US20060275164A1 - High pressure pump - Google Patents
High pressure pump Download PDFInfo
- Publication number
- US20060275164A1 US20060275164A1 US11/503,118 US50311806A US2006275164A1 US 20060275164 A1 US20060275164 A1 US 20060275164A1 US 50311806 A US50311806 A US 50311806A US 2006275164 A1 US2006275164 A1 US 2006275164A1
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- United States
- Prior art keywords
- piston
- high pressure
- pressure pump
- chamber
- ring
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
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- 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
-
- 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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/04—Draining
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
Definitions
- the invention relates to a high pressure pump, which is suitable in particular for use in a fuel injection system for internal combustion engines.
- the lubrication of the sliding bearing between the sliding shoe and the stroke ring is carried out by the fuel in the relief chamber.
- the bearing between the eccentric journal and the stroke ring is lubricated by the fuel in the low pressure chamber.
- fuel has poor lubricating properties and is therefore able to develop only a restricted lubricating action.
- the present invention is, then, based on the object of providing a high pressure pump of the type mentioned at the beginning for very high delivery pressures and large delivery quantities, whose production costs are as low as possible and which is able to satisfy high requirements on the operational reliability and on the lifetime.
- the relief chamber is divided off from the working chamber by the pressure transmission element arranged in the passage in the piston. Therefore, the medium to be delivered, which is fuel, for example, is also separated from the medium in the relief chamber. There is thus no longer any restriction to using the medium to be delivered for the pressure relief and the lubrication of the sliding bearing between the stroke ring and the piston. Instead, a medium which is much more suitable for these tasks can be chosen, which means one with excellent lubricating properties, for example lubrication oil. With the considerably improved lubrication of the sliding bearing and also the bearing between the stroke ring and the crank drive, the risk of these bearings seizing, even under high loading, is reduced sharply, which in turn contributes to increased operational reliability and a long lifetime.
- the pressure transmission element Since the pressure transmission element is pressurized on one side by the medium to be delivered and can be displaced in the direction of the application of pressure, the pressure in the working chamber is transmitted to the medium in the relief chamber, that is to say, when the pressure in the working chamber rises, the pressure in the relief chamber also rises. Therefore, relief of the load on the sliding bearing between stroke ring and piston is achieved which becomes greater as the delivery pressure becomes greater, as is known from the aforementioned prior art.
- This relief of the load on the sliding bearing not only permits higher delivery pressures but also allows an enlargement of the piston area and therefore an increase in the delivery rate without the number of piston pump units necessarily having to be increased for this purpose. This has a beneficial effect on the production costs.
- FIG. 1 shows a first embodiment of a high pressure pump having two piston pump units, in a longitudinal section
- FIGS. 2 and 3 show one of the two piston pump units with the pump piston in various operating positions, in an illustration corresponding to FIG. 1 and on an enlarged scale,
- FIG. 4 shows a section along the line A-A in FIG. 3 .
- FIG. 5 shows a second embodiment of a high pressure pump in an illustration corresponding to FIG. 2 .
- the high pressure delivery pump 1 shown in FIGS. 1-4 which is intended for use in a fuel injection system for internal combustion engines, has two mutually diametrically opposite piston pump units 2 , 2 ′ (plunger pump units), which are constructionally identical and operate in antiphase.
- Each piston pump unit 2 , 2 ′ has a housing block 3 , which is firmly connected to a pump casing 4 and projects into the interior 5 of this pump casing 4 .
- Each piston pump unit 2 , 2 ′ has a piston 6 (plunger), which is guided such that it can move linearly with a close sliding fit in a cylinder bore 7 in the housing block 3 .
- the piston 6 delimits a working chamber 8 and, at its opposite end, widens to form a base part 9 .
- This base part 9 has a flat sliding surface 10 , which rests on a sliding bearing surface 11 which is provided on a stroke ring 12 .
- This stroke ring 12 is common to both piston pump units 2 , 2 ′.
- a crank drive 13 Provided for the harmonic drive of the pistons 6 of the two piston pump units 2 , 2 ′ is a crank drive 13 , which has a drive shaft 14 , illustrated dashed, and an eccentric element 15 firmly connected to the latter.
- the drive shaft 14 is driven in rotation about its axis of rotation 14 a ( FIG. 1 ).
- the stroke ring 12 is seated rotatably but not so as to corotate on the eccentric element 15 .
- the eccentric element 15 is arranged with an eccentricity e ( FIG. 1 ) with respect to the axis of rotation 14 a of the drive shaft 14 .
- the stroke ring 12 is moved firstly parallel to the sliding bearing surfaces 12 and secondly at right angles to the axis of rotation 14 a of the drive shaft 14 , specifically by the amount 2 e in each direction.
- the stroke ring 12 is thus displaced to and fro with respect to the base part 9 of the piston 6 .
- the pistons 6 of the piston pump units 2 , 2 ′ execute a stroke which is likewise 2 e, that is to say twice the eccentricity e.
- a bearing ring 16 Seated on the base part 9 of the piston 6 is a bearing ring 16 , which is used as an abutment for a compression spring 17 which is supported at the other end on the housing block 3 .
- the compression spring 17 keeps the associated piston 6 in continuous contact with the stroke ring 12 .
- an inlet conduit 18 Formed in the housing block 3 is an inlet conduit 18 , which is connected to the working chamber 8 via a pressure-controlled inlet valve 19 ( FIG. 1 ).
- the inlet conduit 18 is connected to a feed line, not illustrated, which is connected to a liquid reservoir, that is to say in the present case to a fuel tank, for example via a pre-delivery pump.
- a feed line not illustrated
- an outlet conduit 20 In the housing block 3 there is also an outlet conduit 20 , which is connected to the working chamber 8 via a pressure-controlled outlet valve 21 ( FIG. 1 ).
- the outlet conduit 20 is connected to a high pressure chamber, for example the common rail of a fuel injection system.
- a relief chamber 22 Formed in the region of the sliding surface 10 in the base part 9 of the piston 6 is a relief chamber 22 , which is open toward the sliding bearing surface 11 .
- a continuous, coaxial passage 23 which on one side is open toward the working chamber 8 and on the other side is open toward the relief chamber 22 (the passage 23 could also be placed off-axis). Belonging to this passage 23 , whose diameter changes, is a longitudinal bore 24 , in which a control piston 25 , which serves as a pressure transmission element, is displaceably guided with a close sliding fit.
- the control piston 25 rests on a compression spring 26 , which is supported at the other end on a spring ring 27 ( FIG. 2 ), which is retained in the piston 6 .
