve component is connected with the hydraulic piston component;
the hydraulic piston assembly comprises a hydraulic piston and a piston sleeve, a piston cavity is arranged between the hydraulic piston and the piston sleeve, and the hydraulic piston drives the valve assembly to reciprocate;
the first distribution cam driving system comprises a first cam, a first hydraulic tappet and a first tappet sleeve, a first tappet cavity is arranged between the first hydraulic tappet and the first tappet sleeve, and the first cam drives the first hydraulic tappet to reciprocate;
the second distribution cam driving system comprises a second cam, a second hydraulic tappet and a second tappet sleeve, a second tappet cavity is arranged between the second hydraulic tappet and the second tappet sleeve, and the second cam drives the second hydraulic tappet to reciprocate;
the combined control valve comprises a P1 oil port, a P2 oil port, an A oil port and a T oil port, the P1 oil port of the combined control valve is communicated with the first tappet cavity, the P2 oil port of the combined control valve is communicated with the second tappet cavity, the A oil port of the combined control valve is communicated with the piston cavity, and the T oil port of the combined control valve is communicated with the low-pressure system;
the valve of the internal combustion engine can realize a single-opening working mode, a secondary-opening working mode in one working cycle, a multi-opening working mode and a non-opening working mode in one working cycle by controlling the communication of a P1 oil port and an A oil port, or the communication of a P1 oil port and a T oil port, the communication of a P2 oil port and the A oil port, or the communication of a P2 oil port and the T oil port of the combined control valve; according to the functional requirements, the invention selects two or more than two valve working modes for use and realizes the mutual switching between the working modes.
As a further technical solution, the valve positions of the combination control valve include at least two valve positions of a first combination valve position, a second combination valve position, a third combination valve position and a fourth combination valve position;
the first combined valve position is that a P1 oil port is communicated with an A oil port, and a P2 oil port is communicated with a T oil port;
the second combined valve is characterized in that a P1 oil port is communicated with a T oil port, and a P2 oil port is communicated with an A oil port;
the third combined valve is characterized in that a P1 oil port and a P2 oil port are communicated with the T oil port;
the fourth combination valve is characterized in that the oil port P1 and the oil port P2 are communicated with the oil port A.
As a further technical scheme, the first distribution cam driving system further comprises a first one-way valve, an oil inlet of the first one-way valve is communicated with the low-pressure system, and an oil outlet of the first one-way valve is communicated with the first tappet cavity; the second distribution cam driving system further comprises a second one-way valve, an oil inlet of the second one-way valve is communicated with the low-pressure system, and an oil outlet of the second one-way valve is communicated with the second tappet cavity.
As a further technical scheme, the number of the hydraulic piston assemblies is one set or two or more sets, and piston cavities of the two sets or more sets of hydraulic piston assemblies are communicated.
As a further technical scheme, in the first and second air distribution cam driving systems, a cam directly drives a planar hydraulic tappet or a roller hydraulic tappet; the cam drives the hydraulic tappet to move through the roller rocker arm assembly or the tappet and push rod assembly.
The hydraulic valve mechanism of the internal combustion engine with variable opening times is arranged on the internal combustion engine. The hydraulic valve mechanism of the internal combustion engine comprises a valve component, a hydraulic piston component, a first valve actuating cam driving system, a second valve actuating cam driving system, a control valve, a low-pressure system and the like.
When the valve seat works, the crankshaft of the internal combustion engine rotates, and the crankshaft drives the first valve actuating cam driving system and the second valve actuating cam driving system to work. In the first and second valve cam drive systems, the cams drive the hydraulic tappet to move.
The working process of the present invention is described below by taking the first aspect as an example:
when the working position of the directional control valve is the first valve position, the tappet cavity is communicated with the piston cavity. When the cam is positioned at the ascending section of the working section, the cam pushes the hydraulic tappet to move, so that hydraulic oil in the tappet cavity enters the piston cavity through the oil port P and the oil port A of the directional control valve, and pushes the hydraulic piston to overcome the spring force of the valve so as to open the valve; when the cam is positioned at the descending section of the working section, the volume of the tappet cavity is increased, hydraulic oil in the piston cavity flows back to the tappet cavity through the direction control valve, and the valve gradually falls back and is closed under the action of the valve spring.
