EP0863308A1 - Pompe à piston pour refoulement des liquides - Google Patents

Pompe à piston pour refoulement des liquides Download PDF

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Publication number
EP0863308A1
EP0863308A1 EP97810125A EP97810125A EP0863308A1 EP 0863308 A1 EP0863308 A1 EP 0863308A1 EP 97810125 A EP97810125 A EP 97810125A EP 97810125 A EP97810125 A EP 97810125A EP 0863308 A1 EP0863308 A1 EP 0863308A1
Authority
EP
European Patent Office
Prior art keywords
piston
recess
liquid
longitudinal axis
work
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.)
Withdrawn
Application number
EP97810125A
Other languages
German (de)
English (en)
Inventor
Klaus Heim
Robert Hofer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wartsila NSD Schweiz AG
Original Assignee
Wartsila NSD Schweiz AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP97810125A priority Critical patent/EP0863308A1/fr
Priority to JP10013679A priority patent/JPH10252602A/ja
Priority to CN98106066A priority patent/CN1116517C/zh
Priority to KR1019980007148A priority patent/KR19980079899A/ko
Publication of EP0863308A1 publication Critical patent/EP0863308A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/243—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movement of cylinders relative to their pistons
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • F02M59/265—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders characterised by the arrangement or form of spill port of spill contour on the piston
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment

Definitions

  • the invention relates to a piston pump device for Pumping liquids, especially fuels and especially heavy oil according to the generic term of Claim 1, and one with such Piston pumping device Reciprocating internal combustion engine according to the preamble of Claim 11.
  • Piston pumping devices generally operate according to the Principle that the working space in the pump housing through the oscillatory, linear movement of a piston periodic volume changes.
  • the following is the movement of the piston, which a reduction in the volume of the work space, called the compression movement and the movement which is an increase in the volume of the work space causes as an expansion movement.
  • piston pumping devices like this to design that the piston at the Expansion movement releases the suction line, so that the Liquid to be pumped penetrate into the work area can.
  • the piston closes the suction line and increases in the Follow the pressure in the liquid that is in the Workspace.
  • the check valve controls the liquid from the work area into the high pressure side pressure line.
  • piston pump devices are, for example, as Injection pumps in injection systems from Reciprocating internal combustion engines, in particular from Diesel engines used. Your job is to get the Press fuel into injection lines, where Injection pressures of up to about 2000 bar can be achieved should.
  • the injection pump pro The amount of fuel delivered is between approx zero and a full load amount can be regulated to each to achieve the desired performance of the machine.
  • a well-known and widely used way of regulating the The amount of fuel delivered is the so-called Bevel control.
  • Bevel control With this is the amplitude of the Stroke movement of the piston is usually constant But piston rotatable about its longitudinal axis.
  • the piston points along its circumference a groove that over a Outflow channel is connected to the work area.
  • the groove is delimited by an edge, which is inclined to Longitudinal axis of the piston and on its outer surface runs. This is the distance between the Work area facing the face of the piston and the The beginning of the groove is not a constant size.
  • piston pump devices are known at which control the amount of liquid delivered by separate upstream of the pumping device Throttling devices.
  • the Pistons usually have a substantially smooth wall designed and the upstream throttling device regulates according to the load in a work cycle in the Amount of liquid flowing into the work area.
  • the dead volume between the throttle device and the working space of the pump device disadvantageous because the liquid in it with each work cycle is put under pressure.
  • Throttling devices for the extraction of heavy oil at least less suitable because heavy oil is chemical is aggressive and very hard deposits, e.g. B. to the Valves of the throttle device, forms what a high Wear or maintenance work results.
  • Special valves for heavy oil have been developed are, however, with a considerable design effort as well as relatively high manufacturing costs.
  • the piston pump device is said to have simple and robust construction and be inexpensive.
  • the piston pump device for solving these tasks Pumping liquids, especially fuels and especially heavy oil is characterized by the characteristics of the characterized independent claim 1.
  • the Piston pumping device according to the invention therefore has a Pump housing, which has a work space as well a movable piston for reduction and Enlargement of the work space.
  • the Piston pumping device according to the invention at least one Inlet opening through which the liquid enters the Work space can be introduced and an outlet opening, through which the liquid from the work space is dissipatable.
  • the inventive Piston pumping device is particularly characterized by this characterized that means to regulate the in the Amount of liquid entering the interior of the pump housing are provided.
  • the Piston pumping device In a preferred embodiment of the Piston pumping device according to the invention are the means to regulate those entering the work area Amount of liquid provided on the piston.
  • the piston can be rotated about its longitudinal axis stored and there is a control device for rotating the Piston provided around its longitudinal axis.
  • the piston is in designed essentially cylindrical and the means to regulate those entering the work area Liquid amount include at least one in the The outer surface of the piston provided recess, which down to the end face facing the work area of the piston extends.
  • the recess geometrically designed so that depending on the Angular position of the piston relative to the pump housing on End of expansion movement - d. H.
  • a symmetrical pressure distribution include the means to regulate the in the work space amount of liquid arriving preferably at least two essentially the same recesses in the lateral surface of the piston provided, preferably diametrically are arranged opposite each other and up to the end face of the piston facing the working space extend.
  • Piston pump device in the interior the pump housing a guide bush for guiding the Piston provided, which at least one Passage opening for the liquid to be pumped having.
  • the position of the guide bush relative to Pump housing can by means of a control device to be changed.
  • the regulation of those entering the work area Liquid amount by turning the guide bush around the longitudinal axis of the piston or by moving the Guide bush in the direction of the longitudinal axis of the piston.
  • These measures change the situation of the Passage opening of the guide bush relative to the Inlet opening of the pump housing.
  • This also changes the cross section of the area through which the Liquid can get into the work area if there is the piston is at its turning point where the volume of the work area is maximum. Because depending on the location of the The guide bush is then a smaller or larger part the inlet opening is closed. That way too the one that gets into the work space Simply regulate the amount of liquid.
  • the piston pump device according to the invention is suitable in particular as an injection pump for an injection system a reciprocating piston internal combustion engine because with it the load-dependent amount of fuel and specifically Heavy oil is easy to regulate. Also leave the high pressures required in diesel engines produce.
