DE112015004242T5 - Liquid jet metering unit and its control method - Google Patents

Abstract

A liquid jet metering unit and its control method, wherein the liquid jet metering unit comprises a jet unit and a metering controller (13), and wherein the jet unit comprises a scroll tube device (18), a plunger pump (8), and a nozzle (23), and wherein the spiral tube device (18) comprises Coil (19), a yoke (20) and a magnetoresistance comprises, and wherein the plunger pump comprises a plunger (12) and a sleeve (11), and wherein the plunger (12) with the sleeve (11) cooperates to a pressure delivery volume (9), and wherein the pressure delivery volume is connected to a liquid inlet valve (16) and a liquid outlet valve (17), and wherein the dosing control device (13) provides a drive signal to the spiral tube device (18), and wherein the dosing control device (13) comprises a Detection device for monitoring the state parameters includes, and wherein the control method an algorithm for egg estimating the effective output power of the scroll tube device (18) by means of the state parameters, and wherein the method further comprises a method of closedly controlling the flow rate of the liquid jet metering unit using the effective output of the scroll tube device (18) as a variable, and wherein the effective Output power of the spiral tube device (18) is the energy required to directly exert a pressure on the liquid in the pressure delivery volume (9) and form a jet. The dosing unit and its control method have a large field of application and high control accuracy.

Description

Field of the invention

The present invention relates to the technical field of metering of the liquid, particularly to the engine fluid jet metering technique, and more particularly to an engine fuel blasting apparatus, engine exhaust gas purification selective catalytic reduction (SCR) system, diesel engine exhaust gas particulate filter manifold (DPF) fuel jet regeneration system and its control technique.

State of the art

Liquid jet metering has a wide range of uses in the chemical, medical, and engine sectors and other fields, and more particularly, liquid jet metering involves several core techniques of combustion drive power.

With the environmental issues becoming more conspicuous, saving energy and reducing emissions has become a major issue in the engine industry. Many countries have been consistently releasing a series of emission standards for the engines and vehicles, for which the internal combustion engine driven vehicles require better combustion control and, moreover, an emissions treatment system is to be arranged to meet increasingly stringent emission requirements. For example, like the vehicle engine, the engine including the spark ignited small engine also uses the electrically controlled fuel spray technique and the 3-way catalyst technology of the exhaust gas; In order to reduce the harmful impurities in the exhaust gas, the direct injection diesel engine or lean-burn gasoline engine uses a selective catalytic reduction (SCR) technique of NOx in an oxygen-rich environment a treatment of the catalytic reduction is carried out; With respect to the particulate emission of the diesel engine, a Diesel Particulate Filter (DPF) particulate filter collector and other technology are used.

All such techniques address the problem with liquid jet metering control. With respect to fuel jet technology, jet metering and feedback as well as fuel jet quantity control are needed; with regard to the DPF regeneration technique, a jet metering is required for the amount of diesel oil injected at the DPF upper-outlet outlet pipe in a nebulising manner; With regard to the SCR technique, metering blasting of the selective reductant of NOx at the headwaters of the SCR catalyst is required, e.g. B. aqueous solution of urea of 32.5% by weight (also referred to as diesel exhaust gas treatment fluid (DEF = Diesel Exhaust Fluid) or AdBlue.

After DEF enters the exhaust pipe of the engine, the exhaust gas is decomposed by the exhaust gas high temperature to the ammonia, which is mixed with the exhaust gas and then enters the SCR catalytic converter. Under the action of the catalyst, the ammonia will have a catalytic reduction reaction with NOx, etc. in the exhaust gas of the engine, so that NOx is decomposed into the harmless N2 and H2O. If the DEF jet quantity does not correspond to the NO x content in the exhaust gas, NO x can not be completely reductively decomposed, so that the emission is increased, or some residual ammonia is released into the atmosphere, causing secondary pollution. Because of this, the SCR system inevitably requires an SCR metering jet device with higher accuracy.

With respect to the SCR jet metering system, since the urea aqueous solution has conductivity and the conventional jet metering system driven by the DC electric pump can not submerge in the working liquid, the prior art usually uses an external diaphragm pump driven by the DC motor the system has a complicated structure, besides the reliability, the system is further relatively affected by the environment, in particular, a complicated thawing device is required for operation in a low-temperature environment, moreover, service and maintenance are relatively difficult.

In the engine field, the fluid jet metering technique includes, but is not limited to, the engine's electronic fuel-jet system including in-cylinder direct injection (GDI) and off-cylinder (MPI) injection, a urea-aqueous solution jet system selective catalytic reduction (SCR) of the nitrogen oxide of the exhaust gas purification of the engine and a regeneration fuel jet system of the exhaust emission particle filtration (DPF) of the diesel engine.

The American patent US20090301067A1 discloses a DEF jet metering apparatus using a plunger-sleeve structure.

The Dosierstrahlvorrichtung is driven by a spiral tube Plunger pump nozzle, which is installed on the exhaust pipe, a low pressure pump is to be added, which provides the device, the working fluid from the DEF liquid container available, moreover, a cooling measure to be taken in order to implement a normal operation.

With respect to the blasting of the DPF regeneration fuel, the blasted diesel oil should be well atomized to improve the combustion efficiency so that with a minimum fuel consumption, a highest DPF temperature is achieved to realize the target of burning the collected particulates such as coal smoke.

However, the prior art usually uses a low-pressure blasting technique. For example, the disclosed technical solution of the American patent (publication no US2007 / 0033927 )
the essential principle and structure of the gasoline inlet opening jet system for metering the fuel, there is a relatively low jet pressure.

In general, the jet metering technique with respect to the engine can be divided into three different categories: nozzle-side control, pump-side control, and nozzle-side pump-side mixing control. In this case, the nozzle-side control is already widely used for the fuel inlet opening jet system and the nozzle-side pump-side mixing control for the direct injection system within the fuel cylinder, while the pump-side control for the direct injection of the fuel within the cylinder, the fuel injection of the single-cylinder gasoline engine and the SCR System, etc. is used.

From the prior art, the above applications are difficult to standardize on an actuator and a dosing method of the same category. One of the root causes is that the commonly used rotary low pressure gasoline pump can not handle the conductive medium, e.g. Aqueous solution of urea, etc. Although another spiral tube plunger pump can handle the conductive and non-conductive fluid, there is a problem that accurate metering is difficult to achieve.

The spiral tube plunger pump can be detailed into two different structures: a plunger sleeve pump where the plunger moves and a barrel plunger pump where the sleeve moves. With respect to the plunger sleeve pump for pressurizing the fuel, this is disclosed American Patent 20030155444A1 a metering control method, namely, a method of estimating the fuel jet amount by predicting the position of the plunger. However, the fuel, especially the gasoline, has a high volatility, and the fluid entering the plunger sleeve typically contains a certain amount of vapor or air, and the jet quantity of the fuel and the position of the plunger do not have a corresponding relationship. Moreover, there is also a difficulty in predicting the displacement of the plunger as in predicting the fuel jet amount, so that there is a certain difficulty in translating.

Because of this, it is very valuable with respect to the spiral tube plunger pump, no matter the plunger sleeve pump or the sleeve plunger pump, to provide a simple structure and an application method that can simultaneously achieve multiple goals, as well as a uniform metering method.

