CN113738471B - Timing unit for exhaust valve driver of marine two-stroke diesel engine - Google Patents
Timing unit for exhaust valve driver of marine two-stroke diesel engine Download PDFInfo
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- CN113738471B CN113738471B CN202111149345.XA CN202111149345A CN113738471B CN 113738471 B CN113738471 B CN 113738471B CN 202111149345 A CN202111149345 A CN 202111149345A CN 113738471 B CN113738471 B CN 113738471B
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- 239000003921 oil Substances 0.000 claims description 43
- 238000001514 detection method Methods 0.000 claims description 16
- 238000005461 lubrication Methods 0.000 claims description 13
- 239000010720 hydraulic oil Substances 0.000 claims description 10
- 239000010687 lubricating oil Substances 0.000 claims description 10
- 238000007789 sealing Methods 0.000 claims description 6
- 238000006243 chemical reaction Methods 0.000 claims description 4
- 238000000034 method Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 238000004880 explosion Methods 0.000 description 5
- 238000002485 combustion reaction Methods 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 239000000446 fuel Substances 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 230000003111 delayed effect Effects 0.000 description 1
- 238000005474 detonation Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
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
- 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
- F01L9/12—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 with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
- F01L9/14—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 with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
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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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
The invention discloses a timing unit of an exhaust valve driver of a marine two-stroke diesel engine, which comprises a top cover, a shell, a stepped piston, a pressure spring, a two-position four-way proportional reversing valve and a position sensor, wherein one side of the shell is fixed at the upper part of one side of an adjacent exhaust valve driver, and a large end piston and a small end piston of the stepped piston are respectively in clearance fit with corresponding counter bore sections of stepped counter bores in the shell. The top cover is fixed on the top end of the shell, and the exhaust plunger at the top center of the stepped piston is in clearance fit with the plunger hole. One end of the exhaust hole is connected with the plunger hole, and the other end of the exhaust hole is led to the outside of one side of the top cover and is closed by the throttle screw plug. The pressure spring is positioned between the lower end of the top cover and the top end of the large-end piston of the stepped piston, the two-position four-way proportional reversing valve is fixed outside one side of the lower end of the shell, and the position sensor is fixed on the middle part of the shell. The invention realizes the adjustability of the exhaust timing, improves the accuracy of exhaust adjustment, reduces the pipeline cost and improves the safety of the hydraulic system of the diesel engine.
Description
Technical Field
The invention relates to a gas distribution device of a diesel engine, in particular to a timing device for controlling the driving of an exhaust valve by a cam of the diesel engine, and belongs to the technical field of internal combustion engines.
Background
The marine two-stroke diesel engine provides power required by the navigation of a large ship, and has the advantages of stable work, continuous and stable effective output power and the like. With the development of automation technology and network technology, the diesel engine also realizes automatic control and integrated design, and the application of an electric control system on the diesel engine is more and more extensive.
Currently, energy conservation, emission reduction and unit oil consumption reduction are important development directions of diesel engines. The economical characteristics of marine two-stroke diesel engines depend on the combustion characteristics in the cylinders, and factors affecting fuel consumption include combustion chamber structure, fuel injection timing, exhaust valve closing timing, intake air amount, and the like. At present, mechanical and semi-electric control two-stroke diesel engines are still used as main propulsion power sources of ships, and an exhaust valve driving system of the mechanical and semi-electric control two-stroke diesel engines is of a traditional cam driven mechanical exhaust valve structure. Compared to electronically controlled exhaust valve actuation systems, cam actuation is greatly limited in the control of exhaust timing, exhaust duration.
In order to optimize the economic performance of the marine two-stroke diesel engine, the oil consumption is reduced by a method for improving the explosion pressure of the cylinder, and the pressure difference (the difference between the explosion pressure and the compression pressure) in the cylinder is increased by simply improving the explosion pressure, so that the heat load of the cylinder is increased. The method has larger damage to parts such as cylinder sleeve piston, and the like, so the method for improving compression pressure and thus improving detonation pressure to optimize the method for reducing oil consumption is more suitable. For a diesel engine with cam driven exhaust valves, fuel consumption reduction may be optimized by varying the timing of the exhaust cam advance. Under the high load working condition, the excessive explosion pressure can cause potential safety hazards such as cylinder explosion, and certain measures are taken to properly reduce the compression pressure under the high load while optimizing the partial load oil consumption of the diesel engine.
