EP2725226A1 - Piston pump - Google Patents
Piston pump Download PDFInfo
- Publication number
- EP2725226A1 EP2725226A1 EP13185479.6A EP13185479A EP2725226A1 EP 2725226 A1 EP2725226 A1 EP 2725226A1 EP 13185479 A EP13185479 A EP 13185479A EP 2725226 A1 EP2725226 A1 EP 2725226A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- pump
- valve
- cylinder
- pump according
- 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.)
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B08—CLEANING
- B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
- B08B3/00—Cleaning by methods involving the use or presence of liquid or steam
- B08B3/02—Cleaning by the force of jets or sprays
- B08B3/026—Cleaning by making use of hand-held spray guns; Fluid preparations therefor
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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
- F04B1/0408—Pistons
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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
- F04B1/0421—Cylinders
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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
- F04B1/0452—Distribution members, e.g. valves
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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
- F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
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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
- 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
- F04B53/10—Valves; Arrangement of valves
- F04B53/12—Valves; Arrangement of valves arranged in or on pistons
- F04B53/125—Reciprocating valves
- F04B53/126—Ball valves
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B08—CLEANING
- B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
- B08B2203/00—Details of cleaning machines or methods involving the use or presence of liquid or steam
- B08B2203/02—Details of machines or methods for cleaning by the force of jets or sprays
- B08B2203/027—Pump details
Definitions
- the present invention relates to a piston pump for high-pressure delivery of a fluid to be conveyed, with a pressure generating device and a control device.
- This piston pump comprises two assemblies in the form of pressure-generating and control components, which are structurally separated from each other. While a first assembly essentially comprises a piston rod with a pump piston, guide bushes, a compression spring with a spring plate and sealing elements, a second assembly unites an inlet and an outlet valve and further electromechanical control elements, in particular for switching on and off an associated drive motor. Both assemblies are interconnected via a compression space and e.g. Positioned at right angles to each other, wherein the drive of the piston rod and associated with this pump piston generally by means of a swash plate, which in turn is rotatably connected to an output shaft of a drive motor.
- a disadvantage of the prior art is that in such a piston pump due to the rectangular arrangement of the two modules to each other a correspondingly large installation space for the piston pump is required.
- An object of the invention is therefore to provide a space-saving, compact and robust piston pump, which can be produced inexpensively and which also ensures high reliability paired with a long service life.
- a piston pump for high pressure delivery of a fluid to be conveyed, with a pressure generating device and a control device, wherein the pressure generating means and the control means are arranged together in a single housing and aligned therein along a common longitudinal axis.
- the invention makes it possible by a linear arrangement of the pressure generating device and the control device compared to a right angle angled arrangement of a conventional piston pump for high-pressure cleaner significantly reduced space requirements. Due to the simple coaxial structure also results in a high reliability, which goes hand in hand with a long service life. With a single embodiment of the piston pump, a whole series of different models in price and flow rates can be realized. In contrast to previously known embodiments, uniformly designed components can be used for different models, which leads to a high cost saving in the production of components, since the components can be manufactured in much higher numbers. In addition, the construction of the invention allows the use of a variety of standardized standard parts, such as bearing balls and cylindrical pins.
- the pressure-generating device has a pump piston that is movable coaxially with respect to the longitudinal axis
- the control device has an inlet valve and outlet valve, which are movable coaxially to the longitudinal axis, for the fluid to be delivered.
- the pump piston is received in a cylinder and fixedly connected to a piston rod, which is received axially displaceably in a guide bush connected to the cylinder and sealed against it by means of at least one sealing ring.
- the piston rod fixedly connected to the pump piston, a particularly simple construction of the pressure-generating device results, wherein the piston rod can preferably be displaced into an oscillating motion by means of a suitable eccentric drive along the longitudinal axis.
- the piston rod is preferably connected by caulking frictionally connected to the pump piston.
- the cylinder preferably has at least one cylinder inlet opening with an approximately elliptical shape and at least one piston inlet opening for the fluid to be delivered is introduced into the pump piston, the at least one piston inlet opening opening into a central channel of the pump piston aligned continuously in the direction of the longitudinal axis.
- the fluid to be delivered passes in a simple manner from the outside through the cylinder wall into the hollow interior of the pump piston.
- the elliptical geometry of the cylinder inlet openings ensures a sufficiently high volume flow and also supports the self-priming of the fluid to be delivered.
- the pump piston and the cylinder form a compression space.
- the pump piston has on a front side a recess for receiving an end face of a valve cage associated with the control device.
- the end face of the valve cage is provided with a circumferential collar and in the end face a blind bore is introduced, wherein in the region of the collar at least one radial recess is introduced, which is in communication with the blind bore.
- the blind bore serves to space-saving guidance of a valve spring of the inlet valve, which has a small depth in order to minimize the dead space volume for penetrating air and at the same time to ensure the highest possible compression.
- valve cage is prestressed by means of a valve cage spring, which is supported between a cylinder cover or a thrust washer lying on the inside thereof and the collar of the valve cage.
- valve cage spring By the valve cage spring a non-positive fit of the valve cage on the pump piston is given.
- substantially (hollow) cylindrical shaft of the valve cage Above the collar, the substantially (hollow) cylindrical shaft of the valve cage has a shoulder for guiding and centering the valve cage spring.
- the central channel of the pump piston merges into a valve seat, in which a ball biased by an inlet valve spring is received as an inlet valve for the fluid to be delivered, the inlet valve spring being clamped between the ball and the blind bore of the valve cage.
- the pump piston has a cylindrical portion, which is followed by a conical portion.
- the conical section decreases by a reduction of the effective sliding area between the pump piston and the cylinder friction losses. Due to its lubricating effect, the fluid to be delivered assists in reducing the friction in the region of the contact surface between the pump piston and the cylinder.
- the pump piston is formed with a high-performance plastic.