Object of the invention

It is an object of the present invention, in view of the above problems, to provide an actuator solution that can realize pump-side control and has good universality and structure, as well as a uniform metering control method. The technical solutions and control methods can be widely used for designing the liquid jet system in the SCR and DPF exhaust purification system of the diesel engine or gasoline engine and the design of the fuel spray system of the spark ignited engine.

To achieve the above object, the present invention uses the following technical solution: a liquid jet metering unit and its control method, characterized in that it comprises a jet unit and a metering control device, the jet unit comprising a spiral tube device, a plunger pump and a nozzle, and wherein the Spiral tube device comprising a coil, a magnetic yoke, a magnetoresistance and an armature, and wherein the magnet yoke and the armature are made of magnetically permeable material, and wherein the magnetoresistance is made of magnetically non-permeable material, and wherein the plunger pump is a plunger and a sleeve and wherein the plunger cooperates with the sleeve to form a pressure delivery volume, and wherein the pressure delivery volume is connected to a fluid inlet valve and a fluid outlet valve, and wherein the fluid flows through the fluid inlet valve i ns pressure delivery volume and is discharged through the liquid outlet valve, and wherein the Dosiersteuergerät the spiral tube device a A drive signal provides, and wherein the Dosiersteuergerät comprises a detection device for monitoring the state parameters, comprising an algorithm for estimating the effective output of the spiral tube device by means of the state parameters and a method for controlling the closed flow rate of the Flüssigkeitsstrahldosiereinheit, wherein the effective output of the spiral tube device as a variable is used. The effective output of the spiral tube device is the energy needed to directly apply pressure to the fluid in the pressure delivery volume and to form a jet.

Regarding the control of the scroll tube device, it is a most common method to use a PWM single drive, the method does not provide feedback and correction for the spiral tube enforcement results, and inconsistent targets and results may occur, which may be due to the change in liquid state (eg, a two-phase flow occurs), the change in the drive voltage and the change in the resistance value of the spiral tube caused effects on the enforcement results are not fully covered.

For the above liquid jet metering unit, an optional solution is a sleeve plunger pump structure, namely, comprising a return spring, the sleeve having a reciprocating motion under the drive of the spiral tube device and the return spring, resulting in a changing change in the size of the pressure delivery volume.

For the above liquid jet metering unit, another optional solution is a plunger sleeve pump structure, namely, comprising a return spring, the plunger being reciprocated under drive by the scroll tube device and the return spring, resulting in a varying change in the size of the pressure delivery volume.

For the plunger sleeve pump structure, it is a further specified solution that the plunger includes an armature, the armature being approximately a cylindrical body, and the armature including a through hole led out through the two end surfaces. The through-hole may comprise a certain conicity, with the tapered hole being widened in the pressure-conveying direction of the liquid in order to realize a directed flow of the liquid in the inner space in order to cool the liquid-jet metering unit and improve its operational stability.

The return spring in the above solution may be replaced with another spiral tube device to provide the force needed to return the sleeve or plunger.

In the above solution, a high pressure line may be disposed between the liquid outlet channel and the nozzle, the high pressure line being made of metal or polymeric material and may be both a molded rigid tube and a flexible flexible tube. In addition, the liquid from the liquid container to flow through a filter, then it can enter the interior of the Flüssigkeitsstrahldosiereinheit.

It is an optional solution: comprising a gas-liquid mixing chamber, whereby the liquid is first injected through the nozzle into the gas-liquid mixing chamber, after mixing between the liquid and the gas, they are injected through an injector into the exhaust pipe of the engine , The injector may be both a simple throttle nozzle and a swirl nozzle provided with no nozzle valve. In a different application, the solution can achieve the following different objectives: first, it is conducive to the atomization of the liquid and the increase of the oxygen content of the exhaust pipe, secondly, a blockage caused by freezing and damage to the delivery pipe can be avoided, third, by the precipitated crystals of the Jet liquid such as aqueous solution of urea after evaporation of the solvent such as water caused blockage of the pipeline can be avoided, fourthly, a stoppage of the nozzle caused by combustible components in the liquid can be avoided.

In the above solution, if the engine does not require liquid injection, the high-pressure gas is further supplied to remove the residual liquid between the gas-liquid mixing chamber and the injector.

It is another injection solution used for the engine exhaust treatment system that the liquid is injected via the high pressure line through the nozzle directly into the exhaust pipe of the engine. Further, when the injected liquid is DEF, a small amount of DEF may be injected except for the DEF to be injected to reduce NOx emission to prevent overheating or clogging of the nozzle. To prevent freezing of the high-pressure line, a tau device should be arranged along the high-pressure line, for. For example, a thawing is performed by electrical heating or heating of the cooling water of the engine.

The energy balance method estimates the effective output of the spiral tube device by estimating the total energy output by the metering controller, the power consumption of the resistance of the spiral tube, and the inductive energy storage of the spiral tube device. In this way: the effective output of the spiral tube = the total energy output by the dosing controller - power consumption of the resistance of the spiral tube - the inductive energy storage of the spiral tube device - power consumption of the flow resistance - energy storage of the return spring.

As the state parameter of the spiral tube device, the following can be selected: the current flowing through the coil and the voltage at both ends of the coil.

Q

– Flüssigkeitsstrahlmenge;

Wn

– effektive Ausgangsleistung der Spiralrohrvorrichtung;

Et

– in die Spiralrohrvorrichtung eingegebene Gesamtenergie, Et0 – entsprechendes Et bis zum Anfangen der Einspritzung;

Er

– Energieverbrauch des Widerstandes der Spule, Er0 – entsprechendes Er bis zum Anfangen der Einspritzung;

Ein

– aktuelle induktive Energiespeicherung der Spiralrohrvorrichtung, Ein0 – entsprechendes Ein bis zum Anfangen der Einspritzung;

Wr

– Leistungsverbrauch des Strömungswiderstandes, Wr0 – entsprechendes Wr bis zum Anfangen der Einspritzung;

Es

– Energiespeicherung der Rückstellfeder, Es0 – Energiespeicherung der Rückstellfeder beim Anfangen der Einspritzung, Esi – Voraus-Energiespeicherung der Rückstellfeder beim Ausüben des Stroms auf die Spule.

ergibt sich Folgendes: Wn = η·Q, η ist der Verhältniskoeffizient zwischen der effektiven Ausgangsleistung und der Strahlmenge, Wn = Et – Er – Ein – Wr – (Es – Esi), Et0 = Er0 + Ein0 + Wr0 + (Es0 – Esi), oder Wn = (Et – Et0) – (Er – Er0) – (Ein – Ein0) – (Wr – Wr0) – (Es – Es0), und die jeweiligen Formeln sind wie folgt: Et = int(Id·Vd), Er = int(Id²·r), r ist der Widerstand der Spule, Ein = L·Id²/2, L ist die Induktivität der Spiralrohrvorrichtung, Es = K·X²/2, K ist der Elastizitätsmodul der Rückstellfeder, X ist die Kompressionsmenge der Feder, (Wr – Wr0) = ζ·Q, ζ ist ein Verhältniskoeffizient,
dabei steht int für die Integration der Zeit nach der Anschaltung der Spule;
Aufgrund dessen, Q = [(Et – Et0)0 – (Er – Er0) – (Ein – Ein0) – (Es – Es0)]/a, a = η + ζ. More specifically, an integral of the product of sensed current of the coil is obtained times voltage relative to the total energy output by the dosing controller. An integral of the product of the square of the detected current of the coil times the resistance of the spiral tube with respect to time approaches the power consumption of the resistance of the coil. With the detected current of the spiral tube, the inductive energy storage of the spiral tube device is calculated. The power consumption of the flow resistance of the liquid and the energy storage of the return spring can be easily treated so as to have a linear relationship with the injection amount after the start of the injection. For the above energy balance relationship, the following mathematical expression may be used:
Under the assumption:

