Fluid conveyance system for a fluid

Abstract

The invention relates to a fluid conveyance system for a fluid, comprising a low-pressure conveyance system having a low-pressure pump (2) and a high-pressure conveyance system having a high-pressure pump (8), which are connected by means of a connecting line, wherein the fluid conveyance system has a pressure damper (19). According to the invention, a fluid conveyance system is provided, by means of which a pulsation of the fluid caused by flow-rate waves or pressure waves in the fluid is damped. This is achieved in that the pressure damper (19) is arranged in the lower-pressure conveyance system and is a hydraulic pressure damper (19). Said hydraulic damper (19) has a piston (21) arranged in a cylinder (20), which piston can be moved against the force of a compression spring (23) and the vapor pressure present in a compression-spring chamber (22) accommodating the compression spring.

Claims

1. A fluid conveyance system for a fluid, comprising a low-pressure conveyance system with a low-pressure pump (2) and a high-pressure conveyance system with a high-pressure pump (8) which are connected via a connecting line, wherein fluid flows in the connecting line in a downstream direction, and wherein the fluid conveyance system has a pressure damper (19), characterized in that the pressure damper (19) is arranged in the low-pressure conveyance system and is a hydraulic pressure damper (19), wherein the hydraulic pressure damper (19) has a piston (21) arranged in a cylinder (20) and subjected to a force of a compression spring (23), wherein the compression spring (23) is arranged in a compression spring chamber (22) and a damper chamber (24) lies opposite the compression spring chamber (22) on an opposite side of the piston, wherein the damper chamber (24) is connected via a damper supply line (25) to the connecting line at a branch point (26), wherein the compression spring chamber (22) is connected by a compression spring chamber line (28) directly or indirectly to the connecting line at a point downstream of the branch point (26), and wherein the compression spring chamber line (28) has at least one of a choke (31) and a check valve (29) closing toward the compression spring chamber (22), such that, upon movement of the piston (21) in a direction of the damper chamber (24), vapor occurs by separation out of the fluid in the compression spring chamber (22) due to expansion in the compression spring chamber (22).

2. The fluid conveyance system as claimed in claim 1, characterized in that the connecting line has a second choke (30) between the damper supply line (25) and the compression spring chamber line (28).

3. The fluid conveyance system as claimed in claim 1, characterized in that the fluid conveyance system is a fuel delivery system and the fluid is fuel.

4. The fluid conveyance system as claimed in claim 1, wherein the at least one of the choke (31) and the check valve (29) closing toward the compression spring chamber (22) includes only the choke (31).

5. The fluid conveyance system as claimed in claim 1, wherein the at least one of the choke (31) and the check valve (29) closing toward the compression spring chamber (22) includes only the check valve (29) closing toward the compression spring chamber (22).

6. The fluid conveyance system as claimed in claim 1, wherein the piston does not include any passages permitting fluid flow between the compression spring chamber (22) and the damper chamber (24).

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The drawings show:

(2) FIG. 1 a system diagram of a fuel delivery system with two optional installation possibilities for a hydraulic pressure damper,

(3) FIG. 2 a first variant of an embodiment of a hydraulic pressure damper, and

(4) FIG. 3 a second variant of an embodiment of a hydraulic pressure damper.

DETAILED DESCRIPTION

(5) FIG. 1 shows a fluid conveyance system formed as a fuel delivery system for a common rail injection system. The fuel delivery system has a low-pressure conveyance system which comprises a low-pressure pump 2 installed in a tank 1, with a prefilter 3 and a check valve 5, a filter 4 and a connecting line in the form of a supply line 6 connecting the above-mentioned components together. Furthermore, the low-pressure conveyance system includes a connecting line in the form of a return line 7 which opens into the tank 1 and which is also connected to fuel injectors (not shown) in order to discharge leakage fuel. Furthermore, the return line 7 is connected to the high-pressure conveyance system, in particular a high-pressure pump 8, in order to discharge fuel not required by the high-pressure pump 8 and fuel which is pumped through the high-pressure pump for lubrication and cooling purposes. The high-pressure pump 8 has a pump housing 9, shown diagrammatically, in which a camshaft chamber 10 is formed. The camshaft chamber 10 is connected to the supply line 6 and has a camshaft 12 which is mounted on bearings 11a, 11b and is configured for example as a double camshaft. At least one high-pressure pump element cooperates with the camshaft 12 and consists substantially of a roller plunger, a pump piston 13 and a pump cylinder formed integrally with a pump cylinder head which is part of or integrated in the pump housing. On a rotary movement of the camshaft 12, the pump piston 13 is moved alternately up and down in the pump cylinder, and via a high-pressure line 15 pumps a fuel introduced into a pump working chamber 14 to a high-pressure accumulator 16, from where the fuel stored under high pressure is extracted by the fuel injectors for injection into assigned combustion chambers of an internal combustion engine.

