CN100510383C - Pump nozzle oil supply system and method thereof - Google Patents

Abstract

The present invention discloses one kind of oil supplying pump-oil nozzle system and method. The oil supplying pump-oil nozzle system has one first oil path and one second oil path connected to the hydraulic oil source system to provide back flow high pressure oil, one third oil path communicated to the oil passage inside the plunger sleeve, one two-position three-way solenoid valve connected to the first oil path, the second oil path and the third oil path, one first plunger inside the plunger sleeve, one jib with roller, one push rod hinged to one rocking arm, one second plunger connected to one oil injector and other parts. The oil supplying pump-oil nozzle system in the technological scheme of the present invention has no rotating part for driving pump-oil nozzle to spray oil and stable oil injecting pressure under different engine operation modes.

Description

A kind of pump nozzle oil supply system and method

Technical field

The present invention relates to technical field of engines, relate in particular to a kind of pump nozzle oil supply system and method.

Background technique

Traditional pump nozzle oil supply system is that engine crankshaft rotates the Injection Pump work that promotes by the cam on the fuel cam axle of a pair of fuel injection timing gear drive.In the oil supply system of this structure, oil spout is to guarantee by the cam profile on timing gear and the camshaft constantly, and fuel injection characteristic guarantees that by cam profile fuel injection quantity is to be determined by the position of plunger pull bar drive plunger skewed slot in the Injection Pump.

Hydraulic free-piston engine is a kind of novel engine that stroke piston combustion engine and pluger type hydraulic pump are become one.This motor is that the to-and-fro motion with piston can drive loaded work piece by being converted into hydraulic pressure with the rigidly connected hydraulic plunger of piston.Be with traditional crank engine main difference point structurally: this motor has not had connecting rod, has not promptly had rotating machinery.Owing to there has not been rotating machinery, the driving of the oil supply system of this kind motor is if adopt the pump nozzle arrangements of the camshaft actuated of conventional engines to be difficult to then realize that the oil supply system that therefore needs a kind of non-rotating mechanism to drive realizes the fuel delivery of hydraulic free-piston engine.

Summary of the invention

The objective of the invention is to propose a kind of pump nozzle oil supply system and method, can be under the situation of not using rotary component driven pump nozzle fuel feeding, and can guarantee that motor injection pressure under various operating modes is stable.

For reaching this purpose, the present invention by the following technical solutions:

A kind of pump nozzle oil supply system; Be applicable to hydraulic free-piston engine; Comprise first oil duct 12; Second oil duct 15; Two-bit triplet magnetic valve 2; The 3rd oil duct 13; Plunger cover 4; First plunger 3; Tappet 6; Push rod 7; Rocking arm 8; Second plunger 9; Return spring 10 and fuel injector 11; One end of described first oil duct is communicated with the hydraulic oil source system 1 of described hydraulic free-piston engine; Be used for providing hydraulic oil; One end of described second oil duct is communicated with the hydraulic oil source system 1 of described hydraulic free-piston engine; Be used for the backflow hydraulic oil; Described two-bit triplet magnetic valve and described plunger cover are installed on the body 14 of described hydraulic free-piston engine; Two openings of described two-bit triplet magnetic valve respectively with described first oil duct; The other end of second oil duct connects; Another opening of described two-bit triplet magnetic valve is connected with an end of described the 3rd oil duct; The other end of described the 3rd oil duct is communicated with asphalt channel in the described plunger cover; Described first plunger is installed in the described plunger cover; The roller of the corresponding described tappet of one end of described first plunger; The lower end of described push rod is placed in the described tappet; The upper end of described push rod by hinge be connected rocking arm one end and connect; The described rocking arm other end connects the upper end of described second plunger; The lower end of described second plunger is connecting described fuel injector, is covered with described return spring at described second plunger.

Also comprise clearance adjusting screw 16, described clearance adjusting screw is positioned on the described push rod, is used to adjust the length of described push rod.

Described first plunger and described second plunger are the T type, and the upper end diameter of section is bigger than the lower end.

