JP2004138062A - Pressure limiting valve and fuel system equipped therewith - Google Patents

Pressure limiting valve and fuel system equipped therewith Download PDF

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Publication number
JP2004138062A
JP2004138062A JP2003354288A JP2003354288A JP2004138062A JP 2004138062 A JP2004138062 A JP 2004138062A JP 2003354288 A JP2003354288 A JP 2003354288A JP 2003354288 A JP2003354288 A JP 2003354288A JP 2004138062 A JP2004138062 A JP 2004138062A
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Prior art keywords
pressure
limiting valve
pressure limiting
spring
fuel
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JP2003354288A
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JP4488486B2 (en
Inventor
Shiyuumatsuhaa Mateiasu
Helmut Rembold
Bernd Schroeder
Heinz Siegel
ハインツ ジーゲル
ヘルムート レムボルト
ベルント シュレーダー
マティアス シューマッハー
Original Assignee
Robert Bosch Gmbh
ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツングRobert Bosch Gmbh
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Priority to DE10327411.1A priority patent/DE10327411B4/en
Application filed by Robert Bosch Gmbh, ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツングRobert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of JP2004138062A publication Critical patent/JP2004138062A/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/02Fuel-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
    • F02M63/0225Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/023Means for varying pressure in common rails
    • F02M63/0235Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/0245Means for varying pressure in common rails by bleeding fuel pressure between the high pressure pump and the common rail
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46Valves
    • F02M59/462Delivery valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46Valves
    • F02M59/466Electrically operated valves, e.g. using electromagnetic or piezo-electric operating means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0031Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0031Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/005Pressure relief valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0031Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0054Check valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/02Fuel-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
    • F02M63/0225Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20Varying fuel delivery in quantity or timing
    • F02M59/36Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366Valves being actuated electrically

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a pressure limiting valve from being opened undesirably owing to a pressure pulsation of a high pressure pump. <P>SOLUTION: The pressure limiting valve for a fuel system 10 of an internal combustion engine is provided with a pressure side, an outlet and a valve member 74 preloaded toward a valve seat 72. The pressure side is loaded with a pressure in a high pressure range 14 of the fuel system 10. In the valve member which is formed to hydraulically connect the inlet and the outlet, when a differential pressure exceeds a predetermined value between an inlet and the outlet, the outlet of the pressure limiting valve 56 is hydraulically connected to a transfer chamber 60 of a high pressure pump 30 of the fuel system 10. <P>COPYRIGHT: (C)2004,JPO

Description

The present invention is a pressure limiting valve for a fuel system of an internal combustion engine, provided with an inlet and an outlet, and further provided with a preloaded valve member, wherein the valve member has an inlet and an outlet. A hydraulic connection between the inlet and the outlet when the pressure difference between them exceeds a specified value.

Such pressure limiting valves are on the market and are well known. Such a pressure limiting valve is used in a fuel system used in a gasoline direct injection internal combustion engine. Such fuel systems typically have a low pressure region and a high pressure region. An electric front feed pump pumps fuel from the tank to a low pressure region, where fuel is pumped through a high pressure pump to a fuel collecting line (called a common rail). The pressure in the fuel collecting line is usually regulated by a pressure regulating valve or a quantity control valve.

However, in order to obtain protection against very high pressures in the fuel collecting line, a pressure limiting valve is provided in the high pressure area of the fuel system. This pressure limiting valve is generally a pressure limiting valve with a valve element pressed against a valve seat by a spring. When the pressure in the fuel collecting line exceeds a specified limit value, the valve member lifts from the valve seat so that fuel can flow from the inlet of the pressure limiting valve to the outlet and from the outlet to the low pressure region of the fuel system. .

This known pressure limiting valve already operates very well and very reliably. However, there are limitations on the possible placement of the pressure limiting valve in the fuel system:
In general, the pressure limiting valve must be arranged in the area of the fuel collecting line, that is, at a distance from the high-pressure pump. The reason for this is that high pressure pumps generate pressure pulsations during operation, the peak of which can exceed the opening pressure of the pressure limiting valve. If the pressure limiting valve is located in the immediate vicinity of the high pressure pump, there is a risk that the pressure limiting valve will open due to pressure pulsations even though the maximum system pressure has not yet been reached. Only at some distance from the high-pressure pump does the pressure pulsation become smooth, based on the throttle effect in the fuel line and the shrinkage of the fuel.

Alternatively, it is also possible to design the pressure limiting valve in such a way that its opening pressure lies above a pressure peak due to pressure pulsations. A pressure limiting valve designed in this way can be placed in the immediate vicinity of the high-pressure pump or can be integrated into the high-pressure pump. In emergency operation (Notlaufbetrieb), that is, when the pressure regulation in the fuel collecting line no longer functions properly and the pressure higher than the normal system pressure is present in the fuel collecting line, the internal combustion engine must be reliably operated. Operation must be guaranteed. This also means that the components of the high-pressure region of the fuel system must be designed for their function for the high opening pressure of the pressure-limiting valve. However, such components are expensive.

In the pressure limiting device described in German Patent Application No. 101 18 936 by the same applicant, which has not yet been published, the pressure pulsation is eliminated by the compensation chamber, so that the pressure limiting device is operated during normal operation of the fuel pump. However, it does not open despite the pressure pulsation caused by the high pressure pump. This also allows for the placement of the pressure limiting device near the high pressure pump.
German Patent Application No. 10118936

An object of the present invention is to avoid an undesired opening of a pressure limiting valve which may occur due to pressure pulsation of a high-pressure pump.

In order to solve this problem, according to the configuration of the present invention, there is provided a pressure limiting valve for a fuel system of an internal combustion engine, wherein a pressure side, an outlet, and a valve member preloaded toward a valve seat are provided. The pressure side is loaded by the pressure in the high pressure region of the fuel system, and the valve member hydraulically connects the inlet and the outlet when the pressure difference between the inlet and the outlet exceeds a specified value. In the above type, the outlet of the pressure limiting valve is hydraulically connected to the transfer chamber of the high pressure pump of the fuel system.

In the pressure-limiting valve according to the invention, an undesired opening is prevented by the following in that the pressure pulsations caused by the high-pressure pump during the discharge stroke are exerted on the valve member from both sides, i.e. from the inlet and the outlet. You. As a result, the pressure pulsation, ie the pressure pulsation whose maximum value can obviously exceed the opening pressure of the pressure limiting valve, does not exert any hydraulic force on the valve member. This reliably prevents the valve member from lifting from its valve seat during the discharge stroke and thus opening the pressure limiting valve.