Q

- Fluid jet quantity;

Wn

- Effective output of the spiral tube device;

et

Total energy input into the spiral tube device, Et0 - corresponding Et until injection commencement;

He

- energy consumption of the resistance of the coil, Er0 - corresponding to it until the beginning of the injection;

One

- Current inductive energy storage of the spiral tube device, Ein0 - A corresponding to the beginning of the injection;

Wr

- Power consumption of the flow resistance, Wr0 - corresponding Wr until starting the injection;

It

- Energy storage of the return spring, Es0 - Energy storage of the return spring when starting the injection, Esi - Pre-energy storage of the return spring when applying the current to the coil.

the following results: Wn = η · Q, η is the ratio coefficient between the effective output power and the jet quantity, Wn = Et - He - One - Wr - (Es - Esi), Et0 = Er0 + Ein0 + Wr0 + (Es0 - Esi), or Wn = (Et-Et0) - (Er-Er0) - (On-Ein0) - (Wr-Wr0) - (Es-Es0) and the respective formulas are as follows: Et = int (Id · Vd), Er = int (Id ² · r), r is the resistance of the coil, A = L · Id ^2/2, L is the inductance of the spiral tube device, It = K * X ^2/2, K is the elastic modulus of the return spring, X is the compression amount of the spring, (Wr - Wr0) = ζ · Q, ζ is a ratio coefficient,
where int is the integration of the time after the connection of the coil;
Because of that, Q = [(Et - Et0) 0 - (Er - Er0) - (Ein - Ein0) - (Es - Es0)] / a, a = η + ζ.

The respective variables included on the right side of the above formulas are the state parameters of the spiral tube device that can be detected in real time:
Id, Vd, constants: r, K, L, and indefinite coefficient: α. In this case, α can be calibrated by the actual measurement of the flow quantity,
if the above physical relationship is relatively complete, α should be a constant; L can be theoretical calculation or be considered as indefinite coefficients and by a actual measurement of multipoint flow rates to be calibrated.

In practice, it is also appropriate to treat the energy storage (Es - Es0) of the return spring to be proportional to Q so that the equation of the jet quantity does not explicitly include the energy storage of the return spring.

Preferably, Er-Er0 and Ein-Ein0 can be treated in each case or simultaneously simplified so that they are directly proportional to the jet quantity Q, so that the expression of the jet quantity can be considerably simplified, namely
Q = (Et - Et0) / μ, μ is an indefinite coefficient and can be calibrated by measuring the flow rate. It is in line with the simplified model that the amount of jet flux is simulated by integrating the product from current to voltage with respect to time.

As mentioned above, the power consumption of the flow resistance can also be approximated with a further refined model, e.g. For example, if the resistance is directly proportional to the square of the flow rate, the affected indefinite coefficient can be calibrated by testing the multipoint flow rates of the liquid jet metering unit.

The American patent US7273038B2 discloses a simplified method in which immediately with the integration of the current with respect to time the amount of jet flux is simulated, here the factor of the change of the voltage of the current source is disregarded, in particular the influence on the effective output power of the spiral tube device caused by the transient voltage fluctuations.

Another option is as follows: the time T3 required to reduce the electrical dynamic potential to the reference voltage after the coil is turned off is defined as the state parameter of the spiral tube device, and the effective output of the spiral tube device is in good agreement with T3. A simplified correspondence relationship is to treat T3 and the effective output of the spiral tube as a linear relationship.

When the liquid flow amount injected within a unit time is defined as the control target, an optional control mode is: the single-pulse jet amount of the liquid jet metering unit is obtained invariably, namely, the effective output of the spiral tube device is set to each pulse, by changing the operating efficiency of the liquid jet metering unit, the target is achieved. It is another control mode: the operation efficiency of the liquid jet metering unit is kept unchanged, by the change of the effective output power of the spiral tube device, the target is achieved. The objective can also be achieved with a combination of the two methods, namely the operating efficiency of the liquid jet metering unit and the effective output of the spiral pipe device are changed.

The present invention comprises a method for measuring the liquid level within the liquid container, wherein an average measurement for the flow resistance of the movable element of the plunger pump is performed by a measurement of the liquid level. The resistance can be determined by detecting the characteristics of the above state parameters of the spiral tube.

The liquid jet metering unit and its control method according to the present invention may be used for the following three aspects: fuel injection system of the engine management system, urea aqueous solution jet metering system of the engine SCR aftertreatment system, and regenerative fuel jet metering apparatus of the engine DPF aftertreatment system , Incidentally, other applications such as injection-type injection quantity mixing apparatus of the motor fuel, auxiliary combustion jetting apparatus for starting the engine at a low temperature exist.

The plunger pump of the present invention may be disposed both inside the liquid container and at the outside of the liquid container. If the SCR jet system, the plunger pump is located inside the liquid container, the required devices for thawing in the winter can be reduced. When the liquid jet metering unit is disposed on the outside of the liquid container, the filter apparatus can be integrally formed with the liquid jet metering unit, whereby the liquid can reach the filter by gravity or an added low pressure pump from the bottom portion of the liquid container through the liquid delivery tubing and then enter the liquid jet metering unit the return opening through an externally connected return pipe reach the top of the liquid container.

Among the various solutions for the liquid jet unit and the control method, it is a relatively practical solution: a metering module comprising a taurine tube Holder, wherein the jet unit is attached to one end of the holder and the controller at the other end of the holder. The solution is particularly suitable for forming an injection system of the urea aqueous solution of SCR, the dosing module can be placed vertically or horizontally in the liquid container, an end serving to secure the controller is attached to the liquid container, and the controller is exposed outside the liquid container and an end for attaching the jet unit is located at the bottom portion inside the liquid container.

In the context of figures and detailed embodiments, the present invention will be explained in more detail below.

Brief description of the drawings

1 FIG. 13 shows a structural logic diagram of the liquid jet metering unit with a sleeve plunger pump according to the present invention. FIG.

2 shows a logical structural view of the Flüssigkeitsstrahldosiereinheit with a plunger sleeve pump according to the present invention.

3a shows an embodiment of the Flüssigkeitsstrahldosiereinheit with a sleeve plunger pump according to the present invention.

3b shows an embodiment of the Flüssigkeitsstrahldosiereinheit with a plunger sleeve pump according to the present invention.

4 FIG. 12 is a principle measurement diagram of the state parameter of the scroll tube apparatus of the liquid jet metering unit according to the present invention. FIG.

5a 10 shows a circuit of voltage measurement of the state parameter of the spiral tube device of the liquid jet metering unit according to the present invention.

5b Fig. 12 shows a circuit of current measurement of the state parameter of the spiral tube device of the liquid jet metering unit according to the present invention.

6 shows a logic diagram of the active closed-loop control of the flow rate of Flüssigkeitsstrahldosiereinheit according to the present invention.

7a FIG. 12 is a diagram showing the physical definition of the state parameter T3 of the scroll tube apparatus of the liquid jet metering unit according to the present invention. 7b FIG. 12 is a diagram showing the measurement circuit of the state parameter T3 of the scroll tube apparatus of the liquid jet metering unit according to the present invention. 8th FIG. 12 shows a logic diagram of the passive closed flow control of the liquid jet metering unit according to the present invention. FIG.