- annular groove 28 Formed in the housing block 3 is an annular groove 28 , which extends around the piston 6 and is open toward the cylinder bore 7 .
- a transverse bore 29 In the piston 6 there is a transverse bore 29 , which passes through the piston 6 and which is connected to the annular groove 28 at both ends.
- a discharge conduit 30 Connected to the annular groove 28 is a discharge conduit 30 , which extends in the housing block 3 and which is connected to a return line, not shown, which leads to a collecting reservoir, which can be the fuel tank. Seepage, which is fed back via the discharge conduit 30 , collects in the annular groove 28 in a manner still to be described.
- the eccentric element 15 is provided with a lubricating groove 31 , which extends along a part of the circumference and is open toward the stroke ring 12 .
- the lubricating groove 31 is connected via a radial bore 32 in the eccentric element 15 to a feed duct 33 , which extends in the direction of the axis of rotation 14 a of the drive shaft 14 and which is connected to a lubricant reservoir via a lubricant pump, not shown.
- a lubricant preferably lubricating oil, is supplied at a pressure of, for example, 2-6 bar.
- the lubricating groove 31 which is permanently connected to the feed duct 33 , is, however, connected to a connecting duct 34 , 35 only in specific rotational positions of the eccentric element 15 , as can be seen from FIGS. 1-3 .
- FIGS. 1-4 The functioning of the high pressure pump 1 will now be described in more detail by using FIGS. 1-4 .
- FIG. 1 shows that rotational position of the eccentric element 15 in which the piston 6 of the one piston pump unit 2 , the upper one in the figures, is located in the lower end position, that is to say at the end of the suction stroke.
- the piston 6 of the other, lower piston pump unit 2 ′ has reached the end of the delivery stroke and therefore its upper end position.
- the connecting ducts 34 , 35 are connected neither to the lubricating groove 31 nor to the associated relief chamber 22 .
- the delivery stroke begins for the piston 6 of the upper piston pump unit 2 , that is to say the piston 6 will be displaced upward in the direction of the arrow A ( FIG. 2 ).
- the inlet valve 19 is closed, which also applies to the outlet valve 21 at the beginning of the delivery stroke.
- the pressure in the working chamber 8 rises, the control piston 25 , which is pressurized on its end face facing the working chamber 8 by the pressure of the liquid in the working chamber 8 , is moved downward in the direction of the arrow D in FIG. 2 , counter to the action of the compression spring 26 .
- FIG. 2 The situation following a rotation of the drive shaft 14 through 90° is illustrated in FIG. 2 .
- the piston 6 has reached its middle position during the delivery stroke. There is no connection between the lubricating groove 31 and the relief chamber 22 of the upper piston pump unit 2 .
- the relief chamber 22 is connected to the lubricating groove 31 .
- the stroke ring 12 assumes its right-hand end position, which is illustrated dashed in FIG. 4 and is designated 12 ′.
- the delivery stroke of the piston 6 is completed.
- the piston 6 is then moved downward in the opposite direction, that is to say in the direction of the arrow B ( FIG. 3 ), for the suction stroke.
- the outlet valve 21 remains closed.
- a negative pressure is produced in the working chamber 8 , which results in the inlet valve 19 opening and allowing liquid to flow into the working chamber 8 .
- the pressure prevailing in the relief chamber 22 and the region of the passage 23 underneath the control piston 28 together with the compression spring 26 , effects upward displacement of the control piston 25 in the direction of the arrow E ( FIG. 3 ).
- FIG. 3 The situation following the rotation of the drive shaft 14 through a total of now 270° is illustrated in FIG. 3 .
- the piston 6 has reached its middle position during the suction stroke.
- the stroke ring 12 now assumes its left-hand end position, which is illustrated by continuous lines in FIG. 4 .
- This FIG. 4 reveals that the stroke ring 12 executes a total stroke C in the direction of the sliding bearing surface 11 which is equal to 2 e, that is to say twice the eccentricity e.
- the connecting duct 34 in the stroke ring 12 is now connected to the relief chamber 22 and the lubricating groove 31 .
- liquid that is to say fuel
- lubricant that is to say lubricating oil
- liquid fuel
- lubricant lubricating oil
- the mixture of liquid (fuel and lubricant (lubricating oil)) in the annular groove 28 is led away via the discharge conduit 30 and, for example, led back into the liquid reservoir, that is to say the fuel tank.
- annular groove 36 is additionally formed, which is arranged coaxially with respect to the relief chamber 22 and is open toward the sliding bearing surface 11 .
- This annular groove 36 is connected to a longitudinal groove 37 which is formed in the stroke ring 12 and which is open toward the sliding surface 10 .
- This longitudinal groove 37 is offset with respect to the section plane of FIG.
- the second embodiment of a high pressure pump 1 ′ differs from the first embodiment according to FIGS. 1-4 through a different configuration of the pressure transmission element arranged in the piston 6 .
- FIG. 5 which in terms of illustration corresponds to FIG. 2 , the same designations as in FIGS. 1-4 are used for parts which are the same in both embodiments.
- the piston 6 comprises a piston element 38 guided in the cylinder bore 7 and a ring 39 , which is firmly connected to the piston element 38 at the end of the latter facing away from the working chamber 8 , for example by being pressed on or shrunk on.
- the ring 39 rests with a sliding surface 10 on the sliding bearing surface 11 on the stroke ring 12 and has a flange 40 , on which the compression spring 17 is supported. As described by using FIGS. 1-3 , this compression spring 17 ensures that the ring 39 remains in contact with the stroke ring 12 .
- the sliding surface 10 is formed on the ring 39 .
- the flange 40 could also be formed as a separate part, analogous to the bearing ring 16 of FIG. 2 .
- a diaphragm 41 Arranged between the ring 39 and the piston element 38 is a diaphragm 41 which can be deflected elastically and is clamped firmly in a sealing manner along its edge region between the ring 39 and the piston element 38 .
- This diaphragm 41 serving as a pressure transmission element, spans the relief chamber 22 delimited by the inner wall 39 a of the ring and divides this relief chamber 22 from a chamber 42 formed in the piston element 38 .
- Into this chamber 42 there opens a longitudinal bore 43 which extends in the direction of the longitudinal axis of the piston element 38 and via which the chamber 42 is connected to the working chamber 8 .
- the longitudinal bore 43 and the chamber 42 form the passage 23 .
- the chamber 42 is filled with the liquid to be delivered, that is to say with fuel.
- the pressure in the chamber 42 changes in the same direction as the pressure in the working chamber 8 .