The pressure limiting valve according to the invention also prevents unacceptably high pressures in the high-pressure region of the fuel system during the suction stroke of the high-pressure pump. In other words, in this case, the check valve between the transfer chamber of the high-pressure pump and the high-pressure area of the fuel system is closed, and the high pressure generated in some cases in the high-pressure area of the fuel system opens the valve member of the pressure limiting valve. As a result, the pressure is extinguished or reduced.

The pressure limiting valve according to the invention has a very simple construction and differs from the solutions known from the prior art mainly by the circuit configuration or arrangement according to the invention. Basically, the advantages according to the invention can be obtained with seat valves and slide valves.

In another configuration of the present invention, the pressure limiting valve has a casing having a valve seat and a spring chamber, a spring is provided in the spring chamber, and the spring is supported at one end by the casing, and The other end is supported by the valve member, and the spring chamber is hydraulically connected to the outlet. Such an arrangement substantially corresponds to the known pressure limiting valve according to the prior art, which according to the invention is hydraulically connected to the transfer chamber of the fuel-based high-pressure pump. ing.

In another embodiment of the pressure limiting valve according to the invention, the pressure limiting valve has a spring holder, and a spring is provided between the spring holder and the valve seat, the spring being supported at one end by the spring holder. And is supported by the valve member at the other end. With this arrangement, the pressure limiting valve can be integrated into the high-pressure fuel pump in various mounting positions. Furthermore, the manufacture of the pressure limiting valve is simplified.

In another embodiment of the invention, the spring holder is connected to the valve seat, so that the production, inspection and adjustment of the pressure limiting valve can be performed outside the high-pressure fuel pump. . Further, measuring and adjusting the opening pressure of each pressure limiting valve prior to installation also improves the operating characteristics of the fuel high pressure pump.

Alternatively, the spring holder may be fixed in a bore of the casing, so that the number of components can be reduced. In this case, the spring holder can be press-fitted and / or welded into the bore.

To prevent the spring from escaping laterally, it is advantageous if the spring holder has a supporting mandrel.

In another configuration which simplifies the manufacture of the pressure limiting valve, the valve seat is arranged on a seated sleeve, which is fixed in a bore of the casing, for example by press-fitting and / or welding.

In another embodiment of the invention, a separating piston is provided between the spring chamber and the outlet in a sealing manner in the casing or the spring holder, the separating piston being provided between the outlet and the spring chamber. When there is a predetermined pressure difference, it is mounted on the valve member. That is, the separation piston is lifted from the valve member during the suction phase of the high pressure pump. In this way, pressure fluctuations in the transfer chamber are moved away from the valve member during the suction stroke, which improves the precision of the adjustment of the pressure limiting valve.

Further, a preloaded additional spring is provided between the separation piston and the valve member, and the additional spring lifts the separation piston from the valve member in the suction phase of the fuel high-pressure pump. The effect can be further enhanced in a particularly simple manner.

In a further refinement of the function of the pressure limiting valve according to the invention, a spring catch is provided between the spring and / or the additional spring and the valve member. With this configuration, it is not necessary to relate the sizing of the valve member and the spring to each other, so that the design of the individual components is facilitated.

If it is desired to optimize the supply rate of the high-pressure pump, it is advantageous if the additional spring is arranged between the separating piston and the casing, so that the additional spring always opens the separating piston. It can be kept in contact with the member.

In a further refinement of the mode of operation of the pressure limiting valve according to the invention, the spring chamber is connected to a leak line.

The present invention also relates to a fuel system for supplying fuel for an internal combustion engine, comprising a fuel tank, a first fuel pump connected to the fuel tank on an inlet side, and a fuel connection to the first fuel pump. A high-pressure pump, which is a second fuel pump connected on the inlet side via a section, and a pressure limiting valve for limiting the pressure in the fuel line at the outlet side of the high-pressure pump. .

In order to be able to make such a fuel system as variable as possible without additional costs, in the present invention the pressure limiting valve is configured as described above.

In this case, in the configuration of the fuel system according to the present invention, the high-pressure pump has one one-cylinder piston pump. In such a high-pressure pump, the conveying pulsation is particularly pronounced, so that the pressure limiting valve according to the invention works very effectively in this case.

In a particularly advantageous embodiment of the fuel system according to the invention, the pressure limiting valve is mounted on the high-pressure pump, and is preferably integrated in the high-pressure pump. Such a configuration in which the pressure limiting valve is disposed inside the fuel system has the advantage that the return line from the pressure limiting valve to, for example, the low pressure region of the fuel system can be omitted. With such a configuration, the cost of the fuel system according to the present invention can be significantly reduced.

Next, an embodiment of the present invention will be described with reference to the drawings.

FIG. 1 shows a fuel system indicated generally by reference numeral 10. The fuel system 10 has a low pressure region 12 and a high pressure region 14.

The low pressure region 12 has a fuel tank 16 in which fuel is stored. The fuel 18 is transported from the fuel tank 16 by a first fuel pump 20. The first fuel pump 20 is an electric fuel pump. The electric fuel pump 20 conveys fuel into the low-pressure fuel line 22. A filter 24 is initially provided in the low-pressure fuel line 22 behind the electric fuel pump 20 when viewed in the flow direction. In front of the filter 24 in the direction of flow, a first branch line 26 branches off from the low-pressure fuel line 22 and returns fuel to the fuel tank 16. A pressure limiting device 28 is arranged in the first branch line 26.

The low pressure fuel line 22 communicates with the high pressure pump 30. The high-pressure pump 30 is driven by a camshaft of an internal combustion engine (not shown) in a type not shown. The high-pressure pump 30 is a one-piston high-pressure pump. A pressure damping device 32 and a suction valve 34 are further arranged upstream of the high-pressure pump 30 in the low-pressure fuel line 22. A second branch line 36 branches from the low-pressure fuel line 22 between the filter 24 and the pressure damping device 32, and a low-pressure adjusting device 38 is disposed in the branch line 36. The second branch line 36 likewise leads to the fuel tank 16. From the high-pressure pump 30, a leak line 40 leads to a second branch line 36.

On the output side, the high-pressure pump 30 pumps the fuel to the high-pressure fuel line 42, which communicates with the fuel collecting line 46 via the check valve 44. Fuel injection valves 48 are further connected to the fuel collecting line 46, and these fuel injection valves 48 inject fuel into a combustion chamber of an internal combustion engine (not shown). The pressure in the fuel collecting line 46 is detected by a pressure sensor 50.