The diameter of described first plunger and the pass between the high pressure oil pressure that provides, return spring power and the oil sprayer injection pressure be $\frac{{\mathrm{\&pi;<figure-callout\; id="2"\; label="d"\; filenames="C200710175744E00101.png"\; state="\{\{state\}\}">d</figure-callout>}}^2}{4}\&CenterDot;P={\mathrm{<figure-callout\; id="1"\; label="F"\; filenames="C200710175744E00101.png"\; state="\{\{state\}\}">F</figure-callout>}}_1+{\mathrm{<figure-callout\; id="2"\; label="F"\; filenames="C200710175744E00101.png"\; state="\{\{state\}\}">F</figure-callout>}}_2,$ Wherein, d represents first plunger diameter, and P represents high pressure oil pressure, F ₁Expression return spring power, F ₂Expression oil sprayer injection pressure;

The length of described first plunger and the second plunger range, promptly the pass between largest loop fuel injection quantity and the guiding needed height is $Q_{\max }=\frac{{\mathrm{\&pi;<figure-callout\; id="2"\; label="D"\; filenames="C200710175744E00101.png"\; state="\{\{state\}\}">D</figure-callout>}}^2}{4}\&CenterDot;s\&CenterDot;\mathrm{\&lambda;},$ L 〉=1.5d, wherein Q _MaxExpression largest loop fuel injection quantity, D represents second plunger diameter, the required minimum length of the normal guiding of 1 expression, second plunger, s represents first plunger stroke, and λ represents the rocking arm ratio, and h=s λ represents the second plunger range, d represents first plunger diameter, and then first plungers length is max{s, l};

Described the 3rd oil duct flow is not less than the flow of described two-bit triplet solenoid valve.

Described two-bit triplet solenoid valve and described plunger bushing are installed on the body by screw thread.

Plunger bushing is a tubular structure, endoporus is to cooperate periphery with plunger, the outside is the ladder axis structure, outside thread is arranged at the top that external diameter is bigger, and with interior hole circle is positive six side's pits in incircle is provided with, be convenient to spanner binding thread is installed, corresponding positions is equipped with internal thread on the body, and plunger bushing is installed on the body by screw thread.

A kind of pump nozzle fuel supply method may further comprise the steps:

A, two-bit triplet solenoid valve get electric opening;

B, high pressure oil enter plunger bushing by the two-bit triplet solenoid valve through first oil duct;

C, high pressure oil promote first plunger and move upward along plunger bushing;

D, first plunger promote tappet and move upward, and tappet drives push rod and moves upward;

E, push rod promote rocking arm and clockwise rotate around its axis, and the rocking arm the other end moves downward;

F, rocking arm promote the second plunger actuation oil sprayer to fuel oil pressurization and ejection, and the return spring that is enclosed within second plunger is compressed;

G, two-bit triplet solenoid valve dead electricity, plunger bushing inner high voltage oil is back to fuel tank by the two-bit triplet solenoid valve through second oil duct;

H, return spring stretch and drive the second plunger return, and rocking arm rotates counterclockwise around its axis;

I, under the drive of rocking arm, push rod, tappet and the first plunger resile.

Adjust screw by the adjusting play, there is pre compressed magnitude in return spring under the feasible installation original state.

Adopted technological scheme of the present invention, come the driven pump nozzle oil supply system by electronic control hydraulic pressure, can avoid rotary component, this is very practical for the motor that does not have rotating machinery, and, therefore can guarantee that motor injection pressure under various operating modes is constant because the rotating speed of injection pressure and motor is irrelevant.

Description of drawings

Fig. 1 is the schematic diagram of pump nozzle oil supply system in the specific embodiment of the invention;

Fig. 2 is the structural representation of pump nozzle oil supply system in the specific embodiment of the invention.

Embodiment

Further specify technological scheme of the present invention below in conjunction with accompanying drawing and by embodiment.

Overall thought of the present invention is: utilize hydraulic coupling to drive the effect that the motion of hydraulic plunger in plunger bushing replaces cam drive power, utilize the electronically controlled opening and closing that are connected on the two-bit triplet solenoid valve in the oil hydraulic circuit to replace the timing and the phase place of cam constantly, utilize length current"on"time of controlling the two-bit triplet solenoid valve to control the fuel delivery of oil sprayer.

