WO2022195043A1

WO2022195043A1 - Flow control valve for closed-loop or open-loop controlling of a mass flow of a fluid, arrangement with a flow control valve of this type, and method for operating a flow control valve of this type

Info

Publication number: WO2022195043A1
Application number: PCT/EP2022/057063
Authority: WO
Inventors: Bernd Niethammer
Original assignee: Bernd Niethammer
Priority date: 2021-03-17
Filing date: 2022-03-17
Publication date: 2022-09-22
Also published as: DE102021106523A1

Abstract

The present invention relates to a flow control valve (10) for closed-loop or open-loop controlling of a mass flow of a fluid, comprising an inlet (14) and at least one outlet (16), a first pressure chamber (34) which is connected fluidically to the inlet (14), a second pressure chamber (70) which is connected fluidically to the outlet (16), a tappet (76), a valve seat (46), and a piston (38) which is mounted in the valve housing (12) movably along the longitudinal axis (L) and can be moved by means of the tappet (76) along the longitudinal axis (L) between a first end position and a second end position, forms a passage channel (50) which connects the first pressure chamber (34) and the second pressure chamber (70) to one another fluidically at least in the second end position, has a sealing portion (40) which bears against the valve seat (46) in the first end position and disconnects the first pressure chamber (34) from the second pressure chamber (70) fluidically in the first end position, and has a control groove (62) which provides a flow cross-sectional area which connects the passage channel (50) and the first pressure chamber (34) or the passage channel (50) and the second pressure chamber (70) to one another fluidically when the piston (38) is situated between the first end position and the second end position, wherein the size of the flow cross-sectional area is variable in a manner which is dependent on the position of the piston (38) between the first end position and the second end position. Moreover, the invention relates to a method for operating a flow control valve (10) of this type.

Description

Flow control valve for controlling or regulating a mass flow of a fluid, arrangement with such a flow control valve and method for operating such a flow control valve

The present invention relates to a flow control valve for controlling or regulating a mass flow of a fluid. In addition, the invention relates to an arrangement with such a flow control valve and a method for operating such a flow control valve.

Catalytic converters, which are used for the aftertreatment of exhaust gases that are emitted by internal combustion engines of motor vehicles, require a minimum operating temperature in order to be able to treat the exhaust gases in full. The lower limit of the minimum operating temperature is approximately in the range of 160°C to 180°C. So far, the thermal energy contained in the exhaust gas has been used to heat up the catalytic converter, which, however, leads to the situation that the minimum operating temperatures are only reached after the combustion engine has been in operation for at least 10 minutes on average. The minimum operating time depends on many factors, of which the outside temperature and the type of route driven are two of the most important factors. The lower the outside temperatures, the longer the minimum operating time. The type of route traveled is to be understood in particular as the speed profile. If you drive in "stop-and-go" mode, the minimum operating time is longer than if you drive constantly at higher speeds. In addition, modern vehicles are equipped with an automatic start-stop system to save fuel in "stop-and-go" mode, switches off the combustion engine when it is stationary, which further extends the minimum operating time. Studies have shown that in many cases a motor vehicle is not operated continuously for more than 10 minutes. As a result, the emitted exhaust gases are in many cases not or only partially treated, which leads to correspondingly high concentrations of pollutants, especially in large cities.

In order to counteract the high concentrations of pollutants, the "Euro 7 emission standard" was issued. In order to be able to meet this emission standard, it is necessary to bring the catalytic converter of a motor vehicle with a combustion engine to the above-mentioned operating temperature within 1 minute The thermal energy contained in the exhaust gas is not sufficient, which is why the catalytic converter has to be actively heated.

For this purpose it is known to use electric heaters. However, to heat the catalytic converter from ambient temperature to the above-mentioned operating temperature, high power is required, which is in the range from 10 to 30 kW and more. The commonly used vehicle batteries quickly reach their limits, with hybrid vehicles being particularly affected.

In order to protect the vehicle batteries, the catalytic converter can be heated with the chemical energy contained in the fuel instead of electrical energy. However, a corresponding burner, with which the catalyst is heated to the operating temperature and in which the fuel is injected using injection nozzles, requires only very small amounts of fuel. The corresponding mass flows are around 1 to 2 kg/h. In order to bring the catalytic converter up to the operating temperature in the most fuel-efficient manner possible bring, it is therefore necessary to precisely regulate the smallest mass flows of fuel. For this purpose, valves can be used, for example, which are disclosed, for example, in DE 102012 214 734 A1, DE 4111 537 A1, DE 102016 121 206 A1, DE 102006 040 311 A1 and DE 2813 090 A1.

In principle, two different types of valves can be used, namely a seat valve on the one hand and a slide valve or piston valve on the other. However, seat valves have the disadvantage that they release a comparatively large flow cross-sectional area per stroke unit, so that they are not or only partially suitable for controlling the amounts of fuel required here with sufficient precision.

Controlling the smallest amounts of fuel is much easier to implement with a slide or piston valve. Here, the shut-off body designed as a piston is provided with a control groove, which releases a larger or smaller cross-sectional flow area depending on the position of the piston in the valve. Due to the principle, however, spool or piston valves have a certain amount of leakage. If, for example, a motor vehicle were not moved for a long period of time, a large quantity of fuel could accumulate in an uncontrolled manner, which could cause problems when igniting. In order to remedy this situation, it is known to connect a seat valve and a spool or piston valve in series. The seat valve is used to seal a line without leaks, while the spool or piston valve is used to control the mass or volumetric flow. However, the cost of providing them is relatively high here, since two components are required, which also require a corresponding amount of space. In addition, the poppet valve and the spool or piston valve can be coordinated with each other in terms of control technology, which further increases the effort.

Further valves are disclosed, for example, in DE 102012 214 734 A1, DE 4111 537 A1, DE 102016 121 206 A1, DE 10 2006 040 311 A1 and DE 28 13 090 A1.

The object of one embodiment of the present invention is to propose a flow control valve with which even small mass flows can be regulated without leaks and with sufficient precision. In addition, an embodiment of the invention is based on the object of specifying a method for operating such a flow control valve.

This object is achieved with the features given in claims 1, 17 and 21. Advantageous embodiments are the subject matter of the dependent claims.

One embodiment of the invention relates to a flow control valve for controlling or regulating a mass flow of a fluid, comprising

- at least one input and at least one output,

- a fluidically connected to the input first pressure chamber,

- a fluidically connected to the outlet second pressure chamber, wherein the first pressure chamber along a longitudinal axis is arranged axially offset to the second pressure chamber,

- a plunger, which is movably mounted along the longitudinal axis and can be moved along the longitudinal axis by means of an actuation device that can be energized,

- a valve seat, and - a piston, which o is mounted so that it can move along the longitudinal axis and can be moved by means of the ram along the longitudinal axis between a first end position and a second end position, o forms a through-channel that fluidically connects the first pressure chamber and the second pressure chamber at least in the second end position with each other, o has a sealing section which rests against the valve seat in the first end position and fluidly separates the first pressure chamber from the second pressure chamber in the first end position, and o has a control groove which provides a cross-sectional flow area which separates the passage channel and the first The pressure chamber or the passage channel and the second pressure chamber are fluidly connected to one another when the piston is between the first end position and the second end position, with the size of the flow cross-sectional area depending on the position of the piston between the first end position and the second end change position is cash.