9a FIG. 12 shows a set of measurement data of the first energy model based prediction for the flow amount. FIG.

9b FIG. 12 shows a set of measurement data of the second energy model based prediction for the flow amount. FIG.

9c Fig. 12 shows a set of measurement data of the third energy model based prediction for the flow amount.

9d FIG. 12 shows a set of measurement data of the fourth energy model based prediction for the flow amount. FIG.

10 shows an example of a liquid jet metering unit used for the electric blast system of the engine according to the present invention.

11 shows an example of a liquid jet metering unit used for the SCR system according to the present invention.

12 FIG. 12 shows an example of a liquid jet metering unit used for the DPF regeneration system according to the present invention. FIG.

Description of the preferred embodiments

As in 1 3 is a structural logic diagram of the liquid jet metering unit including a sleeve plunger pump according to the present invention including a plunger pump 8th , a spiral tube device 18 , a control unit 13 , a nozzle 23 and a return spring 10 , In this case, the plunger pump device comprises 8th a sleeve 11 , a plunger 12 , a liquid inlet valve 16 and a liquid outlet valve 17 , where the sleeve 11 tight with the plunger 12 interacts to create a pressure delivery volume 9 train. The spiral tube device 18 includes a coil 19 , a magnetic yoke 20 , a magnetic gap 21 and an anchor 12a , The anchor 11a and the sleeve 11 can be integrally formed with each other, being the anchor 12a the sleeve 11 inside, and where the magnetic yoke 20 and the anchor 12a is formed of magnetically permeable material, and wherein the front end surface of the armature 12a near the magnetic gap 21 is located, and wherein after the connection of the coil 19 the anchor 12a and the sleeve 11 under drive by the spiral tube device 18 to move forward so that the pressure delivery volume 9 decreases. The liquid in the pressure delivery volume 9 is pressed and undergoes an increase in pressure, causing the liquid outlet valve 17 leads, the liquid reaches the nozzle 23 , Under the effect of pressure, the nozzle becomes 23 opened and the liquid is blasted; after terminating the connection of the coil 19 catch the sleeve 11 under the action of the return spring 10 with a return movement, during the return process, the liquid inlet valve 16 opened, then new liquid enters the pressure conveying space 9 one to prepare for the injection next cycle.

As in 2 3 is a structural logic diagram of the liquid jet metering unit with a plunger sleeve pump according to the present invention including a plunger pump 8th , a spiral tube device 18 , a control unit 13 , a nozzle 23 and a return spring 10 , In this case, the plunger pump device comprises 8th a sleeve 11 , a plunger 12 , a liquid inlet valve 16 and a liquid outlet valve 17 , where the plunger 12 tight with the sleeve 11 interacts to create a pressure delivery volume 9 train. The spiral tube device 18 includes a coil 19 , a magnetic yoke 20 , a magnetic gap 21 and an anchor 12a , The anchor 12a and the plunger 12 are arranged coaxially einreihend, wherein the magnetic yoke 20 and the anchor 12a is formed of magnetically permeable material, and wherein the front end surface of the armature 12a near the magnetic gap 21 is located, and wherein after the connection of the coil 19 the anchor 12a and the plunger 12 under drive by the spiral tube device 18 to move forward so that the pressure delivery volume 9 decreases. The liquid in the pressure delivery volume 9 is pressed and undergoes an increase in pressure, causing the liquid outlet valve 17 leads, the liquid reaches the nozzle 23 , Under the effect of pressure, the nozzle becomes 23 opened and the liquid is blasted; after terminating the connection of the coil 19 catch the plunger 12 under the action of the return spring 10 with a return movement, during the return process, the liquid inlet valve 16 opened, then new liquid enters the pressure conveying space 9 one to prepare for the injection next cycle.

In the solution of the liquid jet metering unit according to 1 and 2 is the liquid outlet valve 17 a one-way valve whose opening and closing are controlled by the pressure difference, and the liquid inlet valve 16 For example, a one-way valve whose opening and closing are controlled by the pressure difference, and a slider whose opening and closing are controlled by the relative position of the sleeve plunger, or a combination between a one-way valve whose opening and closing are controlled by the pressure difference and a slider whose opening and closing are controlled by the relative position of the sleeve plunger.

As in 3a 1, a detailed embodiment of the liquid jet metering unit with the sleeve plunger pump according to the present invention, comprising a spiral tube device 18 , a plunger pump 8th , a return spring 10 , a pump connection 26 , a high pressure line 25 , a nozzle 23 , a filter 31 .
a low pressure volume 29 and a housing of the output terminal 37 ,

The spiral tube device 18 includes a coil 19 , a first inner magnetic yoke 20a , a second inner magnetic yoke 20d , an external magnetic yoke 20b , an end section 20c of the external magnetic yoke, a magnetic gap 21 and an anchor 12a , The external magnetic yoke 20b is about the plastic deformation of the projection 20b1 with the end section 20c the external magnetic yoke is tightly locked while the coil 19 is also secured therein, wherein the first Innenmagnetjoch 20a an internal drainage channel 28 includes, through which the fluid can flow. The external magnetic yoke 20b , the end section 20c of the external magnetic yoke, the first inner magnetic yoke 20a and the second inner magnetic yoke 20d are made of magnetically permeable material, wherein the magnetic gap 21 made of magnetically non-permeable material. At the anchor 12a are a plurality of straight slots distributed along the circumferential direction 12e provided to reduce the resistance of the reciprocating motion.

The plunger pump 8th includes a sleeve 11 , a plunger 12 , a liquid inlet valve 16 and a liquid outlet valve 17 , The sleeve 11 works closely with the plunger 12 together to a pressure delivery volume 9 train. The sleeve 11 and the anchor 12a can be integrally formed with each other and made with the same or different material, the sleeve 11 is located on the inside of the anchor 12a and includes a plunger hole 27 , an overflow hole 16b1 and a liquid inlet channel 30 , The plunger 12 includes an end face 16b2 , a liquid outlet channel 12d , one at the lower end of the liquid outlet channel 12d located flow restriction hole 12b and one at the end section located projection 12c , The liquid inlet valve 16 is one out of a one way valve 16a and a slider 16b trained combination valve. The one-way valve 16a is through a valve element 16a1 , a valve spring 16a2 and a valve seat 16a3 formed, wherein the valve seat 16a3 with the sleeve 11 can be connected in one piece and is a cone-shaped seat, located at the liquid inlet channel 30 is located and connected to. The slider 16b includes an overflow hole 16b1 and an end face 16b2 of the plunger 12 , Opening and closing the slide 16b are determined by the relative position of the plunger 12 certainly when the plunger 12 to the face 16b2 moves and the highest point of the overflow hole 12b exceeds, the slider is 16b closed. When the time of closing the one-way valve 16a later than the time of covering the overflow hole 16b1 , the start of the pressure-feeding process of the liquid depends on the closing of the one-way valve 16a conversely, the start of the pressure-feeding process of the liquid depends on covering the overflow hole 16b1 from. The liquid outlet valve 17 is a one-way valve and includes a liquid outlet valve element 17a , a liquid outlet valve spring 17b and a liquid outlet valve seat 17c , The liquid outlet valve seat 17c is at the plunger 12 fastened, while the attachment by fitting or welding and other methods can be realized.