Fig. 1 is the schematic diagram of pump nozzle oil supply system in the specific embodiment of the invention.As shown in Figure 1, hydraulic oil source system 1 can be produced by the hydraulic pressure that hydraulic free-piston engine sends, and two-bit triplet solenoid valve 2 is connected in the oil duct.When engine piston motion when needing the position of oil spout, give the energising of two-bit triplet solenoid valve, make a, b termination lead to, high pressure oil enters in the plunger bushing 4 by the ab passage, the elastic force that will overcome return spring 10 at the promotion lower plunger 3 of high pressure oil moves upward, promote tappet 6, move upward, tappet promotes push rod 7 and moves upward, and push rod moves upward and makes rocking arm 8 clockwise rotate compression retracteding position spring, injection pump plunger 9 is moved down fast, to the fuel oil pressurization, the high pressure fuel after the pressurization sprays into cylinder by oil sprayer 11.

When two-bit triplet solenoid valve dead electricity, the b of solenoid valve, c two ends are connected, and high pressure oil flow back into fuel tank by the bc passage, and injection pump plunger is return under the effect of return spring, and oil sprayer stops oil spout, and injection process finishes, and finish oil spout action.The control of fuel injection quantity can realize that current"on"time is long more by the current"on"time that changes the two-bit triplet solenoid valve in this system, and fuel injection quantity is many more.

Fig. 2 is the structural representation of pump nozzle oil supply system in the specific embodiment of the invention.As shown in Figure 2, two-bit triplet solenoid valve 2 is series at height and is pressed into oil duct 12, the fuel-displaced oil duct of low pressure 15 corresponding positions, be anchored on by the mode that is threaded on the body 14 of hydraulic free-piston engine, this two-bit triplet solenoid valve is fast big flow solenoid valve, response time is not more than 3 milliseconds, and flow is not less than 20 liters of per minutes.Height is pressed into oil duct 12, the fuel-displaced oil duct 15 of low pressure is arranged in corresponding position on the body by the mode of boring, the diameter that height is pressed into oil duct 12 depends on that oil sprayer goes out oil pressure, return spring power and push rod spring power, height is pressed into the oil duct diameter should be greater than solenoid valve oil duct diameter, prevent to produce throttling action, influence the ageing of oil spout, the while height is pressed into the oil duct diameter can not be too big, can produce bigger volume effect, equally also can influence the ageing of oil spout, the diameter of the fuel-displaced oil duct of low pressure should be pressed into oily oil duct greater than height.Process the flow that depends on used solenoid valve at the diameter of the oil duct 13 of internal body in addition, promptly the oil duct flow is not less than the solenoid valve flow.

Plunger bushing 4 is installed on the body by screw thread, plunger bushing is a tubular structure, endoporus is that highi degree of accuracy cooperates periphery with plunger, the outside is the ladder axis structure, and the top that external diameter is bigger processes outside thread, and is positive six side's pits in the incircle processing with interior hole circle, be convenient to binding thread is installed with spanner, erection column plug sleeve relevant position processes internal thread on the body, and plunger bushing is installed on the body by screw thread, and the plunger bushing axial position can be by the spacer thickness adjustment on the plunger bushing bottom plane.

Asphalt channel connects by the oil duct 13 of processing at internal body in two-bit triplet solenoid valve asphalt channel and the plunger bushing, the plunger bushing position should be corresponding with the roller of tappet 6, plunger 3 is installed in the plunger bushing 4 by Spielpassung, the diameter of plunger 3 and the pass between the high pressure oil pressure that provides, return spring power and the oil sprayer injection pressure be $\frac{{\mathrm{\&pi;<figure-callout\; id="2"\; label="d"\; filenames="C200710175744E00101.png"\; state="\{\{state\}\}">d</figure-callout>}}^2}{4}\&CenterDot;P={\mathrm{<figure-callout\; id="1"\; label="F"\; filenames="C200710175744E00101.png"\; state="\{\{state\}\}">F</figure-callout>}}_1+{\mathrm{<figure-callout\; id="2"\; label="F"\; filenames="C200710175744E00101.png"\; state="\{\{state\}\}">F</figure-callout>}}_2,$ Wherein, d represents plunger 3 diameters, and P represents high pressure oil pressure, F ₁Expression return spring power, F ₂Expression oil sprayer injection pressure.