Disclosure of Invention
The invention aims to provide a timing unit of an exhaust valve driver of a marine two-stroke diesel engine, which realizes automatic control of the closing timing of an exhaust valve through structural optimization of an exhaust valve actuator, shortens the time delay of a working process and precisely controls the action of the exhaust valve.
The invention is realized by the following technical scheme:
The timing unit comprises a top cover, a shell, a stepped piston, a pressure spring, a two-position four-way proportional reversing valve and a position sensor, wherein one side of the shell is fixed at the upper part of one side of an adjacent exhaust valve driver, the stepped piston is vertically embedded into a stepped counter bore in the shell downwards, and a large end piston and a small end piston of the stepped piston are respectively in clearance fit with corresponding counter bore sections of the stepped counter bore; the top cover is fixed on the top end of the shell, and the lower end of the top cover is embedded and positioned in a big end hole of the stepped counter bore and is sealed through an end face sealing ring; the top center of the stepped piston extends upwards to form an exhaust plunger, and the exhaust plunger is in clearance fit with a plunger hole in the center of the top cover; one end of the exhaust hole is vertically intersected with the top end of the plunger hole, and the other end of the exhaust hole is led out of one side of the top cover and is closed by the throttle screw plug; the pressure spring is positioned between the lower end of the top cover and the top end of the large-end piston of the stepped piston, the two-position four-way proportional reversing valve is fixed outside one side of the lower end of the shell, and the position sensor is fixed on the middle part of the shell.
The object of the present invention can be further achieved by the following technical means.
Further, a plurality of lubrication ring grooves are respectively arranged at intervals in the axial direction of the large end piston and the axial direction of the small end piston of the stepped piston; the upper end of the small-end piston is provided with a detection ring groove, the detection ring groove is positioned above a plurality of lubrication ring grooves of the small-end piston and is adjacent to the lower end of the large-end piston, the width of the detection ring groove is larger than that of the lubrication ring groove, and the depth of the detection ring groove is larger than that of the lubrication ring groove; one end of the position sensor is screwed into the middle of the shell and is sealed by a sealing ring, and a detection part of one end head of the position sensor faces to the detection ring groove.
Further, an output pipeline of the high-pressure oil pump is connected with a high-pressure lubricating oil output channel of the cam box seat plate through a connecting flange, the high-pressure lubricating oil output channel sequentially vertically penetrates through the cam box seat plate and the cam box body to enter a first port of the two-position four-way proportional reversing valve, and a second port of the two-position four-way proportional reversing valve sequentially passes through the cam box body and a high-pressure lubricating oil lower output channel at one side of the shell to be introduced into the lower end of a stepped counter bore of the shell; the high-pressure lubricating oil upper output channel of the upper cavity of the large-end piston sequentially passes through the side wall of the shell and the upper box of the exhaust valve driver and is led into the top cavity of the exhaust valve driver; the exhaust valve driver top chamber enters the exhaust valve top through an exhaust valve oil input channel.
Further, the exhaust valve driver top cavity oil drain pipeline is connected with the exhaust valve top oil drain pipeline and is connected with the exhaust valve driver lower shell oil drain pipeline and then sequentially led to the hydraulic oil tank through a third port and a fourth port of the two-position four-way proportional reversing valve; and the oil drain pipeline at the position corresponding to the position of the large-end piston in the middle part of the shell is communicated with the hydraulic oil tank through a third port and a fourth port of the two-position four-way proportional reversing valve.
Further, the model of the two-position four-way proportional reversing valve is 4WE10HB20B, the highest oil pressure is 31.5Mpa, and the maximum flow L=63 liters/min. The position sensor is an electric heat release type proximity switch, the model is DW-AD-603-M10E-637, and the reaction frequency is as follows: 800HZ, rated voltage 10-30V, rated current 200mA.