A throttle (not shown) may be provided in the high-pressure fuel line 42 in front of the fuel collecting line 46 in order to improve the operation characteristics of the high-pressure region 14 of the fuel system 10. This restrictor avoids pressure fluctuations and prevents unwanted noise generation in the high-pressure area 14.

The pressure in the high-pressure fuel line 42 and the fuel collecting line 46, that is, the pressure in the high-pressure region 14 of the fuel system 10 is regulated via the high-pressure side quantity control valve 52 in the embodiment shown in FIG. The quantity control valve 52 connects the high pressure fuel line 42 located between the check valve 44 and the fuel collecting line 46 to the low pressure fuel line 22 located between the suction valve 34 and the pressure damping device 32. Connected to the area. This connection is made via a third branch line 54. The quantity control valve 52 is controlled by a control and regulation unit, not shown in FIG. 1, which receives a signal from the pressure sensor 50. In this way, a closed regulating circuit for regulating the pressure in the high pressure region 14 of the fuel system 10 is obtained. 4 to 8, the pressure regulation in the high-pressure region is performed by a quantity control valve arranged on the suction side.

In order to avoid overpressure in the fuel collecting line 46 which may impair the normal functioning of the fuel injection valve 48 in the event of a failure of the quantity control valve 52, a pressure limiting valve 56 is incorporated in the high-pressure pump 30. The structure and function of the pressure limiting valve 56 will be described below with reference to FIG. 2 and FIGS.
In the first embodiment of the pressure limiting valve 56 according to the invention shown in FIG. 2, the pressure limiting valve 56 is integrated in the casing 58 of the high-pressure pump 30. A transfer chamber 60 is provided in the casing 58, and the transfer chamber 60 is limited on one side by a piston 62 of the high-pressure pump 30. The piston 62 vibrates or reciprocates in the hole 64 of the casing 58. The drive for the piston 62 is not shown in FIG. The reciprocation of the piston 62 is indicated by a double arrow 66 in FIG.

低 The low-pressure fuel line 22 provided with the suction valve 34 is opened in the transfer chamber 60. Similarly, a third branch conduit 54 branches off from the transfer chamber 60, and a quantity control valve 52 is arranged in the branch conduit 54. Further, a high-pressure fuel line 42 having a check valve 44 branches from the transfer chamber 60.

見 て Behind the check valve 44 in the flow direction, a fourth branch line 70 branches, and the branch line 54 connects the high-pressure fuel line 42 to the transfer chamber 60. The fourth branch line 70 comprises sections 70a and 70b.

The pressure limiting valve 56 is formed as a ball valve in the embodiment shown in FIG. However, in the present invention, it is also possible to use seat valves and slide valves of other shapes.

The casing 58 is formed with a valve seat 72, which cooperates with a valve member 74 formed as a ball in a manner known per se. A spring 76 supported at one end by the casing 58 and at the other end by the valve member 74 defines the opening pressure of the pressure limiting valve 56 by its preload or preload. The spring 76 is housed in a spring chamber 78 of the casing 58.

When the spring chamber 78 and thus the back side of the valve member 74 are loaded by the pressure in the transfer chamber 60, the valve member 74 is connected to the transfer chamber 60 or the high-pressure fuel line 42 during the discharge stroke of the high-pressure fuel pump 30. Even when pressure pulsation occurs, it does not lift from the valve seat 72. That is, the check valve 44 is open during the discharge stroke, so that the pressures in the high pressure fuel line 42, the fourth branch line 70, the spring chamber 78 and the transfer chamber 60 are equal, and thus the valve member 74 The acting hydraulic pressures cancel each other.

Only during the suction stroke, i.e. when the pressure in the transfer chamber 60 decreases and the check valve 44 closes, a pressure difference between the section 70a of the fourth branch line 70 and the spring chamber 78 arises, The result is a hydraulic pressure on the valve member 74. If this hydraulic pressure exceeds the closing force exerted on the valve member 74 by the spring 76, the pressure limiting valve 56 will open and an unacceptably high pressure in the high pressure fuel line 42 will pass through the fourth branch line 70. And lowers in the transfer chamber 60.

As can be seen from the description of the first embodiment, the pressure limiting valve 56 according to the present invention has a simple structure like other pressure limiting valves known based on the prior art.

Due to the circuit arrangement according to the invention, the pressure limiting valve 56 according to the invention remains closed even during the occurrence of pressure pulsations during the discharge stroke of the high-pressure fuel pump 30. Thereby, the pressure build-up during normal operation of the internal combustion engine takes place as desired. Only if the pressure in the high-pressure fuel line 42 exceeds the opening pressure of the pressure-limiting valve 56 during the suction stroke of the high-pressure pump 30 will the pressure-limiting valve 56 be opened, thereby allowing a pressure drop in the high-pressure fuel line 42. To

FIG. 3 shows the course of the pressure in the transfer chamber 60 and in the high-pressure fuel line 42 behind the check valve 44 in relation to the stroke of the piston 62 of the high-pressure pump 30.

The first line 80 shows the distance of movement of the piston 62 in the hole 64. The movement from bottom dead center (UT) to top dead center (OT) is called the discharge stroke and is indicated by double arrow 82 in FIG.

The movement distance of the piston from the OT to the UT is called the suction stroke 84.

A second line 86 indicated by a solid line indicates the pressure in the transfer chamber 60. As is apparent from FIG. 3, a so-called pressure pulsation 85 occurs during the discharge stroke. That is, a pressure peak having a maximum value P max is formed, and this pressure peak is clearly located above the opening pressure P DBV of the pressure limiting valve 56.

A third line 88, shown in broken lines in FIG. 3, indicates the pressure in the high pressure fuel line 42 behind the check valve 44 and the pressure in the section 70a of the fourth branch line 70. As can be seen from FIG. 3, the line 88, the pressure in the high-pressure fuel line 42, is the pressure in the transfer chamber 60 (second line 86) even if the pressure exceeds the opening pressure PDBV of the pressure limiting valve 56. Is following. Only if the pressure in the transfer chamber 60 drops strongly during the suction stroke 84 (see second line 86) can a pressure difference between the pressure in the high-pressure fuel line 42 and the pressure in the transfer chamber 60 be formed. it can. In the operating state of the fuel system shown in FIG. 3, the pressure in the high-pressure fuel line 42 during the suction stroke remains equal to the opening pressure P DBV of the pressure limiting valve 56, while the pressure in the transfer chamber 60 is Drops strongly. In other words, the pressure limiting valve 56 generates an unacceptably high pressure during the suction stroke, and the amount of fuel transferred to the fuel collecting line 46 during the discharge stroke is relaxed to the transfer chamber 60 again during the suction stroke. By doing so.