  • the improved one is particularly favorable Efficiency of the invention Piston pumping device, which is economical and allows inexpensive operation as well as the waiver external throttle devices suitable for heavy oil Regulate those entering the work area Amount of fuel.
  • the inventive Piston pump device for conveying liquids, especially of fuels and especially heavy oil comprises a pump housing 2 (Fig. 1), which one Has working space 3 and a movable piston 4th to reduce and enlarge the work area 3, at least one inlet opening 21 through which the Liquid can be introduced into the working space 3 and one Outlet opening 22 through which the liquid from the Workspace 3 is removable.
  • a pump housing 2 FIG. 1
  • a movable piston 4th to reduce and enlarge the work area 3
  • one Outlet opening 22 through which the liquid from the Workspace 3 is removable.
  • a heavy oil compatible Piston pump device refers to that as an injection pump for big ones working according to the diesel principle Reciprocating internal combustion engines, e.g. B. marine engines, suitable is. So it becomes related to such applications taken, in which the liquid to be pumped heavy oil is. It is understood that the invention is not based on such applications is limited. That to be funded Medium can also be another fuel or whole generally be a liquid. Furthermore, the Piston pumping devices according to the invention do not Applications in injection systems limited but suitable are also suitable for other areas of application in which a controllable amount of liquid should be promoted.
  • the piston pump device works the well-known principle that the work area 3 in Pump housing 2 through the oscillatory, rectilinear Movement of the piston 4 a periodic change in volume experiences.
  • the movement of the piston 4 which is a reduction in the volume of the work space 3 causes, referred to as compression movement and the Movement, which is an increase in the volume of the Work space 3 causes, as an expansion movement.
  • Farther becomes the turning point at which the piston 4 at maximum volume of the work space 3 is located as designated first reversal point and the one in which the piston 4 with a minimal volume of the working space 3 is the second reversal point.
  • the illustration 1 is the compression movement Upward movement of the piston 4, the expansion movement the downward movement, the first reversal point of the piston 4 the bottom and the second reversal point the top.
  • Fig. 1 are for understanding the invention essential parts of a first embodiment of the Piston pumping device according to the invention, the whole is designated by the reference number 1, schematically in a longitudinal section and partially symbolized.
  • the reference number 1 schematically in a longitudinal section and partially symbolized.
  • Such Details such as sealing oil lines, inlets, outlets, piston springs, seals and Adjustment screws can be made in a manner known per se, such as e.g. B. in commercially available injection pumps, which after Working principle of the inclined edge control, designed and are not explained here.
  • the piston 4 is essentially cylindrical and rotatably supported about its longitudinal axis A.
  • a Control device which comprises a control rod 6, is the Piston 4 rotatable about its longitudinal axis A as this through the indicated by the reference symbol C double arrow is.
  • the control rod 6 is with teeth on its the piston 4 facing side, which engages with a teeth 7 arranged on the jacket of the piston 4 stand.
  • By moving the control rod accordingly 6 in the direction of the double arrow B can thus Piston 4 in both directions C about its longitudinal axis A rotate.
  • Such control devices for rotating the piston 4 are known per se and therefore do not require any further details Explanation.
  • the stroke movement of the piston 4 for Reduction or enlargement of the work space 3 can also take place in a manner known per se.
  • a driven camshaft 10 rotates, causing the Cam 11 a transmission device 12 according to the Representation in Fig. 1 moved up. This moves the piston 4 does not counter the force of one shown piston spring upwards (according to the Representation in Fig. 1) and compresses the work space 3rd After the cam 11, the transmission device 12 happened, the piston 4 moves down, from which an enlargement of the work space 3 results.
  • at least two substantially identical recesses in the outer surface of the piston 4 is provided are preferably arranged diametrically opposite and in each case up to the working room 3 End face 49 of the piston 4 extend.
  • you can more than two such recesses 5 are also provided be, which is preferably evenly distributed in the Shell surface of the piston 4 are arranged. It understands that in cases where several recesses 5 more are arranged in the outer surface of the piston provided as an inlet opening 21 in the pump housing can be. Since it is sufficient for understanding, in the following, only one of the possibly several Recesses 5 considered.
  • the recess 5 serves the controllable in the operating state Introducing heavy oil into the work area 3.
  • the piston roughly at its first reversal point (maximum volume of the work area 3).
  • the Recess 5 a connection between the inlet opening 21 and the work room 3. That for combustion prepared heavy oil passes through a suction line 13, which is connected to the inlet opening 21 for Inlet opening 21, as symbolically represented by the Reference symbol BE provided arrow is indicated, and by there through the recess 5 into the work area 3.
  • the subsequent compression movement closes the Piston the inlet opening 21 and compresses the Workroom 3, which causes the heavy oil in it is put under pressure.
  • the piston pump device takes place the load-dependent regulation of the amount of heavy oil extracted by regulating those entering work area 3 Heavy oil quantity and not, as is the case with known pumps e.g. B. with inclined edge control, is common in which the amount of heavy oil brought in per working cycle is essentially constant and the regulation by high pressure side backflow is realized.
  • Fig. 1 takes place the regulation of those entering the work area 3 Heavy oil quantity by turning the piston 4 around its Longitudinal axis (double arrow C).
  • the recess 5 in the The lateral surface of the piston 4 is geometrically such designed that depending on the angular position of the piston 4 relative to the pump housing 2 more or less welding oil in can get into the work area 3 when the piston 4 located in the area of its first turning point.
  • angular position is the position of the Piston with respect to the rotation about its longitudinal axis A meant, such as in a cylindrical Coordinate system can be described by the azimuth angle would.