The timing unit consisting of the top cover, the shell, the stepped piston, the pressure spring, the two-position four-way proportional reversing valve and the position sensor is additionally arranged on one side of the exhaust valve driver, so that the cam-controlled exhaust valve is compact in structure, high in reliability and wide in application range, and the conversion from mechanical control to electronic control of the cam-controlled exhaust valve is realized. The invention realizes the automatic control of the diesel engine, thereby realizing the adjustability of the exhaust timing, improving the accuracy of exhaust regulation and optimizing the performance of the diesel engine. In addition, the high-pressure oil duct and the oil drain duct adopt structures integrated in the exhaust valve driver shell and the timing unit shell, so that the system structure is simplified, oil leakage caused by pipeline vibration is avoided, the pipeline cost is reduced, and the safety of a diesel engine hydraulic system is improved.
Advantages and features of the invention will be illustrated and explained by the following non-limiting description of preferred embodiments, given by way of example only with reference to the accompanying drawings.
Drawings
FIG. 1 is a hydraulic schematic of the present invention;
FIG. 2 is a front view of the present invention;
FIG. 3 is a right side view of FIG. 2;
FIG. 4 is a cross-sectional view A-A of FIG. 3;
FIG. 5 is a B-B cross-sectional view of FIG. 3;
FIG. 6 is a cross-sectional view of C-C of FIG. 3;
fig. 7 is a D-D cross-sectional view of fig. 2.
Detailed Description
The invention is further described below with reference to the drawings and examples.
In the description of the present invention, terms such as "upper," "lower," "left," "right," "first," and "second," etc., indicate orientation, position, and order, are based on the orientation shown in the drawings, or are merely for simplifying the description, and do not indicate or imply that the present invention must have a particular orientation, position, and order.
As shown in fig. 1 to 5, the present embodiment includes a top cover 1, a housing 2, a stepped piston 3, a compression spring 4, a two-position four-way proportional directional valve 5, and a position sensor 6, and the left side of the housing 1 is fixed to the upper right side of an adjacent exhaust valve driver 20. The stepped piston 3 is vertically downwards embedded into the stepped counter bore 21 in the shell 2, and the large end piston 31 and the small end piston 32 of the stepped piston 3 are respectively in clearance fit with corresponding counter bore sections of the stepped counter bore 21, so that the clearance fit ensures that the stepped piston 3 can freely move, and the clearance oil drainage quantity is small enough, so that the high-pressure oil pressure cannot be influenced. The top cover 1 is fixed on the top end of the shell 2, and the lower end of the top cover 1 is embedded and positioned in a big end hole 211 of the stepped counter bore 21. The top center of the stepped piston 3 extends upward to form a vent plunger 33, and the vent plunger 33 is in clearance fit with the plunger hole 12 in the center of the top cover 1. The left end of the exhaust hole 13 is perpendicularly intersected with the top end of the plunger hole 12, and the right end of the exhaust hole 13 is led out of the right side of the top cover 1 and is closed by the throttle screw plug 7. The throttle screw plug 7 is mainly used for releasing air in the upper space of the stepped piston 3, and prevents the closed air from affecting the smooth upward movement of the stepped piston 3. The pressure spring 4 is positioned between the lower end of the top cover 1 and the top end of the large-end piston 31 of the stepped piston 3, and the two-position four-way proportional reversing valve 5 is fixed outside the right side of the lower end of the shell 2. The position sensor 6 is fixed on the middle part of the housing 2.