The piston has on the one hand a sealing section and on the other hand a control groove. With the sealing section, the flow control valve can be closed without leakage in the first end position. Consequently, the first end position can also be referred to as the closed position. With the control groove, the flow cross-sectional area through which the fluid must flow can be selected depending on the position of the piston between the first and the second end position. The fluid can in particular be fuel, which is used to heat up a catalyst by means of a burner the use of the flow control valve is not limited to any particular type of fluid. The proposed flow control valve therefore combines the advantages of a seat valve (leak-free seal) with the advantages of a slide or piston valve (precise control of even the smallest mass flows). There is no need for coordination of control and regulation technology, as is necessary with seat valves and spool or piston valves connected in series. In addition, installation space can be saved since the flow control valve can be made more compact than separate seat valves and spool or piston valves. Since only one valve has to be manufactured, a contribution is made to the resource-saving use of raw materials. If there is a sufficient quantity, cost advantages can also be expected.

According to a further embodiment, the control groove can have a depth that changes along the longitudinal axis. Since the depth of the cam can change linearly, so that it forms a certain angle of inclination to the longitudinal axis. In this embodiment, the control groove can be manufactured in a particularly simple manner. However, it is just as possible to give the control groove a certain profile, so that the depth of the control groove does not change linearly. This can be desirable for technical control reasons.

In a further developed embodiment, the control groove can have a width that changes along the longitudinal axis. Here, too, the width of the control groove can change linearly or by means of a certain profile. Both the changing width and the changing depth of the control groove ensure that the flow cross-sectional area changes depending on the position of the piston between the first end position and the second end position changes. The mass flow can be set accordingly by the flow control valve.

In a further developed embodiment, the piston can be pretensioned by means of a first spring in the first end position. As mentioned, the sealing section is in contact with the valve seat in the first end position. As a result, the flow control valve is closed without leakage. As he also mentions, the piston is moved along the longitudinal axis with the aid of the plunger by means of an energizable actuating device. In the event that the power supply fails for whatever reason, the first spring ensures that the flow control valve is closed. In particular, when the flow control valve is used to control or regulate a mass flow of a fuel with which a catalytic converter is heated to the operating temperature, the first spring ensures that the flow control valve is closed when the motor vehicle in question is shut down and not in operation. An uncontrolled accumulation and/or escape of fuel is avoided.

In a further embodiment, the ram can have a first end face and a second end face and a ram bore running between the first end face and the second end face, the first end face interacting with the piston in order to move it and the ram bore is fluidically connected to the through-flow channel . In this case, a third pressure chamber can be provided, into which the tappet bore opens at the second end face. In this embodiment it is possible to set the same pressure in the first pressure chamber and in the third pressure chamber. As a result, the plunger only has to oppose that exerted by the first spring Biasing force can be moved, but not against a dif- ferential pressure. The actuating device can therefore either have smaller dimensions or be operated with a lower current. In addition, the ram can be accelerated more quickly, so that control can take place more quickly and dynamically.

A further developed embodiment can be characterized in that the tappet is prestressed against the piston by means of a second spring. The second spring supports the actuating device in moving the tappet, so that the tappet can also be accelerated more quickly as a result, which in turn leads to faster and more dynamic regulation. In addition, the ram is prevented from hitting the piston in an uncontrolled manner. As a result, noise and damage are avoided. In addition, the constant contact of the piston on the ram means that there is always a flow of force between the piston and the ram.

According to a further embodiment, the flow control valve comprises a first screw plug for adjusting the biasing force of the first spring and/or a second screw plug for adjusting the biasing force of the second spring. With the screw plug, the first spring and the piston in the flow control valve are set to a specific flow rate at a specific flow during assembly. The prestressing force of the second spring acting on the tappet and thus also on the piston can be adjusted with the second locking screw, with the prestressing force of the first spring and that of the second spring acting in opposite directions. The flow control valve can be calibrated in this way and guarantee a common reference point for operation in the Vehicle and the parameter data stored there in order to be able to regulate the amount of fluid precisely.

According to a further embodiment, a contact piston can be connected to the piston, the contact piston interacting with the first end face of the plunger. Depending on the configuration of the piston, the control groove can start from that piston end face which interacts with the tappet. In this respect, the end face in question can be damaged in the position on the plunger on the same. This damage, in turn, can also affect the control groove, which can change its shape. The change in shape can cause a change in flow cross-sectional area, which can adversely affect the control or regulation of mass flow through the flow control valve. The contact piston can be designed and arranged in such a way that the piston end face in question is protected, so that the influences on the control groove mentioned above can be prevented.

In accordance with a further embodiment, the contact piston can have a through bore which fluidly connects the through-channel and the tappet bore. The contact piston can be essentially tubular and thus be designed in a simple manner. This ensures that the pressures in the first pressure chamber and in the third pressure chamber can equalize.

In a further developed embodiment, the contact piston can have at least one further bore opening into the through bore, which fluidically connects the through bore to the control groove. Consequently, the passage channel is also fluidly connected to the other bores. In this Embodiment, the contact piston is integrated into the flow path of the fluid through the flow control valve. The constructive configuration of the contact piston can be kept simple as a result.

In a further developed embodiment, the first pressure chamber and the second pressure chamber as well as the valve seat can be formed from an insert part that can be inserted into the flow control valve. The insert is also referred to as a "cartridge". The use of an insert simplifies the manufacture of the flow control valve significantly, so that the manufacturing costs can be kept low.

A further embodiment can be designed in such a way that a sealing element is arranged in the sealing section, which has a polygonal cross section in relation to a sectional plane running through the longitudinal axis. In many cases, the sealing elements are designed as O-rings, which have a circular or elliptical cross section. Due to the circular or elliptical cross-section, the O-rings have a comparatively small contact surface in the relevant groove, which results in a relatively strong deformation when the flow control valve is in the first end position and the O-ring is loaded accordingly. If the flow control valve is to be opened, the deformations must first be overcome, which requires a certain stroke. However, this hub is then no longer available for controlling the mass flows, which has a negative effect on the dynamics and the accuracy of the control.

If the sealing element has a polygonal cross section, it can bear against the groove in question over a large area, as a result of which the deformation in the first end position is significantly reduced can be. As a result, the flow control valve opens even with smaller strokes, which improves the accuracy and the dynamics of the control of the mass flows. In the case of sealing elements with a polygonal cross section, it is particularly advisable to arrange the groove in question either in the valve housing or on the piston, which increases design freedom.

In a further embodiment, the flow control valve can have a temperature sensor for determining the temperature of the fluid in the inlet. The viscosity and density of fluids are generally temperature dependent. Knowing the temperature of the fluid at the inlet can be taken into account when controlling the flow control valve and, in particular, when determining the axial position of the piston. As a result, the size of the flow cross-sectional area can be adjusted so that the required mass flow can be provided by the control valve regardless of the temperature of the fluid.

A further developed embodiment can be characterized in that the flow control valve has a first pressure sensor for determining the pressure of the fluid in the inlet. The mass flow of the fluid through the flow control valve depends on the pressure of the fluid. As already described for the temperature, the pressure that the fluid has in the inlet can be taken into account when controlling the flow control valve. As a result, the desired mass flow can be set independently of the pressure of the fluid in the inlet.