When the working position of the directional control valve is the second valve position, the tappet cavity is communicated with the low-pressure system. In the motion process of the cam, hydraulic oil in the tappet cavity flows into the low-pressure system through the P oil port and the T oil port of the directional control valve, and the motion rule of the valve is not influenced by the cam.
By controlling the first directional control valve and the second directional control valve to carry out the combination of different working positions, four valve working modes can be formed:
(1) when the working position of the first direction control valve is a first valve position and the working position of the second direction control valve is a second valve position, the first tappet cavity is communicated with the piston cavity, the second tappet cavity is communicated with the low-pressure system, the motion law of the valve depends on the cam molded line of the first cam, and the second cam does not influence the motion law of the valve.
(2) When the working position of the first direction control valve is the second valve position and the working position of the second direction control valve is the first valve position, the first tappet cavity is communicated with the low-pressure system, the second tappet cavity is communicated with the piston cavity, the motion law of the valve depends on the cam molded line of the second cam, and the first cam does not influence the motion law of the valve.
(3) When the working position of the first direction control valve and the working position of the second direction control valve are both the second valve positions, the first tappet cavity and the second tappet cavity are communicated with the low-pressure system, the first cam and the second cam do not influence the motion law of the valve, and the valve is in a non-opening working mode.
(4) When the working position of the first direction control valve and the working position of the second direction control valve are both the first valve positions, the first tappet cavity and the second tappet cavity are communicated with the piston cavity, and the motion law of the valve is determined by the cam molded line of the first cam and the cam molded line of the second cam. If only the first cam is in the working section, the motion law of the valve depends on the cam profile of the first cam; if only the second cam is in the working section, the motion law of the valve depends on the cam profile of the second cam; if the first cam and the second cam are in the working section at the same time, the motion law of the valve depends on the coupling effect of the first cam and the second cam.
When the first directional control valve and the second directional control valve are combined into a combined control valve for application, the combined control valve can functionally realize four valve working modes consisting of the first directional control valve and the second directional control valve.
According to the functional requirements, the first cam or the second cam can be provided with one bulge, or two or more bulges can be arranged; the invention can be provided with two gas distribution cam driving systems and corresponding directional control valves, and also can be provided with three or more than three gas distribution cam driving systems and corresponding directional control valves.
When the tappet cavity is communicated with the low-pressure system and the cam is positioned at the descending section of the working section, the hydraulic oil discharged into the low-pressure system flows back to the tappet cavity through the control valve. The check valve (the first check valve or the second check valve) arranged in the distribution cam driving system can increase the backflow area of hydraulic oil in the low-pressure system flowing to the tappet cavity, so that the flow resistance is reduced.
The check valve is arranged in the valve actuating cam driving system, and when hydraulic oil in the mechanism leaks, the hydraulic oil in the tappet cavity and the piston cavity in each working cycle can be supplemented in time.
The number of the hydraulic piston assemblies is one set or two or more sets, and the piston cavities of the two sets or more sets of hydraulic piston assemblies are communicated. When one hydraulic piston is only contacted with one valve component, the direct drive of one valve can be realized; when one hydraulic piston is contacted with a plurality of valve assemblies through a valve bridge, the hydraulic piston can drive a plurality of valves to move simultaneously.
In the first and second air distribution cam driving systems, the hydraulic tappet can be a plane hydraulic tappet or a roller hydraulic tappet; the cam can directly drive the hydraulic tappet to reciprocate, and can also drive the hydraulic tappet to reciprocate through the roller rocker arm assembly; when the valve mechanism is of a structure with the lower camshaft, the cam can drive the hydraulic tappet to reciprocate through the tappet and push rod assembly.