- the diaphragm 41 is deflected downward in the direction of the application of pressure, that is to say toward the sliding bearing surface 11 .
- annular groove 28 together with discharge conduit 30 for collecting and leading seepage away present in the first exemplary embodiment according to FIGS. 1-3 , is not shown but can likewise be provided if required.
- the diaphragm 41 is fitted to the end surface 6 a of the piston 6 facing away from the working chamber 8 .
- the diaphragm 41 could be fixed by welding the same on or, in a manner analogous to that in FIG. 5 , could be fixed with a screwed, pressed or shrunk retaining part.
- the passage 23 is then located underneath the diaphragm 41 , it is filled with the lubricant and communicates directly with the relief chamber 22 .
- FIG. 5 The action of the embodiment illustrated in FIG. 5 corresponds to the mode of operation described by using FIGS. 1-4 .
- the exemplary embodiments of a high pressure pump 1 , 1 ′ according to the invention, described in conjunction with FIGS. 1-5 , have the advantage that, as a result of arranging a pressure transmission element, that is to say a control piston 25 or diaphragm 41 , in the passage 23 connecting the working chamber 8 and the relief chamber 22 , the media in the working chamber 8 and in the relief chamber 22 are separated from each other.
- a pressure transmission element that is to say a control piston 25 or diaphragm 41
- the media in the working chamber 8 and in the relief chamber 22 are separated from each other.
- the desired pressure relief of the sliding bearing which is formed by the sliding surface 10 of the piston 6 and the sliding bearing surface 11 on the stroke ring 12 is achieved.
- the piston 6 has no transverse bore 29 . Because of the close sliding fit and the pressure relationships achieved according to the invention on both sides of the control piston 25 , the leakage from the side facing the working chamber 8 into the relief chamber 22 can be kept very low.
- control piston 25 has a larger diameter than illustrated in FIGS. 1-3 .
- the longitudinal bore 24 for guiding the control piston 25 with a close sliding fit can be open at the top in the direction of the working chamber 8 .
- the part of the passage 23 which has a narrower cross section is again located under the control piston 25 and communicates directly with the relief chamber 22 .
- the control piston 25 is installed in the piston 6 from above.
- a spring ring analogous to the spring ring 27 according to FIG. 2 , then prevents the control piston emerging above the end surface 6 a.
- the longitudinal bore 24 can also be continuous in the piston 6 .
- the remaining part of the passage 23 has the same diameter as the longitudinal bore 24 . It is also conceivable to form the remaining section of the passage 23 slightly larger than the diameter of the longitudinal bore 24 .
- FIGS. 3 and 4 annular groove 36 and longitudinal groove 37 . If the flat sliding surface 10 of the base part 9 and the sliding surface 11 of the stroke ring 12 do not rest exactly on each other, for example because of a forced skewed position of the two sliding surfaces 10 and 11 , the lubrication losses are detrimentally affected. Constructional measures for preventing such a state can be: forming the base part 9 with a certain elasticity, such that the sliding surface 10 can adapt to the sliding surface 11 by means of slight elastic deformation of the base part 9 .
- piston pump unit 2 instead of two piston pump units 2 , 2 ′, as shown in FIG. 1 , only one piston pump unit 2 can also be provided. Conversely, more than two piston pump units with corresponding sliding surfaces 11 of the stroke ring 12 can also be fitted radially, for example 3 piston pump units offset by 120°, or 4 offset by 90°, or 6 offset by 60°, with a common stroke ring 12 .
- high-pressure pumps 1 , 1 ′ described are provided for use in fuel injection systems of internal combustion engines, in particular of diesel engines, these pumps can also find applications in other fields.
- control piston 25 is moved solely by the compressive forces acting on the two ends.
- control piston 25 it is also possible to form the control piston 25 with two different diameters. Then, if the end face facing the working chamber 8 is larger than that facing the relief chamber, a step up in pressure takes place; in the opposite case a step down in pressure. In the case of these refinements, it may be advantageous to form the control piston 25 from two separate parts each having the appropriate diameter. If the bore having the correspondingly larger diameter and that having the correspondingly smaller diameter are not aligned exactly, tolerance and friction problems can be prevented in this way.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Reciprocating Pumps (AREA)
- Fuel-Injection Apparatus (AREA)
- Superconductors And Manufacturing Methods Therefor (AREA)
Abstract
A piston (6) of a piston pump unit (2), which can be displaced in a translatory manner, is guided in a cylinder bore (7). The piston (6) is driven by a crank drive (13) comprising an eccentric element (15) which is arranged on a drive shaft (14). A stroke ring (12) is rotationally mounted on the eccentric element (15) but does not rotate therewith. A sliding surface (10) of the piston (6) is arranged on a sliding bearing surface (11) on the stroke ring (12). A discharge chamber (22) is embodied inside the piston (6) on an end opposite the stroke ring (12). Said discharge chamber is open towards the sliding bearing surface (11). The discharge chamber (22) is connected in a pressure-wise manner to a working chamber (8) by means of a passage (23) in the piston (6). A displaceable control piston (25) is guided in a longitudinal bore (24) pertaining to said passage (23). Said control piston (25) is impinged upon on one side by a medium in the working chamber (8) and on the other front side by a pressure medium in the discharge chamber (22). The control piston (25) separates the medium which is to be transported from the pressure medium in the discharge chamber (22) and ensures that the pressure in the discharge chamber (22) increases if the pressure increases in the working chamber (8). This results in decompression of the sliding bearing between the piston (6) and the stroke ring (12).
Description
- This application is a continuation of co-pending application U.S. Ser. No. 10/544,004, the subject matter of which is incorporated herein by reference in its entirety.
- The invention relates to a high pressure pump, which is suitable in particular for use in a fuel injection system for internal combustion engines.
- In DE-A-197 05 205 and the corresponding U.S. Pat. No. 6,077,056, a generic high pressure pump for a fuel injection device for internal combustion engines is described in which the piston of a piston pump unit is driven harmonically by an eccentric drive. At its end facing away from the working chamber of the piston pump unit, the piston bears a sliding shoe which rests with a sliding surface against a sliding bearing surface of a stroke ring. The stroke ring is rotatably mounted on an eccentric journal of a drive shaft and is driven rotatably but does not rotate. The drive shaft, the eccentric journal, the stroke ring and the sliding shoe are all accommodated in a low pressure chamber, which is used as a feed chamber for the medium to be delivered, that is to say fuel. Formed in the sliding shoe is a relief chamber, which is open toward the sliding bearing surface and has a direct hydraulic connection to the working chamber via a passage which extends in the longitudinal direction of the pump piston. The relief chamber is accordingly filled with the fuel to be delivered.