The pump connection 26 includes a pump port inlet port 26c , a support rod 26a and a stopper element 26b , wherein the liquid inlet channel 30 allows the support bar 26a extends inward and the one-way valve element 16a1 touched, and wherein the stop element 26b for limiting the return of the anchor 12a is used. Within a distance of the anchor 12a to the pump connection 26 keeps the support bar 26a the contact with the one-way valve element 16a1 prevents and prevents its falling to the seat, so that on the one hand, the one-way valve 16a kept open when the anchor 12a is reset to the starting position, so that the liquid sufficient time to enter the pressure delivery volume 9 on the other hand, the gas in the pressure delivery volume 9 continue through the one-way valve 16a be drained when the anchor 12a the pump connection 26 leaves and moves forward to a distance, so that the metering accuracy of the liquid is ensured.

The nozzle 23 is a ball valve nozzle and includes a front valve seat 38 the nozzle, a hemispherical valve element, a rear valve seat 41 the nozzle, a valve spring 42 the nozzle and a nozzle hole 39 , wherein the front valve seat 38 the nozzle comprises a cone-shaped seat surface which coincides with the spherical surface of the hemispherical valve element 40 can be sealed, and wherein the rear valve seat 41 the nozzle comprises a plane coincident with the plane of the hemispherical valve seat 43 can form a seal, and wherein the front valve seat 38 the nozzle and the rear valve seat 41 the nozzle are connected by welding together, and wherein therein after the connection a required movement space for opening the hemispherical valve element 40 is recessed, and wherein at the inlet opening of the ball valve nozzle 23 a filter screen 44 is arranged.

The high pressure line 25 includes one with the projection 12c the end portion of the plunger 12 docked quick connection 25a and one with the lead 23a the end portion of the nozzle 23 docked quick connection 25b , The pump body 1 and the high pressure line 25 are over an O-ring 32 sealed, with the nozzle and the high pressure line 25 over an O-ring 33 are sealed.

The filter 30 includes an inner skeleton 34 , a filter cloth 35 and a filter internal cavity 36 ,

The working process of the liquid jet unit is as follows:
At the movement starting position, it approaches under the action of the return spring 10 the stop element 26b tight, now is the one-way valve 16a under the effect of the support rod 26a in the open state, and the overflow hole 16b1 and the pressure delivery volume 9 are in a connected state, and the components of the contained gases can easily enter the pressure delivery volume 9 escape, and the pressure delivery volume 9 is filled with the liquid. If the anchor 12a under the action of electromagnetic force begins to collide with the sleeve 11 moved forward, a portion of the fluid in the pressure delivery volume 9 through the liquid inlet channel 30 and the overflow hole 16b1 drained, with some of the gases contained. If the anchor 12a moves by a certain distance, the overflow hole 16b1 through the surface of the plunger 12 covered. The anchor 12a continues to move, and the pressure delivery volume 16 decreases steadily when the ball surface of the one-way valve element 16a1 on the conical valve seat 16a3 is set, is the one-way inlet valve 16a closed, and the printing process begins. The fluid pressure in the pressure delivery volume 9 increases gradually. When the on the liquid outlet valve element 17a pressure exerted the effectiveness of the spring 17a of the liquid outlet valve, the liquid outlet valve becomes 17 open. The liquid enters the liquid outlet channel 12d enters through the flow restriction hole 12b in the high pressure line 25 and reached through the filter screen 44 the hemispherical valve element 40 , When the pressure difference between the front and rear side of the hemispherical valve element 40 increases until the effectiveness of the nozzle valve spring 42 can be overcome leaves the hemispherical valve element 40 the sealing cone surface of the front valve seat 38 the nozzle and touches the sealing plane of the rear valve seat 41 the nozzle is tight, now the liquid is through the nozzle hole 39 spouted.

After the anchor 12a applied electromagnetic force has disappeared, the anchor begins 12a under the action of the return spring 10 with the return stroke, now is a pressure reduction due to the expansion of the pressure delivery volume 9 causes, so that the liquid outlet valve 17 closed, the one-way valve 16a will be opened. Under the effect of the pressure difference, the liquid quickly enters the pressure delivery volume 9 one. After the anchor 12a Moving further a certain distance, first the movement of the liquid inlet valve element 16a1 through the support bar 26a prevented, then are the overflow hole 16b1 and the pressure delivery volume 9 again connected to each other, and a part of the liquid can also through the overflow hole 16b1 into the pressure delivery volume 9 occur, the further return of the anchor 12a is through the stop element 26b prevented and terminated, so the cycle is ended.

During the above process, the overflow hole may become 16b1 be redesigned so that the order of times for closing the overflow hole 16b1 and the liquid inlet valve 16a is reversed.

During the above working process, the liquid exits the filter internal cavity 36 through the pump port fluid inlet port 26c in the entire anchorage 12d and enters through the liquid inlet channel 14 into the pressure delivery volume 16 a, due to the consumption of electrical energy and heat generation, it causes some of the liquid in the armature space 12d is vaporized, and the vaporized steam exits the inner drainage channel 28 into the low pressure volume 29 and enters through the bladder outlet 29a on the housing 37 the output terminal is discharged to the outside. The bladder outlet 29a includes a mounting step step 29a , which can be used to install a bladder discharge tube, so that the gases are effectively discharged from the pump body.

As in 3b illustrated another detailed embodiment of the Flüssigkeitsstrahldosiereinheit with the plunger sleeve pump according to the present invention, the difference from the embodiment according to 3a is that in the liquid jet metering unit 1 in the present embodiment, a synchronous movement between the plunger 12 and the anchor 12a is used, wherein the sleeve 11 is a solid structure. The anchor 12a is essentially a cylindrical body and includes a through hole 45 which is passed through the two end surfaces. The through hole 45 may comprise a certain conicity, wherein the hole is widened with the conicity in the pressure conveying direction of the liquid in order to realize a directed flow of the liquid in the inner space to the Flüssigkeitsstrahldosiereinheit 1 to cool and to improve its operational stability.

The anchor 12a and the plunger 12 can be integrally formed with each other or via a connecting element 12b perform a motion transfer. The sleeve 11 is coaxial with the housing 37 attached to the output terminal, wherein the de sleeve 11 a side overflow hole 16b1 and an axial straight-tenon hole 27 are arranged for connection. The plunger 12 is about a precise sliding fit in the sleeve 11 installed and its upper part touches over the connecting element 12b the anchor 12a always. The overflow hole 16b1 and the frontal area 16b2 of the plunger form a liquid inlet valve 16 out. The liquid outlet valve 17 is through a liquid outlet valve element 17a , a liquid outlet valve spring 17b and a liquid outlet valve seat 17c formed, wherein the liquid outlet valve seat 17c one with the liquid outlet valve element 17a interacting conical surface is and at the end 11a the sleeve 11 located. The return spring 10 is between the plunger 12 and the bottom portion of the anchor space 12d arranged.

The through the inlet opening 46 entered liquid passes through the overflow hole 16b1 into the pressure delivery volume 9 one. If the anchor 12a When driven down by the electromagnetic force, the plunger will go over the connecting element 12b driven to come down. Once the overflow hole 16b1 through the wall surface of the plunger 12 is covered, the liquid inlet valve 16 closed, and the printing process begins. The pressure of the liquid in the pressure delivery volume 9 increases, leaving the liquid outlet valve 17 is opened, the pressure fluid enters the liquid outlet 47 and the high pressure line 25 and reaches the nozzle 23 , Once the pressure is the opening pressure of the nozzle 23 exceeds the nozzle ejects the liquid mist. The nozzle is a lifting valve, which is opened by the pressure.