Plunger 3 length determine according to injection pump plunger 9 ranges and guiding needed height, the length of plunger 3 and injection pump plunger 9 ranges, and promptly the pass between largest loop fuel injection quantity and the guiding needed height is $Q_{\max }=\frac{{\mathrm{\&pi;<figure-callout\; id="2"\; label="D"\; filenames="C200710175744E00101.png"\; state="\{\{state\}\}">D</figure-callout>}}^2}{4}\&CenterDot;s\&CenterDot;\mathrm{\&lambda;};$ L 〉=1.5d, wherein Q _MaxExpression largest loop fuel injection quantity, D represents injection pump plunger 9 diameters, the required minimum length of the normal guiding of 1 expression plunger, s represents plunger 3 strokes, and λ represents the rocking arm ratio, and h=s λ represents injection pump plunger 9 ranges, d represents plunger diameter, and then plungers length is max{s, l}.

The plunger head diameter is big than the plunger bottom, be convenient to contact transmission power with tappet roller, adjust screw 16 by the adjusting play, make that original state is installed guarantees that return spring has certain pre compressed magnitude, push rod 7 lower ends are positioned in the tappet, and the upper end links to each other with rocking arm 8 hinges by clearance adjusting screw, and the rocking arm the other end is pressed on the injection pump plunger 9, the upper end diameter of injection pump plunger is bigger, and return spring is fastened between the projection and oil sprayer 11 of injection pump plunger.

Electronic control fluid clutch nozzle system comprises in the concrete implementation step on the hydraulic free-piston engine: when engine piston motion when needing the position of oil spout, two-bit triplet solenoid valve 2 gets electric opening, height is pressed into conducting between oil duct 12 and the two-bit triplet solenoid valve asphalt channel, high pressure oil is pressed into oil duct 12 through height and enters in the plunger bushing 4 by the two-bit triplet solenoid valve oil duct 13 of flowing through, high pressure oil promotes plunger 3 and moves upward along the elastic force that plunger bushing 4 overcomes return spring 10, plunger 3 promotes tappet 6 and moves upward, tappet drives push rod 7 and moves upward, under the effect of push rod; rocking arm 8 clockwise rotates around its axis; make the rocking arm right-hand member move downward; promotion injection pump plunger 9 moves downward to fuel oil and pressurizes; through oil sprayer 11, the ejection high pressure oil.When piston motion during to the needs end of injection, two-bit triplet solenoid valve dead electricity, conducting between fuel-displaced oil duct 15 of low pressure and the two-bit triplet solenoid valve asphalt channel, then the high pressure oil in the plunger bushing flows back to fuel tank by the two-bit triplet solenoid valve through the fuel-displaced oil duct 15 of low pressure, the instantaneous reduction of pressure, injection pump plunger begins return under the effect of return spring, oil sprayer stops oil spout; rocking arm rotates counterclockwise around its axis; under the drive of rocking arm; push rod, tappet and plunger resile, finishes the action of an oil spout, realizes fuel feeding.

The above; only for the preferable embodiment of the present invention, but protection scope of the present invention is not limited thereto, and anyly is familiar with the people of this technology in the disclosed technical scope of the present invention; the variation that can expect easily or replacement all should be encompassed within protection scope of the present invention.Therefore, protection scope of the present invention should be as the criterion with the protection domain of claim.

Claims (8)