- During the delivery stroke of the piston pump unit, the piston and the sliding shoe fixed to the latter are pressed against the stroke ring by the pressure acting in the working chamber. At the same time, there is also an increase in the pressure in the relief chamber connected to the working chamber, as a result of which the force acting on the sliding shoe and directed away from the stroke ring is increased. Relief of the load on the sliding bearing between the sliding shoe and the stroke ring is therefore achieved. This hydrostatic relief of the load on the sliding bearing leads to a reduction in the friction between the sliding surface on the sliding shoe and the sliding bearing surface on the stroke ring.
- The lubrication of the sliding bearing between the sliding shoe and the stroke ring is carried out by the fuel in the relief chamber. The bearing between the eccentric journal and the stroke ring is lubricated by the fuel in the low pressure chamber. However, as is known, fuel has poor lubricating properties and is therefore able to develop only a restricted lubricating action.
- The present invention is, then, based on the object of providing a high pressure pump of the type mentioned at the beginning for very high delivery pressures and large delivery quantities, whose production costs are as low as possible and which is able to satisfy high requirements on the operational reliability and on the lifetime.
- This object is achieved by a high pressure pump having the features of
claim 1. - The relief chamber is divided off from the working chamber by the pressure transmission element arranged in the passage in the piston. Therefore, the medium to be delivered, which is fuel, for example, is also separated from the medium in the relief chamber. There is thus no longer any restriction to using the medium to be delivered for the pressure relief and the lubrication of the sliding bearing between the stroke ring and the piston. Instead, a medium which is much more suitable for these tasks can be chosen, which means one with excellent lubricating properties, for example lubrication oil. With the considerably improved lubrication of the sliding bearing and also the bearing between the stroke ring and the crank drive, the risk of these bearings seizing, even under high loading, is reduced sharply, which in turn contributes to increased operational reliability and a long lifetime.
- Since the pressure transmission element is pressurized on one side by the medium to be delivered and can be displaced in the direction of the application of pressure, the pressure in the working chamber is transmitted to the medium in the relief chamber, that is to say, when the pressure in the working chamber rises, the pressure in the relief chamber also rises. Therefore, relief of the load on the sliding bearing between stroke ring and piston is achieved which becomes greater as the delivery pressure becomes greater, as is known from the aforementioned prior art. This relief of the load on the sliding bearing not only permits higher delivery pressures but also allows an enlargement of the piston area and therefore an increase in the delivery rate without the number of piston pump units necessarily having to be increased for this purpose. This has a beneficial effect on the production costs.
- Preferred further refinements of the high pressure pump according to the invention form the subject matter of the dependent claims.
- In the following text, by using the drawings, exemplary embodiments of the subject matter of the invention will be explained in more detail. In the drawings, purely schematically:
-
FIG. 1 shows a first embodiment of a high pressure pump having two piston pump units, in a longitudinal section, -
FIGS. 2 and 3 show one of the two piston pump units with the pump piston in various operating positions, in an illustration corresponding toFIG. 1 and on an enlarged scale, -
FIG. 4 shows a section along the line A-A inFIG. 3 , and -
FIG. 5 shows a second embodiment of a high pressure pump in an illustration corresponding toFIG. 2 . - The high
pressure delivery pump 1 shown inFIGS. 1-4 , which is intended for use in a fuel injection system for internal combustion engines, has two mutually diametrically oppositepiston pump units piston pump unit housing block 3, which is firmly connected to a pump casing 4 and projects into theinterior 5 of this pump casing 4. Eachpiston pump unit cylinder bore 7 in thehousing block 3. With oneend face 6a, thepiston 6 delimits aworking chamber 8 and, at its opposite end, widens to form abase part 9. Thisbase part 9 has a flat slidingsurface 10, which rests on a sliding bearingsurface 11 which is provided on astroke ring 12. Thisstroke ring 12 is common to bothpiston pump units pistons 6 of the twopiston pump units crank drive 13, which has adrive shaft 14, illustrated dashed, and aneccentric element 15 firmly connected to the latter. Thedrive shaft 14 is driven in rotation about its axis ofrotation 14 a (FIG. 1 ). Thestroke ring 12 is seated rotatably but not so as to corotate on theeccentric element 15. Theeccentric element 15 is arranged with an eccentricity e (FIG. 1 ) with respect to the axis ofrotation 14 a of thedrive shaft 14. During rotation of thedrive shaft 14, thestroke ring 12 is moved firstly parallel to the sliding bearingsurfaces 12 and secondly at right angles to the axis ofrotation 14 a of thedrive shaft 14, specifically by the amount 2 e in each direction. During operation, thestroke ring 12 is thus displaced to and fro with respect to thebase part 9 of thepiston 6. Thepistons 6 of thepiston pump units - Seated on the
base part 9 of thepiston 6 is abearing ring 16, which is used as an abutment for acompression spring 17 which is supported at the other end on thehousing block 3. Thecompression spring 17 keeps the associatedpiston 6 in continuous contact with thestroke ring 12. - Formed in the
housing block 3 is aninlet conduit 18, which is connected to theworking chamber 8 via a pressure-controlled inlet valve 19 (FIG. 1 ). Theinlet conduit 18 is connected to a feed line, not illustrated, which is connected to a liquid reservoir, that is to say in the present case to a fuel tank, for example via a pre-delivery pump. In thehousing block 3 there is also anoutlet conduit 20, which is connected to theworking chamber 8 via a pressure-controlled outlet valve 21 (FIG. 1 ). Theoutlet conduit 20 is connected to a high pressure chamber, for example the common rail of a fuel injection system. - Formed in the region of the
sliding surface 10 in thebase part 9 of thepiston 6 is arelief chamber 22, which is open toward the sliding bearingsurface 11. - In the longitudinal direction of the