During the process, the through the inlet opening 46 entered liquid together with the air bubbles therein through the bladder outlet 28 (allows the bladder discharge opening also the passage of the liquid), the anchor space 12d and the through hole 45 directly into the bladder outlet 29a to form a liquid return flow, thus the heat is dissipated.

As in 4 12 is a principle measurement principle diagram of the state parameter of the scroll tube apparatus of the liquid jet metering unit according to the present invention, wherein it includes a main control chip 13a , which is a microcontroller, a semiconductor switching transistor 13b for controlling the spiral tube device 19 , a circuit 13c for measuring the current flowing through the coil, a circuit 13d for measuring the voltages at both ends of the coil and a T3 generation circuit 13e includes.

5a FIG. 12 shows a detailed circuit of the voltage measurement of the state parameter of the scroll tube apparatus of the liquid jet metering unit according to the present invention, which is an ordinary voltage dividing circuit for measuring the voltage and two resistors 102 includes.

5b FIG. 12 shows a voltage measurement circuit of the state parameter of the scroll tube apparatus of the liquid jet metering unit according to the present invention, which is an operational amplifier. FIG 101 and a corresponding resistor 102 includes.

As in 6 1, the closed-loop active closed-loop control logic of the liquid jet metering unit according to the present invention comprises the following steps:
step 111 the relationship between the jet quantity Q and the effective output power Wn of the spiral tube apparatus (hereinafter abbreviated as effective output power) is established from the multi-point flow amount test of the liquid jet metering unit, the relationship may be both discrete data and a relational formula simulated based on the discrete data. and α is then scaled, then the data or relationship formulas in the controller 13 saved;
step 112 by means of the target beam quantity Qo the intended effective output power Wno is determined;
step 113 : the control unit 13 applies a voltage through the semiconductor switching transistor 13b on the spool 19 out;
step 114 : with a certain interval, the current Id and the voltage Vd of the coil 19 detected;
step 115 with another method of the present invention, the actual effective output power Wnc is calculated;
step 116 : the intended effective output power Wno and the actual effective output power Wnc are compared with each other;
step 117 : if Wno - Wnc is smaller than a legal small amount e, it is indicated that the beam target is reached, and this driving is stopped. Otherwise the drive will continue and it will return to the step 114 back to continue real-time monitoring.

As in 7a 1, the physical definition of the state parameter T3 of the spiral tube device of the liquid jet metering unit according to the present invention is as follows: after the coil is turned off 19 the inductive electric dynamic potential at both ends of the coil will increase suddenly and then along the curve 103 When the voltage drops to a reference voltage V, the time interval between the turn-off of the coil decreases 19 up to the current time defined as T3, and the microcontroller 13a can be based on the measurement signal 104 obtained detailed values from T4.

The measuring signal 104 of T3 can be generated by a circuit, the measurement circuit of the state parameter T3 of the liquid jet metering unit according to the present invention is as in FIG 7b 4, the reference voltage Vf is formed by the voltage division of the resistor for the power supply voltage Vcc, see FIG 4 , is the signal of one end M of the coil to an input terminal of the operational amplifier 101 connected, Vd is at another input terminal of the same operational amplifier 101 connected, the output terminal of the amplifier 101 is to an input terminal of another operational amplifier 101b connected while the reference voltage Vf to another input terminal of the operational amplifier 101b is connected so that at the output terminal of the operational amplifier 101b a T3 signal can be detected, which is a square wave signal (as in 7a shown).

As in 8th 1, an actively closed control logic of the flow quantity of the liquid jet metering unit according to the present invention can be designed on the basis of the T3 signal, namely it comprises the following steps:
step 121 From the test of the multipoint flow quantities of the liquid jet metering unit, a relationship between the jet quantity Q and T3 is established, the relationship may be both discrete data and a relationship formula simulated based on the discrete data, then the data or relationship formulas are pre-determined in the controller 13 saved;
step 122 The relationship of the liquid jet metering unit of T1 = f (T3) is obtained by simple experiments, and from the discrete data, the differential relation between T3 and T1 is obtained, namely dT1 = df (dT3), the data becomes discrete or in the functional expressions and Relationship formulas simulated in advance in the controller 13 saved;
step 123 : from the target beam amount Qo, target T3 is detected, namely T3o;
step 124 from the previously stored relationship formula T1 = f (T3), the drive pulse width T1 for realizing T3o is estimated;
step 125 : from the last cycle feedback, the dynamic correction amount dT1 of T1 is detected;
step 126 : based on the pulse width T1 + dT1 becomes the coil 19 driven;
step 127 : Signal value of T3 is detected;
step 126 : the difference value between current T3 and target T3 is calculated, namely dT3 = T3o - T3;
step 127 : on the basis of the step 122 in the control unit 13 stored in advance, the correction amount of t1 is calculated dT1 = df (dT3);
To the step 125 The information from dT1 in the control unit returns 13 saved.

The above passive closed control for the jet amount of the liquid jet unit can externally realize the control target accurately at the current pulse, but two adjacent pulses have a very small time interval, so that the change of the state of the liquid jet unit and the fluid in the environment during the period can be neglected , because of which actually better control accuracy can be realized.

9a shows a group of measurement data based on a first energy model and its linear simulation relationship. Here, the energy model refers to Wn = Et-Et0, namely, the power consumption of the coil resistance, the inductive energy storage of the spiral tube device, the power consumption of the flow resistance of the liquid and the energy storage of the return spring and other factors are neglected, while the total energy input to the spiral tube device is differentiated Namely, the difference between the currently inputted total energy and the total energy input before injection is treated as the effective output of the spiral tube device, the simplified energy model and the jet quantity Q does not have a good linear match, but there are some actual meanings as well Changing the state of the jet unit caused influencing factors on the jet quantity can be eliminated.

9b shows a group of the measurement data based on a second energy model and its linear simulation relationship, the second energy model is based on the fact that based on the first energy model an influencing factor of the energy consumption of the coil resistance is added, namely Wn = (Et - Eto) - (Er - Ero). It can be found that the second-energy-model-based prediction of the jet quantity Q is improved compared to the first energy model, but the improvement is not significant.

9c shows a group of the measurement data based on a third energy model and its linear simulation relationship, the third energy model is based on the fact that based on the second energy model an influencing factor of the inductive energy storage is added, namely Wn = (Et - Eto) - (Er - Ero) - (One - One). It can be found that the prediction of the jet quantity Q based on the third energy model has a very good accuracy.

9d shows a group of measurement data based on a fourth energy model and its linear simulation relationship, the fourth energy model is that the effective output power and T3 become linear with each other, namely Wn = λ (T3-T30), where T3o is T3 when the injection occurs, λ is an indeterminate coefficient that can be determined by the flow rate measurement experiments. It can be found from the measurement results that with the fourth energy model, better prediction results for the jet quantity can be output.

