EP1552140B1 - Volume flow rate regulating valve - Google Patents

Volume flow rate regulating valve Download PDF

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Publication number
EP1552140B1
EP1552140B1 EP03757826A EP03757826A EP1552140B1 EP 1552140 B1 EP1552140 B1 EP 1552140B1 EP 03757826 A EP03757826 A EP 03757826A EP 03757826 A EP03757826 A EP 03757826A EP 1552140 B1 EP1552140 B1 EP 1552140B1
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EP
European Patent Office
Prior art keywords
control
piston
volume flow
regulating valve
section
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Expired - Lifetime
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EP03757826A
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German (de)
French (fr)
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EP1552140A1 (en
Inventor
Martin Werner
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Siemens AG
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Siemens AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D7/00—Other fuel-injection control
    • F02D7/002—Throttling of fuel passages between pumps and injectors or overflow passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0056—Throttling valves, e.g. having variable opening positions throttling the flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/16—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by means for metering continuous fuel flow to injectors or means for varying fuel pressure upstream of continuously or intermittently operated injectors
    • F02M69/18—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by means for metering continuous fuel flow to injectors or means for varying fuel pressure upstream of continuously or intermittently operated injectors the means being metering valves throttling fuel passages to injectors or by-pass valves throttling overflow passages, the metering valves being actuated by a device responsive to the engine working parameters, e.g. engine load, speed, temperature or quantity of air