According to the structural requirement, when the first directional control valve and the second directional control valve share one set of low-pressure system, the T oil port of the first directional control valve is communicated with the T oil port of the second directional control valve; when the first direction control valve and the second direction control valve are respectively provided with a set of low-pressure system, the T oil port of the first direction control valve is not communicated with the T oil port of the second direction control valve.
The low-pressure system comprises an energy accumulator, an oil pool and an overflow valve, the energy accumulator is communicated with the oil pool, and an oil inlet of the overflow valve is communicated with the low-pressure system. When the oil pressure of a low-pressure system is changed, the energy accumulator reduces vibration and impact caused by oil pressure fluctuation through volume change; when the pressure of the hydraulic oil in the low-pressure system exceeds the opening pressure of the overflow valve, the overflow valve discharges part of the hydraulic oil out of the low-pressure system. The combined action of the accumulator and the relief valve maintains the relative pressure within the low pressure system, typically between 0MPa and 2 MPa. The hydraulic oil in the low-pressure system is supplied by the lubrication system of the internal combustion engine.
The invention has the beneficial effects that:
1. the invention discloses a hydraulic valve mechanism with variable opening times for an internal combustion engine, which can realize a single-opening working mode, a secondary-opening working mode, a multi-opening working mode and a non-opening working mode of a valve of the internal combustion engine in one working cycle by controlling the working modes of the valve through a directional control valve or a combined control valve, realize the mutual switching among a plurality of working modes of the valve, and flexibly match the internal combustion engine to realize a plurality of working modes such as a normal working mode, a cylinder deactivation mode, an internal EGR mode, an exhaust braking mode and the like.
2. The directional control valve or the combined control valve only needs to act when the working mode of the valve opening is switched, the structure is simple and reliable, and the manufacturing cost is low.
3. In the switching process of the valve opening working mode, the valve can be switched stably, quickly and without impact.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate exemplary embodiments of the invention and together with the description serve to explain the invention and not to limit the invention.
FIG. 1 is a schematic diagram of a hydraulic valvetrain employing two directional control valves;
FIG. 2 is a schematic illustration of a first position K1 and a second position K2 of a directional control valve;
FIG. 3 is a schematic view of a valve lift curve;
FIG. 4 is a schematic view of a cam driving a hydraulic tappet through a roller rocker arm assembly;
FIG. 5 is a schematic view of a cam driving a hydraulic tappet through a tappet + push rod assembly;
FIG. 6 is a schematic diagram of a valvetrain employing a combination control valve;
reference numerals:
1. a valve component, 2, a hydraulic piston component, 2-1, a hydraulic piston, 2-2, a piston sleeve, 3-1, a first hydraulic tappet, 3-2, a first tappet sleeve, 4, a first direction control valve, 5, a first check valve, 6, a second direction control valve, 7, a second check valve, 8-1, a second hydraulic tappet, 8-2, a second tappet sleeve, 9, a second cam, 10, an energy accumulator, 11, an oil pool, 12, a first cam, 13, an overflow valve, 14, an oil filter, 15, an oil pan, 16, an oil pump, 17, a roller rocker arm component, 18, a tappet and push rod component, 19, a combined control valve, K1, a first valve position, K2, a second valve position, M, a piston cavity, N1, a first cylinder cavity, N2, a second tappet cavity, a first valve actuating system, b, a second valve actuating system, c. a low pressure system.
Detailed Description
It is to be understood that the following detailed description is exemplary and is intended to provide further explanation of the invention as claimed. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the invention. As used herein, the singular forms "a", "an", and/or "the" are intended to include the plural forms as well, unless the invention expressly state otherwise, and it should be understood that when the terms "comprises" and/or "comprising" are used in this specification, they specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof;
example 1
The embodiment provides a hydraulic valve mechanism of an internal combustion engine with variable opening times of two directional control valves, which can realize mutual switching of working modes of an intake valve and realize a large-load working mode, an internal EGR mode and a cylinder deactivation mode by matching with a four-stroke internal combustion engine.
As shown in fig. 1 and 2, the present embodiment includes a valve assembly 1, a hydraulic piston assembly 2, a first and a second valve cam drive system a, b, a first and a second direction control valve 4, 6 and a low pressure system c.
