CN112761838A - Modular diesel engine double-valve common rail system with flexibly adjustable oil injection rule - Google Patents
Modular diesel engine double-valve common rail system with flexibly adjustable oil injection rule Download PDFInfo
- Publication number
- CN112761838A CN112761838A CN202110100024.4A CN202110100024A CN112761838A CN 112761838 A CN112761838 A CN 112761838A CN 202110100024 A CN202110100024 A CN 202110100024A CN 112761838 A CN112761838 A CN 112761838A
- Authority
- CN
- China
- Prior art keywords
- oil
- module
- pressure
- valve
- cavity
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
- F02M55/025—Common rails
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The invention aims to provide a modularized diesel engine double-valve common rail system with flexibly adjustable oil injection rule, wherein a high-pressure oil pump is respectively connected with an oil tank and a common rail pipe, the common rail pipe is connected with an electric control oil injector through a high-pressure oil pipe, and the electric control oil injector is connected with the oil tank through an oil return pipe; the electric control oil sprayer comprises a pressure increasing control valve module, a pressure increasing module, a fastening module, a piezoelectric driving module, an oil injection control module and a nozzle module, wherein the pressure increasing control valve module is positioned above the pressure increasing module, the pressure increasing module and the piezoelectric driving module are installed in the fastening module, the lower part of the fastening module is positioned in the nozzle module, and the oil injection control module is positioned in the nozzle module. The plunger sleeve plays a role in pressurizing, and simultaneously plays a role in controlling the opening and closing of an oil way, so that the complexity of the system structure is reduced. The control cavity is constantly communicated with the common rail pipe, so that the system has the capability of realizing a regular form of first slow and then fast oil injection, and the whole working quality of the diesel engine is favorably improved.
Description
Technical Field
The invention relates to an oil injection system, in particular to a common rail system of a diesel engine.
Background
The fuel oil system is the heart of the diesel engine, is the core technology for improving the emission level of the diesel engine and improving the fuel economy and the dynamic property, and the ideal fuel oil system of the diesel engine has the characteristics of high fuel injection pressure, flexible control of fuel injection rule, fuel injection pressure and fuel injection timing and the like. The traditional mechanical fuel oil system is difficult to control the timing, the quantity and the rule of oil injection under different working conditions, has the defects of low control precision and slow dynamic response, is difficult to realize the optimal control of the transient process of the diesel engine, and limits the further optimization of the emission and the fuel economy of the diesel engine. The electronic control of a fuel system is a necessary trend in the development of modern diesel engines, and the electronic control fuel system is used as a central adjusting device of the diesel engine, is very important for optimizing and improving the comprehensive performance of the diesel engine, and becomes a core subject of competitive research in the diesel engine industry.
The high-pressure common rail fuel system is a multi-physical-field coupling nonlinear complex system integrating mechanical, electrical, magnetic and liquid, and is accompanied with processes of electromagnetic conversion, mechanical motion, high-pressure fuel pressure fluctuation, high-speed leakage flow of fuel at a sealing conical surface, high-speed jet flow at a jet hole and the like in the working process. However, although the common rail system shows an outstanding advantage in improving the overall performance of the diesel engine, there is still a great room for improvement in terms of injection pressure, injection regularity, response speed, and the like.
Disclosure of Invention
The invention aims to provide a modularized diesel engine double-valve common rail system with flexibly adjustable oil injection rules, which has high reliability and high response speed and can realize the slow-to-fast oil injection rules.
The purpose of the invention is realized as follows:
the invention relates to a modularized diesel engine double-valve common rail system with flexibly adjustable oil injection rule, which is characterized in that: the high-pressure oil pump is respectively connected with the oil tank and the common rail pipe, the common rail pipe is connected with the electric control oil injector through a high-pressure oil pipe, and the electric control oil injector is connected with the oil tank through an oil return pipe; the electric control oil sprayer comprises a pressure increasing control valve module, a pressure increasing module, a fastening module, a piezoelectric driving module, an oil injection control module and a nozzle module, wherein the pressure increasing control valve module is positioned above the pressure increasing module, the pressure increasing module and the piezoelectric driving module are installed in the fastening module, the lower part of the fastening module is positioned in the nozzle module, and the oil injection control module is positioned in the nozzle module.
The present invention may further comprise:
1. the pressure boost module comprises a pressure boost module upper shell, a pressure boost module lower shell, a pressure boost plunger and a plunger sleeve are arranged in a space formed by the pressure boost module lower shell, the lower part of the plunger sleeve is sleeved outside the pressure boost plunger, the pressure boost plunger and the plunger sleeve form a plunger cavity, the pressure boost plunger, the plunger sleeve and the pressure boost module lower shell form an annular oil drainage cavity, a driving cavity is formed between the plunger sleeve and the pressure boost module upper shell, a main oil inlet is formed in the pressure boost module upper shell, the main oil inlet is connected with an A port of the pressure boost control valve module, an oil supply port is arranged on the pressure boost module lower shell side, an oil drainage hole is formed below the pressure boost module lower shell, the oil drainage hole is communicated with the annular oil drainage cavity, a common rail pipe is connected with a.