In the second embodiment of the pressure limiting valve 56 according to the invention shown in FIG. 4, the pressure limiting valve 56 is a pre-assembled component unit, a seated sleeve 102 having a valve seat 72 and a bore 104, a spring with a spring. It comprises a holder 106, a spring 76 and a valve member 74. In the lower part of FIG. 4, such a pre-assembled pressure limiting valve 56 is shown enlarged outside the high pressure fuel pump, and in the upper part of FIG. Are shown incorporated in a casing 58 of FIG. As can be seen from the detailed view of the pressure limiting valve 56 shown in FIG. 4, the spring holder 106 is rigidly connected to the seated sleeve 102 by edge bending and welding (see welding seam 109). The spring 76 is supported at one end by the spring holder 106 and at the other end by the valve member 74. After the seated sleeve 102 and the spring holder 106 have been connected to each other, the opening pressure of the pressure limiting valve 56 can be further adjusted by the spring 76 being still somewhat compressed in the direction of its longitudinal axis. It is. As a result, the preload applied to the valve member 74 from the spring 76 and, consequently, the opening pressure of the pressure limiting valve 56 are increased. The pressure limiting valve 56 according to the present invention can be assembled and adjusted completely outside the high-pressure fuel pump. This provides advantages in terms of manufacturing time or costs. Furthermore, the variability of the operating characteristics of the various pressure limiting valves 56 according to the invention in mass production is significantly reduced.

In the upper part of FIG. 4, the pressure limiting valve 56 is press-fitted or otherwise fixed in the casing 58 of the high-pressure pump 30 with its seating sleeve 102. In this case, the pressure limiting valve 56 enters the transfer chamber 60. The piston 62 has a cylindrical notch 108, and the pressure limiting valve 56 enters the notch 108 when the piston 62 approaches its top dead center. Such an arrangement in particular saves space and at the same time minimizes the dead space or dead space of the transfer chamber. This increases the hydraulic efficiency of the high-pressure pump 30. The control side of the pressure limiting valve 56 is loaded by the rail pressure in the high pressure line 42 or the fuel collecting line 46 via the fourth branch line 70, bypassing the check valve 44.

量 In the high-pressure pump 30 shown in a sectional view in FIG. 4, the quantity control valve 52 is not visible. Similarly, in this drawing, the hydraulic connection between the low-pressure fuel line 22 and the transfer chamber 60, that is, the connection with the suction valve 34 disposed therebetween, is not visible. In FIG. 4, the hydraulic connection between the pressure damping device 32 and the low-pressure fuel line 22 is clear by means of a connection hole 110 formed as a stepped hole.

FIG. 5 shows another embodiment of the pressure limiting valve 56 according to the present invention. In FIG. 5, the casing 58 is shown in a top view perpendicular to the longitudinal axis of the piston 62. That is, the piston bottom of the piston 62 can be seen in FIG. In this embodiment, a high-pressure fuel line 42, a low-pressure fuel line 22, and a fourth branch line 70 composed of sections 70 b and 70 a open to the transfer chamber 60. The quantity control is then effected by the direct operation of the suction valve 34, as described below:
The section 70a of the fourth branch conduit 70 is configured as a stepped hole. The seated sleeve 102 is press-fitted into the stepped hole, that is, the seated sleeve 102 is axially fixed to the step portion of the stepped hole. The spring holder 106 is likewise pressed into the stepped hole and then welded in this position if the spring 76 arranged between the spring holder 106 and the valve member 74 has sufficient preload. You. The weld seam is designated by reference numeral 109 in FIG. In this embodiment of the pressure limiting valve 56 according to the present invention, there is no direct connection between the seated sleeve 102 and the spring holder 106. To prevent the spring 76 from escaping in the lateral direction, the spring holder 106 is provided with a support mandrel 112. Since the third branch line 54 and the section 70b of the fourth branch line 70 are located on a common axis, these holes can be manufactured in one forming operation, clamping or mounting. And there are no additional outward sealing points.

で は In this embodiment, the suction valve 34 is configured as a plate valve having the valve plate 111. The valve plate 111 is pressed against the valve seat 115 of the suction valve 34 by a spring 76. During the suction stroke of the high pressure pump 30, the valve plate 111 lifts from the valve seat 115, and fuel can flow from the low pressure fuel line 22 into the transfer chamber 60. The quantity control valve 52 is arranged on the suction side in this and the later described embodiments, and when the quantity control valve 52 is correspondingly controlled, the valve plate 111 is moved by means of a push rod 113 during the discharge stroke 82. From the valve seat 72. When the valve plate 111 is not mounted on the valve seat 115, the suction valve 34 is open. As a result, no pressure builds up in the transfer chamber 60 and no fuel pressure feed to the high pressure fuel line 42 is performed as long as the suction valve 34 is open. In this way, the pressure in the fuel collecting line 46 can also be adjusted by the amount control valve 52 disposed on the suction side.

FIG. 6 shows another embodiment of the pressure limiting valve 56 according to the present invention. The structure of the pressure limiting valve 56 substantially corresponds to the pressure limiting valve 56 shown in FIG. However, in the embodiment shown in FIG. 6, the mounting is somewhat different. In this embodiment, the low-pressure fuel line 22, the suction valve 34 and the quantity control valve 52 are not shown.

圧 力 The pressure limiting valve 56 according to the present invention is disposed in the stepped hole 114 of the casing 58. The stepped hole 114 is arranged perpendicular to the high-pressure fuel pipe 42 that opens to the transfer chamber. The stepped hole 114 also opens into the fourth branch line 70. Similarly, as in the embodiment shown in FIG. 5, the seated sleeve 102 and the spring holder 106 are press-fit into the stepped holes 114. The spring holder 106 is firmly connected to the casing 58 by the welding seam 109 as soon as it occupies the proper position.

FIG. 7 shows another embodiment of the pressure limiting valve 56 according to the present invention. The same reference numerals are used for the same members, and the description in FIG. 2 and FIG. 3 corresponds thereto. In FIG. 7, the casing 58 is shown in cross section at the height of the transfer chamber 60. FIG. 7 shows the piston 62 guided in the bore 64. Perpendicular to the bore 64, in a transfer chamber 60, not shown, a high-pressure fuel line 42 with a check valve 44 and a third branch line 54 with a quantity control valve 52, not shown And have branched. The low pressure fuel line 22 is not shown in FIG. With the arrangement shown in FIG. 7, a very compact construction is possible. This is because, in this case, the pressure limiting valve 56 according to the invention is arranged at the same height as the transfer chamber 60 (not shown).