The valve assembly 1 is an intake valve assembly of a four-stroke internal combustion engine.
The hydraulic piston assembly 2 comprises a hydraulic piston 2-1 and a piston sleeve 2-2, a piston cavity M is arranged between the hydraulic piston 2-1 and the piston sleeve 2-2, and the hydraulic piston 2-1 drives the valve assembly 1 to reciprocate.
The first valve cam driving system a comprises a first cam 12, a first hydraulic tappet 3-1, a first tappet sleeve 3-2 and a first one-way valve 5, wherein a first tappet cavity N1 is arranged between the first hydraulic tappet 3-1 and the first tappet sleeve 3-2. The bulge of the first cam 12 is correspondingly arranged on the air inlet stroke of the four-stroke internal combustion engine, and the first cam 12 drives the first hydraulic tappet 3-1 to reciprocate. An oil inlet of the first check valve 5 is communicated with the low-pressure system c, and an oil outlet of the first check valve 5 is communicated with the first tappet cavity N1.
The second distribution cam driving system b comprises a second cam 9, a second hydraulic tappet 8-1, a second tappet sleeve 8-2 and a second one-way valve 7, and a second tappet cavity N2 is arranged between the second hydraulic tappet 8-1 and the second tappet sleeve 8-2. The bulge of the second cam 9 is correspondingly arranged on the exhaust stroke of the four-stroke internal combustion engine, and the second cam 9 drives the second hydraulic tappet 8-1 to reciprocate. An oil inlet of the second one-way valve 7 is communicated with the low-pressure system c, and an oil outlet of the second one-way valve 7 is communicated with the second tappet cavity N2.
The first direction control valve 4 comprises a P oil port, an A oil port and a T oil port, the P oil port of the first direction control valve 4 is communicated with the first tappet cavity N1, the A oil port of the first direction control valve 4 is communicated with the piston cavity M, and the T oil port of the first direction control valve 4 is communicated with the low-pressure system c.
The second directional control valve 6 comprises a P oil port, an A oil port and a T oil port, the P oil port of the second directional control valve 6 is communicated with the second tappet cavity N2, the A oil port of the second directional control valve 6 is communicated with the piston cavity M, and the T oil port of the second directional control valve 6 is communicated with the low-pressure system c.
The first directional control valve 4 and the second directional control valve 6 are solenoid-controlled two-position three-way directional control valves each including a first valve position K1 and a second valve position K2. The first valve position K1 is characterized in that a P oil port is communicated with an A oil port, and a T oil port is closed; the second valve position K2 is that the P oil port is communicated with the T oil port, and the A oil port is closed.
The low-pressure system c comprises an energy accumulator 10, an oil pool 11 and an overflow valve 13, wherein the energy accumulator 10 is communicated with the oil pool 11, an oil inlet of the overflow valve 13 is communicated with the oil pool 11, and an oil outlet of the overflow valve 13 is communicated with an oil pan 15; the combined action of the accumulator 10 and the relief valve 13 maintains the relative pressure in the low pressure system c, typically between 0MPa and 2 MPa.
The hydraulic oil of the low-pressure system c is supplied by the engine lubrication system. In the lubricating system of the internal combustion engine, hydraulic oil is fed from an oil pan 15 by an oil pump 16 to an oil filter 14, filtered by the oil filter 14, and then fed to a low-pressure system c.
The hydraulic valve mechanism of the internal combustion engine using the variable opening times of the two directional control valves provided in the present embodiment is mounted on a four-stroke internal combustion engine. When the valve timing mechanism works, the crankshaft of the internal combustion engine rotates, and the crankshaft drives the first valve timing cam driving system a and the second valve timing cam driving system b to work. In the first valve cam driving system a, a first cam 12 drives a first hydraulic tappet 3-1 to move; in the second valve cam drive system b, the second cam 9 drives the second hydraulic tappet 8-1 to move.