2. The fastening module comprises a fastening module shell, an oil inlet hole and an oil supply pipe are arranged on the fastening module shell, the oil inlet hole is normally communicated with the port A of the pressure-increasing control valve module and the driving cavity, the oil supply pipe is normally communicated with the oil supply port, and a plug is arranged at the end part of the oil supply port.
3. The piezoelectric driving module comprises a piezoelectric stack mounting sleeve, the piezoelectric stack mounting sleeve is provided with a piezoelectric stack and a rotary valve driving block, the tail end of the piezoelectric stack is in contact with the rotary valve driving block, the outer sleeve of the rotary valve driving block is provided with a piezoelectric stack return spring, the tail end of the rotary valve driving block is provided with two inclined plane pins, the inclined plane angles of the two pins are opposite, the piezoelectric stack mounting sleeve is provided with a low-pressure oil interface, and the low-pressure oil interface is communicated with an oil drainage hole in a normal mode.
4. The oil injection control module comprises a transition block, a rotary valve and a rotary valve sleeve, the rotary valve is arranged in the rotary valve sleeve, the rotary valve sleeve is arranged in the transition block, the left side of the transition block is provided with an oil inlet throttling hole, the lower end of the transition block is provided with a transition oil groove, the upper end of the transition block is provided with an annular oil groove, the annular oil groove is communicated with the transition oil groove through a transition oil pipe, the upper right side of the transition block is also provided with a main oil return path, the bottom end of the rotary valve sleeve is provided with an oil return throttling hole, the diameter of the oil return throttling hole is larger than that of the oil inlet throttling hole, the left end and the right end of the rotary valve are respectively provided with a left oil groove and a right oil groove, the right oil groove and the main oil return path are on the same plane, when the rotary valve moves circumferentially, the, the two valve grooves are opposite in inclined angle and are respectively matched with the two inclined plane pins at the tail end of the rotary valve driving block, a circular groove is further formed in the center of the upper end of the rotary valve, and a torsion spring is mounted in the circular groove.
5. The nozzle module comprises a needle valve and a needle valve sleeve, the needle valve is installed in the needle valve sleeve and forms an oil containing groove with the needle valve, a needle valve reset spring is sleeved outside the needle valve, the needle valve forms a control cavity with a circular groove of an oil injection control valve block, an oil conveying pipe, a high-pressure oil interface and an oil tank interface are arranged in the needle valve sleeve, one end of the oil conveying pipe is constantly communicated with the oil containing groove, the other end of the oil conveying pipe is constantly communicated with a transition oil groove, the high-pressure oil interface is constantly communicated with a high-pressure oil pipe and an oil inlet throttling hole.
6. When the pressure increasing control valve module is not electrified, the port A of the pressure increasing control valve module is communicated with the port T, low-pressure fuel oil in the oil tank sequentially passes through the oil inlet metering hole and the main oil inlet to enter a groove arranged above the plunger sleeve, the plunger sleeve is pushed to generate displacement, and the low-pressure fuel oil enters the driving cavity and the plunger cavity; when the pressurizing control valve module is electrified, the port A is communicated with the port P and is not communicated with the port T any more, at the moment, high-pressure fuel in the common rail pipe enters a driving cavity through an oil inlet hole and a main oil inlet, the plunger sleeve moves downwards under the driving of high-pressure oil, the fuel leaked by the downward movement of the plunger sleeve flows into an oil tank through an annular oil discharge cavity, an oil discharge hole and a low-pressure oil interface, the plunger cavity is gradually sealed by the lower shell of the pressurizing module along with the downward movement of the plunger sleeve, the plunger cavity is communicated with an oil supply port, at the moment, ultrahigh-pressure fuel in the plunger sequentially passes through the oil supply port and the oil supply pipe to enter an annular oil groove, and a part of the ultrahigh-pressure fuel entering the annular, the transition oil hole and the return orifice enter the control cavity, the other part of the transition oil hole and the return orifice enter the oil containing groove through the transition oil pipe, the transition oil groove and the oil conveying pipe, and the needle valve is at the initial position under the combined action of the pretightening force of the needle valve return spring and the hydraulic pressure in the control cavity.