In a further embodiment, it may be appropriate for the flow control valve to have a second pressure sensor for determining the pressure of the fluid in the outlet. Usually atmospheric pressure prevails at the outlet. However, there can also be operating states in which there is a negative pressure at the output. As a result, a suction effect occurs, which in turn influences the mass flow through the flow control valve. In the event that the flow control valve has both the first pressure sensor and the second pressure sensor, a differential pressure between the input and the output can be determined, which in turn can be taken into account when controlling the flow control valve, also with the aim of achieving the desired mass flow to be able to be set as precisely as possible by the flow control valve. In this case, the flow control valve can also be used as a pressure control valve. This case can occur, for example, when a certain pressure is required for the function of the injection nozzle. In this case, the injection nozzles can be designed in such a way that they allow a specific quantity of fuel to flow through over an available cross section and existing pressure. This characteristic of an injection nozzle, i.e. the relationship between the available cross-section, prevailing pressure and the resulting mass flow, can be stored on a corresponding unit. Thus, the pressure can be used to control or regulate the mass flow through the injection nozzle to the burner by means of the pressure sensor. The mass flow flowing through the control groove is pressure-dependent, which is why the pressure level upstream of the control groove is determined with the first pressure sensor in order to place the control groove in the correct position. The second pressure sensor is used, for example, to determine the pressure in front of or at a throttle or orifice that is arranged downstream of the control groove. In this respect, one embodiment of the invention also relates to the use of the flow control valve according to one of the previous embodiments as a pressure control valve. In this case, the term "flow control valve" can be replaced by the term "pressure control valve". A further developed embodiment can be characterized in that the flow control valve has a position determination unit for determining the piston. As mentioned, the piston can be biased into the first end position by means of the first spring. Due to the friction of the piston on the adjacent components, a more or less large hysteresis occurs, which can change during operation of the flow control valve and can be influenced by dirt and particles. As a result, the relationship set between the strength of the energization and the resulting position of the piston also changes. This can mean that the mass flow can no longer be controlled or regulated with the desired accuracy. Such hysteresis occurs particularly when the direction of movement of the piston is reversed. In particular, one cannot make a statement with the necessary certainty as to whether the flow control valve is actually in the first end position and is consequently closed. In this respect, a certain amount of leakage can occur unnoticed. If, for example, a motor vehicle would not be moved for a long time, a larger amount of fuel could collect in an uncontrolled manner, which could cause problems when igniting.

With the position determination unit, a statement about the position of the piston can be made. In the simplest case, the position determination unit can include a contact switch, which generates a corresponding signal when the piston is in the first end position. Consequently, it can be determined whether the flow control valve is actually closed or not. However, the position determination unit can also be designed in such a way that the current position of the piston can be determined continuously or quasi-continuously. Consequently, the actual position of the piston can be determined and compared with the target position. If there is a deviation, it can be corrected accordingly. A closed control loop can thus be implemented. It can also be determined if the piston should get stuck in the flow control valve. A corresponding warning signal can be issued, which indicates the corresponding fault and recommends a visit to the workshop.

One embodiment of the invention relates to an arrangement for controlling or regulating a mass flow of a fluid, with a flow control valve and a burner which has a combustion chamber, the flow control valve comprising at least one inlet and at least one outlet, the outlet being fluidically connected to the combustion chamber , a first pressure chamber which is fluidically connected to the inlet, a tappet which is mounted in the valve housing so that it can move along the longitudinal axis and can be moved along the longitudinal axis by means of an actuating device which can be energized, a valve seat, and a piston which is mounted in the valve housing so that it can be moved along the longitudinal axis and can be moved by means of the plunger along the longitudinal axis between a first end position and a second end position, o forms a passage channel which fluidly connects the first pressure chamber and the combustion chamber at least in the second end position, o has a sealing section which rests against the valve seat in the first end position and fluidly separates the first pressure chamber from the combustion chamber in the first end position, and o provides a flow cross-sectional area between the piston and the through-channel, which connects the through-channel and the first pressure chamber or the through-channel and the Combustion chamber fluidly connects with each other when the piston is between the first end position and the second end position, the size of the flow cross-sectional area depending on the position of the piston between the first end position and the second end position being changeable.

In this version, the burner injection nozzle is integrated into the flow control valve. Consequently, the injection nozzle can be directly controlled or regulated by means of the actuation device that can be energized, as a result of which the precision of the mass flow that is injected into the combustion chamber can be further increased. In addition, the number of components is reduced, which increases the reliability of the arrangement.

According to a further embodiment, the piston has a swirl structure which causes the fluid to swirl as it flows into the combustion chamber. The swirl structure can have grooves and/or projections, which specify a certain direction for the fluid, in particular impart a radial directional component. As a result, the fuel used in the combustion chamber is better distributed compared to a piston without a swirl structure, resulting in finer particles that lead to better combustion. A variant of the device relates to a device for controlling or regulating a mass flow of a fluid, comprising

- a fluid reservoir for holding the fluid,

- a main line through which the fluid can be conducted to a consumer,

- a feed pump arranged in the main line for conveying the fluid in the same,

- a burner, which has a combustion chamber,

- A secondary line branching off from the main line and opening into the combustion chamber, and

- A arranged in the secondary line flow control valve according to one of the aforementioned embodiments, with which the mass flow into the combustion chamber can be controlled or regulated.

The technical effects and advantages that can be achieved with the proposed device before, correspond to those that have been discussed for the present flow control valve. In summary, it should be pointed out that with the present flow control valve it is possible to control or regulate even the smallest mass flows with sufficient accuracy without leakage occurring. It is not necessary to use spatially separated poppet valves and slide or piston valves. Voting for control or regulation purposes can be omitted.

According to a further variant, a branch is arranged between the flow control valve and the combustion chamber, in which a low-pressure line branches off from the secondary line and opens into the combustion chamber, wherein

- In the secondary line, a first throttle and/or - A second throttle is arranged in the low-pressure line and

- in the bypass a bypass valve and/or

- In the low-pressure line, a low-pressure valve are net angeord, which releases or blocks the secondary line and / or the low pressure line depending on the pressure between the flow control valve and the junction.

For example, the first throttle can be a high-pressure throttle and the second throttle can be a low-pressure throttle. If only a small amount of heat is required, the fuel can be injected through the second throttle into the combustion chamber. At higher heat outputs, the fuel can be introduced into the combustion chamber through the first throttle at a higher pressure and a higher mass flow. The burner can thus be operated with different outputs. The mass flow of the fuel introduced into the combustion chamber can be better adapted to the heat output actually required. The fuel consumption can be reduced as a result.

In order to keep the throttling losses of the bypass valve and/or the low-pressure valve low, return springs with a degressive or falling spring characteristic can be used. Once the pressure required to switch the valve is reached, there is no further resistance to the switching process and the maximum cross-section is released almost immediately. As a result of the falling force over the stroke, digital switching behavior occurs in the respective valves.

In the context of the present disclosure, a throttle should also be understood to mean an aperture. In particular, the Whether the pressure drop is temperature dependent or not is irrelevant.

One embodiment of the invention relates to a method for operating a flow control valve according to one of the previous embodiments, comprising the following steps:

- Prestressing of the piston into the first end position by means of the first spring, so that the sealing section rests against the valve seat,

- Energizing the actuating device to move the plunger along the longitudinal axis in such a way that o the piston is displaced along the longitudinal axis against the prestressing force of the first spring and the sealing section is moved away from the valve seat and o the control groove moves the passage channel and the first pressure chamber or the passage channel and fluidically connects the second pressure chamber with one another, the size of the flow cross-sectional area of the control groove depending on the position of the piston between the first end position and the second end position being changeable by means of the energization of the actuating device.

The technical effects and advantages that can be achieved with the proposed method before, correspond to those that have been discussed for the present flow control valve are the. In summary, it should be pointed out that with the present flow control valve it is possible to control or regulate even the smallest mass flows with sufficient accuracy without leakage occurring. It is not necessary spatially separate seat valves and spool or piston valves to use. Voting for control or regulation purposes can be omitted.