piston 6 there extends a continuous,coaxial passage 23, which on one side is open toward theworking chamber 8 and on the other side is open toward the relief chamber 22 (thepassage 23 could also be placed off-axis). Belonging to thispassage 23, whose diameter changes, is alongitudinal bore 24, in which acontrol piston 25, which serves as a pressure transmission element, is displaceably guided with a close sliding fit. Thecontrol piston 25 rests on acompression spring 26, which is supported at the other end on a spring ring 27 (FIG. 2 ), which is retained in thepiston 6. - Formed in the
housing block 3 is anannular groove 28, which extends around thepiston 6 and is open toward thecylinder bore 7. In thepiston 6 there is atransverse bore 29, which passes through thepiston 6 and which is connected to theannular groove 28 at both ends. Connected to theannular groove 28 is adischarge conduit 30, which extends in thehousing block 3 and which is connected to a return line, not shown, which leads to a collecting reservoir, which can be the fuel tank. Seepage, which is fed back via thedischarge conduit 30, collects in theannular groove 28 in a manner still to be described. - The
eccentric element 15 is provided with alubricating groove 31, which extends along a part of the circumference and is open toward thestroke ring 12. Thelubricating groove 31 is connected via aradial bore 32 in theeccentric element 15 to afeed duct 33, which extends in the direction of the axis ofrotation 14 a of thedrive shaft 14 and which is connected to a lubricant reservoir via a lubricant pump, not shown. Via thisfeed duct 33, a lubricant, preferably lubricating oil, is supplied at a pressure of, for example, 2-6 bar. Formed in thestroke ring 12 are two connectingducts inner surface 12 a of thestroke ring 12 to one of the sliding bearing surfaces 11. The lubricatinggroove 31, which is permanently connected to thefeed duct 33, is, however, connected to a connectingduct eccentric element 15, as can be seen fromFIGS. 1-3 . - The functioning of the
high pressure pump 1 will now be described in more detail by usingFIGS. 1-4 . -
FIG. 1 shows that rotational position of theeccentric element 15 in which thepiston 6 of the onepiston pump unit 2, the upper one in the figures, is located in the lower end position, that is to say at the end of the suction stroke. Thepiston 6 of the other, lowerpiston pump unit 2′ has reached the end of the delivery stroke and therefore its upper end position. The connectingducts groove 31 nor to the associatedrelief chamber 22. - Starting from this initial position, only the operation of the upper
piston pump unit 2 will be described below. The operation of the other, lowerpiston pump unit 2′ is equal but opposite. - If the
drive shaft 14 rotates in the counterclockwise direction, then the delivery stroke begins for thepiston 6 of the upperpiston pump unit 2, that is to say thepiston 6 will be displaced upward in the direction of the arrow A (FIG. 2 ). During this delivery stroke, theinlet valve 19 is closed, which also applies to theoutlet valve 21 at the beginning of the delivery stroke. The pressure in the workingchamber 8 rises, thecontrol piston 25, which is pressurized on its end face facing the workingchamber 8 by the pressure of the liquid in the workingchamber 8, is moved downward in the direction of the arrow D inFIG. 2 , counter to the action of thecompression spring 26. The result of this is that the pressure of the lubricant which is located in therelief chamber 22 and in the region of thepassage 23 underneath thecontrol piston 25 is increased. As a result, a force is exerted on thepiston 6 which is directed away from thestroke ring 12 and which counteracts the force exerted on thepiston 6 by the liquid in the workingchamber 8. In this way, hydrostatic relief of the load on the sliding bearing formed by the slidingsurface 10 on thebase part 9 and the slidingbearing surface 11 on thestroke ring 12 is achieved, as described in DE-A-197 05 205 and U.S. Pat. No. 6,077,056 already mentioned. An optimum relief action is achieved when the diameter DA of therelief chamber 22 is slightly smaller than the diameter DP of theend face 6 a of thepiston 6 which faces the working chamber 8 (seeFIG. 2 ). - The situation following a rotation of the
drive shaft 14 through 90° is illustrated inFIG. 2 . Thepiston 6 has reached its middle position during the delivery stroke. There is no connection between the lubricatinggroove 31 and therelief chamber 22 of the upperpiston pump unit 2. By contrast, in the lowerpiston pump unit 2′, not shown, therelief chamber 22 is connected to the lubricatinggroove 31. After the rotation of thedrive shaft 14 through 90°, illustrated inFIG. 2 , thestroke ring 12 assumes its right-hand end position, which is illustrated dashed inFIG. 4 and is designated 12′. - As soon as the pressure in the working
chamber 8 in the course of the delivery stroke of the piston reaches a value which is greater than the closing force of theoutlet valve 21, the latter is opened and the liquid is expelled from the workingchamber 8 into theoutlet conduit 20 and then into the high pressure chamber. - Following a rotation of the
drive shaft 14 through 180° from the position shown inFIG. 1 , the delivery stroke of thepiston 6 is completed. Thepiston 6 is then moved downward in the opposite direction, that is to say in the direction of the arrow B (FIG. 3 ), for the suction stroke. During this suction stroke, theoutlet valve 21 remains closed. During the downward movement of thepiston 6 in the direction of the arrow B, a negative pressure is produced in the workingchamber 8, which results in theinlet valve 19 opening and allowing liquid to flow into the workingchamber 8. The pressure prevailing in therelief chamber 22 and the region of thepassage 23 underneath thecontrol piston 28, together with thecompression spring 26, effects upward displacement of thecontrol piston 25 in the direction of the arrow E (FIG. 3 ). The situation following the rotation of thedrive shaft 14 through a total of now 270° is illustrated inFIG. 3 . Thepiston 6 has reached its middle position during the suction stroke. Thestroke ring 12 now assumes its left-hand end position, which is illustrated by continuous lines inFIG. 4 . ThisFIG. 4 reveals that thestroke ring 12 executes a total stroke C in the direction of the slidingbearing surface 11 which is equal to 2 e, that is to say twice the eccentricity e. In this left-hand end position of thestroke ring 12, shown inFIGS. 3 and 4 , the connectingduct 34 in thestroke ring 12 is now connected to therelief chamber 22 and the lubricatinggroove 31. This means that pressurized oil can get into therelief chamber 22 via thefeed duct 33, the radial bore 32, the lubricatinggroove 31 and the connectingduct 34. In this way, the lubricant which has been lost during the delivery stroke as a result of leakage along the slidingbearing surface 11 and along the outer surface of thecontrol piston 25 is replaced. - Following a rotation of the