7. When the diesel engine needs oil injection, the piezoelectric stack is electrified to extend and push the rotary valve driving block to generate vertical displacement, the vertical displacement of the rotary valve driving block is converted into circumferential displacement of the rotary valve, the left oil groove and the transition oil hole are not on the same plane, ultrahigh pressure fuel oil cannot enter the control cavity through the rotary valve, the control cavity, the oil return throttling hole, the transition oil hole, the right oil groove, the main oil return path, the oil tank interface and the oil tank form a passage, and when the resultant force of the hydraulic pressure applied to the control cavity and the pretightening force of the needle valve reset spring is smaller than the hydraulic pressure applied to the tail end of the needle valve, the needle valve; after the piezoelectric stack is powered off, under the combined action of the elastic force of a reset spring of the piezoelectric stack and the elastic force of a torsion spring, the rotary valve driving block and the piezoelectric stack are restored to the initial state, after the rotary valve is reset, ultrahigh pressure fuel oil enters the control cavity through the rotary valve again, when the pressure in the control cavity reaches a threshold value enabling the needle valve to start to move downwards, the needle valve starts to reset until the needle valve is seated to close the spray hole, and the oil injection process is ended; and then the pressure increasing control valve module is powered off, the port A is communicated with the port T again, the plunger sleeve moves upwards, and when the plunger sleeve moves to the position where the plunger cavity is communicated with the driving cavity, the fuel pressure in the plunger cavity is reduced, so that one working cycle is finished.
The invention has the advantages that: the modularized design of the modularized diesel engine double-valve common rail system with flexibly adjustable oil injection rule enables the system to have stronger universality and easy disassembly and assembly; the plunger sleeve contained in the pressurizing module plays a role in pressurizing, and simultaneously plays a role in controlling the opening and closing of an oil way, so that the complexity of the system structure is reduced. In addition, the control cavity and the common rail pipe are constantly communicated, so that the system has the capability of realizing a regular form of slow-to-fast oil injection, and the whole working quality of the diesel engine is favorably improved.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic diagram of an electrically controlled fuel injector;
FIG. 3 is a schematic view of a boost module;
FIG. 4 is a schematic view of a fastening module;
FIG. 5 is a schematic view of a piezoelectric drive module;
FIG. 6 is a schematic view of a rotary valve drive block;
FIG. 7 is a schematic diagram of an injection control module;
FIG. 8 is a schematic view of a rotary valve;
FIG. 9 is a schematic view of a nozzle module.
Detailed Description
The invention will now be described in more detail by way of example with reference to the accompanying drawings in which:
with reference to fig. 1-9, the modularized diesel engine double-valve common rail system with flexibly adjustable oil injection rule of the invention is composed of an oil tank 1, a filter 2, a high-pressure oil pump 3, a common rail pipe 4, a high-pressure oil pipe 5 and an electric control oil injector 6. The common rail pipe 4 is connected with an electric control fuel injector 6 through a high-pressure fuel pipe 5, a plurality of fuel injectors can be connected to the common rail pipe 4, and the specific number depends on the number of cylinders of the internal combustion engine.
The electric control oil injector 6 is composed of a pressure increasing control valve module 7, a pressure increasing module 8, a fastening module 9, a piezoelectric driving module 10, an oil injection control module 11 and a nozzle module 12. The pressure increasing control valve module 7 is mounted uppermost, assembled with the fastening module 9. The pressurizing module 8 and the piezoelectric driving module 10 are installed in the fastening module 9 from top to bottom, and the fuel injection control module 11, the needle valve 51 and the needle valve return spring 50 are installed in the nozzle module 12. The nozzle block 12 is screwed to the fastening block 9.
The pressure increasing control valve module 7 is installed at the uppermost end of the electric control fuel injector 6, is essentially a two-position three-way valve, does not have special requirements on the structure, and needs to meet the flow requirement of system operation. The port A is communicated with the electric control oil injector 6, and the port P and the port T are respectively communicated with the common rail pipe 4 and the oil tank 1. According to the electrification condition of the pressure increasing control valve module 7, the port A can be respectively communicated with the port P and the port T.
The pressurizing module 8 is mounted at the uppermost end in the fastening module 9 and consists of an oil drainage hole 13, a plunger cavity 14, a plunger sleeve 15, a positioning pin 16, a main oil inlet 17, an upper pressurizing module shell 18, a driving cavity 19, an oil supply port 20, a pressurizing plunger 21 and an annular oil drainage cavity 22. The center of the upper shell 18 of the pressurizing module is provided with a main oil inlet 17, the left side of the lower shell of the pressurizing module 8 is provided with an oil supply port 20, and the oil supply port 20 can be communicated with the plunger cavity 14 when the plunger sleeve 15 moves to a certain displacement. The upper housing 18 of the pressurizing module and the lower housing of the pressurizing module 8 are connected together by two positioning pins 16, and the rest of the components of the pressurizing module 8 are assembled in the space formed by the two. The upper end of the plunger sleeve 15 is provided with a groove to limit the displacement of the plunger sleeve, the plunger sleeve 15 is sleeved on a pressurizing plunger 21 and is matched with an upper shell 18 of a pressurizing module to form a driving cavity 19, a plunger cavity 14 is formed above the plunger, an annular oil drainage cavity 22 is formed at the lower part of the pressurizing module 8, and the annular oil drainage cavity 22 is communicated with the oil drainage hole 13.
The fastening module 9 is installed below the boost control valve module 7, and has a hollow structure to install the components such as the boost module 8 therein. The fastening module 9 mainly comprises an oil inlet hole 23, an oil supply pipe 25, a plug 24 and other structures, wherein the oil inlet hole 23 is arranged in the center above the fastening module 9 and is constantly communicated with the port A of the pressure increasing control valve module 7 and the driving cavity 19. The oil supply pipe 25 is in constant communication with the oil supply port 20, and the fabrication hole is sealed by a plug 24.