Exemplary embodiments of the invention are explained in more detail in the fol lowing with reference to the accompanying drawings. Show it

FIG. 1 shows a perspective view of a first embodiment of a proposed flow control valve,

Figure 2 is a side view of the flow control valve shown in Figure 1,

Figure 3 shows a sectional view through the flow control valve along the sectional plane A-A defined in Figure 2,

FIG. 4 shows an enlarged view of section B defined in FIG. 3,

FIG. 5 shows an enlarged representation of section C defined in FIG. 4,

FIG. 6 shows an enlarged representation of a second embodiment of a flow control valve based on the representation selected in FIG. 5,

Figures 7A to 7D different versions of the cam

Figures 8A and 8B is an enlarged view of a third

embodiment based on the representation chosen in Figure 4, FIGS. 9A and 9B show an enlarged representation of a fourth exemplary embodiment based on the representation chosen in FIG. 4,

FIG. 10 shows a circuit diagram of a first exemplary embodiment of a device for controlling or regulating a mass flow of a fluid,

FIG. 11 shows a circuit diagram of a second exemplary embodiment of a device for controlling or regulating a mass flow of a fluid,

FIG. 12 shows a circuit diagram of a third exemplary embodiment of a device for controlling or regulating a mass flow of a fluid,

FIG. 13 shows a circuit diagram of a fourth exemplary embodiment of a device for controlling or regulating a mass flow of a fluid,

FIG. 14 shows a circuit diagram of a fifth exemplary embodiment of a device for controlling or regulating a mass flow of a fluid,

Figure 15 is a sectional view through a third second embodiment of the flow control valve, and

FIG. 16 shows a partial representation of a piston with a swirl structure.

In the figures 1 and 2 is an embodiment of a flow control valve 10 according to the present invention based shown a perspective view or based on a Seitenan view. The flow control valve 10 has a valve housing 12 with an inlet 14 and an outlet 16 . At the input 14, a supply line, not shown here, can be ruled out, with which a fluid, for example fuel, can be supplied to the flow control valve 10 from a pressure source. Accordingly, a discharge line, also not shown, can be connected to the output 16, with which the fluid that has flowed through the flow control valve 10 can be passed on to a consumer, for example a burner (see FIG. 10 for example). Furthermore, a temperature sensor 18 is attached to the valve housing 12, with which the temperature of the fluid in the input 14 is determined by whoever can. Furthermore, a first pressure sensor 20 is attached to the housing 12 Ventilge, which serves to determine the pressure of the fluid in the input 14. In addition, the flow control valve 10 includes a second pressure sensor 22 which can be used to determine the pressure of the fluid in the outlet 16 . In addition, an actuating device 24 is shown in FIG. 1, which can be energized. Correspondingly, power connections 26 can be seen in FIG. The exact function of the actuating device 24 will be discussed in more detail below.

FIG. 3 shows a sectional illustration of the flow control valve 10 illustrated in FIGS. 1 and 2 along the sectional plane AA defined in FIG. It can be seen that the valve housing 12 is designed as a valve block 28 and is consequently solid. In the valve block 28 a sleeve-shaped insert part 30 is used, for which purpose the valve block 28 has a corresponding valve block bore 32 . Within the insert part 30, a first pressure chamber 34 is arranged, which is fluidly connected to an input bore 36 with the input 14. The term "fluidically connected" can be understood below to mean that a fluid can flow between the fluidically connected components without these necessarily being mechanically connected to one another.

Within the insert part 30, a piston 38 is mounted slidably along a longitudinal axis L defined by the valve block bore 32. As can be seen in particular from FIG. 4, which shows enlarged detail B in FIG that is. The piston 38 is pressed against a valve seat 46 formed by the insert part 30 by a first spring 44 . The piston 38 is designed in such a way that the sealing section 40 rests against the valve seat 46, in this case with the O-ring 42. Alternatively, a metallic sealing seat (not shown) can also be provided, in which the piston 38 has an outer cone , Which can be pressed against an inner cone of a spare part 30. The first spring 44 is supported on a first screw plug 48 which is screwed into the spare part 30, as can be seen in particular from FIG. The prestressing of the first spring 44 can be adjusted with the first locking screw 48 . A spare part 30 is covered with a cover 49 at the left end.

Referring to FIG. 4, the piston 38 is provided with a through-channel 50 which includes a blind bore 52 and a number of radial bores 54 running perpendicularly to the longitudinal axis L in the area of the closed end. A contact piston 56 is connected to the piston 38 at the free end of the passage channel 50 . The contact piston 56 is equipped with egg ner through hole 58, which is approximately with the Passage channel 50 is aligned. In addition, the contact piston 56 has a number of further bores 60 which run perpendicular to the longitudinal axis L and open into the passage bore 58 . As can be seen in particular from FIG. 5, which shows the section C marked in FIG Piston end face 64 of the piston 38 goes out.

Figures 7A to 7D show some embodiments of this control groove 62. Figures 7A to 7B are a basic plan view of the control groove 62 and of the piston 38, while Figures 7C and 7D are a basic sectional view through the control groove 62 and consequently through the piston 38 It can be seen from FIGS. 7A and 7B that the control groove 62 can have a width W that changes along the longitudinal axis L. While the width W of the control groove 62 shown in FIG. 7A changes linearly along the longitudinal axis L, the width W of the control groove 62 shown in FIG. 7B changes along the longitudinal axis L by means of a non-linear relationship.

FIGS. 7C and 7D show that the depth T of the control groove 62 along the longitudinal axis L can change. Again, the depth in the control groove 62 shown in FIG. 7C changes linearly along the longitudinal axis L, while the depth T of the control groove 62 shown in FIG. 7D changes along the longitudinal axis L with a non-linear relationship. The control groove 62 shown in FIG. 5 essentially corresponds to that shown in FIG. 7C. It can also be seen from FIG. 5 that the contact piston 56 is constructed in the shape of a mushroom and forms an edge 66 that protrudes radially outwards. This edge 66 projects along the longitudinal axis L beyond the piston end face 64, so that an intermediate space 68 is formed between the piston 38 and the edge 66. This gap 68 joins the other bores 60 of the contact piston 56 radially outward Shen.

Referring in particular to FIGS. 4 and 5, a second pressure chamber 70 is arranged in the spare part 30, which is fluidically connected to the outlet 16 by means of an outlet bore 72, which is particularly clear from FIG.

It can also be seen from FIG. 3 that the actuating device 24 includes an electromagnet 74 with which a plunger 76 mounted concentrically to the longitudinal axis L can be displaced along the longitudinal axis L. The plunger 76 has a first end face 78 which can be seen particularly well in FIG. 5 and which can be brought into contact with the contact piston 56 . In addition, the tappet 76 has a second end face 80, which is shown in FIG. Between the first end face 78 and the second end face 80 there extends a tappet bore 82 which surface 80 opens into a third pressure chamber 83 on the second end face. It can be seen from FIG. 5 that the tappet bore 82 in the region of the first end face 78 is fluidically connected to the through bore 58 of the contact piston 56 and consequently also to the through-channel 50 of the piston head. In addition, it can be seen from FIG. 3 that a second spring 84 is at least partially arranged in the third pressure chamber 83 and prestresses the plunger 76 against the contact piston 56 . The second spring 84 is supported on a second locking screw 86, with which the biasing force of the second spring 84 can be adjusted.

Referring to FIG. 2, it becomes clear that two transverse bores 90 connect the tappet bore 82 to an armature space 92 . Furthermore, the electromagnet 74 has a cone 94, an armature 96, a copper coil 98 and a non-magnetic sleeve. The copper coil 98 can also consist of another suitable material. In this way it is achieved that the magnetic field is directed in such a way that the magnetic force applied by the electromagnet can be transmitted as effectively as possible to the plunger 76 and can be converted into a linear movement of the plunger.