  • FIGS. 2a-2d are several variants for the Design of the recess 5 in each case vertical projection onto a first projection plane shown.
  • This first projection plane is parallel to the longitudinal axis A of the piston 4.
  • the projections are with denotes the reference number 51a -51d.
  • this projection representation corresponds to a view the outer surface of the piston 4 from a direction that is perpendicular to the longitudinal axis A of the piston 4.
  • the piston 4 is drawn with its longitudinal axis A; the Pump housing 2 is indicated and the position is indicated by dashed lines the inlet opening 21.
  • FIGS. 2a-2d show the piston 4 approximately at its first reversal point (maximum Volume of the work space 3) as well as in one Angular position that indicates a medium flow rate Corresponds to heavy oil.
  • the projection 51a shown in FIG. 2a extends the recess 5 initially in the form of a groove 511a the end face 49 of the Piston 4 along the lateral surface parallel to Longitudinal axis A and then goes into a substantially V-shaped Part 512a over, with the open side of the V-shaped Part 512a substantially parallel to Longitudinal axis A of the piston 4 lies.
  • the tapered Recess 5 along a circumferential direction of the piston 4, d. H. as shown in Fig. 2a the Recess 5 narrower towards the right.
  • FIGS. 2b-2d show an analogous representation to FIG. 2a the projections 51b-51d for further variants of the Design of the recess 5.
  • the principle Operation is the same as related to Fig. 2a explains so that the related Explanations also for those in FIGS. 2b-2d shown variants in the same way To apply.
  • Fig. 2b shows a variant in which the Projection 51b of the recess 5 is a triangle, the one side lies in the end face 49 of the piston 4. In particular, this triangle is rectangular, with the both cathets are at least so long that the Recess 5, the inlet opening 21 at least for one The angular position of the piston 4 is essentially perfect releases.
  • the Projection 51b of the recess 5 is a triangle, the one side lies in the end face 49 of the piston 4.
  • this triangle is rectangular, with the both cathets are at least so long that the Recess 5, the inlet opening 21 at least for one
  • the angular position of the piston 4 is essentially perfect releases.
  • the projection 51c is also in the recess 5 essentially a triangle, but with one side of the Triangle through the end face 49 of the piston 4 is cut off.
  • the triangle is dimensioned so that the Recess 5, the inlet opening 21 at least for one The angular position of the piston 4 is essentially perfect releases.
  • Fig. 2d is the vertical projection 51d of the recess 5 onto the first Projection plane, which is parallel to the longitudinal axis A of the Piston 4 lies, essentially a square and especially a rectangle, with this quadrilateral as well it is dimensioned that the recess 5 is the inlet opening 21 at least for an angular position of the piston 4 in releases essentially complete.
  • 3a-3d illustrate some examples, such as the recess 5 in radial direction can be configured.
  • the Fig. 3a-3d show vertical projections for different ones Embodiments of the recess 5, but on one second projection plane, which is also parallel to the Longitudinal axis A of the piston 4 is, however, perpendicular stands on the first projection level.
  • this projection representation corresponds to a view the outer surface of the piston 4 from a direction that is perpendicular to the longitudinal axis A of the piston 4.
  • FIG. 2a-2d is the viewing direction 3a-3d by 90 ° around the longitudinal axis A of the piston 4 rotated.
  • Reference numerals 52a-52d designate each the vertical projection onto this second one Projection levels.
  • Fig. 3a-3d each also a part of the piston 4 and its Drawn in longitudinal axis A; is the pump housing 2 indicated and the inlet opening 21 shown.
  • the 3a-3d each show the piston 4 approximately in its first reversal point (maximum volume of the work area 3).
  • the circumferentially V-shaped part 512a - in Fig. 3a drawn in dashed lines - also tapers radially Direction so that it is shown in the illustration according to FIG. 3a appears as a triangle.
  • the groove 511a that the V-shaped Connects part 512a to the end face 49 of the piston 4, is square in this projection 52a.
  • the recess 5 in radial direction can also be designed such that the vertical projection 52b-52d onto the second Projection plane essentially a quadrilateral (projection 52b in Fig. 3b), a triangle (projection 52c in Fig. 3c) or an at least partially curvilinear area (Projection 52d in Fig. 3d), e.g. B. is a segment of a circle.
  • the cross-sectional areas of the recess 5 are with the Reference numerals 53a-53d.
  • the Recess 5 each have a cross-sectional area 53a or 53b perpendicular to the longitudinal axis A of the piston 4, which in is essentially triangular, with one side of the Triangle lies on the outer surface of the piston 4.
  • the the longitudinal axis A of the piston 4 facing side of the The triangle can either be straight, as shown in Fig. 4a, or it can also be curvilinear, such as shown in Fig. 4b. Then at least two sides of the substantially triangular cross-sectional area 53b curvilinear, so that the cross-sectional area 53b the circumference of the piston 4 nestles.
  • a cross-sectional area 53c of the recess 5 perpendicular to the longitudinal axis A of the Piston 4 essentially in the form of a segment of a circle has a boundary line on the lateral surface the piston 4 is.
  • Fig. 4d shows yet another possibility in particular also in connection with that in FIG. 2a projection 51a shown can be combined.
  • the substantially triangular cross-sectional area 53d below the drawing level (shown in dashed lines) and is via a groove with the end face 49 of the piston 4th connected.
  • FIGS. 4a-4d 53a-53d has in common that when the Piston 4 about its longitudinal axis A the radial depth T of Recess in the inlet opening 21 opposite area changes.
  • cross-sectional area shown takes, for example radial depth T of the recess 5 in the direction of the circumference of the piston.
  • the change in the radial depth T has Consequence that depending on the angular position of the piston 4 radially more or less deep part of the recess At least partially releases the inlet opening.
  • this measure namely the change in radial depth T of the recess in the circumferential direction, can be Rotate the piston 4 about its longitudinal axis A in the Working space 3 heavy oil quantity in a simple manner regulate.