Unlike the first embodiment shown in FIG. 2, for example, a separation piston 90 is provided between the spring chamber 60 and the valve member 74 so as to be guided inside the casing 58 while being sealed. The separation piston 90 has a push rod 92, which enters the spring chamber 78. An additional spring 96 is contracted between the separation piston 90 and the spring receiver 94 mounted on the valve member 74. Due to the action of this additional spring 96, if the same pressure is present on both sides of the separating piston 90, ie in the spring chamber 78 and in the section 70 b of the fourth branch line 70 or in the spring chamber 60, the push rod 92 Will not rest or contact the spring receiver 94. Only when there is a pressure difference between the transfer chamber 60 and the spring chamber 78, the separating piston 90 is moved toward the spring receiver 94 and presses the valve member 74 against the seat 72 via the spring receiver 94. . By arranging the separation piston 90, the dead space in the transfer chamber 60 is reduced, thereby improving the volumetric efficiency of the high-pressure pump 30.

The spring chamber 78 is connected to a non-pressure leak line 98 or a low-pressure fuel line 22 in this embodiment. That is, the separation piston 90 presses the valve member 74 during the discharge stroke of the high-pressure pump 30, thereby preventing the pressure limiting valve 56 from opening during the discharge stroke 82. During the suction stroke of the high-pressure pump 30, the additional spring 96 urges the separating piston 90 to the left as viewed in FIG. 7, so that the separating piston 90 is lifted from the spring receiver 94. Thereby, the separation piston 90 and the valve member 74 are separated or disconnected from each other. As a result, the pressure fluctuation occurring in the transfer chamber 60 of the high-pressure pump 30 during the suction stroke becomes small, and as a result, the pressure fluctuation occurs due to the pressure fluctuation. The adjustment characteristics of 56 are no longer adversely affected.

By selecting the diameter of the separation piston 90 and the valve seat 72, it is possible to hydraulically increase the liquid pressure applied to the valve member 74 from the separation piston 90 during the discharge stroke.

If it is desired to maximize the supply rate of the high-pressure pump 30, an additional spring 96 can also be arranged in the section 70b of the fourth branch line 70 (see arrow 100), in which case the additional spring 96 becomes It is supported on the one hand by the casing 58 and on the other hand by the separating piston 90, which keeps the separating piston 90 in contact with the spring receiver 94 continuously. With such a configuration, the pressure formation in the transfer chamber 60 during the discharge stroke of the high-pressure pump 30 and, consequently, the pressure formation in the high-pressure fuel pipe 42 are accelerated.

に も The embodiment of FIG. 8 also shows a pressure limiting valve 56 with a separating piston 90. This pressure limiting valve 56 can be formed and regulated completely outside the high-pressure pump 30, as in the embodiment shown in FIG. This is because, in this case, a sleeve 116 having at least one lateral hole 118 is provided between the seated sleeve 102 and the spring holder 106. The sleeve 116 is welded to the spring holder 106 and the seated sleeve 102 when the preload of the spring 76 is sized to achieve the desired opening pressure of the pressure limiting valve 56. Of course, it is also possible to couple the sleeve 116 with the spring holder 106 and / or the seated sleeve 102 by means different from the welding seam 109.

The pre-assembled and adjusted pressure limiting valve 56 is press-fitted into a section 70 a of the fourth branch line 70 formed as a stepped bore, and is surrounded by a closure plug 120 welded to the casing 58. Sealed against. A groove 122 is milled in the closing plug 120 on the end face side facing the pressure limiting valve 56, and the groove 122 is formed in a fourth branch pipe opening to a transfer chamber (not shown). A hydraulic connection between the section 70b of the passage 70 and the separation piston 90 is enabled. The diameter of the separation piston 90 is set so that the pressure limiting valve 56 does not open even if a pressure shock or an excessive rise in pressure occurs in the transfer chamber (not shown in FIG. 8) during the discharge stroke of the high-pressure pump 30. Dimensions are set.

The low-pressure fuel line 22, not shown, extends upwards in this embodiment and opens into a pressure damping device 32 (not shown here, see FIG. 4).

The main functions of the pressure limiting valve according to the present invention are as follows:
During normal operation, the system pressure of the fuel injection device during engine braking operation (Schubbetrieb) of the internal combustion engine is limited even if the pressure in the fuel collecting line 46 increases due to heating of the fuel by the engine heat.

During normal operation, for example, when the amount control valve 52 is clamped, that is, when the fuel high-pressure pump 30 is caught at a position where the entire discharge amount is always pumped, the system pressure of the fuel injection device is similarly limited.

In the embodiment shown in FIG. 2, when the amount control valve 52 is completely opened during the engine braking operation (emergency operation), the maximum amount of fuel pumped from the high-pressure pump 30 returns to the transfer chamber 60 to the maximum extent. And can be discharged. The pressure rise due to heating of the fuel in the fuel collecting line 46 cannot be compensated. Therefore, in such a case, a large amount of fuel is injected into the combustion chamber (not shown) via the injection valve 48, so that an unacceptable pressure increase in the high pressure region of the fuel system 10 is prevented. I have.

The pressure limiting valve 56 shown in FIGS. 7 and 8 discharges a complete amount of fuel both in normal operation and in emergency operation, and thus in any case, without any additional operation of the engine control, reduces the pressure. Can be realized. Furthermore, it is advantageous to reduce the maximum engine speed in emergency operation in order to obtain sufficient time for the pressure in the fuel collecting line 46 to drop during the suction stroke of the high-pressure pump 30.