When the operating position of the directional control valve is the first valve position K1, the tappet cavity communicates with the piston cavity M. When the cam is positioned at the ascending section of the working section, the cam pushes the hydraulic tappet to move, so that hydraulic oil in the tappet cavity enters the piston cavity M through the oil port P and the oil port A of the directional control valve, and the hydraulic piston 2-1 is pushed to overcome the spring force of the valve so as to open the valve; when the cam is positioned at the descending section of the working section, the volume of the tappet cavity is increased, hydraulic oil in the piston cavity M flows back to the tappet cavity through the direction control valve, and the valve gradually falls back and is closed under the action of the valve spring.
When the operating position of the directional control valve is the second valve position K2, the tappet chamber communicates with the low pressure system c. When the cam is positioned at the ascending section of the working section, the cam pushes the hydraulic tappet to move, so that hydraulic oil in the tappet cavity flows into the low-pressure system c through a P oil port and a T oil port of the directional control valve, and the cam does not influence the movement rule of the valve; when the cam is positioned at the descending section of the working section, the volume of the tappet cavity is increased, and hydraulic oil flowing into the low-pressure system c is supplemented into the tappet cavity through the directional control valve and/or the one-way valve.
The present embodiment controls the valve operation mode by the first directional control valve 4 and the second directional control valve 6. As shown in the valve lift profile diagram of FIG. 3, the intake valve may be opened once during the intake stroke for a high load operating mode; can not be started, and is used for a cylinder deactivation mode; or may be opened once during each of the intake and exhaust strokes for the internal EGR mode.
(1) When the internal combustion engine is in a high-load working mode, the working position of the first directional control valve 4 is a first valve position K1, the working position of the second directional control valve 6 is a second valve position K2, the first tappet cavity N1 is communicated with the piston cavity M, the second tappet cavity N2 is communicated with the low-pressure system c, the motion law of the valve depends on the cam profile of the first cam 12, the second cam 9 does not influence the motion law of the valve, and the valve lift curve refers to a valve single-opening curve in FIG. 3.
(2) When the internal combustion engine is in the cylinder deactivation mode, the working position of the first directional control valve 4 and the working position of the second directional control valve 6 are both the second valve position K2, the first tappet cavity N1 and the second tappet cavity N2 are both communicated with the low-pressure system c, the first cam 12 and the second cam 9 do not affect the motion law of the valve, the valve lift is zero, and the valve non-opening curve in fig. 3 is referred.
(3) When the internal combustion engine is in the internal EGR mode, the working position of the first directional control valve 4 and the working position of the second directional control valve 6 are both the first valve position K1, the first tappet cavity N1 and the second tappet cavity N2 are both communicated with the piston cavity M, the motion law of the valve is determined by the cam profile of the first cam 12 and the cam profile of the second cam 9, and the valve lift curve refers to the valve secondary opening curve in FIG. 3.
In the first valve cam driving system a, the first cam 12 can directly drive the first hydraulic tappet 3-1 to reciprocate, and can also drive the first hydraulic tappet 3-1 to reciprocate through a roller rocker arm assembly 17 shown in fig. 4; when the valvetrain is an under-camshaft configuration, the first cam 12 may drive the first hydraulic lifter 3-1 to reciprocate via a "lifter + pushrod" assembly 18 as shown in FIG. 5. This way of cam-driving the hydraulic tappet to move is also applicable to the second valve train b.
Example 2
The embodiment provides the internal combustion engine hydraulic valve mechanism with the variable opening times by using the combined control valve, which can realize the mutual switching of the working modes of exhaust valves and realize a normal work mode, an exhaust braking mode and a cylinder deactivation mode by matching with a four-stroke diesel engine.
As shown in fig. 6, the present embodiment is different from embodiment 1 mainly in the following three points:
(1) the four-stroke diesel engine comprises two sets of valve assemblies 1 and two sets of hydraulic piston assemblies 2, piston cavities M of the two sets of hydraulic piston assemblies 2 are communicated with each other, and the two sets of valve assemblies 1 are exhaust valve assemblies of a four-stroke diesel engine.
