阅读说明：本技术 高压共轨喷油器的偏位控制阀组件 (Offset control valve assembly of high-pressure common rail oil injector ) 是由 刘义亭 吴小勇 庄福如 沙有胜 鞠得雨 王进 钱音瑶 赵波 李明 于 2020-05-09 设计创作，主要内容包括：一种高压共轨喷油器的偏位控制阀组件,包括执行器、控制阀芯、控制阀座、节流阀、执行弹簧和执行弹簧座,在执行器、控制阀芯、控制阀座、节流阀之间设置了独特的控制油路,能快速地实现对喷油嘴偶件的开启和关闭。采用本发明的控制阀组件就能取消常规喷油器的液力伺服结构,由节流阀直接控制油嘴,提高了响应速度,可实现降低持续期,提高喷射密度的益处；当执行器失电时,节流阀芯被密封在节流阀的端面上,因此高压液体施加在节流阀芯上的力比较小,工作时需要的电磁力较小,可以减小执行器和节流阀芯等零部件的体积,有利于喷油器总成布置；工作时执行器部分的发热量也会减小,可提高喷油器总成工作的可靠性。(A deviation control valve component of a high-pressure common-rail oil sprayer comprises an actuator, a control valve core, a control valve seat, a throttle valve, an execution spring and an execution spring seat, wherein a unique control oil path is arranged among the actuator, the control valve core, the control valve seat and the throttle valve, and the opening and closing of an oil nozzle matching part can be quickly realized. By adopting the control valve assembly, a hydraulic servo structure of a conventional oil sprayer can be cancelled, and the throttle valve directly controls the oil nozzle, so that the response speed is improved, and the benefits of reducing the duration and improving the spray density can be realized; when the actuator is powered off, the throttle valve core is sealed on the end surface of the throttle valve, so that the force applied by high-pressure liquid on the throttle valve core is smaller, the electromagnetic force required during working is smaller, the volumes of the actuator, the throttle valve core and other parts can be reduced, and the fuel injector assembly is favorable for arrangement; the heating value of the actuator part is reduced during working, and the working reliability of the fuel injector assembly can be improved.)

1. An offset control valve component of a high-pressure common rail oil sprayer is characterized in that: the hydraulic control valve comprises an actuator (2), a control valve core (3), a control valve seat (4), a throttle valve (5), an execution spring (8) and an execution spring seat (14), wherein an actuator oil inlet channel (22) and a spring channel (21) are designed on the actuator (2);

a valve core guide hole (41), a comprehensive cavity (42), an oil inlet conical surface (43), an oil through ring groove (44), a valve seat oil inlet channel (45), an inclined oil channel (46), a valve seat upper end surface (47), a valve seat lower end surface (48) and a valve core cavity (49) are designed on a control valve seat (4), the valve core guide hole (41), the oil inlet conical surface (43), the oil through ring groove (44) and the valve core cavity (49) are coaxially arranged, the oil through ring groove (44) is arranged on the valve core guide hole (41), the valve core cavity (49) and the comprehensive cavity (42) are arranged at the upper end and the lower end of the valve core guide hole (41), the oil inlet conical surface (43) is arranged between the comprehensive cavity (42) and the lower end surface of the valve core guide hole (41), the inclined oil path channel (46) is arranged between the valve seat oil inlet channel (45) and the oil through ring groove (44), and the upper end surface (47) and the lower end surface (48) of the valve seat are both planes; the center of the valve core guide hole (41) and the center of the control valve seat (4) are arranged in a staggered manner;

the control valve core (3) comprises a valve core column and an armature disc (30), the valve core column comprises a guide column (31), a middle sealing section (32), an inner concave space (33), an oil storage groove (34), an end face groove (35), a guide rod lower end face (36), an oil storage groove conical surface (37), an axial limiting column (38) and a spring limiting section (39), the middle sealing section (32), the inner concave space (33) and the oil storage groove (34) are all arranged on the guide column (31), the axial limiting column (38) is arranged at the lower end of the guide column (31), the spring limiting section (39) is arranged at the upper end of the guide column (31), the end face groove (35) is arranged at the center of the guide rod lower end face (36), the oil storage groove conical surface (37) is arranged on the lower edge of the oil storage groove (34), the guide post (31) and the middle sealing section (32) of the valve stem are in matching type precise clearance fit with the valve core guide hole (41) of the control valve seat (4); the anchor plate (30) comprises a cover top surface (301) and an anchor plate middle hole (302), the anchor plate middle hole (302) is formed in the center of the cover top surface (301), and the anchor plate (30) is fixedly and integrally connected with the guide column (31) through interference fit of the anchor plate middle hole (302); after the fuel injector assembly is assembled, the top surface (301) of the cover of the armature plate (30) is lower than the upper end surface (47) of the valve seat when the fuel injector assembly is in a working state without injecting fuel, and an opening and closing top gap (15) is formed between the top surface and the upper end surface;