  • Figs. 2a-2d, 3a-3d and 4a-4d illustrated corners or edges of the recess 5, such as the tip of the V-shaped part 512a (Fig. 2a) can also be slightly rounded, what especially for manufacturing reasons can be advantageous.
  • the recess 5 are particularly advantageous because they are allow different functional relationships between the rotation of the piston 4, which according to FIG. 1 by the Displacement of the control rod 6 (double arrow B) fixed is, and the one entering the work area 3 Realize heavy oil quantity. So the recess 5 z. B. be designed so that the in the work room 3rd amount of heavy oil arriving is essentially linear with the Shift of the control rod 6 changes. Has the recess 5 for example, such a form that its projections correspond to the representations in FIGS. 2a and 3a and their cross-sectional area of the representation in Fig. 4d, so depends on the quantity change in the work area 3 heavy oil arriving approximately square from the Shift the control rod 6 from.
  • the high efficiency of the is particularly advantageous Piston pumping device according to the invention.
  • Efficiency is the ratio of useful power to performance spent.
  • the Piston pumping device is a high pressure side
  • Backflow of the liquid is not necessary, because always only so much liquid introduced into the work area 3 will, as must really be promoted, d. H. the per work cycle entering the work area 3
  • the amount of liquid is variable or adjustable.
  • the Energy that is used for such processes should be saved, which means that the Increased economy and reduced operating costs will.
  • Piston pumping device Another advantage of the invention Piston pumping device is that the sealing surface between the piston wall and the inlet opening 21 larger is than, for example, in known pumps, which Bevel edge control work. This results in one significantly smaller leak rate, which is the efficiency also positively influenced and an efficient Energy use contributes.
  • the first embodiment of the invention Piston pumping device can also be designed that the recess 5, or if several recesses 5 are provided on the piston 4, at least one of these Recesses with more than one inlet opening 21 in the Pump housing for controlling the in the work space 3 interact with the amount of liquid flowing in.
  • inlet opening 21 in the drawing only has exemplary character and may well be others Have configurations. So it can e.g. B. for Realization of a desired control characteristic be advantageous, the inlet opening 21 and the Inlet openings, for example, slit or oval to design.
  • Embodiment also one Guide bushing between the outer wall of the piston 4 and the pump housing can be provided, which at least one passage opening for the to be funded Has liquid.
  • the regulation of the amount of liquid then takes place in the same manner as in the front described, e.g. B. by the recess 5 a larger or smaller part of the passage opening, if the piston 4 is in the region of its first reversal point located.
  • the essential parts Fig. 5 in a schematic Longitudinal representation shows is in the interior of the Pump housing 2, a guide bushing 8 for guiding the Piston 4 provided which at least one Passage opening 81 for the liquid to be conveyed having.
  • a control device 9 is also provided, to the position of the guide bushing 8 relative to To change pump housing 2.
  • the second Embodiment for the sake of a symmetrical Pressure distribution preferred if at least two Passage openings 81 in the guide bushing 8 are provided that are uniform over the scope of the Guide bushing 8 are distributed.
  • 5 is the drive for the compression or expansion movement of the piston 4 not shown. He can in the same, in itself be realized in a known manner as described above.
  • the piston 4 is designed essentially smooth-walled and not rotatable about its longitudinal axis A.
  • the regulation of amount of liquid entering the work area, by the guide bushing 8 by means of the control device 9 is moved in the direction of the longitudinal axis 4 of the piston, like this one with the reference symbol D. Double arrow indicates.
  • This movement can, for example be realized by means of a transmission linkage.
  • the passage openings 81 a more or less large part of the inlet openings 21 free when the piston 4 is in the area of its first Reversal point is located.
  • 5 shows the piston 4 approximately at its first turning point.
  • the guide bush 8 arrives at a medium amount Liquid into the work area 3.
  • the guide bushing 8 is shown in FIG Fig. 5 moved up, the amount should be reduced the guide bush is moved down.
  • At guide tube 8 has a maximum amount of liquid such a position that the passage openings 81 the Uncover inlet openings 21 essentially completely, if the piston is in the area of its first turning point located. If no liquid is to be pumped, then the guide bushing is lowered so far (according to the Representation in Fig. 5) moves that they Inlet openings essentially complete closes. In this way, too, the amount of amount of liquid entering the work area regulate easily.
  • the guide bushing 8 is not in the direction of Longitudinal axis A of the piston is movable, but around the Longitudinal axis A of the piston 4 is rotatable.
  • the Control device 9 can then in a similar manner be designed as the control device for turning of the piston 4 in the first embodiment.
  • the piston pump device according to the invention is suitable especially as an injection pump for injection systems from Reciprocating internal combustion engines, especially those after work on the diesel principle and heavy oil as fuel use. Such machines find z. B. as Marine engines use.
  • inventive Piston pumping device can be the high pressure side required pressure in the heavy oil, from about 1000-2000 bar create easily. Because of their high efficiency enables the piston pump device according to the invention an efficient use of energy and thus achieves make a significant contribution to an economic and inexpensive operation of the reciprocating piston internal combustion engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
EP97810125A 1997-03-05 1997-03-05 Pompe à piston pour refoulement des liquides Withdrawn EP0863308A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP97810125A EP0863308A1 (fr) 1997-03-05 1997-03-05 Pompe à piston pour refoulement des liquides
JP10013679A JPH10252602A (ja) 1997-03-05 1998-01-27 液体を供給するためのピストン・ポンプ装置及び同ピストン・ポンプ装置を有する内燃式往復ピストン・エンジン
CN98106066A CN1116517C (zh) 1997-03-05 1998-03-02 用于输送液体的活塞泵装置
KR1019980007148A KR19980079899A (ko) 1997-03-05 1998-03-04 유체를 전송하기 위한 피스톤 펌프 장치