drive shaft 14 through a total of 360°, thepiston 6 is located at the end of the suction stroke and assumes the lower end position illustrated inFIG. 1 again. The operating cycle described starts from the beginning. - Although the
piston 6 is guided in the cylinder bore 7 with a close sliding fit, on the one hand liquid, that is to say fuel, can pass through the gap between thepiston 6 and the wall of the cylinder bore 7 and, on the other hand, lubricant, that is to say lubricating oil, can pass out of theinterior 5 of the pump casing 4. This seepage is collected in theannular groove 28 as a liquid-lubricant mixture, that is to say as a fuel-lubricating oil mixture. - In addition, it is possible that liquid (fuel) can pass out of the working
chamber 8 via the upper section of thepassage 23 and through the very small gap between thecontrol piston 25 and the wall of thelongitudinal bore 24. This seepage likewise passes into theannular groove 28 via the transverse bore 29 in thepiston 6. Furthermore, lubricant (lubricating oil) from therelief chamber 22 can pass through the narrow gap between thecontrol piston 25 and the wall of thelongitudinal bore 24. This leakage-lubricant likewise passes into theannular groove 28 via thetransverse bore 29. - The mixture of liquid (fuel and lubricant (lubricating oil)) in the
annular groove 28 is led away via thedischarge conduit 30 and, for example, led back into the liquid reservoir, that is to say the fuel tank. - In the following text, a variant of the embodiment shown in
FIGS. 1 and 2 will be described in which, in thebase part 9 of thepiston 6, in the region of the slidingsurface 10, anannular groove 36 is additionally formed, which is arranged coaxially with respect to therelief chamber 22 and is open toward the slidingbearing surface 11. Thisannular groove 36 is connected to alongitudinal groove 37 which is formed in thestroke ring 12 and which is open toward the slidingsurface 10. Thislongitudinal groove 37 is offset with respect to the section plane ofFIG. 3 (which extends at right angles to the axis ofrotation 14 a and in the center of the stroke ring 12) in the direction of the axis ofrotation 14 a of thedrive shaft 14 and opens into theinterior 5 of the pump casing 4 at both ends (FIG. 4 ). The seepage (lubricating oil) entering thisannular groove 36 is led back into theinterior 5 via thelongitudinal groove 37. - As a result of the provision of the
annular groove 36, the pressure distribution on the slidingsurface 10 and the slidingbearing 37 in the radial direction toward the outside from therelief chamber 22 is changed, which has a beneficial influence on the amount of the seepage. - The second embodiment of a
high pressure pump 1′, shown inFIG. 5 , differs from the first embodiment according toFIGS. 1-4 through a different configuration of the pressure transmission element arranged in thepiston 6. In thisFIG. 5 , which in terms of illustration corresponds toFIG. 2 , the same designations as inFIGS. 1-4 are used for parts which are the same in both embodiments. - In this second embodiment according to
FIG. 5 , thepiston 6 comprises apiston element 38 guided in the cylinder bore 7 and aring 39, which is firmly connected to thepiston element 38 at the end of the latter facing away from the workingchamber 8, for example by being pressed on or shrunk on. Thering 39 rests with a slidingsurface 10 on the slidingbearing surface 11 on thestroke ring 12 and has aflange 40, on which thecompression spring 17 is supported. As described by usingFIGS. 1-3 , thiscompression spring 17 ensures that thering 39 remains in contact with thestroke ring 12. The slidingsurface 10 is formed on thering 39. Theflange 40 could also be formed as a separate part, analogous to thebearing ring 16 ofFIG. 2 . - Arranged between the
ring 39 and thepiston element 38 is adiaphragm 41 which can be deflected elastically and is clamped firmly in a sealing manner along its edge region between thering 39 and thepiston element 38. Thisdiaphragm 41, serving as a pressure transmission element, spans therelief chamber 22 delimited by theinner wall 39 a of the ring and divides thisrelief chamber 22 from achamber 42 formed in thepiston element 38. Into thischamber 42 there opens alongitudinal bore 43, which extends in the direction of the longitudinal axis of thepiston element 38 and via which thechamber 42 is connected to the workingchamber 8. Thelongitudinal bore 43 and thechamber 42 form thepassage 23. Thechamber 42 is filled with the liquid to be delivered, that is to say with fuel. - The pressure in the
chamber 42 changes in the same direction as the pressure in the workingchamber 8. With increasing pressure in thechamber 42, thediaphragm 41 is deflected downward in the direction of the application of pressure, that is to say toward the slidingbearing surface 11. This leads to an increasing pressure in therelief chamber 22 containing lubricant, and therefore to hydrostatic pressure relief, as has already been described by usingFIGS. 1-4 . Since the pressures on both sides of thediaphragm 41 are virtually identical, the stressing of thediaphragm 41 is low. The latter can therefore be thin-walled and elastic. - In the variant according to
FIG. 5 , theannular groove 28 together withdischarge conduit 30 for collecting and leading seepage away, present in the first exemplary embodiment according toFIGS. 1-3 , is not shown but can likewise be provided if required. - In a further variant, not illustrated, the
diaphragm 41 is fitted to theend surface 6 a of thepiston 6 facing away from the workingchamber 8. Thediaphragm 41 could be fixed by welding the same on or, in a manner analogous to that inFIG. 5 , could be fixed with a screwed, pressed or shrunk retaining part. Thepassage 23 is then located underneath thediaphragm 41, it is filled with the lubricant and communicates directly with therelief chamber 22. - The action of the embodiment illustrated in
FIG. 5 corresponds to the mode of operation described by usingFIGS. 1-4 . - The exemplary embodiments of a
high pressure pump FIGS. 1-5 , have the advantage that, as a result of arranging a pressure transmission element, that is to say acontrol piston 25 ordiaphragm 41, in thepassage 23 connecting the workingchamber 8 and therelief chamber 22, the media in the workingchamber 8 and in therelief chamber 22 are separated from each other. This permits the use of a suitable lubricant in the region of thestroke ring 12 and of thecrank drive 13, irrespective of the medium (fuel) to be delivered. In addition, without great constructional expenditure, the desired pressure relief of the sliding bearing which is formed by the slidingsurface 10 of thepiston 6 and the slidingbearing surface 11 on thestroke ring 12 is achieved. - It goes without saying that various variants of the exemplary embodiments shown are possible. Reference will be made to some of these variants below.