The flow control valve 10 is operated in the following manner: In the de-energized state, which is shown in Figures 3 to 5, the piston 38 is pressed with the first spring 44 against the valve seat 46 so that the piston 38 assumes a first end position. in which the control valve is sealed leak-free in particular with the O-ring 42 . It is therefore a "normally closed" flow control valve 10. The second spring 84 presses the plunger 76 against the contact piston 56. Since the biasing force exerted by the second spring 84 is less than the biasing force exerted by the first spring 44, the Piston 38 is not moved away from the valve seat 46. In the first end position, the fluid which is present at the inlet 14 with a specific inlet pressure can only flow via the inlet bore 36 into the first pressure chamber 34 and up to the valve seat 46, but no further Now the actuator 24 is energized, the plunger 76 is moved to the contact piston 56 and the Kol ben 38, as a result of which the piston 38 together with the contact piston 56 against the direction of action of the biasing force the first spring 44 and against the valve seat 46 we kenden differential pressure between the input 14 and the output 16 is displaced. Based on the representation selected in FIGS. 3 to 5, the plunger 76, the contact piston 56 and the piston 38 are moved to the left. As a result, the sealing portion 40 is moved away from the valve seat 46. As soon as the radial bores 54 are displaced beyond the valve seat 46 into the first pressure chamber 34, the first pressure chamber 34 and the through-channel 50 are fluidically connected to one another, as a result of which the fluid flows from the first pressure chamber 34 through the through-channel 50 to the through-bore 58 and on through the others Holes 60 to the gap 68 between the piston 38 and the edge 66 of the contact piston 56 can flow. At the same time, the fluid also continues to flow through the ram bore 82 and the transverse bores 90 into the armature chamber 92 and into the third pressure chamber 83. This ensures that the hydraulic axial forces are compensated and the electromagnet 74 only works against the force of the first spring 44 works. The fluid can then flow into the control groove 62 . It can be seen from FIG. 5 that a certain overlap D remains between the end of the control groove 62 pointing to the second pressure chamber 70 and a wall 88 of the second pressure chamber 70 in the first end position. This overlap D ensures that no fluid flows into the outlet bore 72 when the valve seat 46 is opened.

The fluid can only flow completely through control groove 62 and into the second pressure chamber 70 occur. From there it can flow on to the outlet 16 via the outlet bore 72 . As already mentioned, the ram 76 has the ram bore 82 which runs between the first end face 78 and the second end face 80 . Consequently, the fluid can enter from the through hole 58 of the contact piston 56 into the ram hole 82 and from there continue to flow into the armature space 92 and the third pressure space 83 . This ensures that the pressure in the third pressure chamber 83 corresponds to the pressure in the first pressure chamber 34 . As a result, the plunger 76, the contact piston 56 and the piston 38 must not be moved against a dif ference pressure as soon as fluid communication between the first pressure chamber 34 and the third pressure chamber 83 has been established. It can be seen in particular from FIG. 4 that a certain distance along the longitudinal axis L remains between the valve seat 46 and the radial bores 54 when the piston 38 is in the first end position. In the first end position, this distance is less than the overlap D already mentioned. As a result, the pressure equalization between the first pressure chamber 34 and the third pressure chamber 83 does not take place immediately after the piston 38 begins to move away from the valve seat 46, but first at O -Ring 42 is moved out of the valve seat 46. Rather, the piston 38 must be moved by a certain distance in order to be able to produce the pressure equalization. As long as this pressure equalization has not yet been established, the piston 38, the contact piston 56 and the plunger 76 must be moved against the differential pressure, for which purpose the actuating device 24 can be subjected to a "peak current". As soon as the pressure equalization has been established , the piston 38, the contact piston 56 and the plunger 76 only have to be moved against the difference between the prestressing force of the first spring 44 and the prestressing force of the second spring 84. A significantly lower current is required for this Position of the piston 38, in which the pressure equalization has already been established, but the overlap D is indeed reduced ver, but not yet been completely eliminated. Therefore, no fluid can yet flow from the control groove 62 into the second pressure chamber 70 .

Referring in particular to FIGS. 5 to 7D, it can be seen that, depending on the position of the piston 38, the size of the flow cross-sectional area that the control groove 62 releases changes. As long as the control groove 62 does not protrude into the second pressure chamber 70 , it can be assumed that the fluid cannot flow from the control groove 62 into the second pressure chamber 70 . The further the control groove 62 protrudes into the second pressure chamber 70, the greater the flow cross-sectional area released by the control groove 62 and consequently the mass flow. Accordingly, the mass flow of the fluid through the flow control valve 10 can be adjusted by means of the position of the piston 38, for which purpose the actuating device 24 is energized to a greater or lesser extent. When the current supply decreases, the prestressing force of the first spring 44 ensures that the piston 38 is displaced in the direction of the valve seat 46, to the right in FIGS. When the piston 38 has been displaced so far against the direction of action of the first spring 44, to the left in FIGS. 3 to 5, that the fluid flows directly from the space 68 between the piston 38 and the edge 66 of the contact piston 56 into the second pressure chamber 70 can flow, the control groove 62 loses its influence on the mass flow of the fluid through the flow control valve 10. In this case, the piston 38 is in a second end position. In the second end position, a very high mass flow can be set. If the energization of the actuating device 24 is removed, the first spring 44 pushes the piston 38 back into the first end position. The mass flow of the fluid through the flow control valve 10 depends not only on the size of the flow cross-sectional area released by the control groove 62, but also, among other things, on the temperature and pressure of the fluid in the input 14. For this reason, the temperature of the fluid in the Input 14 with the temperature sensor 18 and the pressure of the fluid in the input 14 with the first pressure sensor 20 determines who the. Atmospheric pressure is usually present at the outlet 16, so that the pressure of the fluid in the inlet 14 can also be used to determine a pressure difference. Depending on the area of application of the pressure control valve, however, it can also happen that there is a vacuum at the outlet 16 and suction effects therefore occur. The pressure of the fluid in the outlet 16 can be determined with the second pressure sensor 22 , so that a differential pressure between the inlet 14 and the outlet 16 can also be determined in the event of a negative pressure at the outlet 16 . The temperature measured by the temperature sensor 18 and the pressures of the fluid measured by the first pressure sensor 20 and the second pressure sensor 22 can be taken into account when controlling the flow control valve 10. The energization of the actuating device 24 can be selected in such a way that the desired mass flow through the Pressure control valve adjusts even with changing temperature and pressure conditions.

FIG. 6 shows a second exemplary embodiment of a flow control valve 10 based on the representation selected in FIG. The essential structure of the flow control valve 10 according to the second embodiment corresponds largely to that of the first embodiment. The manner in which the two flow control valves 10 are operated is also largely the same. However, if you compare the control grooves 62, you will find that the control groove 62 according to the one shown in Figure 6 The flow control valve 10 shown is greater than the control groove of the flow control valve 10 shown in FIG. 5. In particular, the depth T (cf. FIGS. 7A to 7D) is greater. The mass flow of the fluid that can flow through the control groove 62 is correspondingly greater, so that the flow control valve 10 shown in FIG 1 to 5 shown flow control valve 10 is suitable for cars.

It should also be noted that a compensating ring 102 can be seen in FIG. 6, with which the position of the contact piston 56 with respect to the longitudinal axis L can be adjusted. Different compensation rings 102, which have different extensions along the longitudinal axis L, can be used here. Manufacturing inaccuracies can be compensated with the compensation ring 102.

With the screw plug 48, the first spring 44 and the piston 38 in the flow control valve 10 are set to a specific flow rate during assembly at a specific current. The flow control valve 10 can be calibrated in this way and guarantee a common reference point for operation in the vehicle and the parameters stored there, in order to be able to precisely control the amount of fuel.