The piezoelectric driving module 10 is installed in the fastening module 9 and below the pressurizing module 8, and is composed of a piezoelectric stack reset spring 26, a piezoelectric stack installation sleeve 27, a low-pressure oil interface 28, a piezoelectric stack 29 and a rotary valve driving block 30, wherein the piezoelectric stack installation sleeve 27 is of a hollow structure, and the low-pressure oil interface 28 is arranged above the piezoelectric stack installation sleeve and is normally communicated with the oil drainage hole 13. The piezoelectric stack 29 is installed at the uppermost end of the piezoelectric stack installation sleeve 27, the tail end of the piezoelectric stack 29 is in contact with the rotary valve driving block 30, and the piezoelectric stack return spring 26 is supported by the rotary valve driving block 30. The end of the rotary valve drive block 30 is terminated by two angled beveled pins, the beveled angles of the two pins being opposite.
The oil injection control module 11 mainly comprises a transition oil groove 31, a transition oil pipe 32, a rotary valve 33, a main oil return path 34, a right oil groove 35, a valve groove 36, a left oil groove 37, an annular oil groove 38, a rotary valve sleeve 39, an oil inlet throttling hole 40, a transition block 41, a torsion spring 42, an oil return throttling hole 43 and a transition oil hole 44, a stepped hole is formed in the middle of the oil injection control module, the oil inlet throttling hole 40 is formed in the left side, the transition oil groove 31 is formed in the lower end of the oil injection control module, and the annular oil groove 38 is. The upper right of the transition block 41 is also provided with a main oil return path 34, and the main oil return path 34 and the rest structures arranged on the transition block 41 are not on the same plane. The rotary valve sleeve 39 is arranged in the upper half part of a stepped hole arranged in the center of the transition block 41, the upper end of the rotary valve sleeve 39 is provided with a circular groove, the bottom end of the rotary valve sleeve 39 is provided with a return orifice 43, the diameter of the return orifice 43 is larger than that of the oil inlet orifice 40, the left end and the right end of the rotary valve 33 are respectively provided with a left oil groove 37 and a right oil groove 35, and the right oil groove 35 and the main oil return path 34 are on the same plane. When the rotary valve 33 generates a circumferential movement, the return orifice 43, the transition oil hole 44, the right oil groove 35, and the main oil return passage 34 may form a passage. The rotary valve 33 is installed in a circular groove at the upper end of the rotary valve sleeve 39, and a transition oil hole 44 is formed at the center of the rotary valve 33 and communicated with the left oil groove 37 and the return oil orifice 43. The left and right ends of the upper half part of the rotary valve 33 are respectively provided with a bevel valve groove 36 with a certain angle, and the bevel angles of the two valve grooves 36 are opposite. Which are mounted in engagement with two beveled pins, respectively, at the end of the rotary valve drive block 30. The rotary valve 33 is also provided with a circular groove at the center of the upper end thereof, and a torsion spring 42 is installed inside the circular groove.
The nozzle module 12 is installed at the lowest part of the electric control fuel injector 6 and consists of a fuel containing groove 45, a fuel delivery pipe 46, a fuel tank interface 47, a control cavity 48, a high-pressure fuel interface 49, a needle valve return spring 50, a needle valve 51 and a spray hole 52. The fuel injection control module 11, the needle valve 51 and the needle valve return spring 50 are installed inside the fuel injection control module 11, the needle valve 51 and a circular groove arranged in the center of the lower half portion of the fuel injection control module 11 are assembled to form a control cavity 48, and meanwhile the fuel injection control module 11 also plays a role of a spring seat for the needle valve return spring 50. An oil delivery pipe 46 is arranged on the right side of the nozzle module 12, one end of the oil delivery pipe 46 is constantly communicated with the oil containing groove 45, and the other end of the oil delivery pipe 46 is constantly communicated with the transition oil groove 31. The nozzle module 12 is further provided with a high-pressure oil port 49 and a tank port 47, the high-pressure oil port 49 is constantly communicated with the high-pressure oil pipe 5 and the oil inlet orifice 40, and the tank port 47 is constantly communicated with the main oil return path 34.
The modularized diesel engine double-valve common rail system with flexibly adjustable oil injection rule has the working process as follows:
the low-pressure fuel in the oil tank 1 enters the high-pressure oil pump 3 after being filtered by the filter 2, then enters the common rail pipe 4 after being pressurized by the high-pressure oil pump 3, and the high-pressure fuel in the common rail pipe 4 is then distributed to each electronic control fuel injector 6 through the high-pressure fuel pipe 5. Part of the high-pressure fuel distributed to the electronic control fuel injector 6 enters the pressure increasing control valve module 7 to be communicated with the port P, and the other part of the high-pressure fuel enters the control cavity 48 through the high-pressure fuel interface 49 and the fuel inlet throttling hole 40.
When the pressure increasing control valve module 7 is not electrified, the port A of the pressure increasing control valve module 7 is communicated with the port T, low-pressure fuel in the oil tank 1 sequentially passes through the oil inlet hole 23 and the main oil inlet 17 to enter a groove arranged above the plunger sleeve 15, the plunger sleeve 15 is pushed to generate small displacement, and the low-pressure fuel enters the driving cavity 19 and the plunger cavity 14. When the pressure increasing control valve module 7 is electrified, the port A is communicated with the port P and is not communicated with the port T, at the moment, high-pressure fuel in the common rail pipe 4 can rapidly enter the driving cavity 19 through the oil inlet hole 23 and the main oil inlet 17, because the stress area of the plunger sleeve 15 needs the stress area of the plunger cavity 14, the plunger sleeve 15 is determined to move downwards under the driving of high-pressure oil, and the fuel leaked by the downward movement of the plunger sleeve 15 flows into the oil tank 1 through the annular oil drainage cavity 22, the oil drainage hole 13 and the low-pressure oil interface 28. As the downward movement of the plunger sleeve 15 progresses, the plunger chamber 14 is gradually sealed by the lower housing of the pressurizing module 8, and the fuel pressure in the plunger chamber 14 is caused to rise. Since the radial direction of the plunger sleeve 15 is limited by the lower housing of the pressurizing module 8, only axial displacement of the plunger sleeve 15 is possible. As the plunger sleeve 15 moves downwards continuously, the plunger cavity 14 is communicated with the oil supply port 20, at the moment, the ultrahigh-pressure fuel oil in the plunger sequentially enters the annular oil groove 38 through the oil supply port 20 and the oil supply pipe 25, one part of the ultrahigh-pressure fuel oil entering the annular oil groove 38 enters the control cavity 48 through the left oil groove 37, the transition oil hole 44 and the return orifice 43, and the other part of the ultrahigh-pressure fuel oil enters the oil containing groove 45 through the transition oil pipe 32, the transition oil groove 31 and the oil delivery pipe 46. Since the force-receiving area of control chamber 48 is greater than the force-receiving area of the end of needle 51, needle 51 is now at rest in the initial position under the combined action of the biasing force of needle return spring 50 and the hydraulic pressure in control chamber 48.
When the diesel engine needs to inject oil, the piezoelectric stack 29 starts to be electrified, and after the piezoelectric stack 29 is electrified, the piezoelectric stack will extend due to the inverse piezoelectric effect and push the rotary valve driving block 30 to generate vertical displacement. Since the two pins at the end of the rotary valve driving block 30 are in inclined engagement with the valve slots 36 on the rotary valve 33 and the vertical direction of the rotary valve 33 is constrained by the rotary valve sleeve 39, the vertical displacement of the rotary valve driving block 30 will tend to translate into a circumferential displacement of the rotary valve 33, i.e., the rotary valve 33 will rotate due to the elongation of the piezoelectric stack 29. After the rotary valve 33 rotates, the left oil groove 37 and the transition oil hole 44 are not on the same plane, and the ultrahigh pressure fuel oil cannot enter the control chamber 48 through the rotary valve 33. Meanwhile, the control cavity 48, the return orifice 43, the transition oil hole 44, the right oil groove 35, the main oil return path 34, the oil tank interface 47 and the oil tank 1 form a passage, although the high-pressure fuel from the common rail pipe 4 still enters the control cavity 48 through the high-pressure oil interface 49 and the oil inlet orifice 40 at the moment, the oil pressure in the control cavity 48 still drops because the diameter of the return orifice 43 is larger than that of the oil inlet orifice 40, and when the resultant force of the hydraulic pressure applied to the control cavity 48 and the pretightening force of the needle valve return spring 50 is smaller than that applied to the tail end of the needle valve 51, the needle valve 51 lifts upwards to open the spray hole 52, and the system starts to spray oil. When the piezoelectric stack 29 is powered off, the inverse piezoelectric effect disappears, and at this time, under the combined action of the elastic force of the piezoelectric stack return spring 26 and the elastic force of the torsion spring 42, the rotary valve 33, the rotary valve driving block 30 and the piezoelectric stack 29 are rapidly restored to the initial state, so that the response speed of the system is improved. After the rotary valve 33 is reset, the ultrahigh pressure fuel enters the control chamber 48 again through the rotary valve 33, the pressure in the control chamber 48 can be quickly built up because the common rail pipe 4 is always communicated with the control chamber 48, when the pressure in the control chamber 48 reaches a threshold value which enables the needle valve 51 to start moving downwards, the needle valve 51 starts to reset until the needle valve is seated and closed to the spray hole 52, and the injection process is ended. Subsequently, the pressure boost control valve module 7 is de-energized, port a is again communicated with port T, and the oil pressure in the drive chamber 19 rapidly drops. Because the ultrahigh-pressure fuel of the system still has a certain residual pressure, the plunger sleeve 15 moves upwards under the driving of the residual pressure, and when the plunger sleeve 15 moves to the state that the plunger cavity 14 is communicated with the driving cavity 19, the fuel pressure in the plunger cavity 14 also drops rapidly, so that the system is restored to the initial state, and a working cycle is ended.