(2) The bulge of the first cam 12 is correspondingly arranged on the exhaust stroke of the four-stroke diesel engine; the second cam 9 comprises a first projection and a second projection, the first projection is correspondingly arranged at the end of the compression stroke of the four-stroke diesel engine, and the second projection is correspondingly arranged at the end of the exhaust stroke of the four-stroke diesel engine.
(3) The present embodiment controls the valve operation mode by the combination control valve 19.
The combined control valve 19 is an electromagnet-controlled three-position four-way directional control valve and comprises a P1 oil port, a P2 oil port, an A oil port and a T oil port, the P1 oil port of the combined control valve 19 is communicated with a first tappet cavity N1, the P2 oil port of the combined control valve 19 is communicated with a second tappet cavity N2, the A oil port of the combined control valve 19 is communicated with a piston cavity M, and the T oil port of the combined control valve 19 is communicated with a low-pressure system c. The valve positions of the combination control valve 19 include a first combination valve position, a second combination valve position, and a third combination valve position.
When the diesel engine is in a normal power mode, the working position of the combined control valve 19 is a first combined valve position, the first tappet cavity N1 is communicated with the piston cavity M, the second tappet cavity N2 is communicated with the low-pressure system c, the motion law of the valve depends on the cam profile of the first cam 12, the second cam 9 does not influence the motion law of the valve, and the exhaust valve is opened once in the exhaust stroke.
When the diesel engine is in an exhaust braking mode, the working position of the combined control valve 19 is a second combined valve position, the first tappet cavity N1 is communicated with the low-pressure system c, the second tappet cavity N2 is communicated with the piston cavity M, the motion law of the valve depends on the cam profile of the second cam 9, the first cam 12 does not influence the motion law of the valve, and at the moment, the exhaust valve is opened once at the last stage of a compression stroke and the last stage of an exhaust stroke, so that two-stroke braking is realized.
When the diesel engine is in a cylinder deactivation mode, the working position of the combined control valve 19 is a third combined valve position, the first tappet cavity N1 and the second tappet cavity N2 are both communicated with the low-pressure system c, the first cam 9 and the second cam 12 do not influence the motion law of the valve, and the exhaust valve is in a non-opening working mode.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. The utility model provides an internal-combustion engine hydraulic pressure valvetrain of changeable opening number which characterized in that: the valve actuating device comprises a valve assembly, a hydraulic piston assembly, a first valve actuating cam driving system, a second valve actuating cam driving system, a direction control valve and a low-pressure system;
the hydraulic piston assembly comprises a hydraulic piston and a piston sleeve, a piston cavity is arranged between the hydraulic piston and the piston sleeve, and the hydraulic piston drives the valve assembly to reciprocate;
the first valve cam driving system comprises a first cam, a first hydraulic tappet and a first tappet sleeve, a first tappet cavity is arranged between the first hydraulic tappet and the first tappet sleeve, and the first cam drives the first hydraulic tappet to reciprocate;
the second distribution cam driving system comprises a second cam, a second hydraulic tappet and a second tappet sleeve, a second tappet cavity is arranged between the second hydraulic tappet and the second tappet sleeve, and the second cam drives the second hydraulic tappet to reciprocate;
the directional control valve comprises a first directional control valve and a second directional control valve; the first direction control valve comprises a P oil port, an A oil port and a T oil port, the P oil port of the first direction control valve is communicated with the first tappet cavity, the A oil port of the first direction control valve is communicated with the piston cavity, and the T oil port of the first direction control valve is communicated with the low-pressure system;
the second directional control valve comprises a P oil port, an A oil port and a T oil port, the P oil port of the second directional control valve is communicated with the second tappet cavity, the A oil port of the second directional control valve is communicated with the piston cavity, and the T oil port of the second directional control valve is communicated with the low-pressure system.
2. The hydraulic valve train for an internal combustion engine with multiple opening times according to claim 1, wherein: the valve positions of the first directional control valve or the second directional control valve respectively comprise a first valve position and a second valve position; the first valve position is that the oil port P is communicated with the oil port A; the second valve position is that the P hydraulic fluid port is communicated with the T hydraulic fluid port.