(6) The fuel fed into the camshaft chamber 10 is introduced, controlled by a metering unit 17, into the pump working chamber 14, while fuel which is not supplied to the pump working chamber 14 by the metering unit 17 or on idling of the internal combustion engine is discharged via a dump valve 18 into the return line 7. The bearings 11a, 11b are also connected to the return line 7, and a constant fuel quantity is conducted from the camshaft chamber 10 through the bearings 11a, 11b in particular for lubrication thereof.

(7) A hydraulic pressure damper 19 is installed in the supply line 6 and/or the return line 7. The pressure damper 19 may be installed directly in the supply line 6 or the return line 7, or also may be integrated in the pump housing 9 of the high-pressure pump 8 in the region of the connection of the supply line 6 or the return line 7. In the context of the invention, it is expressly possible to install an independent hydraulic pressure damper in both the supply line 6 and in the return line 7, or to arrange a hydraulic pressure damper 19 either in the supply line 6 or in the return line 7.

(8) FIG. 2 shows a first exemplary embodiment of such a hydraulic pressure damper 19 which is here connected to a connecting line in the form of the supply line 6 or return line 7. The hydraulic pressure damper 19 has a damper housing in the form of a cylinder 20 in which a piston 21 is installed. The piston is subjected to the force of a compression spring 23 arranged in the compression spring chamber 22, and pressed in the direction of a damper chamber 24 which lies opposite the compression spring chamber 22 and is separated therefrom by the piston 21. The damper chamber 24 is connected via a damper supply line 25 to the connecting line in the form of the supply line 6 or return line 7 at a branch point 26.

(9) The compression spring chamber 22 is limited opposite the piston 21 by a spring holder 27 on which the compression spring 23 rests and which contains a compression spring chamber line 28. The compression spring chamber line 28 consists of various line portions and opens downstream of the branch point 26 into the connecting line again in the form of a supply line 6 or return line 7. A check valve 29 is placed in the compression spring chamber line 28, which blocks the compression spring chamber line 28 in the direction towards the compression spring chamber 22. The check valve 29 opens at a predefined pressure in the compression spring chamber 22, and fluid present in the compression spring chamber 22 is discharged into the connecting line via the continued compression spring chamber line 28. Between the branch point 26 and the opening of the compression spring chamber line 28, a choke 30 is inserted in the connecting line which creates a differential pressure P=P1P2 at the branch point 26 or the opening of the compression spring chamber line 28. The pressure P1 is present in the damper chamber 24 via the damper supply line 25, and in stable state presses the piston 21 against the compression spring 23. In unstable state, periodic bulk waves or pressure waves of fuel which are generated in particular by the high-pressure pump 8, enter the damper chamber 24 via the damper supply line 25 and press the piston 21 in the direction of the damper chamber 24 against the force of the compression spring 23 and the pressure predominating in the damper chamber 24, which in rest state preferably corresponds at least approximately to atmospheric pressure. This state is achieved by the upward movement of the pump piston 13. On the subsequent downward movement of the pump piston 13, because the bulk wave is then no longer present, the piston 21 is moved by the compression spring 23 in the direction of the damper chamber 24 and the fuel compressed in the damper chamber 24 expands, forming or separating out vapor. This vapor, together with the fuel, with the involvement of the compression spring 23, provides the desirable damping behavior of the hydraulic pressure damper.

(10) The exemplary embodiment in FIG. 2 differs from the exemplary embodiment in FIG. 1 only in that instead of the check valve 29, an outflow choke 31 is inserted in the compression spring chamber line 18. The outflow choke 31 or check valve 29 causes the dissipation, continuously or discontinuously respectively, of leakage which has penetrated into the compression spring chamber 22 along the piston 21.