- the cylinder cover has a bore, which merges into a valve seat, in which a ball biased with an outlet valve spring is received as an outlet valve for the fluid.
- the exhaust valve also has a simple structural design, since it is also constructed with a small number of items.
- the exhaust valve spring and the ball are received in a bore of a end cap which is connected to the cylinder cover.
- valve outlet spring can be supported in the end cover or in a housing part of the piston pump.
- Fig. 1 shows a piston pump 10 with a pressure generating device 30 and a control device 40 according to one embodiment.
- the piston pump 10 illustratively comprises a preferably made with a thermoplastic and / or thermosetting plastic material of suitable elasticity pump piston 12 which oscillates in a cylinder 14 by means of a piston rod 16 along a longitudinal axis 18, in Fig. 1 illustratively movable up and down.
- the piston rod 16 is received axially displaceably in a substantially hollow cylindrical guide bushing 20 and sealed with respect to this via sealing rings 22,24.
- the piston rod 16 is driven by means of a schematically illustrated eccentric drive 26, whereby the pump piston 12 is displaced along the longitudinal axis 18 in the desired oscillating up and down movement in the cylinder 14.
- a suitable eccentric drive is well known to the person skilled in the art and is not the subject matter of the present invention, so that a detailed description of the eccentric drive 26 is omitted here for the sake of brevity of the description.
- the pump piston 12 and the cylinder 14 define a compression space 28 for a by means of the piston pump 10 to be conveyed fluid, which is indicated here by way of example with arrows 46, and thus form the pressure generating means 30 of the piston pump 10.
- An inlet and an outlet valve 32, 34 together form the control device 40 of the piston pump 10.
- cylinder inlet openings embedded with an illustratively elliptical shape, of which here two visible cylinder inlet openings carry the reference numerals 42,44.
- the elliptical geometry of the preferably three cylinder inlet openings ensures a sufficiently high volume flow and thereby supports the self-suction of the fluid 46 to be delivered.
- the cylinder inlet openings are in a hydraulic connection with preferably three piston inlet openings of the pump piston 12, of which only one piston inlet opening 48 is visible here.
- the piston inlet openings 48 each open into a central channel 50 passing through the pump piston 12.
- the central channel 50 merges into a valve seat 52, in which a ball 56 prestressed by means of an inlet valve spring 54 is accommodated, which together form the inlet valve 32.
- the inlet valve spring 54 is braced, with an end pointing away from the ball 56, in a blind bore 58 of a valve cage 60, which is located between the pump piston 12 and a stop disk 62, which Fig. 1 below - a cylinder cover 64 is positioned is arranged.
- the thrust washer 62 has a bore 68 for the passage of the fluid 46 to be delivered.
- valve cage 60 is biased by means of a valve cage spring 66, whereby the valve cage 60 in each operating state of the piston pump 10 frictionally - Fig. 1 on the upper side - rests on the pump piston 12. Accordingly, the piston rod 16 fixedly connected to the pump piston 12 is brought into contact with the eccentric drive 26 due to the action of the valve cage spring 66.
- the valve cage spring 66 can be directly in Fig. 1 on the underside - on the cylinder cover 64 support, so that the thrust washer 62 may be omitted.
- a bore 70 is further introduced, which merges into a valve seat 72, in which a means of an exhaust valve spring 74 mechanically biased ball 76 is formed to form the exhaust valve 34.
- the cylinder cover 64 is - in Fig. 1 - Connected to the top side with a cover cover 78, wherein in the end cover 78, a through hole 80 is introduced, in which a directed away from the ball 76 end of the Auslrawventilfeder 74 is added to secure the position. Via the outlet valve 32 leaves the fluid to be delivered 46, the piston pump 10 in the direction of arrow 82.
- the inlet valve spring 54, the valve cage spring 66 and the Auslrawventilfeder 74 are preferably formed as cylindrical compression springs and made with a metallic, sufficiently elastic material.
- the valve seat 72 in the exit region of the bore 70 has a chamfer and a radius adapted to the ball 76 in order to ensure a reliable sealing effect.
- the Integration into a housing or a pump housing 84 facilitates, wherein the housing 84 may be formed in one embodiment of the cylinder 14. Due to the small number of components required for this purpose, the piston pump 10 is also inexpensive to produce and achieves a long service life with high reliability and low maintenance.
- a plurality of piston pumps 10 can be combined in a modular unit to form a pump unit in a single housing or multiple housings to realize, for example, high-pressure cleaner with different requirements in terms of flow rate and / or delivery pressure of a fluid to be pumped There are further cost-saving potentials.
- This z. B. two inventively designed piston pumps 10 are positioned diametrically opposite to an eccentric drive. In addition, more than two piston pumps can be driven by means of only one eccentric drive.
- the fluid to be delivered 46 is sucked through the cylinder inlet openings 42,44 and the hydraulically connected piston inlet opening 48 and the other, not visible Kolbeneinlassö réelleen in the central channel 50 and from there into the compression chamber 28 when the piston rod 16 and with her the pump piston 12 in the cylinder 14 in the direction of arrow 86 - Fig. 1 down - moves, since the inlet valve 32 in this flow direction of the fluid - after overcoming the unfolded by the inlet spring 54 spring force - opens.
- the inlet valve 32 closes and the fluid sucked into the compression chamber 28 is compressed by the pump piston 12 until the force of the fluid pressure in the compression chamber 28 begins to overcome the spring force of the outlet valve spring 74 and the outlet valve 34 opens, so that the now high-pressure fluid through the holes 68,70,80 the compression space 28 in the direction of the arrow 82, for example, a direction of a delivery point, such. B. a spray lance of a high-pressure cleaner illustrated, can leave. Due to the periodic up and down movement of the pump piston 12, the above-outlined conveying operation of the piston pump 10 is repeated, so that a pulsating and high-pressure fluid flow leaves the outlet valve 34 in the direction of the arrow 82.