- In a further embodiment, the
piston 6 has notransverse bore 29. Because of the close sliding fit and the pressure relationships achieved according to the invention on both sides of thecontrol piston 25, the leakage from the side facing the workingchamber 8 into therelief chamber 22 can be kept very low. - Under certain circumstances, it is also possible to dispense with measures for collecting and discharging seepage along the outside of the
piston 6, that is to say to dispense with theannular groove 28 and thedischarge conduit 30 in thehousing block 3, if no noticeable leakage occurs as a result of the prevailing pressure conditions. - In a further variant, not illustrated, the
control piston 25 has a larger diameter than illustrated inFIGS. 1-3 . Thelongitudinal bore 24 for guiding thecontrol piston 25 with a close sliding fit can be open at the top in the direction of the workingchamber 8. In this case, the part of thepassage 23 which has a narrower cross section is again located under thecontrol piston 25 and communicates directly with therelief chamber 22. Thecontrol piston 25 is installed in thepiston 6 from above. A spring ring, analogous to thespring ring 27 according toFIG. 2 , then prevents the control piston emerging above theend surface 6 a. Thelongitudinal bore 24 can also be continuous in thepiston 6. In this case, the remaining part of thepassage 23 has the same diameter as thelongitudinal bore 24. It is also conceivable to form the remaining section of thepassage 23 slightly larger than the diameter of thelongitudinal bore 24. - Furthermore, there is also a need to keep the lubrication losses from the
relief chamber 22 into theinterior 5 of the housing low. One means for this purpose is illustrated in the embodiment ofFIGS. 3 and 4 (annular groove 36 and longitudinal groove 37). If the flat slidingsurface 10 of thebase part 9 and the slidingsurface 11 of thestroke ring 12 do not rest exactly on each other, for example because of a forced skewed position of the two slidingsurfaces base part 9 with a certain elasticity, such that the slidingsurface 10 can adapt to the slidingsurface 11 by means of slight elastic deformation of thebase part 9. Division ofbase part 9 andpiston 6 into two parts, in a manner analogous to that in DE-A-197 05 205 and the corresponding U.S. Pat. No. 6,077,056 inFIG. 4 , can also be applied. In addition, theinner surface 12 a of thestroke ring 12, together with the associated surface of theeccentric element 15, could be slightly convex in the direction of the axis ofrotation 14 a or even slightly spherical in the longitudinal and transverse direction. In this case, it is recommended to configure thestroke ring 12 in two parts for installation reasons. - Instead of two
piston pump units FIG. 1 , only onepiston pump unit 2 can also be provided. Conversely, more than two piston pump units with corresponding slidingsurfaces 11 of thestroke ring 12 can also be fitted radially, for example 3 piston pump units offset by 120°, or 4 offset by 90°, or 6 offset by 60°, with acommon stroke ring 12. - In addition, it is also possible to arrange two or more individual piston pump units or two or more pairs of mutually opposite
piston pump units rotation 14 a of thedrive shaft 14. - Although the high-pressure pumps 1, 1′ described are provided for use in fuel injection systems of internal combustion engines, in particular of diesel engines, these pumps can also find applications in other fields.
- It is also possible to dispense with the
compression spring 26 and thespring ring 27 supporting the latter. - In this case, the
control piston 25 is moved solely by the compressive forces acting on the two ends. - Finally, it is also possible to form the
control piston 25 with two different diameters. Then, if the end face facing the workingchamber 8 is larger than that facing the relief chamber, a step up in pressure takes place; in the opposite case a step down in pressure. In the case of these refinements, it may be advantageous to form thecontrol piston 25 from two separate parts each having the appropriate diameter. If the bore having the correspondingly larger diameter and that having the correspondingly smaller diameter are not aligned exactly, tolerance and friction problems can be prevented in this way.
Claims (24)
1. A high pressure pump, in particular for a fuel injection system for internal combustion engines, having at least one piston pump unit (2, 2′) which has a piston (6) guided in a cylinder bore (7) and delimiting a working chamber (8), having a crank drive (13) for driving the piston (6), having a stroke ring (12) which is arranged between the crank drive (13) and the piston (6) and which is mounted such that it is driven rotatably with respect to the crank drive (13) but does not rotate and which has a flat sliding bearing surface (11), on which the piston (6) is supported with a sliding surface (10), wherein a connecting duct (34, 35) is formed in the stroke ring (12), said connecting duct (34, 35) opens at one, first end into the sliding bearing surface (11) and is connected to a fluid source by means of a fluid feed conduit (31, 32, 33) provided in the crank drive (13).
2. The high pressure pump as claimed in claim 1 , wherein the fluid is a lubricant and the fluid feed conduct is a lubricant feed conduct.
3. The high pressure pump as claimed in claim 2 , wherein the crank drive (13) has an eccentric element (15) and wherein the connecting duct (34, 35) opens at the other, second end into the inner surface (12 a) of the stroke ring (12) which is in contact with the eccentric element (15), and wherein a lubricating groove (31) is provided on the circumference of the eccentric element (15), said lubricating groove (31) is open toward the outside and is connected to the lubricant source via a connecting line (32, 33) running in the eccentric element (15) and in the drive shaft (14).
4. The high pressure pump as claimed in claim 3 , wherein the lubricating groove (31) extends over part of the circumference of the eccentric element (15).
5. The high pressure pump as claimed in claim 2 , further comprising a relief chamber (22) which is arranged in the region of the sliding surface (10), is open toward the sliding bearing surface (11) and is fluidically separated from the working chamber (8).
6. The high pressure pump as claimed in claim 5 , wherein an annular groove (36) is formed in the piston (6), said annular groove (36) surrounds the relief chamber (22) and is open toward the sliding bearing surface (11).
7. The high pressure pump as claimed in claim 6 , wherein the annular groove (36) is connected to a chamber (5) in which the crank drive (13) and the stroke ring (12) are accommodated.
8. The high pressure pump as claimed in claim 5 , wherein the opening of the relief chamber (22) is completely surrounded by the sliding surface (10) of the piston, said sliding surface (10) acting together with the sliding bearing surface (11) of the stroke ring (12).
9. The high pressure pump as claimed in claim 7 , wherein a longitudinal groove (37) is formed in the stroke ring (12) in the region of the sliding bearing surface (11), said longitudinal groove (37) is open toward the sliding surface (10) and opens into said chamber (5), is offset with respect to the relief chamber (22) in the direction of the axis of rotation (14 a) of the drive shaft (14) and communicates with the annular groove (36).
10. The high pressure pump as claimed in claim 5 , wherein the pressure medium in the relief chamber (22) is a lubricant, preferably lubricating oil.
11. The high pressure pump as claimed in claim 2 , wherein said connecting duct (34, 35) opens into the sliding bearing surface (11) at a point such that it is connected to the relief chamber (22) only in specific positions of the stroke ring (12) with respect to the piston (6) and is connected periodically to said lubricant feed conduit (31, 32, 33).
12. The high pressure pump as claimed in claim 11 , wherein the lubricating groove (15) is arranged such that it is connected to the connecting duct (34, 35) in the stroke ring (12) when this connecting duct (34, 35) is connected to the relief chamber (22).
13. The high pressure pump as claimed in claim 5 , wherein the relief chamber (22) is fluidically separated from the working chamber (8) by a pressure transmission element (25, 41) arranged in a passage (23) in the piston (6), said pressure transmission element (25, 41) is pressurized on one side by the medium to be delivered and on the opposite side by a pressure medium in the relief chamber (22) and can be displaced in the direction of the application of pressure under the action of pressure.