It should be noted that, in the present invention, the injected fuel comes from the plunger cavity 14, and the volume of the plunger cavity 14 is limited, so that no matter the pressure increasing control valve module 7 or the piezoelectric driving module 10 is in failure, the system will not have a condition of always injecting fuel, and therefore, the present invention has high reliability. In addition, according to the description of the operation process of the system, it can be found that after the piezoelectric stack 29 is powered on, the high-pressure fuel from the common rail pipe 4 instead of the ultrahigh-pressure fuel pressurized by the pressurization module 8 enters the control cavity 48, and after the piezoelectric stack 29 is powered off, the ultrahigh-pressure fuel enters the control cavity 48 with higher pressure, so that the needle valve 51 is lifted up not fast due to the high-pressure fuel from the common rail pipe 4 in the lifting process of the needle valve 51, but the response speed of the needle valve 51 is ensured not to be too slow due to the fact that the pressure is not very high compared with the pressure of the fuel in the ultrahigh-pressure fuel common rail pipe 4. For the resetting of the needle 51 after the piezo stack 29 is de-energized, the closing process is much quicker than the opening process of the needle 51 due to the very rapid build-up of pressure in the control chamber 48. Therefore, the invention has the capability of realizing the first slow and then fast (wedge-shaped injection) of the oil injection rule, and can ensure the oil cut to be dry and crisp, thereby achieving the beneficial effect of improving the working efficiency of the diesel engine.
Claims (8)
1. The flexible adjustable modularization diesel engine bivalve of oil spout law is rail system altogether, characterized by: the high-pressure oil pump is respectively connected with the oil tank and the common rail pipe, the common rail pipe is connected with the electric control oil injector through a high-pressure oil pipe, and the electric control oil injector is connected with the oil tank through an oil return pipe; the electric control oil sprayer comprises a pressure increasing control valve module, a pressure increasing module, a fastening module, a piezoelectric driving module, an oil injection control module and a nozzle module, wherein the pressure increasing control valve module is positioned above the pressure increasing module, the pressure increasing module and the piezoelectric driving module are installed in the fastening module, the lower part of the fastening module is positioned in the nozzle module, and the oil injection control module is positioned in the nozzle module.
2. The dual-valve common rail system of the modularized diesel engine with flexibly adjustable oil injection rule according to claim 1, is characterized in that: the pressure boost module comprises a pressure boost module upper shell, a pressure boost module lower shell, a pressure boost plunger and a plunger sleeve are arranged in a space formed by the pressure boost module lower shell, the lower part of the plunger sleeve is sleeved outside the pressure boost plunger, the pressure boost plunger and the plunger sleeve form a plunger cavity, the pressure boost plunger, the plunger sleeve and the pressure boost module lower shell form an annular oil drainage cavity, a driving cavity is formed between the plunger sleeve and the pressure boost module upper shell, a main oil inlet is formed in the pressure boost module upper shell, the main oil inlet is connected with an A port of the pressure boost control valve module, an oil supply port is arranged on the pressure boost module lower shell side, an oil drainage hole is formed below the pressure boost module lower shell, the oil drainage hole is communicated with the annular oil drainage cavity, a common rail pipe is connected with a.
3. The dual-valve common rail system of the modularized diesel engine with flexibly adjustable oil injection rule according to claim 2, is characterized in that: the fastening module comprises a fastening module shell, an oil inlet hole and an oil supply pipe are arranged on the fastening module shell, the oil inlet hole is normally communicated with the port A of the pressure-increasing control valve module and the driving cavity, the oil supply pipe is normally communicated with the oil supply port, and a plug is arranged at the end part of the oil supply port.
4. The dual-valve common rail system of the modularized diesel engine with flexibly adjustable oil injection rule according to claim 3, characterized in that: the piezoelectric driving module comprises a piezoelectric stack mounting sleeve, the piezoelectric stack mounting sleeve is provided with a piezoelectric stack and a rotary valve driving block, the tail end of the piezoelectric stack is in contact with the rotary valve driving block, the outer sleeve of the rotary valve driving block is provided with a piezoelectric stack return spring, the tail end of the rotary valve driving block is provided with two inclined plane pins, the inclined plane angles of the two pins are opposite, the piezoelectric stack mounting sleeve is provided with a low-pressure oil interface, and the low-pressure oil interface is communicated with an oil drainage hole in a normal mode.