the throttle valve (5) comprises an end face throttling channel (51), a side face throttling channel (52), an end face first inclined channel (53), a valve shoulder side face channel (54), an end face second inclined channel (55), a valve core guide hole (56), a valve core upper end face (57) and a valve core oil storage cavity (58), wherein the end face throttling channel (51), the valve core guide hole (56) and the valve core oil storage cavity (58) are coaxially arranged, the valve core oil storage cavity (58) is arranged between the valve core guide hole (56) and the end face throttling channel (51), the side face throttling channel (52) is communicated with the valve core oil storage cavity (58), the end face first inclined channel (53) is communicated with the valve shoulder side face channel (54), and the valve shoulder side face channel (54) is communicated with a low-pressure oil way; the end face throttling channel (51) is communicated with the comprehensive cavity (42) of the control valve seat (4); the end face first inclined channel (53) is communicated with an end face groove (35) of the control valve core (3);

the connection relation of each part is as follows:

the actuator (2), the execution spring seat (14) and the execution spring (8) are sequentially sleeved on a spring limiting section (39) of the control valve core (3), the control valve core (3) is sleeved in a valve core guide hole (41) of the control valve seat (4) through a guide post (31), and the armature plate (30) is fixedly and integrally connected with the guide post (31) through interference fit of an armature plate middle hole (302); the actuator (2) is arranged on the upper end face (47) of the valve seat of the control valve seat (4), the actuator spring seat (14) and the actuator spring (8) are sleeved in the spring channel (21), the actuator oil inlet channel (22) is aligned with the valve seat oil inlet channel (45), the throttle valve (5) is in butt joint with the lower end face (48) of the valve seat of the control valve seat (4), it is guaranteed that the first inclined channel (53) of the end face of the throttle valve (5) is communicated with the end face groove (35), the second inclined channel (55) of the end face is communicated with the valve seat oil inlet channel (45), in a free state, the cover top face (301) of the armature plate (30) is lower than the upper end face (47) of the valve seat, and an opening-closing top gap (; an eccentricity exists between the central axis of the throttle valve (5) and the central axis of the valve core guide hole (41).

2. The offset control valve assembly of the high pressure common rail injector of claim 1, wherein: the lower section of the control valve core (3) is an axial limiting column (38), and the diameter of the axial limiting column (38) is larger than that of the valve core guide hole (41).

The technical field is as follows:

the invention relates to a quick response common rail injector of a diesel engine, in particular to an offset control valve assembly in the injector.

Background art:

in the working process of a common rail fuel injector assembly of a diesel engine, a fuel injector receives a fuel injection starting pulse signal, and a certain delay time is needed to elapse until the fuel injector realizes fuel injection, wherein the delay time is called as opening delay time; receiving an injection closing pulse signal from the oil injector, and ending a certain delay time until the injection is closed, wherein the delay time is called closing delay time; the shorter the opening delay and the closing delay time is, the faster the response of the fuel injector is, and the faster the response of the fuel injector is, the better the working stability of the fuel injector is, the higher the engine speed adapted to the fuel injector assembly is, and the higher the power density of the engine is. In order to control the injection duration of the fuel injector assembly, the current general control valve is provided with a servo mechanism, an oil inlet and outlet metering orifice is arranged in the servo mechanism, and the control of the rail pressure in the servo mechanism is realized by utilizing the flow difference of the oil inlet and outlet metering orifices, so that the control of the response time is realized.

To reduce the duration, it is necessary to reduce the opening or closing delay during injection of the injector assembly, if possible, both. The existing electronic control high-pressure common rail oil injector generally adopts a control valve to control the liquid pressure of a control valve high-pressure cavity by adopting a switch of the control valve, realizes the control on the opening and closing of injection by utilizing the stress balance of the control valve high-pressure cavity and a nozzle tip high-pressure cavity, and controls the liquid pressure of the control valve high-pressure cavity by respectively arranging an oil inlet and outlet metering orifice on the control valve and utilizing the flow change of the oil inlet and outlet metering orifice. The existing control valve scheme has the defects that on the premise that the volume of a high-pressure cavity of a control cavity valve is not changed, in order to reduce the opening delay, the flow difference of an oil inlet metering hole and an oil outlet metering hole can only be increased, but in this way, the closing delay is increased; similarly, to reduce the closing delay, only the flow difference between the inlet and outlet orifices can be reduced, but this results in an increase in the opening delay. That is, current control valve solutions, in order to reduce the duration, have a hyperbolic effect on the effect of opening delay and closing delay, with the ultimate practical effect being limited, if the flow difference between the inlet and outlet orifices is matched by parameters.