In the figures 8A and 8B, a third embodiment of a flow control valve 10 based on the ge selected in Figure 4 is shown enlarged detail. In FIG. 8A, the flow control valve 10 is in the first end position, while in FIG. 8B it is between the first end position and the second end position. The main difference lies in the design of the sealing element 41, which in the third exemplary embodiment shown here is not designed as an O-ring 42, but which has a planar polygonal cross section in relation to a section running through the longitudinal axis L. The sealing element 41 is arranged in a piston 38 arranged in the sealing element groove 43 at.

As can be seen in particular from FIG. 8B, the sealing element 41 has a rectangular cross section. In the first end position (see FIG. 8A), the sealing element 41 rests against the valve seat 46 and is correspondingly deformed. In order to allow the deformation, 46 free spaces are provided radially outside of the valve seat.

In the figures 9A and 9B, a fourth exemplary embodiment of a flow control valve 10 based on the representation selected in FIG. 4 is shown in an enlarged detail. In FIG. 9A, the flow control valve 10 is in the first end position, while in FIG. 9B it is between the first end position and the second end position. In the fourth exemplary embodiment as well, the sealing element 41 has a planar polygonal cross section in relation to a section running through the longitudinal axis L. In this case, the sealing element 41 is equipped with a pentagonal cross section. In contrast to the third exemplary embodiment of the Stromre gelventils 10, the sealing element 41 is arranged in a spare part 30 located in a sealing element groove 43. Due to the pentagonal cross section, the sealing element 41 forms a conical sealing surface, with which the sealing element 41 comes into contact in the first end position with a corresponding conical sealing surface of the piston 38 (see FIG. 9A). In the first end position, the piston 38 is at a Contact surface 104 of the insert part 30 at. This prevents the sealing element 41 from being subjected to excessive loads and correspondingly severe deformation, which in extreme cases could lead to the sealing element 41 being destroyed.

Due to the polygonal cross section of the sealing element 41, it rests over a large area in the sealing element groove 43, which is why the deformation of the sealing element 41, which occurs in the first end position, is kept low compared to the O-ring 42. Due to the lower deformations, the flow control valve 10 opens at a lower stroke than is the case in comparison to the O-ring 42, in which only the defor regulations must be overcome so that the flow control valve 10 opens.

FIG. 10 shows a circuit diagram of a first exemplary embodiment of a device 106i for controlling or regulating a mass flow of a fluid. The device 106i has a fluid reservoir 108 in which a fluid, in this case a fuel, can be stored. A main line 110 is connected to the fluid reservoir 108, through which the fluid can be conveyed to a consumer 112, for example to a combustion engine. In the main line 110, a feed pump 114 is arranged, which promotes the fluid to the consumer 112 and provides the system pressure required for this purpose. A pressure control valve 116 is arranged in the main line 110 to ensure that the necessary system pressure is present at the consumer 112 . Seen from the feed pump 114 behind the pressure control valve 116 from a branch 118 is provided, at which a secondary line 124 branches off from the main line 110, which opens into a combustion chamber 119 egg Nes burner 17. In the secondary line 124 are of the Branch 118 seen from first the temperature sensor 18 already mentioned and then the first pressure sensor 20 is arranged. The flow control valve 10 is arranged behind it. It can also be seen in FIG. 10 that the flow control valve 10 has a position determination unit 120 with which the position of the piston 38 can be determined. Seen from the junction 118 behind the flow control valve 10 of the already mentioned burner 17 is arranged.

All of the components located within the area bordered by dashed lines can be integrated directly in the flow control valve 10 . The mode of operation for controlling or regulating the mass flow of the fluid which is conveyed into the combustion chamber 119 of the burner 17 has already been sufficiently described. At this point it should also be mentioned that the position determination unit 120 can be integrated into a control loop. The position determination unit 120 is able to determine the current actual position of the piston 38 and consequently also the flow cross-sectional area released by the control groove 62 and to compare it with the target position. In the event of deviations, the difference between the actual position and the target position can be reduced and ideally set to zero by means of a corresponding energizing of the actuating device 24 . In addition, it can also be determined whether the piston 38 is actually in the first end position, if this is so desired in order to avoid unintentional leakage. In addition, it can also be determined whether the piston 38 has jammed in the valve housing 12 and is no longer moving. In both cases, a corresponding error signal can be output so that the error can be rectified quickly. FIG. 11 shows a circuit diagram of a second exemplary embodiment of the device IO6 ₂ . The main structure corresponds to that of the device IO6 ₁ according to the first exemplary embodiment of the device IO6 ₁ shown in FIG. 10, which is why the main differences are discussed below. The flow control valve 10 includes not only the first pressure sensor 20 but also the second pressure sensor 22. It can also be seen that the first pressure sensor 20 is arranged upstream of the control groove 62 and the second pressure sensor 22 is arranged downstream of the control groove 62. In this case, the flow control valve 10 is designed as a 3/2 valve. The additional output is pressureless ver connected to the fluid reservoir 108 and serves to relieve pressure.

Due to the fact that the flow control valve 10 has the first pressure sensor 20 and the second pressure sensor 22 in the specified arrangement, the flow control valve 10 in this embodiment can be used as a pressure control valve. In this embodiment, the mass flow of the fluid to the burner 17 can be controlled or regulated with the pressure. To avoid misunderstandings, it may be advisable to designate the flow control valve 10 in this exemplary embodiment as a pressure control valve.

FIG. 12 shows a circuit diagram of a third exemplary embodiment of the device 106 ₃ . The main structure corresponds to that of the device IO6 ₁ according to the first exemplary embodiment of the device IO6 ₁ shown in FIG. 10, which is why the main differences are discussed below. Between the flow control valve 10 and the combustion chamber 119 there is a branch 122 in which a low-pressure line 126 branches off from the secondary line 124 and opens into the combustion chamber 119 . The second pressure sensor 22 is arranged between the flow control valve 10 and the branch 122 . A first throttle 128 is arranged in the secondary line 124 and a second throttle 130 is arranged in the low-pressure line 126 . The first throttle 128 has a larger flow cross-sectional area than the second throttle 130. Furthermore, a bypass valve 132 is arranged in the bypass line 124 and a low-pressure valve 134 is arranged in the low-pressure line 126. The bypass valve 132 is designed as a check valve and the low-pressure valve 134 as a pressure-controlled 2/2 valve. For this purpose, the low-pressure valve 134 is connected to the secondary line 124 for switching purposes between the branch 122 and the low-pressure valve 134 .

Due to the fact that the first choke 128 and the second choke 130 are located adjacent to the combustor chamber 119 and the fluid from the first choke 128 or the second choke 130 flows more or less directly into the combustion chamber, the first choke 128 and the second Throttle 130 Part of an injection nozzle 135.

Depending on the operating state and the heat output, which is to provide the burner 17, a certain pressure is provided by means of the flow control valve 10 downstream of the same. It should be assumed that this pressure is lower than a certain switching pressure, which should be 3 bar in the exemplary embodiment shown. The low-pressure valve 134 is designed in such a way that it is open as long as the pressure between the flow control valve 10 and the branch 122 is lower than the switching pressure. The bypass valve 132 closes the secondary line 124 behind the branch 122, as a result of which the fluid flows through the low-pressure line 126 and then through the second throttle 130 into the combustion chamber 119. Since a low pressure leads to a low mass flow, this condition arises when the burner 17 only has to emit a small amount of heat.