10 shows an example of a liquid jet metering unit used for the electric blast system of the engine according to the present invention. The pump nozzle of the example may be the sleeve plunger pump according to 3a , in the illustrated application, the sleeve-plunger pump according to 3a be placed in reverse, which is more conducive to the elimination of the air bubbles near the liquid inlet valve 16a is. The example includes a fuel tank 132 , a plunger pump 8th , a high pressure blast hose 25 , a nozzle 23 and a controller 13 , The fuel tank 132 includes a mounting projection 132a , the plunger pump 8th can about a screw 131 attached to the mounting projection of the fuel tank and a gasket 138 be sealed. The filter 31 is located inside the fuel tank 132 , where the nozzle 23 at a position of the inlet connection pipe approaching the inlet valve 134 the engine 133 is installed. The control unit 13 is also used as a control unit for the electrical injection of the engine, via a cable 135 becomes the liquid jet metering unit 1 driven to work, and that through the nozzle 23 Spent gasoline is dosed, after mixing with air gasoline enters the cylinder 136 the engine 133 one. Of course, the dosing control unit 13 continue over the cable 137 connected to the other mechanisms of the electric control system of the engine, for. B. Angle mark sensor of the engine, etc.

The liquid jet metering unit in this example may also be used for the direct injection system within the cylinder of the gasoline engine.

11 FIG. 11 shows an example of a liquid jet metering unit used for the SCR system according to the present invention, the pump nozzle of the example may be incorporated in FIG 3a be shown sleeve plunger pump. The example includes a urea container 141 , a holder 142 , a metering jet unit 1 , a control unit 13 , a mixed infusion line 155 , an injector 156 and a drain pipe 157 with an SCR catalytic converter 159 wherein, along the direction of the exhaust gas flow, a temperature sensor successively 158 and a NOx or ammonia sensor 160 are arranged, each on both sides of the catalytic converter 158 are located.

The metering jet unit 1 includes a plunger pump 8th , a high pressure line 25 , a nozzle 23 and a bubble discharge line 145 , The bladder outlet line 145 extends to the top of the solution, with a filter on the opening side 146 is installed to ensure that the clean solution in the plunger pump 8th does not become dirty to prevent the dirt from entering.

The holder 142 includes respective sensors 144 (including temperature sensor, water level sensor, etc.), a mounting projection 144a the plunger pump for attaching the plunger pump 8th , a heater 161 of the circulation water, a gas-liquid mixing chamber at the other end of the holder 142 and a controller installed thereon 13 , The holder 142 is at the upper end surface 141 of the urea container, one end is together with the plunger pump 8th on the mounting projection 144a inside the urea container 141 placed, with the plunger pump 8th extends to the bottom portion of the urea container 141 , The gas-liquid mixing chamber 148 includes one with the inlet channel 150 connected inlet line connection 149 for introducing the high pressure air, one with the liquid outlet channel 151 connected infusion line connection 147 and a nozzle mounting channel 152 so that the nozzle hole 39 the nozzle 23 through the mounting channel 152 into the interior of the mixing chamber 148 extends and through the bracket 142 is fastened sealingly.

The injector 156 is on the drain pipe 157 installed and can be both a simple throttle nozzle as well as provided with no nozzle valve swirl nozzle. In various applications, the solution can achieve the following different objectives: first, it is beneficial for the atomization of the liquid and the increase in the oxygen content of the exhaust pipe; secondly, a blockage caused by freezing and damage to the production pipe can be avoided, and thirdly, a precipitation due to the precipitated urea Fourthly, blockage of the nozzle caused by burning binding of the fuel can be avoided.

The working process of the present invention for the SCR system is as follows.

Based on the state of operation of the engine transmitted by the main control unit of the engine (not shown) and the signals of the exhaust gas temperature sensor 159 , NOx or ammonia sensor 160 and the respective sensors 144 in the liquid container, the dosing control unit calculates 13 the required amount of flow of urea, then it is determined whether the urea jet system can realize a normal operation, if so, the Flüssigkeitsstrahldosiereinheit 1 controlled to work to the urea liquid in the liquid container in the high pressure line 25 pump in and then through the nozzle 23 into the mixing chamber 148 inject. At the same time, the high pressure air passes through the pressure gauge 154 , the solenoid valve 153 , the inlet line connection 149 and the inlet channel 150 into the mixing chamber 148 injected and mixed with the jet liquid therein, between the solenoid valve 153 and the inlet pipe connection 149 For example, a one way valve can be installed so that the airflow has a one way flow. The mixture liquid passes through the liquid outlet channel 151 and the infusion line connection 147 into the mixed infusion line 155 one. At the end, the mixing liquid is passed through the injector 156 in the form of nebulization in the exhaust pipe 157 injected, under the effect of the high temperature exhaust gas of the engine, the urea solution is decomposed warm into the ammonia, which is uniformly mixed with the exhaust gas of the engine and in the SCR catalytic converter 159 In the end, NOx is effectively decomposed into harmless N2 and H2O to achieve the goal of exhaust gas purification.

During the above work process, the controller stops 13 based on the signal of temperature sensor 144 in the liquid container, whether a freezing of the urea solution occurs. If there is a freezing, the water valve (not shown) is controlled, so that the cooling water of the engine into the heater 161 of the circulating water enters the liquid container to realize a warming thaw.

12 FIG. 14 shows an example of a liquid jet metering unit used for the DPF regeneration system according to the present invention, the pump nozzle of the example shown in FIG 3b be shown sleeve plunger pump. The example includes a secondary fuel tank 173 , a plunger pump 8th , a high pressure line 25 , a nozzle 23 , a control unit 13 , an exhaust pipe 170 , a pressure difference sensor 180 and a temperature sensor 181 , The control unit 13 may be both a dosing module for receiving the operating signal of the main control unit and a control unit with a DPF system.

In the example is a diesel engine particulate filter (DPF) 171 at the exhaust pipe 170 installed, before DPF can be an oxidation catalyst DOC 179 be switched, or on the DPF filter directly a noble metal catalyst is applied, at the upper reaches of DPF 171 is a fuel (diesel) nozzle 23 of regeneration DPF 171 arranged, when the regeneration condition is reached, the fuel of specified amount is in the exhaust pipe 170 injected the engine, the fuel has a combustion reaction with the residual air in the engine exhaust 172 so that the temperature of the engine exhaust gas increases, and the exhaust gas enters the DPF 171 a to those in DPF 171 to ignite collected particles whose main constituents are carbon smoke in order to reach the DPF regeneration target. The in the system through the nozzle 23 injected fuel should be as little as possible, but should the engine exhaust 172 a sufficiently high temperature, due to which it is required that the fuel is well nebulized and distributed appropriately. For the nozzle 23 For example, a lift valve structure can be selected that has good resistance to burnt binding and soiling. The invention comprises a secondary fuel tank 173 , The secondary fuel tank 173 is located above the liquid jet metering unit 1 so that the fuel in the secondary fuel tank 173 by gravity into the liquid jet metering unit 1 can occur to form a common fuel supply. The return fuel of the high-pressure jet system of the engine (most preferably the series connection is used) passes through the fuel inlet port 179 in the secondary fuel tank 173 and then returns through the fuel return port 178 back to the main fuel tank of the engine. The fuel of the auxiliary fuel tank 173 may also come directly from the low-pressure fuel supply pump of the high-pressure jet system of the engine, or under the action of an additional pump (such as vacuum pump) or gravity, the fuel is taken from the main fuel tank of the engine. Between the main fuel tank of the engine and the liquid jet metering unit 1 if at least one filter system is to be arranged, if it is the low-pressure return fuel originating from the high-pressure jet system of the engine, there is no need to arrange an additional filter, otherwise another fuel filter may be used 31 be arranged. The fuel tank 173 includes a fuel inlet passage connected to the fuel return passage (not shown) of the combustion system of the diesel engine 179 and a fuel return passage connected to the main fuel tank (not shown) 178 , Through the fuel inlet line 175 leads the fuel inlet opening of the plunger pump 8th from the secondary fuel tank 173 coming through the filter 31 filtered fuel, under the control of the control unit 13 the fuel gets into the jet pipe 177 pumped in and then through the nozzle 23 into the exhaust pipe 170 the engine injected, the control unit 13 At the same time, as the amount of fuel injected is metered, it is determined whether the amount of injected fuel is adequate and whether the injection continues based on the detected operating state of the engine, the pressure and resistance of DPF, the exhaust state, and the DPF temperature (not shown) shall be. The return fuel of the plunger pump 8th returns through the power return line 174 to the upper space of the fuel tank 173 back. The liquid outlet opening 182 of the secondary fuel tank 173 is located at the bottom section while the fluid return port 177 is located at a higher position, so the gas tank 173 can still perform normal operation with a small fuel storage amount.