In order to overcome the defects in the prior art, the invention provides the high-pressure common-rail quick response oil injector controlled in the axial dislocation mode, so that the response time of the oil injector assembly in the working process is shortened, and the response speed is improved. The core technology is a control valve assembly.

The invention content is as follows:

the invention aims to provide an offset control valve component of a high-pressure common rail oil sprayer, which is a core component of the high-pressure common rail quick response oil sprayer controlled in an axial dislocation way.

The technical scheme adopted by the invention is as follows:

an offset control valve component of a high-pressure common rail oil sprayer is characterized in that: the hydraulic control system comprises an actuator, a control valve core, a control valve seat, a throttle valve, an execution spring and an execution spring seat, wherein an actuator oil inlet channel and a spring channel are designed on the actuator;

the control valve seat is provided with a valve core guide hole, a comprehensive containing cavity, an oil inlet conical surface, an oil through ring groove, a valve seat oil inlet channel, an inclined oil channel, a valve seat upper end surface, a valve seat lower end surface and a valve core cavity, wherein the valve core guide hole, the oil inlet conical surface, the oil through ring groove and the valve core cavity are coaxially arranged; the center of the valve core guide hole and the center of the control valve seat are arranged in a staggered manner;

the control valve core comprises a valve core column and an armature disc, the valve core column comprises a guide post, a middle sealing section, an inwards concave space, an oil storage groove, an end face groove, a guide rod lower end face, an oil storage groove conical surface, an axial limiting post and a spring limiting section, the middle sealing section, the inwards concave space and the oil storage groove are all arranged on the guide post, the axial limiting post is arranged at the lower end of the guide post, the spring limiting section is arranged at the upper end of the guide post, the end face groove is arranged at the center of the guide rod lower end face, the oil storage groove conical surface is arranged at the lower edge of the oil storage groove, and coupling precision clearance fit relations are respectively arranged between the guide post and the middle sealing section of the valve core column and a valve core guide hole of the control valve; the armature plate comprises a cover top surface and an armature plate middle hole, the armature plate middle hole is arranged in the center of the cover top surface, and the armature plate is fixedly and integrally connected with the guide column through interference fit of the armature plate middle hole and the guide column; after the oil injector assembly is assembled, the top surface of the armature plate is lower than the upper end surface of the valve seat when the oil injector assembly is in a working state without oil injection, and an opening and closing top gap is formed between the top surface of the armature plate and the upper end surface of the valve seat;

the throttle valve comprises an end face throttling channel, a side face throttling channel, an end face first inclined channel, a valve shoulder side surface channel, an end face second inclined channel, a valve core guide hole, a valve core upper end face and a valve core oil storage cavity, wherein the end face throttling channel, the valve core guide hole and the valve core oil storage cavity are coaxially arranged; the end face throttling channel is communicated with the comprehensive cavity of the control valve seat; the end face first inclined channel is communicated with the end face groove of the control valve core.

The connection relation of each part is as follows:

the actuator, the execution spring seat and the execution spring are sequentially sleeved on the spring limiting section of the control valve core, the control valve core is sleeved in a valve core guide hole of the control valve seat through a guide post, and the armature plate is fixedly and integrally connected with the guide post through interference fit of a middle hole of the armature plate and the guide post; the actuator is arranged on the upper end face of the valve seat of the control valve seat, the actuator spring seat and the actuator spring are sleeved in the spring channel, the oil inlet channel of the actuator is aligned with the oil inlet channel of the valve seat, the throttling valve is butted with the lower end face of the valve seat of the control valve seat, the first inclined channel of the end face of the throttling valve is ensured to be communicated with the end face groove, the second inclined channel of the end face is communicated with the oil inlet channel of the valve seat, the top face of the armature plate is lower than the upper end face of the valve seat in a free state, and; an eccentricity exists between the central axis of the throttle valve and the central axis of the valve core guide hole.

Further, the lower section of the control valve core is an axial limiting column, and the diameter of the axial limiting column is larger than that of the valve core guide hole.

The invention has the following beneficial effects:

the high-pressure common rail oil sprayer can cancel a hydraulic servo structure of a conventional oil sprayer by adopting the control valve component, and the oil nozzle is directly controlled by the throttle valve, so that the response speed is improved, and the benefits of reducing the duration and improving the spray density can be realized; when the actuator is de-energized, the throttle valve core is sealed on the end surface of the throttle valve, so that the force applied by high-pressure liquid on the throttle valve core is smaller, and the electromagnetic force required during the operation can be smaller, so that the volumes of parts such as the actuator and the throttle valve core can be reduced, and the arrangement of an oil injector assembly is facilitated; in addition, because the required electromagnetic force is smaller, the heat productivity of the actuator part is also reduced during the operation, and the operation reliability of the fuel injector assembly can be improved; the structural design of the plane seal of the throttle valve core and the throttle valve can flexibly realize the flexible control of the oil injection rule waveform by changing the area of the seal ring belt in the performance development process of the oil injector assembly, and expand the application range of the oil injector assembly;

experiments can prove that the scheme has excellent technical effect compared with the prior art.