As shown in fig. 4, a plurality of lubrication ring grooves 311 are respectively arranged at intervals in the axial direction of the large end piston 31 and the axial direction of the small end piston 32 of the stepped piston 3, and are used for storing lubricating oil so as to ensure sufficient lubrication during the action process of the stepped piston 3. The upper end of the small end piston 32 is provided with a detection annular groove 321, the detection annular groove 321 is positioned above a plurality of lubrication annular grooves 311 of the small end piston and is adjacent to the lower end of the large end piston 31, the width of the detection annular groove 321 is larger than the width of the lubrication annular groove 311, and the depth of the detection annular groove 321 is larger than the depth of the lubrication annular groove 311. As shown in fig. 7, the right end of the position sensor 6 is screwed into the middle of the casing 2 and sealed by a sealing ring, and the detecting portion 61 of the right end of the position sensor 6 faces the detecting ring groove 321, and is used for detecting the moving position of the stepped piston 3, and providing a position signal of the stepped piston 3 to the control system, and the control system sends a signal to instruct the valve core of the two-position four-way proportional reversing valve 5 to move. When the stepped piston 3 is jammed or does not accord with the action of the control signal in the running process of the diesel engine, the control system can display corresponding alarm. The position sensor 6 of the embodiment is an electric heat release type proximity switch, the model is DW-AD-603-M10E-637, and the reaction frequency is as follows: 800HZ, rated voltage 10-30V, rated current 200mA. The two-position four-way proportional reversing valve 5 is 4WE10HB20B, has the highest oil pressure of 31.5Mpa and the maximum flow L=63 liters/min.
As shown in fig. 1,4 and 6, the output pipe 101 of the high-pressure oil pump 10 is connected with the high-pressure oil output channel 13 of the cam box seat plate 202 through a connecting flange 201, the high-pressure oil output channel 13 sequentially vertically passes through the cam box seat plate 202 and the cam box body 203 to enter the first port 51 of the two-position four-way proportional reversing valve 5, and the second port 52 of the two-position four-way proportional reversing valve 5 sequentially passes through the cam box body 203 and the high-pressure oil lower output channel 14 on one side of the shell 2 to be introduced into the lower end of the stepped counter bore 21 of the shell 2. The high pressure oil upper output passage 15 of the large end piston upper chamber 22 passes through the side wall of the housing 2 and the exhaust valve driver upper tank 204 before and after passing into the exhaust valve driver top chamber 205. High pressure oil from the exhaust valve driver top chamber 205 enters the exhaust valve top through the exhaust valve oil input channel 301 in the direction indicated by the left arrow in fig. 1.
In fig. 1, a vent valve driver top chamber oil drain pipeline 302 is connected with a vent valve top oil drain pipeline 303, and is connected with a vent valve driver lower shell oil drain pipeline 304, and then is led to the hydraulic oil tank 30 through a third port 53 and a fourth port 54 of the two-position four-way proportional reversing valve 5 in sequence. The oil discharge pipeline 305 at the position corresponding to the position of the large-end piston 32 in the middle part of the shell 2 is communicated with the hydraulic oil tank 30 through the third port 53 and the fourth port 54 of the two-position four-way proportional reversing valve. The drain oil at the top of the vent valve is merged with the drain oil of the drain oil pipeline 303 and the drain oil pipeline 305 at the top of the vent valve in the direction indicated by the right arrow in fig. 1, and then enters the hydraulic oil tank 30 through the third port 53 and the fourth port 54 of the two-position four-way proportional reversing valve 5.
O-shaped sealing rings of corresponding specifications are respectively arranged between the connecting positions of the connecting flange 201 and the wheel box seat plate 202, between the lower end of the top cover 1 and the stepped counter bore 21 and between the adjacent surfaces of the shell 2 with the connecting channel and the exhaust valve driver 20, so that hydraulic oil leakage is prevented.