Definitions

  • the invention relates to a volume flow control valve.
  • Such volume flow control valves are used in particular for controlling the fuel volume flow in the inlet to a high-pressure pump, which promotes fuel in a high pressure accumulator of a common rail injection system of an internal combustion engine.
  • the flow control valve must firstly ensure that sufficient fuel is constantly available according to the operating conditions of the internal combustion engine. On the other hand, however, not too much fuel should be pumped into the high pressure accumulator, since the excess fuel is returned via a high pressure valve in the tank of the internal combustion engine and thus leads to heating of the fuel in the tank. In addition, the compression of unneeded fuel reduces the efficiency of the injection system.
  • a valve in particular for the metering of fuel in an injection system of an internal combustion engine is already known.
  • the valve consists of a valve body with an inlet and an outlet opening.
  • a control piston is movably mounted with a control groove.
  • the control piston is moved via an adjusting mechanism against the force of a return spring.
  • the outlet opening is closed or it is released from the piston more or less large passage cross-section in the outlet opening.
  • the fuel flows at an at least partially released outlet opening from the inlet opening via the control groove to the outlet.
  • the control groove is formed by a rotationally symmetrical recess in the control piston. Due to the shape of the control piston results in a linear course of the valve characteristic.
  • a characteristic here is the ratio of drive signal or piston stroke referred to the volume flow.
  • a characteristic curve is frequently desired which permits a flat characteristic curve for low values of the drive signal and a steeper characteristic curve for higher values of the drive signal. This can not be realized with the usual flow control valve.
  • EP 1 199 467 A2 discloses a volume flow control valve with three control edges and two flow areas.
  • the object of the invention is therefore to provide a flow control valve that is simple and inexpensive to manufacture and that allows different slopes of the valve characteristic.
  • the invention is characterized in that the control piston is designed as a stepped piston, which is flowed around the outside and in its lateral surface has a control geometry which is designed such that arise in dependence on the position of the control piston different slopes in the valve characteristic.
  • the advantage of the invention is that even the most complicated control geometries can be easily introduced, for example, by milling in the lateral surface of the stepped piston. A deburring of the control geometry is easily possible because the edge on the lateral surface the control piston is located and thus easily accessible. Through the simple production of even complicated control geometries, a wide variety of valve characteristics can be realized cost-effectively.
  • the inlet and outlet can be made by simple and inexpensive holes in the valve body.
  • the piston stroke can be proportional to the control signal.
  • a proportional relationship between piston stroke and control signal can be achieved with simple and inexpensive actuators, for example, an electromagnetic actuator.
  • a preferred embodiment of the invention provides to introduce the Abströmgeometrie multiple radially distributed over the circumference in the control piston. This can increase the flow and in addition the radial forces are reduced to the valve piston.
  • the volume flow control valve consists essentially of the valve housing 10, the control piston 2 and the return spring 4.
  • the valve housing 10 has an inlet 12 and an outlet 13, which are introduced radially into the valve housing 10.
  • In the axial direction is the valve housing 10 provided with a sliding bore 18 in which the control piston 2 is guided axially movable.
  • an inlet groove 16 is screwed on the inner circumference of the valve housing.
  • the control piston 2 is designed as a stepped piston. Between a first end portions 28 and a second end portion 29 of the control piston 2, a control groove 15 is screwed into the control piston 2.
  • the outflow geometry 8 has a first control edge 19, a second control edge 20 and a third control edge 34, by which a first flow cross-section 21 and a second flow cross-section 22 are delimited.
  • the two flow cross sections 21, 22 are indicated by the dashed lines.
  • the control piston 2 For receiving the return spring 4, the control piston 2 in its first end portion 28, a spring receiving bore 24 which is formed as a blind hole on.
  • the return spring 4 is supported on one side on the end face of the spring receiving bore 24 and on the opposite side in a spring plate 25, which is preferably inserted into the valve housing 10 by pressing.
  • the control piston 2 is displaced by an actuator 11 and a transmission member 27 against the force of the return spring 4.
  • an actuator for example, an electromagnetic, mechanical, hydraulic or pneumatic adjusting is suitable.
  • the adjusting member preferably allows a proportional relationship between the drive signal and the piston stroke.
  • the actuator 11 If the actuator 11 receives a control signal, it shifts the control piston 2 by means of the transmission member 27 against the spring force of the return spring 4.
  • the control piston moves from its first end position 5 out in the direction of a second end position 6, which in Figure 1 a left the first end position is located.
  • the control piston 2 initially sets, starting from its first end position, a stroke length s1 (FIG. 1 b), in which the control piston 2 continues to completely close the inlet 12. After the control piston 2 has covered the stroke length s1, the first control edge 19, the outflow geometry 8 in the control piston 2, overlaps with the inlet edge 30 of the inlet groove 16 in the valve housing 10.
  • a first flow cross-section 21 is initially established and subsequently additionally the second flow cross-section 22 is released.
  • the liquid flows from the inlet 12, through the inlet groove 16, the outflow geometry 8, the control groove 15 to the outlet 13.
  • the Abströmgeometrie 8 is formed in the known embodiment so that a first and a second flow area 21, 22 is formed.
  • the two flow cross sections 21, 22 merge into one another, the transition being characterized by the second control edge 20. Due to the smaller width of the first flow cross-section 21, the increase in cross-section in the region of the first flow cross-section 21 with respect to the piston stroke is less than in the region of the second flow cross-section 22.
  • This behavior illustrates the valve characteristic shown in FIG. In this case, the volumetric flow Q is plotted against the drive current I. At a very low drive current I, ie with a small piston stroke, the inlet groove 16 still remains completely closed, so that no liquid flows through the volume flow control valve flows.
  • the control piston 2 With increasing Anstreuerstrom the control piston 2 is pressed further to the left against the force of the return spring 4. The first flow cross-section 21 is released and liquid can flow through the flow control valve. Since the cross-sectional area increase in this area is only very small, the characteristic curve has only a shallow gradient. If the control piston 2 reaches the inlet region 12, 16 with its second control edge 20, the second flow cross-section 22 is additionally released. Due to the greater width of the second flow cross-section 22, with respect to the first flow cross-section 21, there is a greater increase in the cross-sectional area. This allows more liquid flow through the flow control valve, this is reflected in the steeper course of the valve characteristic.
  • the outflow geometry 8 thus enables a very fine regulation of the volume flow at low drive currents and at high drive currents a fast opening of the valve to provide the required, large amount of liquid.
  • the particular advantage of the invention is that almost any Abströmgeometrie can be realized by the simple introduction of Abströmgeometrie 8 in the lateral surface 7 of the control piston 2.
  • a valve characteristic can be realized with three different slopes. It is conceivable that the characteristic has, for example, at the beginning and at the end a flat and in the middle region a steep course.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Magnetically Actuated Valves (AREA)
  • Lift Valve (AREA)

Description

Die Erfindung betrifft ein Volumenstromregelventil.The invention relates to a volume flow control valve.