The working process of the application system is as follows:
The engine-derived coal smoke is produced by DPF 171 and gradually accumulates therein, as the accumulation amount of the carbon smoke increases, the pressure difference AP gradually increases from the front and rear sides of DPF 171 if the controller 13 through the pressure difference sensor 180 detects that AP exceeds a certain value (the power output of the engine is already or soon to be affected), and by the temperature sensor 181 detects that the temperature exceeds a certain value, and determines, based on the signal of the accelerator pedal of the engine or with another communication method, that the oxygen component in the exhaust pipe 172 the engine exceeds a certain value drives the controller 13 the liquid jet metering unit 1 for injecting the fuel into the exhaust pipe 172 the engine, provided that the carbon smoke in the DPF 171 can be eliminated by means of oxidation, the amount of jet should be kept as small as possible. The amount of jet can in advance in the memory of the controller 13 preset, or with a sensor such as temperature sensor, a feedback control is performed, for. For example, an oxygen sensor can be added further.

In the example according to 12 For example, the fuel supplied to the fuel inlet port of the plunger pump may also be diesel fuel with combustion agent, e.g. As diesel oil with combustion catalyst, in this case, the fuel tank 173 a specific storage tank of regeneration fuel.

Moreover, the fuel metering unit of the present invention may also be used to add on-site a fuel additive of a fixed amount in the fuel, e.g. For example, a supporting catalyst (FBC) is injected directly into the diesel engine's main fuel at a fixed rate to reduce the ignition temperature of the diesel engine's particles, or in the DPF active regeneration fuel, a combustion agent is added immediately to maintain the ignition temperature of the regeneration fuel and fuel To reduce exhaust gas of the engine engineered mixture gas, etc.

The above examples are only used for explaining the present invention, the present invention is not limited thereto. All other modification solutions based on the spirit of the present invention should be considered to be within the scope of the present invention.

Claims (18)

A liquid jet metering unit and control method, characterized in that it comprises a jet unit and a metering controller, the jet unit comprising a scroll tube device, a plunger pump and a nozzle, and wherein the plunger pump comprises a plunger and a sleeve, and wherein the plunger cooperates with the sleeve forming a pressure delivery volume, and wherein the pressure delivery volume is connected to a liquid inlet valve and a liquid outlet valve, and wherein the liquid enters the pressure delivery volume through the liquid inlet valve and is output through the liquid outlet valve, and wherein the dosing controller provides the spiral tube device with a drive signal, and wherein the dosing controller a detection device for monitoring the state parameters, comprising an algorithm for estimating the effective output power of the spiral tube device m That is, the state parameters and a closed-loop flow rate control method of the liquid jet metering unit in which the effective output of the scroll tube device is used as a variable. A liquid jet metering unit and control method according to claim 1, wherein the plunger pump comprises a return spring, and wherein the sleeve has a reciprocating motion under the drive of the scroll tube device and the return spring, resulting in a changing change in the size of the pressure delivery volume. A liquid jet metering unit and control method according to claim 1, wherein the plunger pump includes a return spring, and wherein the plunger is reciprocated under the drive of the scroll tube and the return spring, resulting in a change in the magnitude of the pressure delivery volume. The liquid jet metering unit and control method of claim 3, wherein the plunger comprises an armature, and wherein the armature is approximately a cylindrical body, and wherein the armature comprises a through hole led out through the two end surfaces. Liquid jet metering unit and control method according to claim 2 or 4, characterized in that between the liquid outlet valve and the nozzle, a high-pressure line is arranged. A liquid jet metering unit and control method according to claim 5, characterized in that it comprises a gas-liquid mixing chamber, wherein the liquid is injected into the gas-liquid mixing chamber, and after mixing between the liquid and the gas, it is introduced into the exhaust pipe through an injector the engine is ejected. A liquid jet metering unit and control method according to claim 6, characterized in that the injector is a swirl nozzle. A liquid jet metering unit and control method according to any one of claims 1 to 7, characterized in that the state parameters of the spiral tube device include the current and the voltage flowing through the spiral tube. Liquid jet metering unit and control method according to claim 8, characterized in that the algorithm for estimating the Effective output of the spiral tube device comprises a step of estimating the total energy output by the metering controller, a step of estimating the power consumption of the resistance of the spiral tube and a step of estimating the inductive energy storage of the spiral tube device. A liquid jet metering unit and control method according to claim 9, characterized in that the step of estimating the total energy output by the metering controller comprises a step of integrating the time with respect to the product of the detected current of the spiral tube times voltage. A liquid jet metering unit and control method according to claim 10, characterized in that the step of estimating the power consumption of the resistance of the coil comprises a step of integrating the time with respect to the product of the square of the detected current of the spiral tube times the resistance of the spiral tube. A liquid jet metering unit and control method according to claim 11, characterized in that it comprises a step of calculating with the detected flow of the spiral tube the inductive energy storage of the spiral tube device. A liquid jet metering unit and control method according to claim 12, characterized by comprising a step of, under the conditions of liquid injection, treating the power consumption of the resistance of the coil and the inductive energy storage of the spiral tube device so as to have a linear relationship to the liquid jet amount. A liquid jet metering unit and control method according to any one of claims 1 to 7, characterized in that the state parameters of the spiral tube device include the required time T3 for reducing the electric dynamic potential to the reference voltage after the coil is turned off, the algorithm for estimating the effective output of the spiral tube device Step involves treating the effective output of the spiral tube device and T3 as a linear relationship. A liquid jet metering unit and control method according to any one of claims 1 to 14, characterized in that the target of the jet flow amount within the unit time of the liquid jet metering unit is achieved by maintaining the effective output of the spiral tube apparatus unchanged and adjusting the operating efficiency of the liquid jet metering unit. A liquid jet metering unit and control method according to any one of claims 1 to 14, characterized in that the target of the jet flow amount within the unit time of the liquid jet metering unit is achieved by maintaining the operating efficiency of the liquid jet metering unit unchanged and setting the effective output power of the spiral tube apparatus to each pulse. A liquid jet metering unit and control method according to any one of claims 1 to 14, characterized in that it comprises a method of estimating the liquid level by measuring the flow resistance caused by the liquid for the movable element of the plunger pump. Dosing module, comprising a Flüssigkeitsstrahldosiereinheit and a control method according to any one of claims 1 to 17, characterized in that it comprises a holder formed of tauro tubes, wherein the jet unit is attached to one end of the holder and the control unit at the other end of the holder.

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