If the burner 17 is to provide higher heat conduction, the flow control valve 10 sets the mass flow correspondingly high, which is typically accompanied by an increase in pressure. If the pressure between the flow control valve 10 and the branch 122 exceeds the switching pressure, the bypass valve 132 opens on the one hand and the low-pressure valve 134 closes on the other hand due to the increased pressure in the bypass line 124. The fluid consequently flows through the bypass line 124 and through the first throttle 128130 into the combustion chamber 119. If the pressure falls below the switching pressure again, the bypass valve 132 closes and the low-pressure valve 134 opens, so that the fluid flows back through the low-pressure line 126 and the second throttle 130 into the combustion chamber 119 adjust the required heat output of the burner 17 better, as a result of which the amount of un burned fuel can be reduced.

In this exemplary embodiment, too, the flow control valve 10 is designed as a pressure control valve.

FIG. 13 shows a circuit diagram of a fourth exemplary embodiment of the device IO6 ₄ . The essential structure corresponds to that of the device 106 ₃ according to the third exemplary embodiment illustrated in FIG. 12, which is why the essential differences are discussed below.

There is no low-pressure valve 134 in the low-pressure line 126 arranged. Which is arranged in the bypass line 124 processing valve 132 is formed out as a pressure-controlled 2/2-way valve. As long as the pressure of the fluid between the flow control valve 10 and the branch 122 is below the switching pressure, the bypass valve 132 blocks the passage through the bypass 124. The fluid then flows through the low-pressure line 126 and the second throttle 128-130 into the combustion chamber 119. If the pressure between the flow control valve 10 and the branch 122 rises above the switching pressure, the secondary line valve 132 opens the passage through the secondary line 124. The fluid then flows through the secondary line 124 and the first throttle 128 as well as through the low-pressure line 126 and the second throttle 130 into the combustion chamber 119.

FIG. 14 shows a circuit diagram of a fifth exemplary embodiment of the device IO6 ₅ . Device IO6 ₅ has an arrangement 136 for controlling or regulating a mass flow, which is suitable for a high-pressure injection nozzle 135 (for example for pressures of approximately 3 bar). However, the device 1065 does not have a switching option like the devices 1063, 1064 shown in FIGS. The volume flow for the injection nozzle 135 can be adjusted by means of the pressure sensor 22 . In this exemplary embodiment, too, the flow control valve 10 is designed as a pressure control valve. FIG. 15 shows a flow control valve 10 according to a third exemplary embodiment. For the sake of simplicity, only the most important reference symbols are shown. Reference is made in particular to FIGS. 3 and 4 for the other reference symbols. In principle, however, the device IO6 ₅ is constructed as described in FIG. The main difference is that the first pressure chamber 34 and the second pressure chamber 70 are separate from one another and, regardless of the position of the piston 38, cannot be fluidically connected to one another at least directly, as is the case in the first and second exemplary embodiments of the flow control valve 10.

The valve seat 46 is located at a free end 138 of a tubular boss 140 which is secured to the valve body 12, such as by bolting. The piston 38 is mounted along the longitudinal axis L by means of a first bearing section 142 in the valve housing 12 and by means of a second bearing section 144 in the projection 140 . The first pressure chamber 34 and the second pressure chamber 70 are fluidically separated from one another by the first bearing section 142 . The through-channel 50 is at least partially formed by the annular space between the piston 38 and the projection 140 . The piston 38 has a funnel-shaped free piston end 146, the outer contour of which corresponds approximately to the inner contour of the valve seat 46 and the sealing section 40 forms. The through-channel 50 opens into the combustion chamber 119 of the burner 17 in the area of the valve seat 46. In the first end position, the piston 38 closes the valve seat 46. If the piston 38 is moved into the second end position as a result of a corresponding energization of the actuating device 24 (in FIG 15 to the left), a flow cross-sectional area is released between the passage 50 and the piston 38 in the area of the valve seat 46, through which the fluid flows from the first pressure chamber 34 into the combustion chamber 119 can flow. The size of the cross-sectional flow area can be varied depending on the position of the piston 38 between the first extreme position and the second extreme position. Due to the proximity to the combustion chamber 119, no sealing element 41 is used here.

Furthermore, the already mentioned position determination unit 120 for determining the position of the piston 38 can be seen in FIG. The position determination unit 120 is arranged in the area of the third pressure chamber 83 and includes a Hall sensor. The position determining unit 120 indirectly detects the position of the piston 38 in that it detects the position of the plunger 76 which, however, as described, interacts with the piston 38 and consequently performs the same movement as the piston 38 .

As mentioned, the first pressure chamber 34 and the second pressure chamber 70 are fluidically separated from one another by means of the first bearing section 142 . But you can fluidly connect the first pressure chamber 34 and the second pressure chamber 70 with a connec tion line, not shown. As a result, the same pressures prevail in the first pressure chamber 34, in the second pressure chamber 70 and in the third pressure chamber 83, so that the actuating device 24 does not have to work against a pressure difference between the first pressure chamber 34 and the second pressure chamber 70. Alternatively, the second pressure chamber 70 and the third pressure chamber 83 can also be relieved without pressure towards the fluid reservoir 108 using the outlet bore 72 .

Due to the fact that the piston 38 is comparatively long according to the third exemplary embodiment of the flow control valve 10, the piston 38 can also be referred to as a nozzle needle. Alternatively, the outward-opening piston 38 can also open inward, thereby opening a nozzle bore to the burner 17, in which case the principle of action is reversed. With the same function, the actuating device 24 changes direction and can thereby open the injection nozzle 135 . As a result, smaller cross sections can be realized and correspondingly smaller mass flows can be set with the desired precision. A further flow control valve 147 can be arranged in the secondary line 124 to further refine the adjustment of the mass flow.

FIG. 16 shows the piston 38 in the area of the funnel-shaped free piston end 146 using an isolated representation.

The piston 38 has a swirl structure 148 which is implemented as a multiplicity of swirl grooves 150 in the exemplary embodiment shown. Relative to the longitudinal axis L, the spiral grooves 150 have a helical course. When the fluid flows from passage 50 into combustion chamber 119, swirl grooves 150 impart a radial directional component to the fluid, so that the fluid enters combustion chamber 119 with a swirl. Mixing with the air in the combustion chamber 119 is improved as a result.

Reference List

10 flow control valve 12 valve body 14 inlet

16 exit

17 burners

18 temperature sensor

20 first pressure sensor 22 second pressure sensor 24 actuating device 26 power connection 28 valve block

30 insert part 32 valve block bore 34 first pressure chamber 36 inlet bore 38 piston

40 sealing section

41 sealing element

42 O ring

43 sealing element groove

44 first spring 46 valve seat

48 first locking screw

49 cover

50 passage channel 52 blind hole 54 radial bore 56 contact plunger 58 through hole

60 further bore 62 control groove 64 piston end face 66 edge 68 intermediate space