Solche Volumenstromregelventile werden insbesondere zur Regelung des Kraftstoffvolumenstroms im Zulauf zu einer Hochdruckpumpe, die Kraftstoff in einen Hochdruckspeicher eines Common-Rail-Einspritzsystems einer Brennkraftmaschine fördert eingesetzt. Das Volumenstromregelventil muss zum einen gewährleisten, dass ständig genügend Kraftstoff entsprechend den Betriebsbedingungen der Brennkraftmaschine zur Verfügung steht. Zum anderen soll jedoch nicht übermäßig viel Kraftstoff in den Hochdruckspeicher gepumpt werden, da der überschüssige Kraftstoff über ein Hochdruckventil in den Tank der Brennkraftmaschine zurückgeführt wird und somit zu einer Erwärmung des Kraftstoffes im Tank führt. Zudem verringert sich durch das Verdichten von nicht benötigtem Kraftstoff der Wirkungsgrad des Einspritzsystems.Such volume flow control valves are used in particular for controlling the fuel volume flow in the inlet to a high-pressure pump, which promotes fuel in a high pressure accumulator of a common rail injection system of an internal combustion engine. The flow control valve must firstly ensure that sufficient fuel is constantly available according to the operating conditions of the internal combustion engine. On the other hand, however, not too much fuel should be pumped into the high pressure accumulator, since the excess fuel is returned via a high pressure valve in the tank of the internal combustion engine and thus leads to heating of the fuel in the tank. In addition, the compression of unneeded fuel reduces the efficiency of the injection system.

Aus der DE 38 38 914 A1 ist bereits ein Ventil, insbesondere zur Zumessung von Kraftstoff in einer Einspritzanlage einer Brennkraftmaschine bekannt. Das Ventil besteht aus einem Ventilgehäuse mit einer Einlass- und einer Auslassöffnung. In dem Ventilgehäuse ist ein Steuerkolben mit einer Steuernut bewegbar gelagert. Der Steuerkolben wird über einen Stellmechanismus gegen die Kraft einer Rückstellfeder bewegt. Je nach Lage des Kolbens ist die Auslassöffnung geschlossen oder es wird vom Kolben ein mehr oder wenig großer Durchtrittsquerschnitt in der Auslassöffnung freigegeben. Der Kraftstoff fließt bei einer zumindest teilweise freigegebenen Auslassöffnung von der Einlassöffnung über die Steuernut zum Auslass. Die Steuernut ist durch eine rotationssymmetrische Eindrehung im Steuerkolben ausgebildet. Aufgrund der Form des Steuerkolbens ergibt sich ein linearer Verlauf der Ventilkennlinie. Als Kennlinie wird hierbei das Verhältnis von Ansteuersignal oder Kolbenhub zum Volumenstrom bezeichnet. Für Common-Rail-Einspritzsysteme wird allerdings häufig eine Kennlinie gewünscht, die bei geringen Werten des Ansteuersignals einen flachen Kennlinienverlauf und bei höheren Werten des Ansteuersignals einen steileren Kennlinienverlauf ermöglicht. Dies lässt sich mit dem üblichen Volumenstromregelventil nicht realisieren.From DE 38 38 914 A1 a valve, in particular for the metering of fuel in an injection system of an internal combustion engine is already known. The valve consists of a valve body with an inlet and an outlet opening. In the valve housing, a control piston is movably mounted with a control groove. The control piston is moved via an adjusting mechanism against the force of a return spring. Depending on the position of the piston, the outlet opening is closed or it is released from the piston more or less large passage cross-section in the outlet opening. The fuel flows at an at least partially released outlet opening from the inlet opening via the control groove to the outlet. The control groove is formed by a rotationally symmetrical recess in the control piston. Due to the shape of the control piston results in a linear course of the valve characteristic. As a characteristic here is the ratio of drive signal or piston stroke referred to the volume flow. For common-rail injection systems, however, a characteristic curve is frequently desired which permits a flat characteristic curve for low values of the drive signal and a steeper characteristic curve for higher values of the drive signal. This can not be realized with the usual flow control valve.