3. The hydraulic valve train for an internal combustion engine with multiple opening times according to claim 1, wherein: the first distribution cam driving system further comprises a first one-way valve, an oil inlet of the first one-way valve is communicated with the low-pressure system, and an oil outlet of the first one-way valve is communicated with the first tappet cavity; the second distribution cam driving system further comprises a second one-way valve, an oil inlet of the second one-way valve is communicated with the low-pressure system, and an oil outlet of the second one-way valve is communicated with the second tappet cavity.
4. The hydraulic valve train for an internal combustion engine with multiple opening times according to claim 1, wherein: the number of the hydraulic piston assemblies is one set or two or more sets, and piston cavities of the two sets or more sets of hydraulic piston assemblies are communicated.
5. The hydraulic valve train for an internal combustion engine with multiple opening times according to claim 1, wherein: in the first and second air distribution cam driving systems, the cam directly drives a plane hydraulic tappet or a roller hydraulic tappet; the cam drives the hydraulic tappet to move through the roller rocker arm assembly or the tappet and push rod assembly.
6. A hydraulic valve mechanism of an internal combustion engine with variable opening times is characterized by comprising a valve component, a hydraulic piston component, a first distribution cam driving system, a second distribution cam driving system, a combined control valve and a low-pressure system;
the hydraulic piston assembly comprises a hydraulic piston and a piston sleeve, a piston cavity is arranged between the hydraulic piston and the piston sleeve, and the hydraulic piston drives the valve assembly to reciprocate;
the first valve cam driving system comprises a first cam, a first hydraulic tappet and a first tappet sleeve, a first tappet cavity is arranged between the first hydraulic tappet and the first tappet sleeve, and the first cam drives the first hydraulic tappet to reciprocate;
the second distribution cam driving system comprises a second cam, a second hydraulic tappet and a second tappet sleeve, a second tappet cavity is arranged between the second hydraulic tappet and the second tappet sleeve, and the second cam drives the second hydraulic tappet to reciprocate;
the combined control valve comprises a P1 oil port, a P2 oil port, an A oil port and a T oil port, the P1 oil port of the combined control valve is communicated with the first tappet cavity, the P2 oil port of the combined control valve is communicated with the second tappet cavity, the A oil port of the combined control valve is communicated with the piston cavity, and the T oil port of the combined control valve is communicated with the low-pressure system.
7. The hydraulic valve train for an internal combustion engine with multiple opening times according to claim 6, wherein: the valve positions of the combined control valve comprise at least two valve positions of a first combined valve position, a second combined valve position, a third combined valve position and a fourth combined valve position;
the first combination valve is characterized in that a P1 oil port is communicated with an A oil port, and a P2 oil port is communicated with a T oil port;
the second combined valve is characterized in that a P1 oil port is communicated with a T oil port, and a P2 oil port is communicated with an A oil port;
the third combined valve is characterized in that a P1 oil port and a P2 oil port are communicated with the T oil port;
the fourth combination valve is characterized in that the oil port P1 and the oil port P2 are communicated with the oil port A.
8. The hydraulic valve train for an internal combustion engine with multiple opening times according to claim 6, wherein: the first distribution cam driving system further comprises a first one-way valve, an oil inlet of the first one-way valve is communicated with the low-pressure system, and an oil outlet of the first one-way valve is communicated with the first tappet cavity; the second distribution cam driving system further comprises a second one-way valve, an oil inlet of the second one-way valve is communicated with the low-pressure system, and an oil outlet of the second one-way valve is communicated with the second tappet cavity.
9. The hydraulic valve train for an internal combustion engine with multiple opening times according to claim 6, wherein: the number of the hydraulic piston assemblies is one set or two or more sets, and piston cavities of the two sets or more sets of hydraulic piston assemblies are communicated.