- Fig. 2 to 5 - to which reference is also made to the description of the description at the same time - show a schematic representation of four operating states of the piston pump 10 of Fig. 1 ,
- Fig. 2 shows the pump piston 12 illustratively in a- Fig. 2 bottom dead center position, ie in its lowest position in the compression chamber 28 of the piston pump 10.
- the inlet valve 32 and the outlet valve 34 of the piston pump 10 are closed because the inlet valve spring 54 and the Auslrawventilfeder 74 a sufficiently high spring force on the balls 56 and 76 exercise.
- the inlet valve spring 54 is of particular importance here. In addition to the guiding function of the ball 56 of the inlet valve 32, its main task is to rapidly close the inlet valve 32 as soon as a corresponding suction phase of the fluid 46 to be delivered has ended.
- the spring core line of the inlet valve spring 54 determines the opening pressure of the inlet valve 32. This opening pressure should be in a range between 0.1-0.25 bar, so that it is ensured that any remaining air can be sucked with. By carefully adjusting the spring force of the inlet valve spring 54, a volumetric efficiency of 85-90% is achieved.
- Fig. 3 1 illustrates a corresponding intake phase in which the fluid 46 to be delivered by means of the piston pump 10 is sucked into the compression chamber 28 via the cylinder inlet opening 44 and the piston inlet opening 48 as well as all other cylinder and piston inlet openings not visible here.
- Fig. 4 shows the pump piston 12, starting from its in Fig. 3 shown position further moved - in Fig. 3 and 4 upwards - towards an in Fig. 5 shown, top dead center position.
- the pressure in the compression chamber 28 increases sharply, since the inlet valve 32 and the outlet valve 34 of the piston pump 10 are closed.
- the outlet valve 34 opens only when the pressure of the fluid to be delivered 46 in the compression chamber 28 has risen so far that the resulting force causes the Auslrawventilfeder 74 compress and lift the ball 76 in the exhaust valve 34 from its valve seat and the promotional and under high pressure Standing fluid can escape via the outlet valve 34 and can be brought via a suitable line to a pickup point.
- Fig. 5 shows by way of example a - in Fig. 5 top - Tot Vietnamese sacred center of the pump piston 12.
- the exhaust valve 34 closes again, with a residual amount of the fluid to be delivered 46 remains in the compression chamber 28.
- a depth of the blind bore 58 in the valve cage 60 is dimensioned so small that the inlet valve spring 54 occupies most of the volume of the blind bore 58.
- the so-called dead volume in the compression chamber 28 is reduced to a minimum and the compressibility of the piston pump 10 is increased overall.
- the pressure then dropping in the compression chamber 28 causes the inlet valve 32 to open so that fluid to be conveyed can flow into the compression chamber 28 and thus the entire conveying process is repeated periodically, as described above.
- Fig. 6 shows the pump piston 12 of the pressure generating device 30 of the piston pump of Fig. 1
- This exemplified pump piston 12 constructed symmetrically to the longitudinal axis 18 illustratively has a cylindrical portion 90, to which a conical portion 92 connects.
- the conical section 92 serves for mechanical connection of the piston rod (16 of Fig. 1 ) and also reduces the friction between the pump piston 12 and the cylinder (14 of Fig. 1 ), since the contact surface between the cylinder (14 of Fig. 1 ) and the conical section 92 is negligibly small.
- a sealing portion 94 of the portion 90 is used primarily for sealing the pump piston 12 relative to the cylinder (14 of Fig. 1 ).
- the pump piston 12 is preferably formed with an optionally fiber-reinforced high performance plastic, which has a high wear resistance, a high dimensional stability and a substantial insensitivity to aggressive chemical media. Due to the inherent elasticity of the plastic material, the pump piston 12 can preferably with slight press-fit into the cylinder (14 of Fig. 1 ) of the piston pump (10 of Fig. 1 ) are used, so that no further sealing elements, such as. As piston rings or the like, are necessary.
- At least one and illustratively three, for example, at least substantially elliptical piston inlet openings are introduced into the pump piston 12, of which only the piston inlet opening 48 is visible here.
- the piston inlet openings are preferably uniformly spaced and distributed around the circumference of the pump piston 12 in this introduced.
- the elliptical piston inlet openings whose main axes extend in the direction of the longitudinal axis 18, serve for the flow-optimized supply of the fluid to be delivered (46 of FIG Fig. 1 ), wherein the elliptical shape, a high flow rate is achieved and at the same time the ability of the piston pump (10 of Fig. 1 ) is supported for self-priming.
- the preferred three piston inlet openings are hydraulically connected to a central channel 50, which is formed symmetrically to the longitudinal axis 18 in the pump piston 12.
- Fig. 7 shows the pump piston 12 of Fig. 6 with the cylindrical portion 90, which in the conical portion 92 for connecting the piston rod (16 of Fig. 1 ) passes over.
- the sealing portion 94 as a portion of the cylindrical Section 90, the necessary hermetic seal between the pump piston 12 and the cylinder (14 of Fig.1 ).
- a cup-shaped recess 98 is inserted, which is for receiving the valve cage (60 of FIG Fig.1 ) of the inlet valve (32 of Fig. 1 ) serves.
- the piston inlet opening 48 and a further piston inlet opening 100 and a further - not visible piston inlet opening - each extend at an angle ⁇ of example about 70 ° obliquely upward in the direction of this recess 98.
- the three piston inlet openings are each spaced by 120 ° to each other arranged distributed around the circumference of the pump piston 12 away.
- the center channel 50 formed centrally with respect to the longitudinal axis 18 opens into a valve seat 106 in which the ball 56 is accommodated.
- the valve seat 106 comprises a radius 108, to which, for example, a 45 ° chamfer 110 connects.
- the radius 108 is adapted to the radius of the ball 56 and ensures in cooperation with the chamfer 110 a reliable sealing effect of the ball 56 in the valve seat 106.
