Pressure regulating valve for regulating pressure in a high-pressure fuel accumulator for an internal combustion engine

Abstract

The invention relates to a pressure regulating valve for regulating pressure in a high-pressure fuel accumulator for an internal combustion engine, comprising a valve piston (5) accommodated axially displaceably in a bore (1) in a valve housing (2), acting on a valve closing member (3) in the direction of a valve seat (4), said valve piston being connected at the end thereof facing away from the valve seat (4) to an armature (6) of a magnetic assembly (7) for actuating the pressure regulating valve, wherein the armature (6) is accommodated in an armature chamber (8) and the valve closing member (3) is accommodated in a valve chamber (9). According to the invention, the valve chamber (9) and the armature chamber (8) are hydraulically connected via at least one groove (10) and/or bore (11) formed in the valve housing (2), valve piston (5) and/or in the armature (6), as well as at least one choke point (12).

Claims

1. A pressure regulating valve for regulating pressure in a high-pressure fuel accumulator for an internal combustion engine, the pressure regulating valve comprising a valve piston (5) held axially displaceably in a bore (1) of a valve housing (2) and acting on a valve closing member (3) in a direction of a valve seat (4), said valve piston being connected, at an end facing away from the valve seat (4), to an armature (6) of a magnetic assembly (7) for actuating the pressure regulating valve, wherein the armature (6) is held in an armature chamber (8) and the valve closing member (3) is held in a valve chamber (9), and wherein the valve chamber (9) and the armature chamber (8) are hydraulically connected via at least one groove (10) and/or bore (11) formed in the valve housing (2), valve piston (5) and/or armature (6) and at least one choke point (12), wherein the at least one choke point (12) is formed in the groove (10) and/or bore (11), wherein the groove (10) and/or bore (11) is stepped so as to form the choke point (12), wherein the valve chamber (9) and/or the armature chamber (8) are always connected to a return, and wherein the valve chamber (9) is connected to the return only via the armature chamber (8).

2. The pressure regulating valve as claimed in claim 1, wherein the valve chamber (9) and the armature chamber (8) are always connected to the return.

3. The pressure regulating valve as claimed in claim 1, wherein the valve chamber (9) is always connected to the return.

4. The pressure regulating valve as claimed in claim 1, wherein the armature chamber (8) is always connected to the return.

5. The pressure regulating valve as claimed in claim 1, wherein the at least one choke point (12) is connected upstream of the groove (10) and/or bore (11).

6. The pressure regulating valve as claimed in claim 1, wherein an additional hydraulic volume (18) is provided in the form of a blind bore formed in the valve housing (2).

7. The pressure regulating valve as claimed in claim 6, wherein the pressure regulating valve is a normally closed or normally open valve, wherein a direction of action of a magnetic force of the magnetic coil (20) can be the same or opposite the direction of action of a spring force of a spring (190).

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Preferred embodiments of the invention are explained in more detail below with reference to the enclosed drawings. These show:

(2) FIG. 1 a diagrammatic longitudinal section through a first preferred embodiment of a pressure regulating valve according to the invention;

(3) FIG. 2a a diagrammatic longitudinal section through a second preferred embodiment of a pressure regulating valve according to the invention;

(4) FIG. 2b a derivation of the valve piston shown in FIG. 2a;

(5) FIG. 3 a diagrammatic longitudinal section through a third preferred embodiment of a pressure regulating valve according to the invention;

(6) FIG. 4 a diagrammatic longitudinal section through a fourth preferred embodiment of a pressure regulating valve according to the invention;

(7) FIG. 5 a diagrammatic longitudinal section through a fifth preferred embodiment of a pressure regulating valve according to the invention;

(8) FIG. 6 a diagrammatic longitudinal section through a sixth preferred embodiment of a pressure regulating valve according to the invention;

(9) FIG. 7 a diagrammatic longitudinal section through a seventh preferred embodiment of a the pressure regulating valve according to the invention;

(10) FIG. 8 a diagrammatic longitudinal section through an eighth preferred embodiment of a pressure regulating valve according to the invention;

(11) FIG. 9 a diagrammatic longitudinal section through a ninth preferred embodiment of a pressure regulating valve according to the invention; and

(12) FIG. 10 a diagrammatic longitudinal section through a tenth preferred embodiment of a pressure regulating valve according to the invention.