As shown in fig. 1 and 4, in operation of the diesel engine, particularly in a high load condition, when the camshaft 40 rotates such that the exhaust cam 50 is at a high point position, the roller guide 205 is pushed upward, thereby driving the secondary piston 207 and the primary piston 206 upward, compressing the low pressure oil in the top chamber 204 of the exhaust valve driver, and entering the top of the exhaust valve through the exhaust valve oil input channel 301, thereby opening the exhaust port of the combustion chamber. In order to reduce the compression pressure of the cylinder, the control system sends a signal, the electromagnet of the two-position four-way proportional reversing valve 5 is electrified, the valve core moves to a right driving state, high-pressure oil pumped by the high-pressure oil pump 10 in fig. 1 enters the bottom chamber of the shell 2 through the two-position four-way proportional reversing valve 5, the stepped piston 3 is pushed to move upwards against the weight of the stepped piston 3 and the elastic force of the pressure spring 4, and the stepped piston 3 presses the high-pressure oil in the upper chamber 22 into the top chamber 205 of the exhaust valve driver. When the exhaust cam 50 is at the low point position, the exhaust valve port is closed, and when the primary piston 206 and the secondary piston 207 of the exhaust valve driver move downwards and reset, high-pressure oil is supplemented to the top chamber of the exhaust valve, so that the closing time of the exhaust valve is delayed. When the exhaust valve is closed, the control system signals. The electromagnet of the two-position four-way proportional reversing valve 5 is powered off, the valve core moves to a left unloading state, hydraulic oil in the bottom chamber of the shell 2 is discharged and unloaded through the two-position four-way proportional reversing valve 5, and the exhaust valve, the exhaust valve driver 20 and oil drainage in the shell 2 are converged and then enter the hydraulic oil tank 30 through the second port 53 and the fourth port 54 of the two-position four-way proportional reversing valve 5. The stepped piston 3 is reset by its own weight and the restoring force of the compression spring 4, and the high pressure oil in the exhaust valve driver top chamber 205 partially flows back into the upper chamber 22 of the stepped piston 3.
In addition to the above embodiments, other embodiments of the present invention are possible, and all technical solutions formed by equivalent substitution or equivalent transformation are within the scope of the present invention.
Claims (3)
1. A marine two-stroke diesel exhaust valve driver timing unit, characterized by: the device comprises a top cover, a shell, a stepped piston, a pressure spring, a two-position four-way proportional reversing valve and a position sensor, wherein one side of the shell is fixed at the upper part of one side of an adjacent exhaust valve driver, the stepped piston is vertically embedded into a stepped counter bore in the shell downwards, and a large end piston and a small end piston of the stepped piston are respectively in clearance fit with corresponding counter bore sections of the stepped counter bore; the top cover is fixed on the top end of the shell, and the lower end of the top cover is embedded and positioned in a big end hole of the stepped counter bore and is sealed through an end face sealing ring; the top center of the stepped piston extends upwards to form an exhaust plunger, and the exhaust plunger is in clearance fit with a plunger hole in the center of the top cover; one end of the exhaust hole is vertically intersected with the top end of the plunger hole, and the other end of the exhaust hole is led out of one side of the top cover and is closed by the throttle screw plug; the pressure spring is positioned between the lower end of the top cover and the top end of the large end piston of the stepped piston, the two-position four-way proportional reversing valve is fixed outside one side of the lower end of the shell, and the position sensor is fixed on the middle part of the shell;
A plurality of lubrication ring grooves are respectively arranged at intervals in the axial direction of the large end piston and the axial direction of the small end piston of the stepped piston; the upper end of the small-end piston is provided with a detection ring groove, the detection ring groove is positioned above a plurality of lubrication ring grooves of the small-end piston and is adjacent to the lower end of the large-end piston, the width of the detection ring groove is larger than that of the lubrication ring groove, and the depth of the detection ring groove is larger than that of the lubrication ring groove; one end of the position sensor is screwed into the middle part of the shell and is sealed by a sealing ring, and a detection part of one end head of the position sensor faces the detection ring groove;
The output pipeline of the high-pressure oil pump is connected with a high-pressure lubricating oil output channel of the cam box seat plate through a connecting flange, the high-pressure lubricating oil output channel sequentially vertically passes through the cam box seat plate and the cam box body to enter a first port of the two-position four-way proportional reversing valve, and a second port of the two-position four-way proportional reversing valve sequentially passes through the cam box body and a high-pressure lubricating oil lower output channel at one side of the shell to be introduced into the lower end of a stepped counter bore of the shell; the high-pressure lubricating oil upper output channel of the upper cavity of the large-end piston sequentially passes through the side wall of the shell and the upper box of the exhaust valve driver and is led into the top cavity of the exhaust valve driver; the top chamber of the exhaust valve driver enters the top of the exhaust valve through an exhaust valve lubricating oil input channel;
The exhaust pipeline of the cavity at the top of the exhaust valve driver is connected with the exhaust pipeline at the top of the exhaust valve and is connected with the exhaust pipeline of the lower shell of the exhaust valve driver and then is led to the hydraulic oil tank through the third port and the fourth port of the two-position four-way proportional reversing valve in sequence; and the oil drain pipeline at the position corresponding to the position of the large-end piston in the middle part of the shell is communicated with the hydraulic oil tank through a third port and a fourth port of the two-position four-way proportional reversing valve.