- valve seat 106 forms in cooperation with the spring-loaded ball 56 and the valve cage (60 of Fig. 1 ) the inlet valve (32 of Fig. 1 ) as part of the control device (40 of Fig. 1 ) of the piston pump (10 of Fig. 1 ).
- the sealing portion 94 of the cylindrical portion 90 is preferably also conical, ie, a wall thickness 112 of the sealing portion 94 decreases starting from a bottom 114 of the recess 98 up to the end face 96th
- Fig. 8 shows the valve cage 60 of Fig. 1 by way of example having a substantially cylindrical shape with an approximately cylindrical shank 120 and a radially outward-facing in the region of an end face 122, flange-like collar 124 has. Due to the force effect of the Ventilkafigfe- 66 this collar 124 is in each operating state of the piston pump (10 of Fig. 1 ) firmly on the pump piston (12 of Fig. 1 ) at. In addition, in the region of the end face 122, the blind bore 58 is inserted centrally into the valve cage 60 relative to the longitudinal axis 18.
- the blind bore 58 has a rear abutment shoulder 126 for the intake valve spring (54 of FIG Fig.1 ).
- two and illustratively four recesses - of which only the rear two recesses 128,130 are visible here - are preferably introduced into the valve cage 60.
- the recesses are preferably arranged uniformly over the circumference of the valve cage 60 in a 90 ° pitch and give the geometric cage shape.
- the blind bore 58 is interrupted by the recesses, so that the fluid to be delivered (46 of Fig. 1 ) unhindered and with a low flow resistance in the compression space (28 of Fig. 1 ) can get.
- a depth 132 of the blind bore 58 is dimensioned as small as possible.
- the dead space volume for penetrating air is as small as possible, at the same time a high compression of the piston pump (10 of Fig. 1 ) is achieved.
- a small shoulder 134 is formed, which serves to center the valve cage spring 66 along the longitudinal axis 18.
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Abstract
Description
Die vorliegende Erfindung betrifft eine Kolbenpumpe zur Hochdruckförderung eines zu fördernden Fluids, mit einer Druckerzeugungseinrichtung und einer Steuereinrichtung.The present invention relates to a piston pump for high-pressure delivery of a fluid to be conveyed, with a pressure generating device and a control device.
Aus dem Stand der Technik ist eine derartige Kolbenpumpe bekannt, die z.B. in einem Hochdruckreiniger Anwendung findet. Diese Kolbenpumpe umfasst zwei Baugruppen in der Form von druckerzeugenden und steuernden Komponenten, die baulich voneinander getrennt angeordnet sind. Während eine erste Baugruppe im Wesentlichen eine Kolbenstange mit einem Pumpenkolben, Führungsbuchsen, eine Druckfeder mit einem Federteller und Dichtungselemente beinhaltet, vereinigt eine zweite Baugruppe ein Einlass- und ein Auslassventil sowie weitere elektromechanische Steuerungselemente, insbesondere zur An- und Abschaltung eines zugeordneten Antriebsmotors. Beide Baugruppen sind über einen Kompressionsraum miteinander verbunden und z.B. rechtwinklig zueinander positioniert, wobei der Antrieb der Kolbenstange und des mit dieser verbundenen Pumpenkolbens im Allgemeinen mittels einer Taumelscheibe erfolgt, die wiederum mit einer Abtriebsachse eines Antriebsmotors drehfest verbunden ist.From the prior art, such a piston pump is known, e.g. in a high pressure cleaner application finds. This piston pump comprises two assemblies in the form of pressure-generating and control components, which are structurally separated from each other. While a first assembly essentially comprises a piston rod with a pump piston, guide bushes, a compression spring with a spring plate and sealing elements, a second assembly unites an inlet and an outlet valve and further electromechanical control elements, in particular for switching on and off an associated drive motor. Both assemblies are interconnected via a compression space and e.g. Positioned at right angles to each other, wherein the drive of the piston rod and associated with this pump piston generally by means of a swash plate, which in turn is rotatably connected to an output shaft of a drive motor.
Nachteilig am Stand der Technik ist, dass bei einer derartigen Kolbenpumpe infolge der rechtwinkligen Anordnung der beiden Baugruppen zueinander ein entsprechend großer Einbauraum für die Kolbenpumpe erforderlich ist.A disadvantage of the prior art is that in such a piston pump due to the rectangular arrangement of the two modules to each other a correspondingly large installation space for the piston pump is required.
Eine Aufgabe der Erfindung ist es daher, eine platzsparende, kompakte und robuste Kolbenpumpe bereitzustellen, die sich kostengünstig herstellen lässt und die zudem eine hohe Zuverlässigkeit gepaart mit einer langen Lebensdauer gewährleistet.An object of the invention is therefore to provide a space-saving, compact and robust piston pump, which can be produced inexpensively and which also ensures high reliability paired with a long service life.
Dieses Problem wird gelöst durch eine Kolbenpumpe zur Hochdruckförderung eines zu fördernden Fluids, mit einer Druckerzeugungseinrichtung und einer Steuereinrichtung, wobei die Druckerzeugungseinrichtung und die Steuereinrichtung zusammen in einem einzelnen Gehäuse angeordnet sind und darin entlang einer gemeinsamen Längsachse ausgerichtet sind.This problem is solved by a piston pump for high pressure delivery of a fluid to be conveyed, with a pressure generating device and a control device, wherein the pressure generating means and the control means are arranged together in a single housing and aligned therein along a common longitudinal axis.