DETAILED DESCRIPTION

(13) The depiction in FIG. 1 shows the structure of a first preferred exemplary embodiment of a pressure regulating valve according to the invention. A bore 1 is formed in a valve housing 2, in which bore a valve piston 5 is guided axially displaceably. The guide portion is marked with reference numeral 13. At a first end, the valve housing 2 has an annular receiving chamber for a magnetic coil 20 of a magnetic assembly 7 configured coaxially to and surrounding the bore 1. Next to the receiving chamber is an armature chamber 8 which holds an armature 6 cooperating with the magnetic coil 20 of the magnetic assembly 7. The armature chamber 8 is surrounded by a pot-like cover part 21 so that furthermore a receiving chamber is created for a spring 19, the spring force of which loads the armature 6 in the direction of a valve seat 4.

(14) In the pressure regulating valve shown, the magnetic force of the magnetic coil 20 acts in the same direction as the spring force of the spring 19, so that using the magnetic coil 20 a further closing force can be achieved. To open the valve, the hydraulic pressure present on the valve inlet side, i.e. the pressure in the high-pressure accumulator, must rise such that it at least overcomes the spring force of the spring 19. The invention furthermore comprises pressure regulating valves in which the magnetic force works against the spring force.

(15) The armature 6 is connected to the valve piston 5 guided axially displaceably in the bore 1 of the valve housing 2 such that the spring force of the spring 19 and the magnetic force of the magnetic coil 20 pressurize the armature 6 and valve piston 5 with a closing force in the direction of the valve seat 4. When the power supply to the magnetic coil 20 is interrupted, a rising pressure in the high-pressure fuel accumulator (not shown) can cause the valve to open. The pressure difference between the inlet-side and outlet-side pressure then causes a valve closing member 3, formed in the present case as a ball, to lift away from the valve seat 4. The valve piston 5 and the armature 6 are then moved in the direction of the cover part 21 against the spring force of the spring 19 by the lift of the valve closing member 3. In this switch position, the pressure regulating valve allows a connection of the high-pressure fuel accumulator to a low-pressure circuit (not shown). Fuel flows out from the high-pressure accumulator via a valve inlet 15 configured as a central bore in a valve piece 16, a valve chamber 9 and at least one radial bore 14 serving as a valve outlet, and in this way causes a pressure drop in the high-pressure accumulator. The valve piece 16 is supported via a spacer 17 on the valve housing 2.

(16) The actual invention is in this case implemented by a bore 11 formed in the valve housing 2 and a choke point 12 which hydraulically connect the valve chamber 9 and armature chamber 8. To form the choke point, the bore 11 is formed as a stepped bore, i.e. it has a reduced flow cross section in the region of the choke point 12. The bore 11 or choke point 12 opens into the radial bore 14 serving as a valve outlet, so that the bore 11 and choke point 12 are indirectly connected to the valve chamber 9 via the radial bore 14. In contrast, the other end of the bore 11 opens directly into the armature chamber 8, wherein an additional groove 10 provided in the armature 6 and an additional bore 11 facilitate pressure compensation within the armature chamber 8.

(17) The hydraulic connection created by the choke point 12 and bore 11 between the valve chamber 9 and the armature chamber 8 increases the hydraulic volume available to compensate for pressure fluctuations or pressure waves. To this extent, pressure fluctuations or peaks introduced into the valve chamber via the low-pressure circuit connected on the outlet side can be compensated or at least damped so as to guarantee a higher functional reliability of the pressure regulating valve. The pressure compensation also takes place more quickly.