FIG. 9 shows a sectional view of another embodiment of the pressure limiting valve 56 according to the present invention. The embodiment shown in FIG. 9 is similar to the embodiment shown in FIG. 2, and therefore only the differences will be described here. In the embodiment shown in FIG. 9, a cylindrical guide section 124 is connected to the valve seat 72, and the guide section 124 moves the valve member 74 in the axial direction when the valve member 74 is lifted from the valve seat 72. I will guide you in. The diameter of the guide section 124 and the diameter of the valve member 74 formed as a ball are matched to one another such that a ring-shaped throttle gap 126 is formed between the valve member 74 and the guide section 124. The mode of operation of this embodiment of the pressure limiting valve according to the invention is as follows:
When the pressure in the transfer chamber 60 decreases after the end of the discharge stroke in the emergency operation, the pressure limiting valve 56 is opened by the opening force of the preload of the spring 76 and the liquid pressure acting on the valve member 74. The amount of fuel flowing into the spring chamber 78 from the section 70a of the fourth branch line 70 at the start of opening of the pressure limiting valve 56 is restricted in the restriction gap 126, and the entire projection surface of the valve member 74 is loaded by the blocking pressure. Is done. As a result, as soon as the valve member 74 moves away from the guide section 124 towards the spring chamber 78, the guide section 124 expands towards the spring chamber 78 having a very large diameter, so that the opening movement of the valve member 74 is very rapid. And a sharp increase in the flow cross section is caused. Due to this rapid response of the pressure limiting valve 56, a large amount of fuel can flow back from the high pressure region 14 to the transfer chamber 60 in a short time. The sizing of the throttle gap 126 and the length of the guide section 124 make it possible to optimize the operating characteristics of the pressure limiting valve 56 and to adapt it to the specific application. However, when setting the size of the throttle gap 126, the following must be noted. That is, in this case, when the pressure limiting valve 56 operates in the emergency operation, the throttle action does not occur in the throttle gap 126 based on the pressure increase due to the heating of the fuel. Otherwise, the fuel in the fuel collecting line 46 will drop sharply in response to the pressure stage in the pressure limiting valve 56. However, the excess flow that occurs in this case is so small that the throttle gap 126 can be designed to achieve the operation described above.

In the embodiment shown in FIG. 10, instead of the valve member 74, the spring receiver 94 is guided in the guide section 124 of the casing 58. As a result, a throttle gap 126 is formed between the guide section 124 and the spring receiver 94. With this configuration, the surface loaded by the damming pressure can be selected independently of the diameter of the valve member. This further expands the flexibility in optimizing the dynamic characteristics of the pressure limiting valve 56. By such a structural means, at the time of the high rotation speed (when the amount control valve 52 fails during clamping), the time during the suction stage of the high-pressure pump 30 is previously set in the high-pressure region 14. The problem that the pumped-in fuel quantity is no longer sufficient to completely drain back into the transfer chamber 60 is solved. In particular, during engine braking operation of the internal combustion engine, at the high engine speed, a prescribed amount of fuel is sucked in through the suction valve 34, and as a result, the pressure in the fuel collecting line 46 rises unacceptably.

The following is ensured, in particular, by the embodiments shown in FIGS. That is, in the embodiment of FIGS. 9 and 10, an unacceptable pressure increase in the fuel collecting line 46 can be reliably prevented even when the amount control valve 52 is clamped and / or the control device malfunctions. This is because, in this case, the pressure limiting valve 56 can return a sufficiently large amount of fuel from the high pressure region 14 to the transfer chamber 60 during the suction stroke of the high pressure pump 30.

FIGS. 11 and 12 show still another embodiment of the pressure limiting valve 56 according to the present invention. This embodiment of the pressure limiting valve 56 according to the invention is also manufactured in a cartridge construction (Patronenbauweise). Thus, as in the embodiment shown in FIG. 4, the advantage is obtained that the pressure limiting valve 56 can be assembled, inspected and the opening pressure adjusted before it is incorporated into the casing 58 of the high-pressure pump 30.

The pressure limiting valve 56 shown in FIG. 11 comprises a valve casing 128 having a stepped central hole 130. The valve casing 128 has a first seal ridge 132, a second seal ridge 134, and a third seal ridge 136 on its outer diameter.

The central hole 130 is formed as a blind hole, and is closed on the right side in the position of the pressure limiting valve 56 shown in FIG. A spring 76 is disposed at the closed end of the central hole 130. The springs 76 are guided on both sides by respective guide sleeves 138 in the central bore 130. The spring force of the spring 76 is transmitted to the spring receiver 94 via the guide sleeve 138 and the pin 140 on the left side in FIG. 11, and is transmitted to the valve member 74 therefrom.

中間 An intermediate member 142 is press-fitted into the central hole 130 between the left guide sleeve 138 and the spring receiver 94 in FIG. The intermediate member 142 also serves in particular for guiding the pin 140.

ス リ ー ブ A seat sleeve 102 is press-fitted on the left side of the valve casing 128 in FIG. 11, and the seat sleeve 102 is formed with a valve seat 72. The axial position of the seated sleeve 102 in the central bore 130 is clearly determined by the shoulder of the central bore 130 and the shoulder in the seated sleeve 102. A fuel shib 144 is fixed to the sleeve 102 with a seat. The fuel shib 144 works to keep dirt in the fuel away from the valve seat 72 and the valve member 74 which are seal seats.

The pressure limiting valve 56 is hydraulically incorporated into the high pressure pump 30 as described below. The left side of the valve member 74 via the fourth branch line section 70a is loaded by the fuel pressure in the high pressure region of the high pressure pump 30. Via a fourth branch section 70 b in the valve casing 128 that extends to the central bore 130, the radial bore 146 in the intermediate member 142 is loaded by the pressure in the transfer chamber 60 of the high-pressure pump 30. The intermediate member 142 has two sealing ridges 148 to ensure a secure hydraulic connection between the fourth branch line section 70b and the radial bore 146 in the intermediate member 142. . An outer peripheral groove is present between the two raised portions 142, and the outer peripheral groove forms an annular ring chamber together with the central hole 130 of the valve casing 128. The section 70b in the valve casing 128 is positioned so that the section 70b opens to the ring chamber. Similarly, the radial hole 146 is also positioned to open into the ring chamber, so that regardless of the mutual angular position of the section 70b and the radial hole 146, the radial hole 146 The hydraulic connection between them is always guaranteed. The radial bore 146 opens into a central bore 150 formed as a blind bore, in which the separating piston 152 is slidably and sealingly guided. The separation piston 152 is supported at one end by a spring receiver 94. This causes the separation piston 152 to transmit a force directly proportional to the pressure in the transfer chamber 60 to the spring receiver 94, whereby the opening pressure of the pressure limiting valve 56 increases during the discharge stroke, that is, when the pressure in the transfer chamber 60 is similarly increased. When the pressure is high, the pressure is increased, so that an undesired opening operation during the discharge stroke can be suppressed.

If the pressure in the transfer chamber 60 drops during the suction stroke, no problematic force will be transmitted from the separating piston 152 to the spring receiver 94, so that the opening pressure of the pressure limiting valve 56 at this time Is substantially defined only by the spring 76.