Die Erfindung ermöglicht hierbei durch eine lineare Anordnung der Druckerzeugungseinrichtung und der Steuereinrichtung im Vergleich zu einer rechtwinklig abgewinkelten Anordnung einer hergebrachten Kolbenpumpe für Hochdruckreiniger einen deutlich reduzierten Platzbedarf. Infolge des einfachen koaxialen Aufbaus ergibt sich ferner eine hohe Zuverlässigkeit, die mit einer langen Einsatzdauer einhergeht. Mit einer einzigen Ausführungsform der Kolbenpumpe lässt sich eine ganze Baureihe unterschiedlicher Modelle in Preis und Förderleistungen realisieren. Im Gegensatz zu vorbekannten Ausführungsformen können für verschiedene Modelle einheitlich gestaltete Bauteile Anwendung finden, was zu einer hohen Kosteneinsparung bei der Bauteilfertigung führt, da die Bauteile in wesentlich höheren Stückzahlen gefertigt werden können. Darüber hinaus gestattet die erfindungsgemäße Konstruktion die Verwendung einer Vielzahl von standardisierten Normteilen, wie zum Beispiel Wälzlagerkugeln und Zylinderstiften.The invention makes it possible by a linear arrangement of the pressure generating device and the control device compared to a right angle angled arrangement of a conventional piston pump for high-pressure cleaner significantly reduced space requirements. Due to the simple coaxial structure also results in a high reliability, which goes hand in hand with a long service life. With a single embodiment of the piston pump, a whole series of different models in price and flow rates can be realized. In contrast to previously known embodiments, uniformly designed components can be used for different models, which leads to a high cost saving in the production of components, since the components can be manufactured in much higher numbers. In addition, the construction of the invention allows the use of a variety of standardized standard parts, such as bearing balls and cylindrical pins.
Gemäß einer Ausführungsform weist die Druckerzeugungseinrichtung einen koaxial zur Längsachse beweglichen Pumpenkolben auf und die Steuereinrichtung weist ein jeweils koaxial zur Längsachse bewegliches Einlassventil und Auslassventil für das zu fördernde Fluid auf.According to one embodiment, the pressure-generating device has a pump piston that is movable coaxially with respect to the longitudinal axis, and the control device has an inlet valve and outlet valve, which are movable coaxially to the longitudinal axis, for the fluid to be delivered.
Durch den koaxial zur Längsachse beweglichen Pumpenkolben und das koaxial zur Längsachse bewegliche Einlass- und Auslassventil lassen sich besonders hohe Förderdrücke erzeugen.By the coaxial with the longitudinal axis movable pump piston and the coaxial with the longitudinal axis movable inlet and outlet valve can produce particularly high delivery pressures.
Bevorzugt ist der Pumpenkolben in einem Zylinder aufgenommen und mit einer Kolbenstange fest verbunden, die in einer mit dem Zylinder verbundenen Führungsbuchse axial verschiebbar aufgenommen und gegen diese mittels mindestens eines Dichtrings abgedichtet ist.Preferably, the pump piston is received in a cylinder and fixedly connected to a piston rod, which is received axially displaceably in a guide bush connected to the cylinder and sealed against it by means of at least one sealing ring.
Infolge der fest mit dem Pumpenkolben verbundenen Kolbenstange ergibt sich ein besonders einfacher Aufbau der Druckerzeugungseinrichtung, wobei die Kolbenstange bevorzugt mittels eines geeigneten Exzenterantriebs entlang der Längsachse in eine oszillierende Bewegung versetzbar ist. Die Kolbenstange ist bevorzugt durch Verstemmen kraftschlüssig mit dem Pumpenkolben verbunden.As a result of the piston rod fixedly connected to the pump piston, a particularly simple construction of the pressure-generating device results, wherein the piston rod can preferably be displaced into an oscillating motion by means of a suitable eccentric drive along the longitudinal axis. The piston rod is preferably connected by caulking frictionally connected to the pump piston.
Bevorzugt weist der Zylinder mindestens eine Zylindereinlassöffnung mit einer in etwa elliptischen Formgebung auf und in den Pumpenkolben ist mindestens eine Kolbeneinlassöffnung für das zu fördernde Fluid eingebracht, wobei die mindestens eine Kolbeneinlassöffnung in einen durchgehend in Richtung der Längsachse ausgerichteten Mittelkanal des Pumpenkolbens mündet.The cylinder preferably has at least one cylinder inlet opening with an approximately elliptical shape and at least one piston inlet opening for the fluid to be delivered is introduced into the pump piston, the at least one piston inlet opening opening into a central channel of the pump piston aligned continuously in the direction of the longitudinal axis.
Hierdurch gelangt das zu fördernde Fluid auf einfache Art und Weise von außen durch die Zylinderwandung bis in das hohle Innere des Pumpenkolbens. Die elliptische Geometrie der Zylindereinlassöffnungen gewährleistet einen ausreichend hohen Volumenstrom und unterstützt darüber hinaus die Selbstansaugung des zu fördernden Fluids.As a result, the fluid to be delivered passes in a simple manner from the outside through the cylinder wall into the hollow interior of the pump piston. The elliptical geometry of the cylinder inlet openings ensures a sufficiently high volume flow and also supports the self-priming of the fluid to be delivered.
Gemäß einer Ausführungsform bilden der Pumpenkolben und der Zylinder einen Verdichtungsraum aus.According to one embodiment, the pump piston and the cylinder form a compression space.
Hierdurch wird ein sich aufgrund der Kolbenbewegung periodisch vergrößerndes und verkleinerndes Volumen definiert.This defines a periodically increasing and decreasing volume due to the piston movement.
Gemäß einer Ausführungsform weist der Pumpenkolben auf einer Stirnseite eine Vertiefung zur Aufnahme einer Stirnfläche eines der Steuereinrichtung zugeordneten Ventilkäfigs auf.According to one embodiment, the pump piston has on a front side a recess for receiving an end face of a valve cage associated with the control device.
Hierdurch ist eine zuverlässige Lagesicherung des Ventilkäfigs im Pumpenkolben gegeben.As a result, a reliable position assurance of the valve cage in the pump piston is given.
Vorzugsweise ist die Stirnfläche des Ventilkäfigs mit einem umlaufenden Kragen versehen und in die Stirnfläche ist eine Sackbohrung eingebracht, wobei im Bereich des Kragens mindestens eine radiale Aussparung eingebracht ist, die mit der Sackbohrung in Verbindung steht.Preferably, the end face of the valve cage is provided with a circumferential collar and in the end face a blind bore is introduced, wherein in the region of the collar at least one radial recess is introduced, which is in communication with the blind bore.