5. The modular diesel engine double-valve common rail system with flexibly adjustable oil injection rules according to claim 4, characterized in that: the oil injection control module comprises a transition block, a rotary valve and a rotary valve sleeve, the rotary valve is arranged in the rotary valve sleeve, the rotary valve sleeve is arranged in the transition block, the left side of the transition block is provided with an oil inlet throttling hole, the lower end of the transition block is provided with a transition oil groove, the upper end of the transition block is provided with an annular oil groove, the annular oil groove is communicated with the transition oil groove through a transition oil pipe, the upper right side of the transition block is also provided with a main oil return path, the bottom end of the rotary valve sleeve is provided with an oil return throttling hole, the diameter of the oil return throttling hole is larger than that of the oil inlet throttling hole, the left end and the right end of the rotary valve are respectively provided with a left oil groove and a right oil groove, the right oil groove and the main oil return path are on the same plane, when the rotary valve moves circumferentially, the, the two valve grooves are opposite in inclined angle and are respectively matched with the two inclined plane pins at the tail end of the rotary valve driving block, a circular groove is further formed in the center of the upper end of the rotary valve, and a torsion spring is mounted in the circular groove.
6. The modular diesel engine double-valve common rail system with flexibly adjustable oil injection rules according to claim 5, characterized in that: the nozzle module comprises a needle valve and a needle valve sleeve, the needle valve is installed in the needle valve sleeve and forms an oil containing groove with the needle valve, a needle valve reset spring is sleeved outside the needle valve, the needle valve forms a control cavity with a circular groove of an oil injection control valve block, an oil conveying pipe, a high-pressure oil interface and an oil tank interface are arranged in the needle valve sleeve, one end of the oil conveying pipe is constantly communicated with the oil containing groove, the other end of the oil conveying pipe is constantly communicated with a transition oil groove, the high-pressure oil interface is constantly communicated with a high-pressure oil pipe and an oil inlet throttling hole.
7. The dual-valve common rail system of the modularized diesel engine with flexibly adjustable oil injection rule of claim 6, is characterized in that: when the pressure increasing control valve module is not electrified, the port A of the pressure increasing control valve module is communicated with the port T, low-pressure fuel oil in the oil tank sequentially passes through the oil inlet metering hole and the main oil inlet to enter a groove arranged above the plunger sleeve, the plunger sleeve is pushed to generate displacement, and the low-pressure fuel oil enters the driving cavity and the plunger cavity; when the pressurizing control valve module is electrified, the port A is communicated with the port P and is not communicated with the port T any more, at the moment, high-pressure fuel in the common rail pipe enters a driving cavity through an oil inlet hole and a main oil inlet, the plunger sleeve moves downwards under the driving of high-pressure oil, the fuel leaked by the downward movement of the plunger sleeve flows into an oil tank through an annular oil discharge cavity, an oil discharge hole and a low-pressure oil interface, the plunger cavity is gradually sealed by the lower shell of the pressurizing module along with the downward movement of the plunger sleeve, the plunger cavity is communicated with an oil supply port, at the moment, ultrahigh-pressure fuel in the plunger sequentially passes through the oil supply port and the oil supply pipe to enter an annular oil groove, and a part of the ultrahigh-pressure fuel entering the annular, the transition oil hole and the return orifice enter the control cavity, the other part of the transition oil hole and the return orifice enter the oil containing groove through the transition oil pipe, the transition oil groove and the oil conveying pipe, and the needle valve is at the initial position under the combined action of the pretightening force of the needle valve return spring and the hydraulic pressure in the control cavity.
8. The dual-valve common rail system of the modularized diesel engine with flexibly adjustable fuel injection rule of claim 7, is characterized in that: when the diesel engine needs oil injection, the piezoelectric stack is electrified to extend and push the rotary valve driving block to generate vertical displacement, the vertical displacement of the rotary valve driving block is converted into circumferential displacement of the rotary valve, the left oil groove and the transition oil hole are not on the same plane, ultrahigh pressure fuel oil cannot enter the control cavity through the rotary valve, the control cavity, the oil return throttling hole, the transition oil hole, the right oil groove, the main oil return path, the oil tank interface and the oil tank form a passage, and when the resultant force of the hydraulic pressure applied to the control cavity and the pretightening force of the needle valve reset spring is smaller than the hydraulic pressure applied to the tail end of the needle valve, the needle valve; after the piezoelectric stack is powered off, under the combined action of the elastic force of a reset spring of the piezoelectric stack and the elastic force of a torsion spring, the rotary valve driving block and the piezoelectric stack are restored to the initial state, after the rotary valve is reset, ultrahigh pressure fuel oil enters the control cavity through the rotary valve again, when the pressure in the control cavity reaches a threshold value enabling the needle valve to start to move downwards, the needle valve starts to reset until the needle valve is seated to close the spray hole, and the oil injection process is ended; and then the pressure increasing control valve module is powered off, the port A is communicated with the port T again, the plunger sleeve moves upwards, and when the plunger sleeve moves to the position where the plunger cavity is communicated with the driving cavity, the fuel pressure in the plunger cavity is reduced, so that one working cycle is finished.