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP97810125A EP0863308A1 (fr) 1997-03-05 1997-03-05 Pompe à piston pour refoulement des liquides

Publications (1)

Publication Number Publication Date
EP0863308A1 true EP0863308A1 (fr) 1998-09-09

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EP97810125A Withdrawn EP0863308A1 (fr) 1997-03-05 1997-03-05 Pompe à piston pour refoulement des liquides

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EP (1) EP0863308A1 (fr)
JP (1) JPH10252602A (fr)
KR (1) KR19980079899A (fr)
CN (1) CN1116517C (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1130250A1 (fr) 2000-03-01 2001-09-05 Wärtsilä NSD Schweiz AG Pompe d'injection de carburant haute pression
CN1147406C (zh) * 2000-02-08 2004-04-28 本田技研工业株式会社 车辆用的通信装置

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN202325957U (zh) * 2011-10-20 2012-07-11 重庆红江机械有限责任公司 一种高压高喷射率单体式喷油泵
CN103161725A (zh) * 2011-12-16 2013-06-19 东台兴业股份有限公司 活塞式加压泵

Citations (5)

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Publication number Priority date Publication date Assignee Title
DE564629C (de) * 1931-03-01 1932-11-21 Daimler Benz Akt Ges Brennstoffpumpe
US2044814A (en) * 1934-03-29 1936-06-23 Addison M Rothrock Fuel injection system
DE648653C (de) * 1934-06-13 1937-08-07 Alfred Buri Dr Brennstoffpumpe fuer umsteuerbare Brennkraftmaschinen
DE826802C (de) * 1950-03-11 1952-01-07 Erich Olschewski Einspritzpumpe fuer Dieselkraftstoffe
DE4441113C1 (de) * 1994-11-18 1996-04-04 Bosch Gmbh Robert Kraftstoffhochdruckpumpe für Brennkraftmaschinen

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DE654629C (de) * 1935-10-26 1937-12-27 Schmidt Gerhard R Anordnung an Reklame- und Blickfangvorrichtungen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE564629C (de) * 1931-03-01 1932-11-21 Daimler Benz Akt Ges Brennstoffpumpe
US2044814A (en) * 1934-03-29 1936-06-23 Addison M Rothrock Fuel injection system
DE648653C (de) * 1934-06-13 1937-08-07 Alfred Buri Dr Brennstoffpumpe fuer umsteuerbare Brennkraftmaschinen
DE826802C (de) * 1950-03-11 1952-01-07 Erich Olschewski Einspritzpumpe fuer Dieselkraftstoffe
DE4441113C1 (de) * 1994-11-18 1996-04-04 Bosch Gmbh Robert Kraftstoffhochdruckpumpe für Brennkraftmaschinen

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1147406C (zh) * 2000-02-08 2004-04-28 本田技研工业株式会社 车辆用的通信装置
EP1130250A1 (fr) 2000-03-01 2001-09-05 Wärtsilä NSD Schweiz AG Pompe d'injection de carburant haute pression

Also Published As

Publication number Publication date
CN1116517C (zh) 2003-07-30
KR19980079899A (ko) 1998-11-25
CN1192507A (zh) 1998-09-09
JPH10252602A (ja) 1998-09-22

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