Durch die Aussparungen gelangt das zu fördernde Fluid in den Verdichtungsraum. Die Sackbohrung dient hierbei zu einer platzsparenden Führung einer Ventilfeder des Einlassventils, wobei diese eine geringe Tiefe aufweist, um das Totraumvolumen für eindringende Luft zu minimieren und zugleich eine möglichst hohe Kompression zu gewährleisten.Through the recesses enters the fluid to be pumped into the compression chamber. The blind bore serves to space-saving guidance of a valve spring of the inlet valve, which has a small depth in order to minimize the dead space volume for penetrating air and at the same time to ensure the highest possible compression.
Gemäß einer Ausführungsform ist der Ventilkäfig mittels einer Ventilkäfigfeder vorgespannt, die sich zwischen einem Zylinderdeckel oder einer innenseitig an diesem anliegenden Anlaufscheibe und dem Kragen des Ventilkäfigs abstützt.According to one embodiment, the valve cage is prestressed by means of a valve cage spring, which is supported between a cylinder cover or a thrust washer lying on the inside thereof and the collar of the valve cage.
Durch die Ventilkäfigfeder ist eine kraftschlüssige Anlage des Ventilkäfigs am Pumpenkolben gegeben. Oberhalb des Kragens verfügt der im Wesentlichen (hohl-)zylindrische Schaft des Ventilkäfigs über einen Absatz zur Führung und Zentrierung der Ventilkäfigfeder.By the valve cage spring a non-positive fit of the valve cage on the pump piston is given. Above the collar, the substantially (hollow) cylindrical shaft of the valve cage has a shoulder for guiding and centering the valve cage spring.
Gemäß einer Ausführungsform geht der Mittelkanal des Pumpenkolbens in einen Ventilsitz über, in dem eine mittels einer Einlassventilfeder vorgespannte Kugel als Einlassventil für das zu fördernde Fluid aufgenommen ist, wobei die Einlassventilfeder zwischen der Kugel und der Sackbohrung des Ventilkäfigs eingespannt ist.According to one embodiment, the central channel of the pump piston merges into a valve seat, in which a ball biased by an inlet valve spring is received as an inlet valve for the fluid to be delivered, the inlet valve spring being clamped between the ball and the blind bore of the valve cage.
Hierdurch ist ein konstruktiv einfacher Aufbau des Einlassventils gegeben, der mit einem Minimum an Einzelkomponenten auskommt.As a result, a structurally simple construction of the inlet valve is given, which manages with a minimum of individual components.
Nach Maßgabe einer Ausgestaltung weist der Pumpenkolben einen zylindrischen Abschnitt auf, an den sich ein konischer Abschnitt anschließt.According to one embodiment, the pump piston has a cylindrical portion, which is followed by a conical portion.
Hierdurch ergibt sich eine reibungsarme und dennoch wirkungsvolle Abdichtung des Pumpenkolbens gegenüber dem Zylinder, um die Erzeugung hoher Drücke mit einer vertretbaren Antriebsleistung zu ermöglichen. Insbesondere der konische Abschnitt verringert durch eine Verkleinerung der effektiven Gleitfläche zwischen dem Pumpenkolben und dem Zylinder die Reibungsverluste. Das zu fördernde Fluid unterstützt aufgrund seiner Schmierwirkung die Herabsetzung der Reibung im Bereich der Kontaktfläche zwischen dem Pumpenkolben und dem Zylinder.This results in a low-friction, yet effective sealing of the pump piston relative to the cylinder to allow the generation of high pressures with a reasonable drive power. In particular, the conical section decreases by a reduction of the effective sliding area between the pump piston and the cylinder friction losses. Due to its lubricating effect, the fluid to be delivered assists in reducing the friction in the region of the contact surface between the pump piston and the cylinder.
Vorzugsweise ist der Pumpenkolben mit einem Hochleistungskunststoff gebildet.Preferably, the pump piston is formed with a high-performance plastic.
Hierdurch sind ein geringer Verschleiß und eine lange Lebensdauer des Pumpenkolbens gegeben. Darüber hinaus erlaubt die Eigenelastizität des Hochleistungskunststoffs einen leichten Presssitz des Pumpenkolbens im Zylinder zur Dichtwirkung, so dass zusätzliche Kolbendichtungen entfallen können.As a result, a low wear and a long life of the pump piston are given. In addition, the inherent elasticity of the high-performance plastic allows a slight press fit of the pump piston in the cylinder for sealing effect, so that additional piston seals can be omitted.
Gemäß einer Ausführungsform weist der Zylinderdeckel eine Bohrung auf, die in einen Ventilsitz übergeht, in dem eine mit einer Auslassventilfeder vorgespannte Kugel als Auslassventil für das Fluid aufgenommen ist.According to one embodiment, the cylinder cover has a bore, which merges into a valve seat, in which a ball biased with an outlet valve spring is received as an outlet valve for the fluid.
Hierdurch verfügt das Auslassventil gleichfalls über einen einfachen konstruktiven Aufbau, da es ebenfalls mit einer geringen Anzahl von Einzelteilen aufgebaut ist.As a result, the exhaust valve also has a simple structural design, since it is also constructed with a small number of items.
Gemäß einer Ausführungsform sind die Auslassventilfeder und die Kugel in einer Bohrung eines Abschlussdeckels aufgenommen, der mit dem Zylinderdeckel verbunden ist.According to one embodiment, the exhaust valve spring and the ball are received in a bore of a end cap which is connected to the cylinder cover.
Hierdurch wird der Zusammenbau der Druckerzeugungseinrichtung vereinfacht. Die Ventilauslassfeder kann sich im Abschlussdeckel oder in einem Gehäuseteil der Kolbenpumpe abstützen.As a result, the assembly of the pressure generating device is simplified. The valve outlet spring can be supported in the end cover or in a housing part of the piston pump.