(18) A second preferred embodiment is shown in FIG. 2a. The bore 11 and choke point 12 are here formed in the valve piston 5. The choke point 12 is designed as a transverse bore which connects the valve chamber 9 to the bore 11. Then via the choke point 12, the bore 11 opens directly into the valve chamber 9. A derivation of this embodiment is shown in FIG. 2b in which the choke point 12 is shown as a branch channel with a smaller cross section than the cross section of the bore 11.

(19) A third preferred embodiment is shown in FIG. 3. The bore 11 is again formed in the valve piston 5 and opens into a transverse bore, wherein the bore 11 and the transverse bore have the same cross section. The transverse bore does not open directly into the valve chamber 9 but into a ring gap configured between the valve piston 5 and the valve housing 2 and serving as a guide portion 13. At least in the lower region i.e. in the region between the valve chamber 9 and the bore 11 or the transverse bore, the guide portion 13 therefore has a radial play which leads to the desired choke effect.

(20) FIGS. 4 and 5 show exemplary embodiments similar to that of FIG. 1. Whereas the example in FIG. 4 shows a bore 11 designed as a stepped bore to form the choke point 12, in FIG. 5 an example with a separately formed choke point is shown.

(21) In the exemplary embodiment of FIG. 5, refining measures are shown which can be applied independently of the actual embodiment of the groove 10 and/or bore 11 and choke point 12. To this extent these measures can be implemented alone or cumulatively, also in the embodiments of FIGS. 1 to 4 already described.

(22) A first additional refining measure is shown in FIG. 6. Here the valve housing 2 comprises, in addition to the bore 11, a further axial bore which however is designed as a blind bore and creates an additional hydraulic volume 18 into which the armature chamber 8 expands. The additional hydraulic volume 18 not only promotes the compensation or damping of pressure fluctuations, but also changes the resonant frequency of the pressure control valve in order to counter natural vibrations.

(23) Alternatively or additionally to the refining measures shown in FIG. 6, a bore 11 can be provided in the armature 6, as shown in FIG. 7. The bore 11 can be arranged in the extension of a bore 11 in the valve housing 2 or offset to this. In the latter case, preferably furthermore a groove 10 is provided on the underside of the armature 6 which connects the two bores 11 (see FIG. 1).

(24) It is furthermore advantageous if the connection of the valve chamber 9 to the low-pressure circuit is not made directly via the radial bore 14 but indirectly via the armature chamber 8. In the exemplary embodiment shown in FIG. 8, the valve chamber 9 is connected to the low-pressure circuit via the radial bore 14, the choke point 12, the bore 11 and the armature chamber 8. The significantly extended flow path counters the transmission of pressure fluctuations from the low-pressure circuit. Also the influence of the flow speed of the fuel flowing out via the radial bore 14 is reduced.

(25) A further preferred exemplary embodiment of the invention is shown in FIG. 9, which differs from the preceding example in that the choke point 12 is connected downstream of the bore 11. The bore 11 opens firstly via the choke point 12 into the armature chamber 8, and secondly via the radial bore 14 into the valve chamber 9. Here too, the refining measures shown in connection with FIGS. 6 to 8 can also be implemented.

(26) Finally, FIG. 10 shows a further alternative embodiment. Here the armature 6 is formed as a solenoid plunger and is loaded in the opening direction by the spring force of the spring 19. The valve is therefore designed as a normally open valve. The hydraulic connection of the valve chamber 9 with the armature chamber 8 is in this case created via grooves 10 which are formed running axially in the wall of the bore 1 of the valve housing 2 at equidistant intervals. In a lower region of the bore 1also serving as a guide portion 13the grooves have a reduced cross section so that choke points 12 are formed which connect the grooves 10 to the valve chamber 9. For this exemplary embodiment too, the refining measures shown in FIGS. 6 to 8 can also be implemented.

(27) It is pointed out that with the exception of FIGS. 1 and 10, the drawings are diagrammatic. For example, the valve housing is shown greatly simplified in that for example there is no depiction of the valve seat 4 and/or valve inlet 15, and/or no differentiated depiction of the valve piece 16. Nonetheless these are present. The same applies to the magnetic assembly 7 insofar as not shown or shown greatly simplified.