FIG. 15 is a waveform diagram of a drive signal and injection rate for a conventional fuel injector;

FIG. 16 is a waveform of drive signal and injection rate waveforms for two injectors with the same nozzle tip mating flow. In the figure, the abscissa represents time (unit: ms), and the ordinate represents the drive current value (unit: A) and the injection rate value (unit: mm3/ms), respectively. In both figures, there are 4 sets of curves, where B1 is the injection rate curve; b2 is the drive current curve; b3 is the starting point of the oil injection speed waveform; b4 is the end of the injection rate waveform, and the injection duration Tc is T4-T3.

In this test, the test conditions were: the fixed injection pressure is 160MPa, the peak value of the driving current is 10A, the maintaining current is 5A, and the oil injection quantity is 440mm 3.

The conventional injector shown in fig. 15 has a duration of 2.85ms, whereas the injector shown in fig. 16, which uses the present invention, has a duration of 2.4 ms. By comparing fig. 15 and fig. 16, it can be found that the height of the injection rate curve of the injector obtained by the present invention is significantly higher under the conditions of the same injection pressure, the same driving current and the same injection quantity, which indicates that the injection rate density is greater, and the injection duration is reduced by 0.45ms compared with the conventional injector, which accounts for 16.79%, and has a very significant improvement advantage in power density.

Description of the drawings:

FIG. 1 is a schematic structural view of the present invention;

FIG. 2 is a schematic view of the connection of the injector body;

FIG. 3 is a schematic structural diagram of an actuator;

FIG. 4 is a schematic structural diagram of a control valve core;

FIG. 5 is a schematic view of the construction of an armature plate;

FIG. 6 is a schematic view of the assembled structure of the armature plate and the control valve core;

FIG. 7 is a schematic view of a control valve seat;

FIG. 8 is a schematic view of an assembly structure of the control valve core and the control valve seat;

FIG. 9 is a schematic view of the throttle valve;

FIG. 10 is a schematic view of an assembled structure of the needle valve and the needle valve body;

FIG. 11 is a schematic structural view of a needle valve body;

FIG. 12 is a schematic view of a needle valve;

FIG. 13 is an enlarged sectional view showing the structure at A-A in FIG. 10 (oil feed groove structure);

FIG. 14 is a cross-sectional enlarged structural view (oil feed plan structure) of the structure at A-A in FIG. 10;

FIG. 15 is a waveform diagram of a conventional fuel injector;

FIG. 16 is a waveform of a fuel injector according to the present invention.

In the figure: 1-an injector body; 2-an actuator; 3-control the valve core; 4-control valve seat; 5-a throttle valve; 6-needle valve body; 7-needle valves; 8-an actuating spring; 9-fastening caps; 10-a nipple spring; 11-glib spring seat; 12-a main oil gallery; 13-high pressure oil through passage; 14-implement spring seat; 15-opening and closing the top gap; 21-a spring channel; 22-an actuator oil inlet channel; 30-armature plate; 31-a guide post; 32-a middle seal section; 33-concave space; 34-an oil storage groove; 35-end face grooves; 36-lower end surface of guide rod; 37-conical surface of oil storage groove; 38-axial restraint posts; 39-spring limit section; 41-valve core guide hole; 42-a comprehensive cavity; 43-oil inlet conical surface; 44-oil through ring groove; 45-valve seat oil inlet channel; 46-inclined oil passage; 47-valve seat upper end surface; 48-lower end surface of valve seat; 49-spool chamber; 51-end face throttling channel; 52-side throttling channel; 53-end face first inclined channel; 54-valve shoulder side passage; 55-end face second inclined channel; 56-spool pilot hole; 57-the upper end surface of the valve core; 58-valve core oil storage cavity; 61-upper oil storage cavity; 62-valve needle guide holes; 63-an intermediate oil storage cavity; 64-a lower oil storage cavity; 71-an upper guide bar; 72-an oil inlet guide section; 73-lower rod body; 74-axial oil feed structure; 75-an axial limit surface; 301-top surface of lid, 302-middle hole of armature plate.

The specific implementation mode is as follows:

the following description of the embodiments of the invention is provided by way of example in conjunction with the accompanying drawings: