EP1555432B1 - Pompe hydraulique - Google Patents

Pompe hydraulique Download PDF

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Publication number
EP1555432B1
EP1555432B1 EP04250254A EP04250254A EP1555432B1 EP 1555432 B1 EP1555432 B1 EP 1555432B1 EP 04250254 A EP04250254 A EP 04250254A EP 04250254 A EP04250254 A EP 04250254A EP 1555432 B1 EP1555432 B1 EP 1555432B1
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EP
European Patent Office
Prior art keywords
pumping
pump
piston
bore
stroke
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP04250254A
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German (de)
English (en)
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EP1555432A1 (fr
Inventor
Geoffrey David Bootle
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Delphi Technologies Inc
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Delphi Technologies Inc
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Publication date
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Priority to DE602004003894T priority Critical patent/DE602004003894T2/de
Priority to AT04250254T priority patent/ATE349613T1/de
Priority to EP04250254A priority patent/EP1555432B1/fr
Publication of EP1555432A1 publication Critical patent/EP1555432A1/fr
Application granted granted Critical
Publication of EP1555432B1 publication Critical patent/EP1555432B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0443—Draining of the housing; Arrangements for handling leaked fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0408—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0413—Cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0435—Arrangements for disconnecting the pistons from the actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F04B1/0531—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with cam-actuated distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports

Definitions

  • the present invention relates to an hydraulic pump for pressurising liquid and particularly, but not exclusively, to an hydraulic pump for pumping fuel.
  • the pump may find application as a fuel pump in fuel injection systems for supplying high pressure fuel to an internal combustion engine or the like, and may be particularly suitable for use in common rail fuel injection systems.
  • An APVP consists of a plurality of cylinders, usually four, which are equi-angularly spaced around a driving member, such as a crankshaft, which is itself engine-driven. Each cylinder has a piston slidably mounted therein which is connected at one end to a single crankpin by a respective connecting rod. Rotation of the crankshaft causes each of the pistons to reciprocate within their respective cylinders in a phased, cyclical manner.
  • Two axially spaced ports are located in the wall of each cylinder, one representing an inlet port for the supply of low pressure fluid into the cylinder and the other representing a delivery port for the delivery of high pressure fluid from the cylinder.
  • fuel is drawn into an associated pump chamber through the inlet port and then pressurised to a high level for delivery through the delivery port.
  • the ports are alternately opened and closed by the movement of the piston itself.
  • US 300 24 62 discloses another prior art pump comprising inlet and outlet valves.
  • an hydraulic pump comprising a plurality of pumping bores, each pumping bore including an inlet port for the supply of hydraulic fluid into said pumping bore and a delivery port for the delivery of said hydraulic fluid from said pump, a plurality of pump plungers, each pump plunger being reciprocable within a respective one of said pumping bores and comprising a head portion and a skirt portion, wherein each pump plunger defines with said pumping bore a pumping chamber disposed between said head portion of said pump plunger and one end of said pumping bore and a transfer chamber disposed between said head portion and said skirt portion of said pump plunger, communication means connected between the pumping chamber of each pumping bore and the transfer chamber of an adjacent pumping bore and drive means for reciprocably driving each of the pump plungers within said pumping bores such that hydraulic fluid is drawn into said pumping chamber through the inlet port of an adjacent pumping bore and pumped from said pumping chamber through the delivery port of said adjacent pumping bore, characterised in that said drive means includes
  • each pump plunger is connected by a region of reduced diameter.
  • the arrangement may be such that movement of a pump plunger within its pumping bore in a first direction opens the inlet port and closes the delivery port and movement of the pump plunger in a second, opposite direction opens the delivery port and closes the inlet port.
  • a first one of said pump plungers may be arranged to move in the first direction when or during which the inlet port of an adjacent pumping bore is open and in fluid communication with the transfer chamber of the adjacent pumping bore, the arrangement being such that the pumping chamber of the first pump plunger is caused to fill with hydraulic fluid from the inlet port.
  • the first pump plunger may be arranged to move in the second direction when (during which) the delivery port of the adjacent pump plunger is closed and in fluid communication with the transfer chamber of the adjacent pumping bore, the arrangement being such that the hydraulic fluid in the pumping chamber is caused to be pressurised and delivered from the pump through the delivery port.
  • the drive means may comprise cam means having a cam surface arranged to cooperate with each pump plunger thereby to cause the reciprocating movement thereof.
  • the cam means may be arranged to rotate relative to the pumping bores, rotation of the cam means bringing the cam surface into cooperation with the pump plungers so as to generate reciprocal motion thereof in a substantially phased, cyclical manner.
  • the cam surface comprises one or more cam lobes which are arranged to rotate eccentrically relative to the pumping bores.
  • the means for temporarily halting at least one of the pump plungers may comprise at least one dwell region of the cam surface having a different profile from the remainder of the cam surface.
  • the at least one dwell region comprises a region of the cam surface which is arranged to rotate concentrically relative to the pumping bores.
  • the first pump plunger may be arranged to halt at the top of its stroke thereby to permit the delivery port of the adjacent pumping bore to close prior to movement of the first pump plunger in the first direction.
  • the dwell region of the cam surface with the pump plungers may be arranged to cause the first pump plunger to remain substantially stationary within the cylinder for a predetermined angle of rotation of the cam.
  • the cam surface comprises two dwell regions, substantially diametrically opposed on the cam means and wherein a second one of the dwell regions is arranged to cause the first one of the plungers to halt at the bottom of its stroke, thereby to permit the inlet port of the adjacent pumping bore to close prior to movement of the first pump plunger in the second direction.
  • the pump may comprise four pumping bores, equi-angularly spaced around the drive means. Each pump plunger may be arranged to reciprocate at a phase difference of substantially ⁇ 90° with respect to the pump plunger in an adjacent pumping bore.
  • the invention described in the preceding paragraphs may alleviate or remove the problems suffered by prior art hydraulic pumps by causing each piston in turn to halt at the top of its stroke, immediately after pumping fluid from its pumping chamber.
  • This temporary halting of a piston allows both the inlet and the delivery ports in the adjacent pumping bore to be closed simultaneously, thereby reducing leakage of high pressure fluid into the inlet port, without resulting in hydraulic lock.
  • the hydraulic pump 10 comprises an annular housing 12 having a generally cylindrical aperture 14 extending therethrough.
  • Four cylinder arrangements, identified as arrangements A, B, C and D, are disposed within the housing 12 equi-angularly about the cylindrical bore 14. Cylinders that are spaced 90° from one another are referred to as "adjacent cylinders”.
  • Figure 1 The following description of Figure 1 is made mainly with reference to the cylinder arrangement A, the elements of which are each denoted by reference numerals suffixed by the letter "a".
  • the cylinder arrangements B - D are each substantially identical in construction and arrangement to the cylinder arrangement A and will not be described in detail separately. For clarity, however, throughout the specification elements of the cylinder arrangements B - D corresponding to those of the cylinder arrangement A, where described, are identified with the same reference numerals suffixed by the letters "b", "c” or "d”, respectively.
  • the cylinder arrangement consists of a radially directed pumping bore in the form of a cylinder 16a which extends into the aperture 14 such that it is open at one end.
  • the other end of the cylinder 16a is closed.
  • the open end of the cylinder 16a is referred to hereafter as the lower end of the cylinder.
  • the closed end of the cylinder 16a is referred to hereafter as the upper end of the cylinder.
  • a pump plunger in the form of a plunger piston 20a, is located within the cylinder 16a and is arranged for reciprocating movement therein between the upper and lower ends thereof.
  • the piston 20a comprises a head 22a and a skirt 24a, both of which are generally cylindrical and have a diameter which is sized to fit closely within the cylinder 16a.
  • the space within the cylinder 16a between the upper end thereof and the head 22a of the piston 20a defines a pumping chamber 23a, the volume of which varies as the piston 20a reciprocates within the cylinder 16a.
  • the head 22a and skirt 24a of the piston 20a are separated by a region 26a of reduced diameter, hereafter referred to as a stem, which defines with the walls of the cylinder 16a a transfer chamber 28a.
  • the arrangement is such that the volume of the transfer chamber 28a is fixed irrespective of the position of the piston 20a within the cylinder 16a.
  • the position of the transfer chamber 28a within the cylinder 16a will, however, depend on the position of the piston 20a itself.
  • the cylinder 16a communicates with the cylinder 16b by means of a passage 18a extending therebetween.
  • a first end of the passage 18a is in fluid communication with the pumping chamber 23a of the cylinder 16a whilst the opposite end is in fluid communication with its immediately adjacent cylinder (in a clockwise direction in the drawing, hereafter referred to as its "adjacent leading cylinder") at a region intermediate the upper and lower ends thereof.
  • the passage 18a opens into the cylinder 16b at a location which coincides with the transfer chamber 28b, irrespective of the position of the piston 20b.
  • a second passage 18b connects the pumping chamber 23b of the cylinder 16b with the transfer chamber 28c of its adjacent leading cylinder 16c.
  • Two further passages 18c, 18d connect the pumping chambers 23c, 23d of the cylinders 16c and 16d with the transfer chambers 28d, 28a of the cylinders 16d and 16a, respectively.
  • the purpose of the passages 18a - 18d is described below.
  • the cylinder 16a is provided with first and second ports 30a, 32a disposed in the side walls thereof.
  • the ports 30a, 32a are spaced apart and are aligned in an axial direction along the cylinder wall.
  • the spacing of the ports 30a, 32a is such that when the piston 20a is at the upper end of its stroke, the first port 30a is opened into the transfer chamber 28a, thereby communicating with the pump volume 23d of its adjacent lagging cylinder 16d via the transfer chamber 28a and the passage 18d, whilst the second port 32a is closed or sealed by the skirt 24a of the piston 20a.
  • FIG 1 it is actually the cylinder arrangement B which shows the piston 20b in this situation.
  • the first port 30a - 30d of each cylinder arrangement is connected to a low pressure supply (not shown) of hydraulic fluid such as fuel.
  • the second port 32a - 32d of each cylinder arrangement represents a delivery port for the delivery of high pressure fluid, as described below, and may be connected to an accumulator volume (not shown) for storing pressurised fuel, which is itself connected to one or more injectors of a combustion engine.
  • the lower end of the piston skirt 24a is pivotally connected to one end of a connecting rod 34a, the other end of which is rotatably mounted to a crankpin 36 of an associated crankshaft.
  • the arrangement is such that rotation of the crankshaft causes eccentric rotation of the crankpin 36 relative to the cylinder arrangement which, via the connecting rod, in turn causes the reciprocating movement of the piston 20a within the cylinder 16a, as described above.
  • crankshaft and crankpin 36 is driven, for example by means of a combustion engine so that they rotate in the direction shown by the arrow X.
  • the crankpin 36 rotates in an eccentric manner relative to the cylinder arrangements A - D so that each piston 20a - 20d, to which the crankpin is connected via the respective connecting rod 34a - 34d, is caused to reciprocate within its respective cylinder 16a - 16d.
  • the pistons 20a - 20d reciprocate in a cyclical, phased manner whereby each piston is 90° ( ⁇ /2 radians) out of phase with the pistons in adjacent cylinders.
  • the crankpin is positioned at 90° and is rotating anticlockwise resulting in the piston 20b being at the top of its stroke (with the delivery port 30b fully open and the inlet port 32b fully closed) and the piston 20d being at the bottom of its stroke (with the inlet port 32d fully open and the delivery port 30d fully closed).
  • the pistons 20a and 20c are mid-stroke, the piston 20a moving towards the top of its stroke (i.e. towards the innermost position within the cylinder 16a) and the piston 20c towards the bottom of its stroke (i.e.
  • the piston 20a is in the transition period between closing of the inlet port 32a and opening of the delivery port 30a whilst in the case of the cylinder arrangement C, the piston 20c is in the transition period between closing of the delivery port 30c and opening of the inlet port 32c.
  • the downward movement of the piston 20c reduces the pressure within the pumping chamber 23c below that of the low pressure hydraulic fuel supply. Since the inlet port 32d is open and in communication with the pumping chamber 23c via the passage 18c and the transfer chamber 28d, the pumping chamber 23c therefore fills with fuel from the inlet port 32d.
  • This downward movement of a piston between the top of its stroke and the bottom of its stroke, which occurs as the crankshaft rotates through 180° away from the respective cylinder arrangement, is termed the filling stroke.
  • the upward movement of the piston 20a pressurises the fuel within the pumping chamber 23a, the passage 18a and the transfer chamber 28b. Since the delivery port 30b is open and in fluid communication with the pumping chamber 23a via the passage 18a and the transfer chamber 28b, the fuel therein is forced out of the delivery port 30b in the form of a high pressure jet or wave.
  • This upward movement of a piston between the bottom of its stroke and the top of its stroke, which occurs as the crankshaft rotates through 180° towards the respective cylinder arrangement, is termed the pumping stroke.
  • the pumping chamber 23b, the passage 18b and the transfer chamber 28c are, theoretically, substantially empty, the fuel having been delivered through the delivery port 30c (which in Figure 1 is now closed due to the downward movement of the piston 20c through its filling stroke) by the pumping stroke of the piston 20b during the previous 180° of rotation of the crankpin 36.
  • the swept volume of the piston 20b is significantly less than the total combined volume of the pumping chamber 23b, the passage 18b and the transfer chamber 28c, not all of the fluid contained therein prior to the pumping stroke will have been delivered through the delivery port 30c. A certain amount of residual fuel therefore remains in these spaces following completion of the pumping stroke. This residual fuel remains at a high pressure within the pumping chamber 23b, the passage 18b and the transfer chamber 28c until the filling stroke of the piston 20b commences.
  • crankpin 36 Rotation of the crankpin 36 through a further 90° (in an anti-clockwise direction in the drawing) will result in the piston 20a reaching the top of its pumping stroke, the piston 20c reaching the bottom of its filling stroke and the pistons 20b and 20d reaching mid-stroke, the piston 20d on its pumping stroke and the piston 20b on its filling stroke.
  • the pumping chamber 23c, the passage 18c and the transfer chamber 28d contain "static" fuel which is being neither filled nor delivered. Finally, the fuel in the pumping chamber 23d, the passage 18d and the transfer chamber 28a is being delivered, at high pressure, through the delivery port 30a (this latter now being open due to the position of the piston 20a at the top of its stroke) by virtue of the pumping action of the piston 20d.
  • crankshaft causes the substantially continuous, cyclical reciprocation of each of the pistons 20a - 20d, in the manner described above, to generate a substantially continuous high pressure delivery of fuel from the pump.
  • This form of pump is relatively simple to construct and involves few components. Furthermore, the positively driven valve system is not subject to the detrimental effects of inertia and load that can cause conventional free-sprung poppet valves, ball valves or disc valves to suffer low efficiency.
  • a disadvantage of such devices is that, owing to the substantially continuous sinusoidal motion of the pistons 20a - 20d generated by the rotation of the crank 36, there is a period between closing of the delivery port 30a - 30d and opening of the inlet port 32a - 32d on the filling stroke of the piston 20a - 20d in any given cylinder arrangement A - D during which high pressure fuel in the transfer chamber 28 of the piston 20 (being pressurised by the pumping action of the piston in the immediately lagging cylinder) can leak past the piston skirt 24a - 24d and into the inlet port 32a - 32d of the cylinder.
  • This problem is particularly acute where the pressure difference between the delivery port 30a - 30d and the inlet port 32a - 32d is high, such as when the device is used as an hydraulic pump as described above. This represents a considerable reduction in operational efficiency of the pump.
  • the solution to this problem has been to try to minimise any "overlap" of the inlet and delivery ports 32a- 32d, 30a - 30d, that is to say to minimise the amount by which both ports are open simultaneously. This can be achieved by spacing the ports 30a - 30d, 32a - 32d so that the delivery port is closed some time before the inlet port is opened.
  • the pump becomes prone to "hydraulic lock” whereby the simultaneous closure of both inlet and delivery ports of the cylinder arrangement leaves no outlet for the fluid in the pumping chamber 23a - 23d of the immediately lagging cylinder.
  • the incompressibility of the fuel means that the upwardly moving piston in the lagging cylinder is halted, preventing further rotation of the crank 36 and creating a locked state within the pump.
  • FIG. 1 an improved form of hydraulic pump according to one aspect of the invention is shown generally at 100.
  • like reference numerals are used, as far as possible, to indicate like parts.
  • the pump 100 is similar in form to that illustrated in, and described with reference to, Figure 1.
  • the device 100 features an annular housing 12 with a central aperture 14, four radially directed and equi-angularly spaced cylinder arrangements A - D having respective cylinders or pumping bores 16a - 16d within which respective pistons 20a, 20d are disposed and fluid passages 18a - 18d extending between the pumping chamber 23a - 23d of one cylinder 16a - 16d and a midpoint of the immediately leading cylinder.
  • Each cylinder has an inlet port 32a - 32d and a delivery port 30a - 30d disposed in the sidewalls thereof.
  • each cylinder 16a - 16d is again provided with a narrowed region or stem 26a - 26d between head 22a- 22d and skirt 24a - 24d portions thereof, defining with the walls of the cylinder 16a - 16d a transfer chamber 28a - 28d.
  • Drive means in the form of a rotatable member axially disposed within the central aperture 14, rotates to drive the pistons 20a - 20d in a cyclical, phased manner so that the device operates on a similar principle to the prior art pump of Figure 1.
  • the rotatable member takes the form of a shaft 136 having a cam 140 disposed thereon.
  • the cam 140 includes a cam surface 142, the profile of which is more easily seen in Figure 3.
  • the shaft rotates in the direction of arrow X.
  • the cam 140 generally takes the form of an oblate, circular disc mounted to the shaft 136 eccentrically, that is to say at a point offset from its geometrical centre.
  • the cam surface 142 thus consists of two diametrically opposed lobes 144, 146, which are eccentrically located relative to the shaft 136 and which define, respectively, a pumping ramp and a filling ramp. Orthogonally to the lobes 144, 146, the cam surface 142 also defines two diametrically opposed "flats" or “dwell platforms", the purpose of which is described below.
  • the dwell platforms consist of two circular surfaces 148, 150 which are concentric with the shaft.
  • the eccentricity of the lobes 144, 146 means that the radial distance between the cam surface 142 and any given cylinder 16a - 16d varies as the lobe rotates past the bottom end of the cylinder.
  • their concentricity means that the cam surface 142 remains a constant distance from each cylinder as it rotates past the bottom end thereof.
  • each piston 20a - 20d cooperates with the cam surface 142 by means of a respective spherical bearing or roller 152a - 152d located in a recess 154a - 154d in the bottom of the piston 20a - 20d.
  • a respective spherical bearing or roller 152a - 152d located in a recess 154a - 154d in the bottom of the piston 20a - 20d.
  • each piston 20a - 20d may be biased towards the bottom dead centre position by the pressure of the fluid from the inlet port 32.
  • This may require the provision of a feed pump or the like (not shown) for generating a sufficiently high fluid pressure at the inlet port 32.
  • the use of such a feed pump may also reduce the occurrence of cavitation within the cylinder.
  • each cylinder 16a - 16d may be biased towards the bottom dead centre position by means of a resilient member, such as a return spring or the like (not shown), which is connected or otherwise coupled to the piston 20a - 20d.
  • the return spring biases the piston towards the bottom of its stroke thereby maintaining cooperation of the piston 20a - 20d with the filling ramp 146 as the cam 140 rotates.
  • each piston 20a - 20d is subjected to a dwell period in its movement whereby the piston is made to halt at top and bottom dead centres (i.e. at the top and bottom of its stroke) for a predetermined angle of rotation of the cam, defined by the angle subtended by the dwell platform 148, 150.
  • this angle is between 30° and 50°.
  • the pistons in the immediately adjacent cylinders 16b - 16d are moving between top and bottom dead centre positions at their greatest speed within their respective cylinders. Because the pumping piston 20a is halted at the top of its stroke, the swept volume of the piston is substantially zero and it is possible to arrange for the delivery port 30b in the adjacent leading cylinder 16b to close well before the inlet port 32b is opened.
  • the cam 140 is arranged such that the pumping piston 16a is made to halt at the top of its stroke a predetermined time before the delivery port 30b is closed. This is to ensure that 'wire drawing' of the pumped oil does not damage the edges of the delivery port 30b and the transfer chamber 28b.
  • the inlet port 32b is then opened a predetermined time after the delivery port 30b is closed. There is therefore a period, of predetermined duration, during which both the inlet port 32 and the delivery port 30 of the adjacent leading cylinder (in this case the cylinder 16b) are closed simultaneously without the pump 100 suffering hydraulic lock.
  • the cam 140 and the shaft 136 are able to continue to rotate so that the pumping cycle of the pump 100 is substantially uninterrupted.
  • the effect of closing the delivery port 30b well before the opening of the inlet port 32b is a significant reduction, or even substantial elimination, of high pressure fuel leakage into the inlet port 32b.
  • the ports can be spaced further apart than in the case of the prior art device.
  • the length of the stem 26a - 26d of each piston 20a - 20d can be reduced. Either or both arrangements have the effect that the head portion 22a -22d of each piston 20a - 20d fully closes the respective delivery port 30a - 30d before the skirt portion 24a - 24d opens the inlet port 32a - 32d.
  • each piston 20a - 20d is made to halt temporarily at the top and bottom of its stroke, by virtue of the dwell platform 148, 150 provided on the surface 142 of the cam.
  • This temporary halting of each piston 20a - 20d allows the delivery port 30a - 30d in the respective adjacent leading cylinder to be fully closed before the inlet port 32a - 30d is opened, thereby significantly reducing high pressure fuel leakage, without the danger of hydraulic lock occurring.
  • Figures 4a and 4b illustrate, respectively, the instantaneous positions of the pistons 20a - 20d as they are shown in Figure 2 and their positions following a further rotation of the cam 140 through approximately 40°, together with the cooperation of each piston 20a - 20d with the cam surface 142.
  • Figures 4a and 4b illustrate, respectively, the instantaneous positions of the pistons 20a - 20d as they are shown in Figure 2 and their positions following a further rotation of the cam 140 through approximately 40°, together with the cooperation of each piston 20a - 20d with the cam surface 142.
  • Figures 4a and 4b illustrate, respectively, the instantaneous positions of the pistons 20a - 20d as they are shown in Figure 2 and their positions following a further rotation of the cam 140 through approximately 40°, together with the cooperation of each piston 20a - 20d with the cam surface 142.
  • Figures 4a and 4b illustrate, respectively, the instantaneous positions of the pistons 20a - 20d as they are shown in Figure 2 and
  • the piston 20c is cooperating with the filling ramp 146 of the cam surface 142 and is thus moving downward, midway through its filling stroke. At this point in its stroke, the delivery port 30c is still partly open but the inlet port 32c is fully closed.
  • the piston 20d is cooperating with the second dwell platform 150, having completed its filling stroke and is thus halted at the bottom of its stroke with the inlet port 32d fully open and the delivery port 30d fully closed.
  • FIG. 5 illustrates graphically the simultaneous movement of the pistons 20a - 20d in the pump 100.
  • Trace 200a represents the movement of the piston 20a whilst traces 200b, 200c and 200d represent the movement of the pistons 20b, 20c and 20d, respectively.
  • the trace 200a is shown as lagging behind the trace 200b, since for anticlockwise rotation of the pump 100 shown in Figure 2, the piston 20b leads the piston 20a.
  • the trace 200c is shown as lagging the trace 200d since the piston 20d leads the piston 20a.
  • Figure 6 illustrates the opening and closing of the ports 30b, 32b relative to the stroke timing shown in the graph of Figure 5.
  • the delivery port 30b (trace 230b) is opened as the piston 20b (illustrated by the trace 200b in Figure 5) approaches the top of its stroke and shortly before the commencement of the pumping stroke of the piston 20a (illustrated by the trace 200a in Figure 5).
  • the delivery port 30b remains open during the entire pumping stroke of the piston 20a and closes shortly after the piston 20b begins its filling stroke.
  • the inlet port opens as the piston 20b approaches the bottom of its stroke and shortly before the commencement of the filling stroke of the piston 20a.
  • the inlet port 32b remains open during the entire filling stroke of the piston 20a and closes shortly after the piston 20b begins its pumping stroke.
  • Figure 7 illustrates the pumping rate of the device 100 in terms of pumped fluid volume per degree of rotation of the cam 140.
  • the traces 300a - 300d represent the individual pumping rates of the pistons 20a - 20d respectively and show that a positive pumping rate exists for each piston 20a - 20d only during the pumping stroke of that piston, as shown in Figure 5.
  • rotation of the cam 140 between the positions of approximately 120° and 245°, for example shows a positive pumping rate for the piston 20a, corresponding to the pumping stroke of piston 20a shown by the trace 200a in Figure 5.
  • Figure 7 also illustrates the total pumping rate of the device 100 by the bold trace 310.
  • the pumping rate (shown by the trace 300) is generated virtually exclusively by the piston 20a which is midway through its pumping stroke and moving at its greatest speed within the cylinder 16a (trace 200a in Figure 5).
  • the pumping rate is generated by both the piston 20a nearing the end of its pumping stroke and the piston 20d having just commenced its pumping stroke.
  • the trace 310 therefore represents the sum of the instantaneous pumping rates of each piston 20a - 20d and shows that there is a substantially continuous flow of fluid from the pump 100, which varies by only a small percentage in dependence on the positions of the respective pistons 20a - 20d.
  • the cam 140 can be mounted on the shaft 136 or can be integral therewith and may be formed from any suitable material.
  • the engagement of the cam surface 142 with the pistons 20a - 20d need not be achieved through the use of spherical bearings 152 and any suitable means, such as conventional followers or tappets, may be employed.
  • the angle subtended by the dwell platform may be selected as desired but in the preferred embodiment is between 30° and 50° and, more preferably, between 40° and 45°.
  • cam 140 of the form described is not essential.
  • the function of the cam 140, as opposed to the crankshaft 36 of the prior art, is to allow the provision of a dwell period, the forming of which by the appropriate profiling of a cam is relatively straightforward.
  • any other suitable means can be employed to provide this functionality.
  • the present invention provides a simple yet highly effective hydraulic device, which can be used as a pump, a motor or a fluid flow meter, and which is far less susceptible to hydraulic lock than prior art devices.
  • the invention may find particular application as the basis for a Common Rail Pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (14)

  1. Pompe hydraulique (100) comprenant :
    une pluralité d'alésages de pompage (16a à 16d), chaque alésage de pompage (16a à 16d) comprenant un port d'entrée (32a à 32d) pour l'alimentation en fluide hydraulique dudit alésage de pompage (16a à 16d) et un port de sortie (30a à 30d) pour la sortie dudit fluide hydraulique depuis ladite pompe (100) ;
    une pluralité de pistons plongeurs de pompe (20a à 20d), chaque piston plongeur (20a à 20d) se déplaçant en va-et-vient à l'intérieur de l'un respectif desdits alésages de pompage (16a à 16d) et comprenant une partie de tête (22a à 22d) et une partie de base (24a à 24d), dans laquelle chaque piston plongeur (20a à 20d) définit avec ledit alésage de pompage (16a à 16d) une chambre de pompage (23a à 23d) disposée entre ladite partie de tête dudit piston plongeur et une extrémité dudit alésage de pompage et une chambre de transfert disposée entre ladite partie de tête (22a à 22d) et ladite partie de base (24a à 24d) dudit piston plongeur (20a à 20d), dans laquelle le déplacement dudit piston plongeur (20a à 20d) à l'intérieur dudit alésage de pompage (16a à 16d) dans une première direction a pour résultat que ledit piston plongeur ouvre ledit port d'entrée (32a à 32d) et ferme ledit port de sortie (30a à 30d) et le déplacement dudit piston plongeur dans une seconde direction opposée a pour résultat que ledit piston plongeur ouvre ledit port de sortie (30a à 30d) et ferme ledit port d'entrée (32a à 32d) ;
    des moyens de communication connectés entre la chambre de pompage de chaque alésage de pompage et la chambre de transfert d'un alésage de pompage adjacent ; et
    des moyens d'entraînement (140) pour entraîner en va-et-vient chacun des pistons plongeurs (20a à 20d) à l'intérieur desdits alésages de pompage (16a à 16d) de façon que le fluide hydraulique soit tiré dans ladite chambre de pompage par l'intermédiaire du port d'entrée d'un alésage de pompage adjacent et pompé depuis ladite chambre de pompage par l'intermédiaire du port de sortie dudit alésage de pompage adjacent ;
    dans laquelle les moyens d'entraînement (140) comprennent des moyens pour stopper temporairement au moins l'un des pistons plongeurs (20a à 20d) pendant une partie de sa course.
  2. Pompe hydraulique selon la revendication 1, caractérisée en ce que les moyens d'entraînement (140) comprennent des moyens de came ayant une surface de came (142) disposée pour coopérer avec chaque piston plongeur (20a à 20d) afin de provoquer ainsi son déplacement en va-et-vient.
  3. Pompe hydraulique selon la revendication 2, dans laquelle les moyens de came (140) sont disposés pour tourner par rapport auxdits alésages de pompage (16a à 16d), la rotation des moyens de came (140) amenant la surface de came (142) en coopération avec les pistons plongeurs (20a à 20d) de façon à générer leur déplacement en va-et-vient d'une manière cyclique et sensiblement en phase.
  4. Pompe hydraulique selon la revendication 2 ou la revendication 3, dans laquelle la surface de came (142) comprend un ou plusieurs bossages de came (144, 146) qui sont disposés pour tourner de façon excentrique par rapport aux alésages de pompage (16a à 16d).
  5. Pompe hydraulique selon la revendication 4, dans laquelle les moyens permettant de stopper temporairement au moins l'un des pistons plongeurs comprennent au moins une région d'arrêt (148, 150) de la surface de came (142) ayant un profil différent du reste de la surface de came.
  6. Pompe hydraulique selon la revendication 5, dans laquelle la au moins une région d'arrêt (148, 150) comprend une région de la surface de came qui est disposée de façon à tourner de façon excentrique par rapport auxdits alésages de pompage (16a à 16d).
  7. Pompe hydraulique selon la revendication 6, dans laquelle au moins l'un des pistons plongeurs (20a à 20d) est disposé de façon à stopper au sommet de sa course, afin de permettre ainsi au port de sortie (30a à 30d) d'un alésage de pompage adjacent (16a à 16d) de se fermer avant le déplacement dudit piston plongeur (20a à 20d) dans ladite première direction.
  8. Pompe hydraulique selon l'une quelconque des revendications 5 à 7, dans laquelle la au moins une région d'arrêt (148, 150) de la surface de came (142) est disposée de façon à amener un premier desdits pistons plongeurs (20a à 20d) à rester sensiblement fixe à l'intérieur de l'alésage de pompage (16a à 16d) pour un angle de rotation prédéterminé de la came (140).
  9. Pompe hydraulique selon la revendication 7 ou la revendication 8, dans laquelle ladite surface de came (142) comprend deux régions d'arrêt (148, 150), sensiblement diamétralement opposées sur lesdits moyens de came et dans laquelle une deuxième desdites régions d'arrêt est disposée de façon à amener ledit premier desdits pistons plongeurs à stopper au bas de sa course, afin de permettre ainsi au port d'entrée dudit alésage de pompage adjacent de se fermer avant le déplacement du premier piston plongeur dans ladite seconde direction.
  10. Pompe hydraulique selon l'une quelconque des revendications 5 à 9, dans laquelle la ou chaque région d'arrêt (148, 150) sous-tend un angle compris entre 30 ° et 50 °.
  11. Pompe hydraulique selon la revendication 10, dans laquelle la ou chaque région d'arrêt (148, 150) sous-tend un angle d'approximativement 40 °.
  12. Pompe hydraulique selon l'une quelconque des revendications 2 à 11, dans laquelle chacun desdits pistons plongeurs (20a à 20d) coopère avec lesdits moyens de came (140) via un rouleau ou un palier sphérique respectif (152a à 152d).
  13. Pompe hydraulique selon l'une quelconque des revendications précédentes, possédant quatre alésages de pompage (16a à 16d) espacés angulairement de manière égale autour desdits moyens d'entraînement (140).
  14. Pompe hydraulique selon l'une quelconque des revendications précédentes, dans laquelle chaque piston plongeur (20a à 20d) est disposé de façon à se déplacer en va-et-vient à une différence de phase de ± 90 ° par rapport au piston plongeur dans un alésage de pompage adjacent (16a à 16d).
EP04250254A 2004-01-19 2004-01-19 Pompe hydraulique Expired - Lifetime EP1555432B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE602004003894T DE602004003894T2 (de) 2004-01-19 2004-01-19 Hydraulische Pumpe
AT04250254T ATE349613T1 (de) 2004-01-19 2004-01-19 Hydraulische pumpe
EP04250254A EP1555432B1 (fr) 2004-01-19 2004-01-19 Pompe hydraulique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP04250254A EP1555432B1 (fr) 2004-01-19 2004-01-19 Pompe hydraulique