Um zwei unterschiedliche Steigungen in der Ventilkennlinie zu erreichen wir in der DE 100 23 621 A1 vorgeschlagen, einen innen durchströmten, hülsenförmigen Steuerkolben vorzusehen, in den eine gestufte Steuergeometrie eingebracht wird. Das Einbringen einer derart ausgebildeten Steuergeometrie in den hülsenförmigen Steuerkolben ist allerdings fertigungstechnisch problematisch. Schwierigkeiten ergeben sich auch beim Entgraten der Steuergeometrie, da sich diese im inneren Steuerkolben befindet und nur schwer zugänglich ist.In order to achieve two different slopes in the valve characteristic, we propose in DE 100 23 621 A1 to provide an internally flow-through, sleeve-shaped control piston into which a stepped control geometry is introduced. The introduction of such a trained control geometry in the sleeve-shaped control piston, however, is technically problematic. Difficulties also arise when deburring the control geometry, since it is located in the inner control piston and is difficult to access.

EP 1 199 467 A2 offenbart ein Volumenstromregelventil mit drei Steuerkanten sowie zwei Durchströmquerschnitten.EP 1 199 467 A2 discloses a volume flow control valve with three control edges and two flow areas.

Die Aufgabe der Erfindung ist es daher, ein Volumenstromregelventil bereitzustellen, das einfach und kostengünstig zu fertigen ist und das unterschiedlich Steigungen der Ventilkennlinie ermöglicht.The object of the invention is therefore to provide a flow control valve that is simple and inexpensive to manufacture and that allows different slopes of the valve characteristic.

Die Aufgabe wird gelöst durch die Merkmale des unabhängigen Anspruchs 1. Vorteilhafte Ausgestaltungen der Erfindung sind in den abhängigen Ansprüchen gekennzeichnet.The object is solved by the features of independent claim 1. Advantageous embodiments of the invention are characterized in the dependent claims.

Die Erfindung zeichnet sich dadurch aus, dass der Steuerkolben als Stufenkolben ausgebildet ist, der außen umströmt wird und in seiner Mantelfläche eine Steuergeometrie aufweist, die derart ausgebildet ist, dass sich in Abhängigkeit von der Stellung des Steuerkolbens unterschiedliche Steigungen in der Ventilkennlinie ergeben. Der Vorteil der Erfindung liegt darin, dass auch komplizierteste Steuergeometrien beispielsweise durch Fräsen einfach in die Mantelfläche des Stufenkolbens eingebracht werden können. Ein Entgraten der Steuergeometrie ist problemlos möglich, da sich die Kante an der Mantelfläche des Steuerkolbens befindet und hierdurch gut zugänglich ist. Durch das einfache Herstellen auch komplizierter Steuergeometrien lassen sich kostengünstig unterschiedlichste Ventilkennlinien realisieren. Der Ein- und Auslass kann durch einfache und preiswerte Bohrungen in das Ventilgehäuse hergestellt werden.The invention is characterized in that the control piston is designed as a stepped piston, which is flowed around the outside and in its lateral surface has a control geometry which is designed such that arise in dependence on the position of the control piston different slopes in the valve characteristic. The advantage of the invention is that even the most complicated control geometries can be easily introduced, for example, by milling in the lateral surface of the stepped piston. A deburring of the control geometry is easily possible because the edge on the lateral surface the control piston is located and thus easily accessible. Through the simple production of even complicated control geometries, a wide variety of valve characteristics can be realized cost-effectively. The inlet and outlet can be made by simple and inexpensive holes in the valve body.

Da sich die Steigung der Ventilkennlinie allein durch die Steuergeometrie ergibt, kann der Kolbenhub proportional zum Ansteuersignal erfolgen. Ein proportionaler Zusammenhang zwischen Kolbenhub und Ansteuersignal lässt sich mit einfachen und kostengünstigen Stellgliedern beispielsweise einem elektromagnetischem Stellglied erreichen.Since the slope of the valve characteristic is determined solely by the control geometry, the piston stroke can be proportional to the control signal. A proportional relationship between piston stroke and control signal can be achieved with simple and inexpensive actuators, for example, an electromagnetic actuator.

Eine bevorzugte Ausgestaltung der Erfindung sieht vor, die Abströmgeometrie mehrfach radial über den Umfang verteilt in den Steuerkolben einzubringen. Hierdurch lässt sich der Durchfluss erhöhen und zusätzlich werden die Radialkräfte auf den Ventilkolben reduziert.A preferred embodiment of the invention provides to introduce the Abströmgeometrie multiple radially distributed over the circumference in the control piston. This can increase the flow and in addition the radial forces are reduced to the valve piston.