14. The high pressure pump as claimed in claim 13 , wherein the pressure transmission element is a control piston (25) which can be displaced in a longitudinal bore (24) belonging to said passage (23) and is guided closely in a sliding manner.
15. The high pressure pump as claimed in claim 14 , wherein the control piston (6) on its first end facing the relief chamber (22) is supported on a compression spring (26) which rests on an abutment at the other end.
16. The high pressure pump as claimed in claim 15 , wherein said abutment is formed by a supporting element retained in the control piston (25).
17. The high pressure pump as claimed in claim 16 , wherein said supporting element is a spring ring (27).
18. The high pressure pump as claimed in claim 13 , wherein the pressure transmission element is a diaphragm (41) which can be deflected elastically, covers the passage (23) and is fixed in a sealing manner in its edge region.
19. The high pressure pump as claimed in claim 18 , wherein the piston (6) has a piston element (38) guided in the cylinder bore (7) and a ring (39) which is connected to the piston element (38) at the end of the latter facing away from the working chamber (8).
20. The high pressure pump as claimed in claim 19 , wherein the diaphragm (41) is held firmly in its edge region between the piston element (38) and the ring (39).
21. The high pressure pump as claimed in claim 2 , wherein the crank drive (13) has an eccentric element (15) which is arranged on a rotatably driven drive shaft (14) with an eccentricity (e) and on which the stroke ring (12) is mounted such that it does not rotate with the eccentric element (15).
22. The high pressure pump as claimed in claim 2 , wherein an annular collecting groove (28) is formed in the wall of the cylinder bore (7), said annular collecting groove (28) is open toward the piston (6), is used to collect seepage which passes through the gap between the wall of the cylinder bore (7) and the piston (6) and to which a discharge conduit (30) is connected.
23. The high pressure pump as claimed in claim 2 , wherein the high pressure pump (1, 1′) is designed to deliver fuel.
24. The high pressure pump as claimed in claim 23 , wherein the high pressure pump (1, 1′) is designed to deliver diesel fuel.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US11/503,118 US20060275164A1 (en) | 2003-02-11 | 2006-08-14 | High pressure pump |
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
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CH2022003 | 2003-02-11 | ||
CH202/03 | 2003-02-11 | ||
US10/544,004 US7108491B2 (en) | 2003-02-11 | 2003-12-04 | High pressure pump |
PCT/CH2003/000802 WO2004072477A1 (en) | 2003-02-11 | 2003-12-04 | High pressure pump |
US11/503,118 US20060275164A1 (en) | 2003-02-11 | 2006-08-14 | High pressure pump |
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PCT/CH2003/000802 Continuation WO2004072477A1 (en) | 2003-02-11 | 2003-12-04 | High pressure pump |
US10/544,004 Continuation US7108491B2 (en) | 2003-02-11 | 2003-12-04 | High pressure pump |
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US20060275164A1 true US20060275164A1 (en) | 2006-12-07 |
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ID=32855128
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US11/503,118 Abandoned US20060275164A1 (en) | 2003-02-11 | 2006-08-14 | High pressure pump |
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US10/544,004 Expired - Fee Related US7108491B2 (en) | 2003-02-11 | 2003-12-04 | High pressure pump |
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US (2) | US7108491B2 (en) |
EP (2) | EP1592887B1 (en) |
JP (1) | JP2006514195A (en) |
CN (1) | CN100392241C (en) |
AT (1) | ATE355460T1 (en) |
AU (1) | AU2003281906A1 (en) |
DE (1) | DE50306704D1 (en) |
WO (1) | WO2004072477A1 (en) |
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- 2003-12-04 DE DE50306704T patent/DE50306704D1/en not_active Expired - Lifetime
- 2003-12-04 WO PCT/CH2003/000802 patent/WO2004072477A1/en active IP Right Grant
- 2003-12-04 AU AU2003281906A patent/AU2003281906A1/en not_active Abandoned
- 2003-12-04 AT AT03773421T patent/ATE355460T1/en active
- 2003-12-04 CN CNB2003801096660A patent/CN100392241C/en not_active Expired - Fee Related
- 2003-12-04 JP JP2004568075A patent/JP2006514195A/en not_active Ceased
- 2003-12-04 US US10/544,004 patent/US7108491B2/en not_active Expired - Fee Related
- 2003-12-04 EP EP06026525.3A patent/EP1760312B1/en not_active Expired - Lifetime
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Cited By (11)
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US20090016913A1 (en) * | 2007-07-11 | 2009-01-15 | Gast Manufacturing, Inc., A Division Of Idex Corporation | Balanced dual rocking piston pumps |
US8328538B2 (en) * | 2007-07-11 | 2012-12-11 | Gast Manufacturing, Inc., A Unit Of Idex Corporation | Balanced dual rocking piston pumps |
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US9109558B2 (en) * | 2011-01-24 | 2015-08-18 | Denso Corporation | Fuel pump |
CN103967743A (en) * | 2013-01-29 | 2014-08-06 | 王彦彬 | Magnetic coplanar multi-cylinder multi-level combining compressor |
CN103967745A (en) * | 2013-01-30 | 2014-08-06 | 王彦彬 | Coplanar multi-cylinder multi-stage cam combined compressor |
US11053936B2 (en) | 2015-05-01 | 2021-07-06 | Graco Minnesota Inc. | Two piece pump rod |
WO2018178501A1 (en) * | 2017-03-29 | 2018-10-04 | Wärtsilä Finland Oy | A high pressure fuel pump assembly for an internal combustion piston engine |
CN110691904A (en) * | 2017-03-29 | 2020-01-14 | 瓦锡兰芬兰有限公司 | High-pressure fuel pump assembly for internal combustion piston engine |
Also Published As
Publication number | Publication date |
---|---|
US7108491B2 (en) | 2006-09-19 |
EP1760312B1 (en) | 2013-05-01 |
EP1592887B1 (en) | 2007-02-28 |
ATE355460T1 (en) | 2006-03-15 |
JP2006514195A (en) | 2006-04-27 |
EP1760312A2 (en) | 2007-03-07 |
EP1760312A3 (en) | 2007-09-05 |
US20060062677A1 (en) | 2006-03-23 |
CN100392241C (en) | 2008-06-04 |
AU2003281906A1 (en) | 2004-09-06 |
WO2004072477A1 (en) | 2004-08-26 |
DE50306704D1 (en) | 2007-04-12 |
CN1748083A (en) | 2006-03-15 |
EP1592887A1 (en) | 2005-11-09 |
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