Publications (2)

Publication Number Publication Date
EP1555432A1 EP1555432A1 (fr) 2005-07-20
EP1555432B1 true EP1555432B1 (fr) 2006-12-27

Family

ID=34610225

Family Applications (1)

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EP04250254A Expired - Lifetime EP1555432B1 (fr) 2004-01-19 2004-01-19 Pompe hydraulique

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EP (1) EP1555432B1 (fr)
AT (1) ATE349613T1 (fr)
DE (1) DE602004003894T2 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7435166B2 (ja) * 2020-03-31 2024-02-21 株式会社アドヴィックス 容積式加減圧ポンプ

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB592386A (en) * 1945-05-18 1947-09-16 Tecalemit Ltd Improvements relating to reciprocating pumps, particularly for central lubrication systems
US3002462A (en) * 1957-08-13 1961-10-03 Racine Hydraulics & Machinery Fluid translating apparatus
US3738111A (en) * 1971-11-11 1973-06-12 Deere & Co Variable displacement pump control system
IL128934A (en) * 1999-03-11 2002-11-10 Mapple Technology Ltd Power unit

Also Published As

Publication number Publication date
DE602004003894D1 (de) 2007-02-08
DE602004003894T2 (de) 2007-10-25
ATE349613T1 (de) 2007-01-15
EP1555432A1 (fr) 2005-07-20

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