Ein bekanntes Ausführungsbeispiel wird im folgenden anhand der schematischen Zeichnungen erläutert. Es zeigt:

Figur 1a
einen Längsschnitt durch das Volumenstromregelventil
Figur 1b
einen weiteren Längsschnitt durch das Volumenstromregelventil, wobei die Schnittebene radial um 90° versetzt zu Fig.1 liegt.
Figur 2
eine typische Ventilkennlinie des Volumenstromregelventils
A known embodiment will be explained below with reference to the schematic drawings. It shows:
FIG. 1a
a longitudinal section through the flow control valve
FIG. 1b
a further longitudinal section through the flow control valve, wherein the cutting plane is radially offset by 90 ° to Fig.1.
FIG. 2
a typical valve characteristic of the flow control valve

Figur 1a zeigt einen Längsschnitt durch das Volumenstromregelventil 1. Das Volumenstromregelventil besteht im wesentlichen aus dem Ventilgehäuse 10, dem Steuerkolben 2 sowie der Rückstellfeder 4. Das Ventilgehäuse 10 weist einen Einlass 12 und einen Auslass 13 auf, die radial in das Ventilgehäuse 10 eingebracht sind. In axialer Richtung ist das Ventilgehäuse 10 mit einer Gleitbohrung 18 versehen, in der der Steuerkolben 2 axial beweglich geführt ist. In Höhe des Einlasses 12 ist am Innenumfang des Ventilgehäuses eine Einlassnut 16 eingedreht. Der Steuerkolben 2 ist als Stufenkolben ausgebildet. Zwischen einem ersten Endbereichen 28 und einem zweiten Endbereich 29 des Steuerkolbens 2 ist eine Steuernut 15 in den Steuerkolben 2 eingedreht. Die Abströmgeometrie 8 weist eine erste Steuerkante 19 eine zweite Steuerkante 20 und eine dritte Steuerkante 34 auf, durch die ein erster Durchströmungsquerschnitt 21 und ein zweiter Durchströmungsquerschnitt 22 begrenzt werden. In Figur 1 b sind die beiden Durchströmungsquerschnitte 21, 22 durch die gestrichelten Lienen gekennzeichnet. Zur Aufnahme der Rückstellfeder 4 weist der Steuerkolben 2 in seinem ersten Endbereich 28 eine Federaufnahmebohrung 24, die als Sacklochbohrung ausgebildet ist, auf. Die Rückstellfeder 4 stützt sich auf der einen Seite an der Stirnseite der Federaufnahmebohrung 24 und auf der Gegenseite in einem Federteller 25 ab, der in das Ventilgehäuse 10 vorzugsweise durch Einpressen eingesetzt ist. Der Steuerkolben 2 wird durch ein Stellglied 11 und ein Übertragungsglied 27 gegen die Kraft der Rückstellfeder 4 verschoben. Als Stellglied eignet sich beispielsweise eine elektromagnetisches, mechanisches, hydraulisches oder pneumatisches Verstellglied. Das Verstellglied ermöglicht vorzugsweise einen proportionalen Zusammenhang zwischen dem Ansteuersignal und dem Kolbenhub.1a shows a longitudinal section through the volume flow control valve 1. The volume flow control valve consists essentially of the valve housing 10, the control piston 2 and the return spring 4. The valve housing 10 has an inlet 12 and an outlet 13, which are introduced radially into the valve housing 10. In the axial direction is the valve housing 10 provided with a sliding bore 18 in which the control piston 2 is guided axially movable. In the amount of the inlet 12, an inlet groove 16 is screwed on the inner circumference of the valve housing. The control piston 2 is designed as a stepped piston. Between a first end portions 28 and a second end portion 29 of the control piston 2, a control groove 15 is screwed into the control piston 2. The outflow geometry 8 has a first control edge 19, a second control edge 20 and a third control edge 34, by which a first flow cross-section 21 and a second flow cross-section 22 are delimited. In Figure 1 b, the two flow cross sections 21, 22 are indicated by the dashed lines. For receiving the return spring 4, the control piston 2 in its first end portion 28, a spring receiving bore 24 which is formed as a blind hole on. The return spring 4 is supported on one side on the end face of the spring receiving bore 24 and on the opposite side in a spring plate 25, which is preferably inserted into the valve housing 10 by pressing. The control piston 2 is displaced by an actuator 11 and a transmission member 27 against the force of the return spring 4. As an actuator, for example, an electromagnetic, mechanical, hydraulic or pneumatic adjusting is suitable. The adjusting member preferably allows a proportional relationship between the drive signal and the piston stroke.