When the valve member 74 is lifted from the seal seat 72, fuel can flow out of the section 70 a of the fourth branch line 70, that is, from the high-pressure area 14 of the fuel system 10, through the transverse hole 154 in the valve casing 128. . The lateral hole 154 is disposed between the first seal protrusion 132 and the second seal protrusion 134. The section 70 b in the valve casing 128 is located between the second seal ridge 134 and the third seal ridge 136.

An annular groove 158 is provided between the third seal ridge 136 and the collar 156 of the valve casing 128 so that fuel is supplied in one section of the low-pressure line 22 to the casing 58 of the high-pressure pump 30 in the valve casing. 128 and can further flow to a pressure damping device 32 not shown. The valve casing 128 is welded to the casing 58 at the collar 156. This is indicated by the weld seam 160 in FIG. 11 (see hatched in FIG. 11).

Sealing is achieved by the seal ridges 132, 134, 136, 148 between the casing 58 and the valve casing 128 or between the valve casing 128 and the intermediate member 142 and the welding seam 160, whereby the diffusion of fuel is achieved. Will be blocked. Furthermore, these seal joints do not cause aging of the seal joints, as for example in O-rings made of an elastomeric material.

FIG. 12 shows the pressure limiting valve 56 shown in FIG. From FIG. 12, the hydraulic connection of the pressure limiting valve 56 in the high-pressure pump 30 is well understood. In FIG. 12, some components of the pressure limiting valve 56 are omitted from the reference numerals for easy understanding.

圧 着 By appropriately selecting the diameter of the separation piston 152, it is possible to adjust the pressing force of the spring receiver 94 against the valve member 64, which is related to the pressure in the transfer chamber 60.

The increase in the opening pressure of the pressure limiting valve 56 caused by the transfer chamber pressure is adjusted to the flow resistance between the high-pressure pump 30 and the fuel collecting pipe 46, and the pressure limiting valve 56 does not open during the discharge stroke of the piston 62. It has become.

FIG. 13 shows another embodiment of the pressure limiting valve 56 according to the present invention. This embodiment is in many respects consistent with the embodiment shown and described in FIGS. Therefore, only major differences between the two embodiments will be described below.

In the embodiment shown in FIG. 13, the casing 58 of the pressure limiting valve 56 is at the same time the casing of the high-pressure pump 20, ie, unlike the embodiment shown in FIGS. 11 and 12, the pressure limiting valve in FIG. 56 is not configured in a cartridge structure format. This allows some components to be omitted. However, the opening pressure of the pressure limiting valve 56 can be adjusted when the pressure limiting valve is installed, and variations in operating characteristics can be minimized even during mass production. Such an advantage is obtained because the spring 76 is supported at one end by the spring receiver 94 and at the other end by the intermediate member 142.

The spring catch 94 has at least one longitudinal groove 162 through which the fuel flowing from the section 70 a into the pressure limiting valve 56 when the pressure limiting valve 56 is open is in the low-pressure fuel line 22. Can be discharged to The low-pressure fuel line 22 opens into a spring chamber 78 in this embodiment.

The intermediate member is pressed into the central hole 130 firmly at the seal ridge 148 and with a sealing action against the liquid. Depending on how deep the intermediate member is pressed into the central bore 130, the preload of the spring 76 and thus the opening pressure of the pressure limiting valve 56 is adjusted. After adjusting the opening pressure, the central hole 130 is closed by the cover 164. Cover 164 may be welded to casing 58.

The ring chamber created between the seal ridge 148, the central hole 130 and the intermediate member 142 provides a hydraulic connection between the fourth branch conduit section 70b and the radial hole 146 in the intermediate member 142. Guarantee.

The embodiment shown in FIGS. 7, 8, 11, 12 and 13 is different from the other embodiments in that the pressure drop or pressure disappearance is not directed towards the transfer chamber 60, It differs by what is done into the low pressure fuel line 22.

FIG. 2 is a circuit diagram schematically illustrating a fuel system including a fuel pump to which a pressure limiting valve is attached. FIG. 2 is a sectional view showing a region of a high-pressure pump and a first embodiment of the pressure limiting valve shown in FIG. 1. FIG. 4 is a diagram illustrating the progress of pressure in a transfer chamber and pressure in a high-pressure region of a fuel system, with time plotted on the horizontal axis. FIG. 4 is a view showing another embodiment of the pressure limiting valve according to the present invention. FIG. 4 is a view showing another embodiment of the pressure limiting valve according to the present invention. FIG. 4 is a view showing another embodiment of the pressure limiting valve according to the present invention. FIG. 4 is a view showing another embodiment of the pressure limiting valve according to the present invention. FIG. 4 is a view showing another embodiment of the pressure limiting valve according to the present invention. FIG. 4 is a view showing another embodiment of the pressure limiting valve according to the present invention. FIG. 4 is a view showing another embodiment of the pressure limiting valve according to the present invention. FIG. 4 is a view showing another embodiment of the pressure limiting valve according to the present invention. FIG. 4 is a view showing another embodiment of the pressure limiting valve according to the present invention. FIG. 4 is a view showing another embodiment of the pressure limiting valve according to the present invention.

Explanation of reference numerals

10 fuel system, {12} low pressure region, {14} high pressure region, {16} fuel tank, {18} fuel, {20} fuel pump, {22} low pressure fuel line, {24} filter, {26} branch line, {28} pressure limiting device, {30} high pressure pump, {32} pressure damping device , {34} suction valve, {36} branch line, {38} low pressure regulator, {40} leak line, {42} high pressure fuel line, {44} check valve, {46} fuel collecting line, {48} fuel injection valve, {50} pressure sensor, {52} volume control valve , {54} branch line, {56} pressure limiting valve, {58} casing, {60} transfer chamber, {62} piston, {64} hole, {66} double arrow, {70} branch line, {72} valve seat, {74} valve member, {76} spring, {78} spring chamber, # 80 , 86,88} line, {82,84} double arrow , {90} separate piston, {92} thrust rod, {94} spring receiver, {96} additional spring, {98} leak line, {100} arrow, {102} seated sleeve, {104} hole, {106} spring holder, {108} notch, {109} weld seam, {110} connection hole, {111} valve Plate {112} support stem, {113} thrust rod, {114} stepped hole, 115} valve seat, {116} sleeve, {118} side hole, {120} closure plug, {122} groove, {124} guide section, {126} throttle gap, {128} valve casing, {130} central hole, # 132 , 134, 136 seal ridge, {138} guide sleeve, {140} pin, {142} intermediate member, {144} fuel shib, {146} radial hole, {148} seal ridge, {150} center hole, {1} 2 separating piston, 154 cross-hole, 156 color, 158 annular groove 160 welded seam, 162 longitudinal groove, 164 cover

