EP2725226A1 - Pompe à pistons - Google Patents

Pompe à pistons Download PDF

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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.)
Withdrawn
Application number
EP13185479.6A
Other languages
German (de)
English (en)
Inventor
Stefan Kern
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2725226A1 publication Critical patent/EP2725226A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • 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
    • F04B1/0421—Cylinders
    • 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
    • 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
    • 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
    • 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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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP13185479.6A 2012-10-26 2013-09-23 Pompe à pistons Withdrawn EP2725226A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201210219621 DE102012219621A1 (de) 2012-10-26 2012-10-26 Kolbenpumpe

Publications (1)

Publication Number Publication Date
EP2725226A1 true EP2725226A1 (fr) 2014-04-30

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP13185479.6A Withdrawn EP2725226A1 (fr) 2012-10-26 2013-09-23 Pompe à pistons

Country Status (3)

Country Link
EP (1) EP2725226A1 (fr)
CN (1) CN103790819A (fr)
DE (1) DE102012219621A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
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WO2017148841A1 (fr) * 2016-03-03 2017-09-08 Continental Automotive Gmbh Piston pour pompe à carburant haute pression à piston et pompe à carburant haute pression à piston
CN108787554A (zh) * 2017-05-04 2018-11-13 苏州宝时得电动工具有限公司 手持式高压清洗机
EP3680483A1 (fr) * 2019-01-14 2020-07-15 Graco Minnesota Inc. Montage de manchon de tige de piston pour pompe de pulvérisateur de fluide
US11002271B2 (en) 2017-02-21 2021-05-11 Graco Minnesota Inc. Piston rod assembly for a paint pump

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CN104454419A (zh) * 2014-11-25 2015-03-25 王硕 一种星型液压泵
CN110608165A (zh) * 2018-06-15 2019-12-24 郑州奥特科技有限公司 一种柱塞组件、润滑泵、柱塞及柱塞加工方法
CN109869295A (zh) * 2019-03-27 2019-06-11 宁波水分子电器科技有限公司 柱塞单元、泵及高压清洗机
CN109869296A (zh) * 2019-03-27 2019-06-11 宁波水分子电器科技有限公司 用于高压清洗机的泵单元
CN115143096B (zh) * 2022-09-06 2022-12-02 万向钱潮股份公司 一种汽车电子稳定控制***用柱塞泵

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0892174A2 (fr) * 1997-07-17 1999-01-20 Jürgen Weigel Tête de pompe pour pompe à piston
WO1999006697A1 (fr) * 1997-07-30 1999-02-11 Robert Bosch Gmbh Piston tubulaire produit par formage a froid et bouchon de fermeture pour une pompe a pistons radiaux
DE102004061814A1 (de) * 2004-12-22 2006-07-06 Robert Bosch Gmbh Kolbenpumpe
FR2881799A1 (fr) * 2005-02-10 2006-08-11 Advics Co Ltd Pompe a piston
DE102006054061A1 (de) * 2006-11-16 2008-05-21 Robert Bosch Gmbh Kolbenpumpe für ein Fahrzeugbremssystem
DE102007047418A1 (de) * 2007-10-04 2009-04-23 Robert Bosch Gmbh Kolbenpumpe zur Förderung eines Fluids und zugehöriges Bremssystem

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH513334A (de) * 1969-12-05 1971-09-30 Stenberg Flygt Ab Als Pumpe oder Kompressor verwendbare Kolbenmaschine
DE3001570C2 (de) * 1980-01-17 1983-03-24 Alfred Kärcher GmbH & Co, 7057 Winnenden Einrichtung zur Mengenregulierung für die von einer Mehrkolbenhochdruckpumpe eines Hochdruckreinigers abgegebene Flüssigkeitsmenge
DE3001571C2 (de) * 1980-01-17 1982-10-28 Alfred Kärcher GmbH & Co, 7057 Winnenden Hochdruckreinigungsgerät
DE3218960A1 (de) * 1982-05-19 1983-11-24 Speck Kolbenpumpen Fabrik Pumpe, insbesondere hochdruckpumpe zur foerderung von fluessigkeiten
US4824342A (en) * 1988-02-16 1989-04-25 Hypro Corp. Chemical injector system for piston pumps
DE4240590A1 (de) * 1992-12-03 1994-06-09 Uraca Pumpen Verdrängerpumpe
EP0783923B1 (fr) * 1995-12-19 1998-06-17 Kew Industri A/S Méthode et appareil pour la commande d'écoulement d'un liquide de nettoyage traversant un nettoyeur à haute pression
DE10219787A1 (de) * 2002-05-03 2003-11-13 Bosch Gmbh Robert Hydraulische Fahrzeugbremsanlage mit einer von einem Elektromotor antreibbaren Pumpe
US7134846B2 (en) * 2004-05-28 2006-11-14 Stanadyne Corporation Radial piston pump with eccentrically driven rolling actuation ring
DE102005050009B4 (de) * 2005-10-11 2007-07-05 Alfred Kärcher Gmbh & Co. Kg Hochdruckreinigungsgerät
DE102008043444A1 (de) * 2008-11-04 2010-05-06 Robert Bosch Gmbh Pumpenanordnung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0892174A2 (fr) * 1997-07-17 1999-01-20 Jürgen Weigel Tête de pompe pour pompe à piston
WO1999006697A1 (fr) * 1997-07-30 1999-02-11 Robert Bosch Gmbh Piston tubulaire produit par formage a froid et bouchon de fermeture pour une pompe a pistons radiaux
DE102004061814A1 (de) * 2004-12-22 2006-07-06 Robert Bosch Gmbh Kolbenpumpe
FR2881799A1 (fr) * 2005-02-10 2006-08-11 Advics Co Ltd Pompe a piston
DE102006054061A1 (de) * 2006-11-16 2008-05-21 Robert Bosch Gmbh Kolbenpumpe für ein Fahrzeugbremssystem
DE102007047418A1 (de) * 2007-10-04 2009-04-23 Robert Bosch Gmbh Kolbenpumpe zur Förderung eines Fluids und zugehöriges Bremssystem

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017148841A1 (fr) * 2016-03-03 2017-09-08 Continental Automotive Gmbh Piston pour pompe à carburant haute pression à piston et pompe à carburant haute pression à piston
US11002271B2 (en) 2017-02-21 2021-05-11 Graco Minnesota Inc. Piston rod assembly for a paint pump
US11512694B2 (en) 2017-02-21 2022-11-29 Graco Minnesota Inc. Piston rod assembly for a fluid pump
US11773842B2 (en) 2017-02-21 2023-10-03 Graco Minnesota Inc. Removable piston rod sleeve for fluid pump
US11891992B2 (en) 2017-02-21 2024-02-06 Graco Minnesota Inc. Piston with sleeve for fluid pump
CN108787554A (zh) * 2017-05-04 2018-11-13 苏州宝时得电动工具有限公司 手持式高压清洗机
CN108787554B (zh) * 2017-05-04 2024-01-05 苏州宝时得电动工具有限公司 手持式高压清洗机
EP3680483A1 (fr) * 2019-01-14 2020-07-15 Graco Minnesota Inc. Montage de manchon de tige de piston pour pompe de pulvérisateur de fluide
US11020761B2 (en) 2019-01-14 2021-06-01 Graco Minnesota Inc. Piston rod sleeve mounting for fluid sprayer pump

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DE102012219621A1 (de) 2014-04-30

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