70 second pressure chamber 72 outlet bore 74 electromagnet 76 plunger

78 first face

80 second face

82 tappet bore

83 third pressure room

84 second spring

86 second locking screw

88 wall

90 cross bore 92 armature space 94 cone 96 armature 98 copper coil 100 sleeve

102 compensating ring 104 contact surface 106 device

106i - 1065 device 108 fluid reservoir

110 Main line 112 Consumer 114 Feed pump 116 Pressure control valve

118 turnoff

119 combustion chamber

120 position determination unit 122 junction

124 secondary line

126 low pressure line

128 First Thrush

130 second throttle 132 by-pass valve

134 low pressure valve

135 injector

136 arrangement 138 free end

140 lead

142 first camp section

144 second camp section

146 free piston end

147 further flow control valve

148 twist structure 150 twist groove

D overlap L longitudinal axis T Depth W Width

Claims

patent claims

1. Flow control valve (10) for controlling or regulating a mass flow of a fluid, comprising at least one inlet (14) and at least one outlet (16), a first pressure chamber (34) fluidically connected to the inlet (14), a Outlet (16) fluidically connected second pressure chamber (70), wherein the first pressure chamber (34) along a longitudinal axis (L) is arranged axially offset to the second pressure chamber (70), a plunger (76) along the longitudinal axis (L) movable bar mounted in the valve housing (12) and by means of an energizable actuating device (24) along the longitudinal axis (L) is movable, a valve seat (46), and a piston (38), which o along the longitudinal axis (L) movable in the valve housing ( 12) and can be moved by means of the plunger (76) along the longitudinal axis (L) between a first end position and a second end position, o forms a through-channel (50) which forms the first pressure chamber (34) and the second pressure chamber (70) at least least in the second end o has a sealing section (40) which rests against the valve seat (46) in the first end position and fluidly separates the first pressure chamber (34) from the second pressure chamber (70) in the first end position, and o a control groove (62) having a flow cross-sectional area that provides the through-passage channel (50) and the first pressure chamber (34) or fluidically connects the through-channel (50) and the second pressure chamber (70) to one another when the piston (38) is between the first end position and the second end position, the size of the flow cross-sectional area depending on the position of the piston (38) between the first end position and the second end position can be changed.

2. Flow control valve (10) according to claim 1, characterized in that the control groove (62) has a depth (T) that varies along the longitudinal axis (L).

3. Flow control valve (10) according to one of claims 1 or 2, characterized in that the control groove (62) along the longitudinal axis (L) has changing width (W).

4. Flow control valve (10) according to any one of the preceding claims, characterized in that the piston (38) is biased into the first end position by means of a first spring (44).

5. Flow control valve (10) according to one of the preceding claims, characterized in that the tappet (76) o a first end face (78) and a second end face (80) and o one between the first end face (78) and the second end face (80) running tappet bore (82), wherein the first end face (78) for moving the piston (38) interacts with the same and the tappet bore (82) is fluidically connected to the passage (50), and a third pressure chamber (83) is provided, into which the tappet bore (82) opens at the second end face (80).

6. Flow control valve (10) according to any one of the preceding claims, characterized in that the tappet (76) by means of a second spring (84) is biased against the piston (38).

7. Flow control valve (10) according to claim 6, characterized in that the flow control valve (10) has a first screw plug (48) for adjusting the pretensioning force of the first spring (44) and/or a second screw plug (86) for adjusting the pretensioning force of the second Spring (84) includes.

8. Flow control valve (10) according to any one of the preceding claims, characterized in that a contact piston (56) is connected to the piston (38), the contact piston (56) interacting with the first end face (78) of the tappet (76).

9. Flow control valve (10) according to claim 8, characterized in that the contact piston (56) has a through bore (58) which fluidically connects the passage channel (50) and the tappet bore (82).

10. Flow control valve (10) according to claim 9, characterized in that the contact piston (56) has at least one further bore (60) opening into the through bore (58) which fluidly connects the through bore (58) to the control groove (62). .

11. Flow control valve (10) according to any one of the preceding claims, characterized in that the first pressure chamber (34) and the second pressure chamber (70) and the valve seat (46) are formed by an insert part (30) which can be inserted into the valve housing (12).

12. Flow control valve (10) according to claim 1, characterized in that a sealing element (41) is arranged in the sealing section (40), which has a sectional plane running through the longitudinal axis (L) and has a polygonal cross section.

13. Flow control valve (10) according to any one of the preceding claims, characterized in that the flow control valve (10) has a temperature sensor (18) for determining the temperature of the fluid in the inlet (14).

14. Flow control valve (10) according to any one of the preceding claims, characterized in that the flow control valve (10) has a first pressure sensor (20) for determining the pressure of the fluid in the inlet (14).

15. Flow control valve (10) according to any one of the preceding claims, characterized in that the flow control valve (10) has a second pressure sensor (22) for determining the pressure of the fluid in the outlet (16).

16. Flow control valve (10) according to any one of the preceding claims, characterized in that the flow control valve (10) has a position determination unit (120) for determining the posi tion of the piston (38).

17 arrangement (136) for controlling or regulating a mass flow of a fluid, with a flow control valve (10), and a burner (17) having a combustion chamber (119), the flow control valve (10) comprising at least one inlet (14) and at least one outlet (16), the outlet (16) being fluid connected to the combustion chamber (119), a first pressure chamber (34) fluidically connected to the inlet (14), a tappet (76) which is mounted in the valve housing (12) so that it can move along the longitudinal axis (L) and by means of an actuation device that can be energized (24) can be moved along the longitudinal axis (L), a valve seat (46), and a piston (38), which is mounted in the valve housing (12) so that it can be moved along the longitudinal axis (L) and by means of the tappet (76) along the longitudinal axis (L) can be moved between a first end position and a second end position, o forms a through-channel (50) which fluidly connects the first pressure chamber (34) and the combustion chamber (119) to one another at least in the second end position, o a sealing section (40 ) which in the e rs th end position rests against the valve seat (46) and in the first end position fluidly separates the first pressure chamber (34) from the combustion chamber (119), and o provides a flow cross-sectional area between the piston (38) and the through-channel (38) which provides the through-channel ( 50) and the first pressure chamber (34) or the through-channel (50) and the combustion chamber (119) fluidly connected to each other when the piston (38) is between the first end position and the second end position, wherein the size of the cross-sectional flow area can be changed depending on the position of the piston (38) between the first end position and the second end position.

18. Arrangement (136) according to claim 17, characterized in that the piston (38) has a swirl structure (148) which causes the fluid to swirl as it flows into the combustion chamber (119).

19. Device (106) for controlling or regulating a mass flow of a fluid, comprising a fluid reservoir (108) for storing the fluid, a main line (110) through which the fluid can be passed to a consumer (112), one in the A feed pump (114) arranged in the main line (110) for feeding the fluid in the same, a burner (17) which has a combustion chamber (119), a secondary line (124 ), And in the secondary line (124) arranged flow control valve (10) according to any one of claims 1 to 16, with wel chem the mass flow into the combustion chamber (119) can be controlled or regulated.

20. The device according to claim 19, characterized in that a branch (122) is arranged between the flow control valve (10) and the combustion chamber (119), in which a low-pressure line (126) branches off from the secondary line (124) and into the combustion chamber ( 119) flows out, where a first throttle (128) is arranged in the secondary line (124), a second throttle (130) is arranged in the low-pressure line (126), and a secondary line valve (132) in the secondary line (124) and/or in the low-pressure line ( 126) a low-pressure valve (134) is arranged, which releases or blocks the secondary line (124) and/or the low-pressure line (126) depending on the pressure between the flow control valve (10) and the branch (122).

21. A method for operating a flow control valve (10) according to any one of claims 4 to 16, comprising the following steps:

- Prestressing of the piston (38) into the first end position by means of the first spring (44) so that the sealing section (40) rests against the valve seat (46),

- Energizing the actuating device (24) to move the plunger (76) along the longitudinal axis (L) in such a way that the piston (38) is displaced along the longitudinal axis (L) against the prestressing force of the first spring (44) and the sealing section (40 ) is moved away from the valve seat (46) and o the control groove (62) fluidly connects the through-channel (50) and the first pressure chamber (34) or the through-channel (50) and the second pressure chamber (70), with o the size the flow cross-sectional area of the control groove (62) can be changed depending on the position of the piston (38) between the first end position and the second end position by means of the energization of the actuating device (24).