Claims (28)

  1. A pressure limiting valve for a fuel system (10) of an internal combustion engine, comprising a pressure side and an outlet, and a valve member (74) preloaded toward a valve seat (72), the pressure side being Loaded by the pressure in the high pressure region (14) of the fuel system (10), the valve member hydraulically connects the inlet and the outlet when the pressure difference between the inlet and the outlet exceeds a prescribed value. The outlet of the pressure limiting valve (56) is hydraulically connected to the transfer chamber (60) of the high pressure pump (30) of the fuel system (10). A pressure limiting valve for the fuel system of the internal combustion engine.
  2. 2. The pressure limiting valve according to claim 1, wherein the pressure limiting valve is configured as a seated valve or a slide valve.
  3. A pressure limiting valve (56) having a casing (58) with a valve seat (72) and a spring chamber (78), wherein a spring (76) is provided in the spring chamber (78); The spring (76) is supported at one end by the casing (58) and at the other end by the valve member (74), and the spring chamber (78) is hydraulically connected to the outlet (70b). The pressure limiting valve according to claim 1.
  4. The pressure limiting valve (56) has a spring holder (106), and a spring (76) is provided between the spring holder (106) and the valve seat (72), and the spring (76) is 4. The pressure limiting valve according to claim 1, wherein one end is supported by a spring holder and the other end is supported by a valve member.
  5. The pressure limiting valve according to claim 4, wherein the spring holder (106) is connected to the valve seat (72).
  6. The pressure limiting valve according to claim 4, wherein the spring holder (106) is fixed in the hole (70a, 114) of the casing (58, 128).
  7. 7. The pressure limiting valve according to claim 6, wherein a spring holder (106) is press-fitted and / or welded into said bore (70a, 114).
  8. 8. The pressure limiting valve according to claim 4, wherein the spring holder (106) has a support mandrel (112).
  9. 9. The seat according to claim 3, wherein the valve seat is arranged in a seated sleeve, the seated sleeve being fixed in a bore of the casing. The pressure limiting valve according to any one of the preceding claims.
  10. 10. The pressure limiting valve according to claim 9, wherein the seated sleeve (102) is press-fitted and / or welded into the bore (70a, 114).
  11. 11. The valve seat (72) is connected to a guide section (124), and a throttle gap (126) is formed between the guide section (124) and the valve member (74). The pressure limiting valve according to any one of the preceding claims.
  12. 12. The valve seat (72) connected to a guide section (124), wherein a throttle gap (126) is formed between the guide section (124) and the spring receiver (94). The pressure limiting valve according to any one of the preceding claims.
  13. Between the spring chamber (78) and the outlet (70b) there is provided a separating piston (90) guided in a sealing manner, said separating piston (90, 152) being arranged between the outlet (70b) and the spring chamber (70). Pressure limiting valve according to one of claims 3 to 12, which at least indirectly rests on the valve member (74) when there is a predetermined pressure difference between the pressure limiting valve and the valve member (78). .
  14. 14. Pressure limiting valve according to claim 13, wherein the separating piston (90) is guided in a sealing manner in the casing (58, 128).
  15. The pressure limiting valve according to claim 14, wherein the separating piston (90) is guided in a sealing manner in the spring holder (106).
  16. 16. Pressure limiting valve according to any one of claims 13 to 15, wherein a preloaded additional spring (96) is provided between the separating piston (90) and the valve member (74).
  17. 17. The pressure limiting valve according to claim 3, wherein a spring receiver (94) is provided between the spring (76) and / or the additional spring (96) and the valve member (74).
  18. 18. Pressure limiting valve according to claim 16, wherein the additional spring (96) lifts the separating piston (90) from the valve member (74) during the suction phase.
  19. 19. The pressure limiting valve according to claim 18, wherein the additional spring (96) keeps the separation piston (90) in contact with the valve member (74).
  20. 20. The pressure limiting valve according to any one of claims 13 to 19, wherein the separating piston (90) is hydraulically connected to the transfer chamber (60).
  21. An intermediate member (142) having a radial hole (146) and a center hole (150) is provided in the spring chamber (78), and the separation piston (152) has a sealing action in the center hole (150). The radial hole (146) and the central hole (150) are hydraulically connected, and the radial hole (146) defines a section (70b) of the fourth branch line (70). 16. The fuel supply system according to claim 13, which is hydraulically connected to the transfer chamber via an outlet side of the pressure-limiting valve, and is hydraulically connected to the low-pressure fuel line. A pressure limiting valve according to any one of the preceding claims.
  22. 22. The at least one pin (140) is guided in the intermediate member (142), the at least one pin (140) transmitting the force of a spring (76) to a spring receiver (94). Pressure limiting valve.
  23. 23. The pressure limiting valve according to claim 3, wherein the spring chamber (78) is connected to a leak line (98).
  24. 24. A pressure limiting valve according to any one of claims 3 to 23, wherein the casing (128) has a plurality of annular seal ridges (132, 134, 136).
  25. 25. The pressure limiting valve according to any one of claims 3 to 24, wherein the casing (128) is welded (160) with the high pressure pump (30).
  26. A fuel system (10) for supplying fuel (18) to an internal combustion engine, comprising: a fuel tank (16); a first fuel pump (20) connected to the fuel tank (16) on the inlet side; A high-pressure pump (30) connected on the inlet side to the first fuel pump (20) via a fuel connection (22); and a fuel line (42, 46) on the outlet side of the high-pressure pump (30). ), In which a pressure limiting valve (56) for limiting the pressure is provided, wherein the pressure limiting valve (56) is configured as in any one of claims 1 to 18. A fuel system comprising a pressure limiting valve.
  27. 26. The fuel system (25) according to claim 25, wherein the high pressure pump (30) has one one cylinder piston pump.
  28. 27. The fuel system (10) according to claim 25 or 26, wherein the pressure limiting valve (56) is mounted on the high-pressure pump (30), and is advantageously incorporated in the high-pressure pump (30).
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EP1411238A1 (en) 2004-04-21
ES2256621T3 (en) 2006-07-16
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EP1411238B1 (en) 2006-01-11
JP4488486B2 (en) 2010-06-23

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