Nachfolgend wird die Funktionsweise des Volumenstromregelventils beschrieben. In der dargestellten Ausgangsstellung (Fig.1 a), die einer ersten Endstellung des Steuerkolbens 2 entspricht, ist der Einlass 12 zunächst vom Steuerkolben 2 vollständig verschlossen, so dass keine Flüssigkeit durch das Volumenstromregelventil fließen kann.The operation of the flow control valve will be described below. In the illustrated starting position (FIG. 1 a), which corresponds to a first end position of the control piston 2, the inlet 12 is initially completely closed by the control piston 2, so that no fluid can flow through the volume flow control valve.

Erhält das Stellglied 11 ein Stellsignal, so verschiebt es den Steuerkolben 2 mit Hilfe des Übertragungsglied 27 gegen die Federkraft der Rückstellfeder 4. Der Steuerkolben bewegt sich aus seiner ersten Endstellung 5 heraus in Richtung einer zweiten Endstellung 6, die sich in Figur 1 a links von der ersten Endstellung befindet. Der Steuerkolben 2 legt zunächst, ausgehend von seiner ersten Endstellung, eine Hublänge s1 ( Fig. 1 b) zurück, bei der der Steuerkolben 2 den Einlass 12 weiterhin vollständig verschließt. Nachdem der Steuerkolben 2 die Hublänge s1 zurückgelegt hat kommt es zu einer Überschneidung der ersten Steuerkante 19, der Abströmgeometrie 8 im Steuerkolben 2, mit der Einlasskante 30 der Einlassnut 16 im Ventilgehäuse 10. In Abhängigkeit von dem Wert des Stellsignals wird zunächst ein erster Durchströmungsquerschnitt 21 und nachfolgend zusätzlich der zweite Durchströmungsquerschnitt 22 freigegeben. Die Flüssigkeit strömt vom Einlass 12, durch die Einlassnut 16, die Abströmgeometrie 8, die Steuernut 15 zum Auslass 13.If the actuator 11 receives a control signal, it shifts the control piston 2 by means of the transmission member 27 against the spring force of the return spring 4. The control piston moves from its first end position 5 out in the direction of a second end position 6, which in Figure 1 a left the first end position is located. The control piston 2 initially sets, starting from its first end position, a stroke length s1 (FIG. 1 b), in which the control piston 2 continues to completely close the inlet 12. After the control piston 2 has covered the stroke length s1, the first control edge 19, the outflow geometry 8 in the control piston 2, overlaps with the inlet edge 30 of the inlet groove 16 in the valve housing 10. In dependence on the value of the actuating signal, a first flow cross-section 21 is initially established and subsequently additionally the second flow cross-section 22 is released. The liquid flows from the inlet 12, through the inlet groove 16, the outflow geometry 8, the control groove 15 to the outlet 13.