10. The hydraulic valve train for an internal combustion engine with multiple opening times according to claim 6, wherein: in the first and second air distribution cam driving systems, the cam directly drives a plane hydraulic tappet or a roller hydraulic tappet; the cam drives the hydraulic tappet to move through the roller rocker arm assembly or the tappet and push rod assembly.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202210852911.1A CN115013108A (en) | 2022-07-20 | 2022-07-20 | Internal combustion engine hydraulic valve mechanism with variable opening times |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202210852911.1A CN115013108A (en) | 2022-07-20 | 2022-07-20 | Internal combustion engine hydraulic valve mechanism with variable opening times |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117552852A (en) * | 2024-01-12 | 2024-02-13 | 潍柴动力股份有限公司 | Engine and valve mechanism thereof |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3381311B2 (en) * | 1993-07-19 | 2003-02-24 | 日産自動車株式会社 | Variable valve train for internal combustion engine |
| US6827050B2 (en) * | 2001-12-21 | 2004-12-07 | Caterpillar Inc | Fluid control valve actuating system |
| CN102639842A (en) * | 2009-10-12 | 2012-08-15 | 斯德曼数字系统公司 | Hydraulic internal combustion engines |
| CN103603701A (en) * | 2013-09-27 | 2014-02-26 | 大连理工大学 | Intensive multifunctional fully variable valve actuation system for 4-cylinder internal combustion engine |
| CN104061037A (en) * | 2014-03-27 | 2014-09-24 | 江苏公大动力技术有限公司 | Actuating fluid supply system for variable valve |
| CN104564206A (en) * | 2015-01-23 | 2015-04-29 | 吉林大学 | Cam-driven hydraulic fully variably valve mechanism of internal combustion engine |
| CN106640253A (en) * | 2016-12-13 | 2017-05-10 | 大连理工大学 | Intensive and locking type multi-mode hydraulic variable valve drive system |
| WO2019086492A1 (en) * | 2017-11-01 | 2019-05-09 | Eaton Intelligent Power Limited | Valve train assembly |
| CN110344908A (en) * | 2019-07-12 | 2019-10-18 | 龙口中宇汽车风扇离合器有限公司 | A kind of hydraulic valve mechanism and internal combustion engine for realizing that valve opening number is variable |
-
2022
- 2022-07-20 CN CN202210852911.1A patent/CN115013108A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3381311B2 (en) * | 1993-07-19 | 2003-02-24 | 日産自動車株式会社 | Variable valve train for internal combustion engine |
| US6827050B2 (en) * | 2001-12-21 | 2004-12-07 | Caterpillar Inc | Fluid control valve actuating system |
| CN102639842A (en) * | 2009-10-12 | 2012-08-15 | 斯德曼数字系统公司 | Hydraulic internal combustion engines |
| CN103603701A (en) * | 2013-09-27 | 2014-02-26 | 大连理工大学 | Intensive multifunctional fully variable valve actuation system for 4-cylinder internal combustion engine |
| CN104061037A (en) * | 2014-03-27 | 2014-09-24 | 江苏公大动力技术有限公司 | Actuating fluid supply system for variable valve |
| CN104564206A (en) * | 2015-01-23 | 2015-04-29 | 吉林大学 | Cam-driven hydraulic fully variably valve mechanism of internal combustion engine |
| CN106640253A (en) * | 2016-12-13 | 2017-05-10 | 大连理工大学 | Intensive and locking type multi-mode hydraulic variable valve drive system |
| WO2019086492A1 (en) * | 2017-11-01 | 2019-05-09 | Eaton Intelligent Power Limited | Valve train assembly |
| CN110344908A (en) * | 2019-07-12 | 2019-10-18 | 龙口中宇汽车风扇离合器有限公司 | A kind of hydraulic valve mechanism and internal combustion engine for realizing that valve opening number is variable |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117552852A (en) * | 2024-01-12 | 2024-02-13 | 潍柴动力股份有限公司 | Engine and valve mechanism thereof |
| CN117552852B (en) * | 2024-01-12 | 2024-04-16 | 潍柴动力股份有限公司 | Engine and valve mechanism thereof |
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