Die Erfindung ist anhand von in den Zeichnungen dargestellten Ausführungsbeispielen in der nachfolgenden Beschreibung näher erläutert. Es zeigen:
- Fig. 1
- eine Schnittdarstellung einer Kolbenpumpe mit einer Druckerzeugungseinrichtung und einer Steuereinrichtung gemäß einer Ausführungsform,
- Fig. 2-5
- eine schematische Darstellung von vier Betriebszuständen der Kolbenpumpe von
Fig. 1 , - Fig. 6
- eine vergrößerte Seitenansicht des Pumpenkolbens der Druckerzeugungseinrichtung der Kolbenpumpe von
Fig. 1 , - Fig. 7
- eine Schnittansicht des Pumpenkolbens von
Fig. 6 , und - Fig. 8
- eine vergrößerte Schnittansicht eines Ventilkäfigs der Steuereinrichtung der Kolbenpumpe von
Fig. 1 .
- Fig. 1
- a sectional view of a piston pump with a pressure generating device and a control device according to an embodiment,
- Fig. 2-5
- a schematic representation of four operating states of the piston pump of
Fig. 1 . - Fig. 6
- an enlarged side view of the pump piston of the pressure generating device of the piston pump of
Fig. 1 . - Fig. 7
- a sectional view of the pump piston of
Fig. 6 , and - Fig. 8
- an enlarged sectional view of a valve cage of the control device of the piston pump of
Fig. 1 ,
Der Pumpenkolben 12 und der Zylinder 14 definieren einen Verdichtungsraum 28 für ein mittels der Kolbenpumpe 10 zu förderndes Fluid, das hier beispielhaft mit Pfeilen 46 angedeutet ist, und bilden somit die Druckerzeugungseinrichtung 30 der Kolbenpumpe 10 aus. Ein Einlass- und ein Auslassventil 32,34 bilden zusammen die Steuereinrichtung 40 der Kolbenpumpe 10 aus.The
In den Zylinder 12 sind bevorzugt drei Zylindereinlassöffnungen mit einer illustrativ jeweils elliptischen Formgebung eingelassen, von denen hier zwei sichtbare Zylindereinlassöffnungen die Bezugsziffern 42,44 tragen. Durch die Zylindereinlassöffnungen tritt das zu fördernde Fluid 46 in die Kolbenpumpe 10 ein. Die elliptische Geometrie der bevorzugt drei Zylindereinlassöffnungen gewährleistet einen ausreichend hohen Volumenstrom und unterstützt dabei die Selbstansaugung des zu fördernden Fluids 46. Die Zylindereinlassöffnungen stehen in einer hydraulischen Verbindung mit vorzugsweise drei Kolbeneinlassöffnungen des Pumpenkolbens 12, von denen hier lediglich eine Kolbeneinlassöffnung 48 sichtbar ist. Die Kolbeneinlassöffnungen 48 münden jeweils in einen den Pumpenkolben 12 durchsetzenden Mittelkanal 50 ein.Into the
Der Mittelkanal 50 geht beispielhaft in einen Ventilsitz 52 über, in dem eine mittels einer Einlassventilfeder 54 vorgespannte Kugel 56 aufgenommen ist, die zusammen das Einlassventil 32 ausbilden. Die Einlassventilfeder 54 stützt sich hierbei mit einem von der Kugel 56 weggerichteten Ende in einer Sackbohrung 58 eines Ventilkäfigs 60 ab, der zwischen dem Pumpenkolben 12 und einer Anlaufscheibe 62, die - in
Der Ventilkäfig 60 ist mittels einer Ventilkäfigfeder 66 vorgespannt, wodurch der Ventilkäfig 60 in jedem Betriebszustand der Kolbenpumpe 10 kraftschlüssig - in
In den Zylinderdeckel 64 ist ferner eine Bohrung 70 eingebracht, die in einen Ventilsitz 72 übergeht, in dem eine mittels einer Auslassventilfeder 74 mechanisch vorgespannte Kugel 76 zur Ausbildung des Auslassventils 34 aufgenommen ist. Der Zylinderdeckel 64 ist - in
Aufgrund der linear-koaxialen Anordnung der Druckerzeugungseinrichtung 30 sowie der Steuereinrichtung 40 mit dem Einlass- und dem Auslassventil 32,34 und dem Ventilkäfig 60 entlang der Längsachse 18 ergibt sich im Vergleich zu konventionellen Kolbenpumpen für Hochdruckreiniger ein sehr platzsparender Aufbau der Kolbenpumpe 10, der die Integration in ein Gehäuse bzw. ein Pumpengehäuse 84 erleichtert, wobei das Gehäuse 84 gemäß einer Ausführungsform von dem Zylinder 14 ausgebildet sein kann. Aufgrund der geringen Anzahl der hierzu notwendigen Bauteile ist die Kolbenpumpe 10 zudem kostengünstig herstellbar und erreicht eine lange Lebensdauer bei einer hohen Zuverlässigkeit und einem geringen Wartungsaufwand. Infolge des modularen Aufbaus der Kolbenpumpe 10 lassen sich darüber hinaus mehrere Kolbenpumpen 10 im Baukastenprinzip zu einer Pumpeinheit in einem einzelnen Gehäuse oder mehreren Gehäusen zusammenfassen, um beispielsweise Hochdruckreiniger mit unterschiedlichen Anforderungen hinsichtlich der Fördermenge und/oder des Förderdrucks eines zu fördernden Fluids zu realisieren, woraus sich weitere Kosteneinsparungspotenziale ergeben. Hierbei können z. B. zwei erfindungsgemäß ausgebildete Kolbenpumpen 10 diametral gegenüberliegend zu einem Exzenterantrieb positioniert werden. Darüber hinaus können mehr als zwei Kolbenpumpen mittels nur eines Exzenterantriebs angetrieben werden.Due to the linear coaxial arrangement of the