2. The marine two-stroke diesel exhaust valve driver timing unit of claim 1 wherein: the model of the two-position four-way proportional reversing valve is 4WE10HB20B, the highest oil pressure is 31.5Mpa, and the maximum flow L=63 liters/min.
3. The marine two-stroke diesel exhaust valve driver timing unit of claim 1 wherein: the position sensor is an electric heat release type proximity switch, the model is DW-AD-603-M10E-637, and the reaction frequency is as follows: 800HZ, rated voltage 10-30V, rated current 200mA.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111149345.XA CN113738471B (en) | 2021-09-29 | 2021-09-29 | Timing unit for exhaust valve driver of marine two-stroke diesel engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111149345.XA CN113738471B (en) | 2021-09-29 | 2021-09-29 | Timing unit for exhaust valve driver of marine two-stroke diesel engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113738471A CN113738471A (en) | 2021-12-03 |
| CN113738471B true CN113738471B (en) | 2024-05-28 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111149345.XA Active CN113738471B (en) | 2021-09-29 | 2021-09-29 | Timing unit for exhaust valve driver of marine two-stroke diesel engine |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2006108438A1 (en) * | 2005-04-14 | 2006-10-19 | Man B & W Diesel A/S | Exhaust valve assembly for a large two-stroke diesel engine |
| CN103953412A (en) * | 2014-03-21 | 2014-07-30 | 哈尔滨工程大学 | Multi-stage supercharging exhaust valve |
| WO2018149333A1 (en) * | 2017-02-20 | 2018-08-23 | 山东大学 | Valve lift control device of hydraulic fully variable valve mechanism and internal combustion engine |
| CN109488409A (en) * | 2018-11-20 | 2019-03-19 | 哈尔滨工程大学 | A kind of two stroke diesel engine variable exhaust valve activator and its control method |
| CN212671889U (en) * | 2020-04-28 | 2021-03-09 | 山东理工大学 | Marine intelligent integrated low-speed diesel engine electric hydrostatic exhaust valve system |
| CN215761843U (en) * | 2021-09-29 | 2022-02-08 | 中船动力镇江有限公司 | Timing unit of exhaust valve driver of marine two-stroke diesel engine |
-
2021
- 2021-09-29 CN CN202111149345.XA patent/CN113738471B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2006108438A1 (en) * | 2005-04-14 | 2006-10-19 | Man B & W Diesel A/S | Exhaust valve assembly for a large two-stroke diesel engine |
| CN103953412A (en) * | 2014-03-21 | 2014-07-30 | 哈尔滨工程大学 | Multi-stage supercharging exhaust valve |
| WO2018149333A1 (en) * | 2017-02-20 | 2018-08-23 | 山东大学 | Valve lift control device of hydraulic fully variable valve mechanism and internal combustion engine |
| CN109488409A (en) * | 2018-11-20 | 2019-03-19 | 哈尔滨工程大学 | A kind of two stroke diesel engine variable exhaust valve activator and its control method |
| CN212671889U (en) * | 2020-04-28 | 2021-03-09 | 山东理工大学 | Marine intelligent integrated low-speed diesel engine electric hydrostatic exhaust valve system |
| CN215761843U (en) * | 2021-09-29 | 2022-02-08 | 中船动力镇江有限公司 | Timing unit of exhaust valve driver of marine two-stroke diesel engine |
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| CN113738471A (en) | 2021-12-03 |
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