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110100024.4A CN112761838A (en) | 2021-01-25 | 2021-01-25 | Modular diesel engine double-valve common rail system with flexibly adjustable oil injection rule |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110100024.4A CN112761838A (en) | 2021-01-25 | 2021-01-25 | Modular diesel engine double-valve common rail system with flexibly adjustable oil injection rule |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112761838A true CN112761838A (en) | 2021-05-07 |
Family
ID=75707292
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110100024.4A Pending CN112761838A (en) | 2021-01-25 | 2021-01-25 | Modular diesel engine double-valve common rail system with flexibly adjustable oil injection rule |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112761838A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114165376A (en) * | 2021-12-17 | 2022-03-11 | 中国船舶重工集团公司第七一一研究所 | Fuel injector and fuel injection method |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20020092502A1 (en) * | 2000-11-29 | 2002-07-18 | Horst Harndorf | Pressure controlled injector for injection systems with high pressure collecting area |
| JP2008064108A (en) * | 2004-09-24 | 2008-03-21 | Toyota Motor Corp | Fuel injection device |
| CN101984247A (en) * | 2010-11-04 | 2011-03-09 | 中国第一汽车集团公司 | Pressurizing common-rail oil injection system |
| CN103244324A (en) * | 2013-04-28 | 2013-08-14 | 哈尔滨工程大学 | Piezoelectric electronic-control fuel injector |
| CN107503870A (en) * | 2017-10-10 | 2017-12-22 | 中国第汽车股份有限公司 | Fuel Feeding System for Diesel Engine is united |
| CN109209709A (en) * | 2018-07-26 | 2019-01-15 | 哈尔滨工程大学 | Electric control fuel oil jet system with fluid power compensating piston |
-
2021
- 2021-01-25 CN CN202110100024.4A patent/CN112761838A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20020092502A1 (en) * | 2000-11-29 | 2002-07-18 | Horst Harndorf | Pressure controlled injector for injection systems with high pressure collecting area |
| JP2008064108A (en) * | 2004-09-24 | 2008-03-21 | Toyota Motor Corp | Fuel injection device |
| CN101984247A (en) * | 2010-11-04 | 2011-03-09 | 中国第一汽车集团公司 | Pressurizing common-rail oil injection system |
| CN103244324A (en) * | 2013-04-28 | 2013-08-14 | 哈尔滨工程大学 | Piezoelectric electronic-control fuel injector |
| CN107503870A (en) * | 2017-10-10 | 2017-12-22 | 中国第汽车股份有限公司 | Fuel Feeding System for Diesel Engine is united |
| CN109209709A (en) * | 2018-07-26 | 2019-01-15 | 哈尔滨工程大学 | Electric control fuel oil jet system with fluid power compensating piston |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114165376A (en) * | 2021-12-17 | 2022-03-11 | 中国船舶重工集团公司第七一一研究所 | Fuel injector and fuel injection method |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR100676642B1 (en) | Fuel injection system | |
| CN109578186B (en) | Low oil return high-pressure common rail oil injector | |
| US4550875A (en) | Electromagnetic unit fuel injector with piston assist solenoid actuated control valve | |
| EP1612405B1 (en) | An injection system for an internal-combustion engine | |
| US5720318A (en) | Solenoid actuated miniservo spool valve | |
| CN101535625B (en) | Injector for injecting fuel | |
| JPH07332193A (en) | Fuel injection valve for internal combustion engine | |
| CN1878949A (en) | Injector used to inject fuel into internal combustion chambers in internal combustion engines, particularly, a piezo-actuator controlled common-rail-injector | |
| CN104018964A (en) | Pressure accumulation flow-limiting type piezoelectric control oil sprayer | |
| CN115387944B (en) | Low oil return variable needle valve opening speed electric control oil sprayer | |
| CN114151254B (en) | Piezoelectric direct-drive-pilot double-acting double-needle-valve oil sprayer | |
| EP1612401B1 (en) | An injection system for an internal combustion engine | |
| CN115288902A (en) | Low-oil return amount double-lift-range variable oil injection rule electric control oil injector | |
| CN105201716B (en) | A kind of common-rail injector | |
| CN112761838A (en) | Modular diesel engine double-valve common rail system with flexibly adjustable oil injection rule | |
| CN213063810U (en) | Electric control common rail oil injector with dynamic leakage flow control | |
| US20160230728A1 (en) | Plunger And Fluid-Line System | |
| CN101963119B (en) | Piezoelectric high-pressure common rail electronic control injector | |
| GB2367330A (en) | Common-rail fuel injector | |
| MXPA00012603A (en) | Fuel injector assembly having a combined initial injection. | |
| CN115450811A (en) | Variable oil injection rule electric control oil injector based on needle valve lift adjustment | |
| CN212337508U (en) | High-efficiency electronic control common rail oil injector | |
| MXPA00009987A (en) | Fuel injector assembly having an improved solenoid operated check valve. | |
| CN111237108A (en) | High-pressure common rail oil sprayer for directly controlling opening and closing of oil nozzle | |
| CN113137322A (en) | Novel high-pressure common rail oil sprayer with built-in pressure accumulation chamber |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WD01 | Invention patent application deemed withdrawn after publication | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20210507 |