1; A kind of pump nozzle oil supply system; Be applicable to hydraulic free-piston engine; It is characterized in that; Comprise first oil duct (12); Second oil duct (15); Two-bit triplet magnetic valve (2); The 3rd oil duct (13); Plunger cover (4); First plunger (3); Tappet (6); Push rod (7); Rocking arm (8); Second plunger (9); Return spring (10) and fuel injector (11); One end of described first oil duct is communicated with the hydraulic oil source system (1) of described hydraulic free-piston engine; Be used for providing hydraulic oil; One end of described second oil duct is communicated with the hydraulic oil source system (1) of described hydraulic free-piston engine; Be used for the backflow hydraulic oil; Described two-bit triplet magnetic valve and described plunger cover are installed on the body (14) of described hydraulic free-piston engine; Two openings of described two-bit triplet magnetic valve respectively with described first oil duct; The other end of second oil duct connects; Another opening of described two-bit triplet magnetic valve is connected with an end of described the 3rd oil duct; The other end of described the 3rd oil duct is communicated with asphalt channel in the described plunger cover; Described first plunger is installed in the described plunger cover; The roller of the corresponding described tappet of one end of described first plunger; The lower end of described push rod is placed in the described tappet; The upper end of described push rod by hinge be connected rocking arm one end and connect; The described rocking arm other end connects the upper end of described second plunger; The lower end of described second plunger is connecting described fuel injector, is covered with described return spring at described second plunger.

2, a kind of pump nozzle oil supply system according to claim 1 is characterized in that, also comprises clearance adjusting screw (16), and described clearance adjusting screw is positioned on the described push rod, is used to adjust the length of described push rod.

3, a kind of pump nozzle oil supply system according to claim 1 is characterized in that, described first plunger and described second plunger are the T type, and the upper end diameter of section is bigger than the lower end.

4, a kind of pump nozzle oil supply system according to claim 1 is characterized in that, the diameter of described first plunger and the pass between the high pressure oil pressure that provides, return spring power and the oil sprayer injection pressure be $\frac{\mathrm{\&pi;}{d}^2}{4}\&CenterDot;P=F_1+F_2,$ Wherein, d represents first plunger diameter, and P represents high pressure oil pressure, F ₁Expression return spring power, F ₂Expression oil sprayer injection pressure;

The length of described first plunger and the second plunger range, promptly the pass between largest loop fuel injection quantity and the guiding needed height is $Q_{\max }=\frac{\mathrm{\&pi;}{D}^2}{4}\&CenterDot;s\&CenterDot;\mathrm{\&lambda;},$ L 〉=1.5d, wherein Q _MaxExpression largest loop fuel injection quantity, D represents second plunger diameter, l represents the required minimum length of the normal guiding of first plunger, s represents first plunger stroke, and λ represents the rocking arm ratio, and h=s λ represents the second plunger range, d represents first plunger diameter, and then first plungers length is max{s, l};

Described the 3rd oil duct flow is not less than the flow of described two-bit triplet solenoid valve.

5, a kind of pump nozzle oil supply system according to claim 1 is characterized in that, described two-bit triplet solenoid valve and described plunger bushing are installed on the body by screw thread.

6, a kind of pump nozzle oil supply system according to claim 5, it is characterized in that, described plunger bushing is a tubular structure, endoporus is to cooperate periphery with plunger, and the outside is the ladder axis structure, and outside thread is arranged at the top that external diameter is bigger, and with interior hole circle is positive six side's pits in incircle is provided with, be convenient to spanner binding thread is installed, corresponding positions is equipped with internal thread on the body, and plunger bushing is installed on the body by screw thread.

7, a kind of pump nozzle fuel supply method is characterized in that, may further comprise the steps:

A, two-bit triplet solenoid valve get electric opening;

B, high pressure oil enter plunger bushing by the two-bit triplet solenoid valve through first oil duct;

C, high pressure oil promote first plunger and move upward along plunger bushing;

D, first plunger promote tappet and move upward, and tappet drives push rod and moves upward;

E, push rod promote rocking arm and clockwise rotate around its axis, and the rocking arm the other end moves downward;

F, rocking arm promote the second plunger actuation oil sprayer to fuel oil pressurization and ejection, and the return spring that is enclosed within second plunger is compressed;

G, two-bit triplet solenoid valve dead electricity, plunger bushing inner high voltage oil is back to fuel tank by the two-bit triplet solenoid valve through second oil duct;

H, return spring stretch and drive the second plunger return, and rocking arm rotates counterclockwise around its axis;

I, under the drive of rocking arm, push rod, tappet and the first plunger resile.

8, a kind of pump nozzle fuel supply method according to claim 7 is characterized in that, adjusts screw by the adjusting play, and there is pre compressed magnitude in return spring under the feasible installation original state.

Images