Die Abströmgeometrie 8 ist in dem bekannten Ausführungsbeispiel so ausgebildet, dass ein erster und ein zweiter Durchströmungsquerschnitt 21, 22 entsteht. Die beiden Durchströmungsquerschnitte 21, 22 gehen ineinander über, wobei der Übergang durch die zweite Steuerkante 20 gekennzeichnet ist. Aufgrund der geringeren Breite des ersten Durchströmungsquerschnitt 21 ist die Querschnittszunahme im Bereich des ersten Durchströmungsquerschnitt 21 bezogen auf den Kolbenhub geringer als im Bereich des zweiter Durchströmungsquerschnitt 22. Dieses Verhalten veranschaulicht die in Fig. 2 dargestellte Ventilkennlinie. Aufgetragen ist dabei der Volumenstrom Q über dem Ansteuerstrom I. Bei sehr niedrigem Ansteuerstrom I, d.h. bei kleinem Kolbenhub, bleibt die Einlassnut 16 noch vollständig verschlossen, so dass keine Flüssigkeit durch das Volumenstromregelventil fließt. Mit steigendem Anstreuerstrom wird der Steuerkolben 2 weiter nach links gegen die Kraft der Rückstellfeder 4 gedrückt. Der erste Durchströmungsquerschnitt 21 wird freigegeben und Flüssigkeit kann durch das Volumenstromregelventil fließen. Da die Querschnittsflächenzunahme in diesem Bereich nur sehr gering ist, weist die Kennlinie nur eine flache Steigung auf. Erreicht der Steuerkolben 2 mit seiner zweiten Steuerkante 20 den Einlassbereich 12, 16 so wird zusätzlich der zweite Durchströmungsquerschnitt 22 freigegeben. Aufgrund der größeren Breite des zweite Durchströmungsquerschnitt 22, in Bezug zum ersten Durchströmungsquerschnitt 21, kommt es zu einer stärkeren Querschnittsflächenzunahme. Hierdurch kann mehr Flüssigkeit durch das Volumenstromregelventil fließen, dies zeigt sich im steileren Verlauf der Ventilkennlinie.The Abströmgeometrie 8 is formed in the known embodiment so that a first and a second flow area 21, 22 is formed. The two flow cross sections 21, 22 merge into one another, the transition being characterized by the second control edge 20. Due to the smaller width of the first flow cross-section 21, the increase in cross-section in the region of the first flow cross-section 21 with respect to the piston stroke is less than in the region of the second flow cross-section 22. This behavior illustrates the valve characteristic shown in FIG. In this case, the volumetric flow Q is plotted against the drive current I. At a very low drive current I, ie with a small piston stroke, the inlet groove 16 still remains completely closed, so that no liquid flows through the volume flow control valve flows. With increasing Anstreuerstrom the control piston 2 is pressed further to the left against the force of the return spring 4. The first flow cross-section 21 is released and liquid can flow through the flow control valve. Since the cross-sectional area increase in this area is only very small, the characteristic curve has only a shallow gradient. If the control piston 2 reaches the inlet region 12, 16 with its second control edge 20, the second flow cross-section 22 is additionally released. Due to the greater width of the second flow cross-section 22, with respect to the first flow cross-section 21, there is a greater increase in the cross-sectional area. This allows more liquid flow through the flow control valve, this is reflected in the steeper course of the valve characteristic.

Die Abströmgeometrie 8 ermöglicht somit bei geringen Ansteuerströmen eine sehr feine Regulierung des Volumenstroms und bei höheren Ansteuerströmen ein schnelles öffnen des Ventils um die benötigte, große Flüssigkeitsmenge bereitzustellen.The outflow geometry 8 thus enables a very fine regulation of the volume flow at low drive currents and at high drive currents a fast opening of the valve to provide the required, large amount of liquid.

Der besondere Vorteil der Erfindung liegt darin, das durch das einfache Einbringen der Abströmgeometrie 8 in die Mantelfläche 7 des Steuerkolbens 2 fast jede beliebige Abströmgeometrie realisierbar ist. Durch eine erfindungsgemäße Abströmgeometrie mit vier statt den dargestellten drei Steuerkanten lässt sich eine Ventilkennlinie mit drei unterschiedlichen Steigungen realisieren. Es ist dabei denkbar, dass die Kennlinie beispielsweise zu Beginn und zum Ende einen flachen und im mittleren Bereich einen steilen Verlauf aufweist. In dem man die erfindungsgemäße Abströmgeometrie derart gestaltet, dass der Durchströmungsquerschnitt sich kontinuierlich vergrößert oder verkleinert lässt sich auch ein kurvenförmiger Verlauf der Ventilkennlinie realisieren. Die Erfindung ermöglicht somit die Ventilkennlinie des Volumenstromregelventils einfach und preiswert an die jeweiligen Anforderungen anpassen.The particular advantage of the invention is that almost any Abströmgeometrie can be realized by the simple introduction of Abströmgeometrie 8 in the lateral surface 7 of the control piston 2. By an outflow geometry according to the invention with four instead of the three control edges shown, a valve characteristic can be realized with three different slopes. It is conceivable that the characteristic has, for example, at the beginning and at the end a flat and in the middle region a steep course. By designing the outflow geometry according to the invention in such a way that the throughflow cross section can continuously increase or decrease can also realize a curved course of the valve characteristic. The invention thus allows the valve characteristic of the flow control valve easy and inexpensive to adapt to the respective requirements.