Im Betrieb der Kolbenpumpe 10 wird das zu fördernde Fluid 46 durch die Zylindereinlassöffnungen 42,44 sowie die hiermit hydraulisch verbundene Kolbeneinlassöffnung 48 und der weiteren, nicht sichtbaren Kolbeneinlassöffnungen in den Mittelkanal 50 und von dort in den Verdichtungsraum 28 eingesaugt, wenn sich die Kolbenstange 16 und mit ihr der Pumpenkolben 12 im Zylinder 14 in Richtung eines Pfeils 86 - in
Der Einlassventilfeder 54 kommt hierbei eine besondere Bedeutung zu. Neben der Führungsfunktion der Kugel 56 des Einlassventils 32 liegt ihre Hauptaufgabe im schnellen Schließen des Einlassventils 32, sobald eine entsprechende Ansaugphase des zu fördernden Fluids 46 beendet ist. Die Federkernlinie der Einlassventilfeder 54 bestimmt hierbei den Öffnungsdruck des Einlassventils 32. Dieser Öffnungsdruck sollte in einem Bereich zwischen 0,1- 0,25 bar liegen, damit gewährleistet ist, dass etwaig noch vorhandene Luft mit angesaugt werden kann. Durch eine sorgfältige Abstimmung der Federkraft der Einlassventilfeder 54 wird ein volumetrischer Wirkungsgrad von 85-90 % erreicht. Ein Weglassen der Einlassventilfeder 54 würde zu einer erheblichen Absenkung dieses Wirkungsgrades führen, da zu Beginn der Verdichtungsphase die Kugel 56 nicht schnell genug gegen den Ventilsitz des Pumpenkolbens 12 gedrückt würde und dadurch ein Teil des zu fördernden Fluids aus dem Verdichtungsraum 28 entweichen würde.The
Der Pumpenkolben 12 ist bevorzugt mit einem gegebenenfalls faserarmierten Hochleistungskunststoff gebildet, der eine hohe Verschleißfestigkeit, eine hohe Formstabilität sowie eine weitgehende Unempfindlichkeit gegenüber aggressiven chemischen Medien aufweist. Aufgrund der Eigenelastizität des Kunststoffmaterials kann der Pumpenkolben 12 bevorzugt unter leichtem Pressschluss in den Zylinder (14 von
Vorzugsweise ist in den Pumpenkolben 12 mindestens eine und illustrativ drei z.B. zumindest im Wesentlichen elliptische Kolbeneinlassöffnungen eingebracht, von denen hier lediglich die Kolbeneinlassöffnung 48 sichtbar ist. Die Kolbeneinlassöffnungen sind bevorzugt gleichmäßig beabstandet und um den Umfang des Pumpenkolbens 12 herum verteilt in diesen eingebracht. Die elliptischen Kolbeneinlassöffnungen, deren Hauptachsen in Richtung der Längsachse 18 verlaufen, dienen der strömungsoptimierten Zufuhr des zu fördernden Fluids (46 von
In eine Stirnseite 96 des Pumpenkolbens 12 ist eine topfförmige Vertiefung 98 eingelassen, die zur Aufnahme des hier nicht dargestellten Ventilkäfigs (60 von
In eine der Stirnseite 96 gegenüberliegende Unterseite 102 des Pumpenkolbens 12 ist gleichfalls eine näherungsweise topfförmige Vertiefung 104 eingelassen, die zur kraftschlüssigen Anbindung der Kolbenstange (16 von
Um die Abdichtungswirkung des Pumpenkolbens 12 im Zylinder (14 von
Die Sackbohrung 58 verfügt über eine hintere Anlageschulter 126 für die Einlassventilfeder (54 von
Erfindungsgemäß ist eine Tiefe 132 der Sackbohrung 58 möglichst gering bemessen. Hierdurch ist das Totraumvolumen für eindringende Luft so klein wie möglich, wobei zugleich eine hohe Kompression der Kolbenpumpe (10 von
Claims (13)
Applications Claiming Priority (1)
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DE201210219621 DE102012219621A1 (en) | 2012-10-26 | 2012-10-26 | piston pump |
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EP2725226A1 true EP2725226A1 (en) | 2014-04-30 |
Family
ID=49223656
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EP13185479.6A Withdrawn EP2725226A1 (en) | 2012-10-26 | 2013-09-23 | Piston pump |
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EP (1) | EP2725226A1 (en) |
CN (1) | CN103790819A (en) |
DE (1) | DE102012219621A1 (en) |
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WO2017148841A1 (en) * | 2016-03-03 | 2017-09-08 | Continental Automotive Gmbh | Pump plunger for a reciprocating high-pressure fuel pump, and reciprocating high-pressure fuel pump |
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EP3680483A1 (en) * | 2019-01-14 | 2020-07-15 | Graco Minnesota Inc. | Piston rod sleeve mounting for fluid sprayer pump |
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CN104454419A (en) * | 2014-11-25 | 2015-03-25 | 王硕 | Star-shaped hydraulic pump |
CN110608165A (en) * | 2018-06-15 | 2019-12-24 | 郑州奥特科技有限公司 | Plunger assembly, lubricating pump, plunger and plunger machining method |
CN109869295A (en) * | 2019-03-27 | 2019-06-11 | 宁波水分子电器科技有限公司 | Plunger unit, pump and jetting machine |
CN109869296A (en) * | 2019-03-27 | 2019-06-11 | 宁波水分子电器科技有限公司 | Pump unit for jetting machine |
CN115143096B (en) * | 2022-09-06 | 2022-12-02 | 万向钱潮股份公司 | Plunger pump for automotive electronics stable control system |
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Also Published As
Publication number | Publication date |
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DE102012219621A1 (en) | 2014-04-30 |
CN103790819A (en) | 2014-05-14 |
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