Claims (5)

  1. Volume flow regulating valve (1) comprising a control piston (2) which is mounted in a valve housing (10) and is axially movable from a first terminal position (5) to a second terminal position (6) against the force of a resetting spring (4), the control piston (2) being embodied as a differential piston, being flowed around externally and having a control geometry (8) which is incorporated into the existing cylindrical surface area (7) and is embodied in such a way that a control space is formed in the control piston (2), said control space having only one flow cross-section that is open to the cylindrical surface area (7) and one that is open to a front face of the control piston (2), the flow cross-section that is open to the cylindrical surface area (7) being more or less covered by the valve housing (10) according to the position of the differential piston and thereby enabling a more or less large effective flow cross-section, the control geometry being embodied in such a way that a first and a second through-flow cross-section are produced which merge with one another, resulting in a first control edge (19), a second control edge (20) and a third control edge (34), characterised in that a fourth control edge is present in order to realise a valve characteristic curve having three different gradients.
  2. Volume flow regulating valve according to claim 1,
    characterised in that
    a proportional relationship exists between a control signal and the piston stroke.
  3. Volume flow regulating valve according to one of the preceding claims,
    characterised in that
    the dispersion geometry (8) is incorporated multiply into the control piston (2), radially distributed over the circumference.
  4. Volume flow regulating valve according to one of the preceding claims,
    characterised in that
    the control piston (2) is moved by electromagnetic means.
  5. Volume flow regulating valve according to one of the claims 1 to 3,
    characterised in that
    the control piston (2) is moved by mechanical, hydraulic or pneumatic means.
EP03757826A 2002-10-14 2003-09-11 Volume flow rate regulating valve Expired - Lifetime EP1552140B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10247774 2002-10-14
DE2002147774 DE10247774B4 (en) 2002-10-14 2002-10-14 Flow control valve
PCT/EP2003/010135 WO2004036032A1 (en) 2002-10-14 2003-09-11 Volume flow rate regulating valve

Publications (2)

Publication Number Publication Date
EP1552140A1 EP1552140A1 (en) 2005-07-13
EP1552140B1 true EP1552140B1 (en) 2007-05-16

Family

ID=32038624

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03757826A Expired - Lifetime EP1552140B1 (en) 2002-10-14 2003-09-11 Volume flow rate regulating valve

Country Status (3)

Country Link
EP (1) EP1552140B1 (en)
DE (2) DE10247774B4 (en)
WO (1) WO2004036032A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1398734B1 (en) * 2010-03-04 2013-03-18 Bosch Gmbh Robert SYSTEM FOR FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE

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Publication number Priority date Publication date Assignee Title
DE3642642C3 (en) * 1986-12-13 1994-09-01 Rexroth Mannesmann Gmbh Circuit arrangement for position and feed control of a hydraulic drive
DE3838914A1 (en) * 1988-11-17 1990-05-23 Bosch Gmbh Robert Valve
US5092299A (en) * 1990-11-30 1992-03-03 Cummins Engine Company, Inc. Air fuel control for a PT fuel system
DE4308297A1 (en) * 1992-03-20 1993-09-23 Rexroth Mannesmann Gmbh
DE4443352A1 (en) * 1994-12-06 1996-06-13 Kermi Gmbh Device for controlling a flow, in particular a valve
DE4444417B4 (en) * 1994-12-14 2005-01-05 Robert Bosch Gmbh Fuel supply system
EP0762256B1 (en) * 1995-08-14 2001-10-31 LuK Fahrzeug-Hydraulik GmbH & Co. KG Flow control valve
DE19933198A1 (en) * 1999-07-15 2001-01-18 Fev Motorentech Gmbh Pressure regulation process for liquid fuel injection device, involving regulating pressure in store cavity by controllable pressure holding valve
DE10023621A1 (en) * 2000-05-13 2001-11-15 Bosch Gmbh Robert Fuel injection system for internal combustion engine has valve piston with at least one, preferably several, radial control openings connected to suction side of high pressure pump
JP2002004977A (en) * 2000-06-26 2002-01-09 Denso Corp Flow control device
US7178510B2 (en) * 2000-10-16 2007-02-20 Woodward Governor Company Fuel system

Non-Patent Citations (1)

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Title
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Also Published As

Publication number Publication date
DE10247774A1 (en) 2004-04-22
EP1552140A1 (en) 2005-07-13
DE10247774B4 (en) 2005-09-29
WO2004036032A1 (en) 2004-04-29
DE50307301D1 (en) 2007-06-28

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