EP2634426B1 - Pompe à deux étages - Google Patents

Pompe à deux étages Download PDF

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Publication number
EP2634426B1
EP2634426B1 EP20120157913 EP12157913A EP2634426B1 EP 2634426 B1 EP2634426 B1 EP 2634426B1 EP 20120157913 EP20120157913 EP 20120157913 EP 12157913 A EP12157913 A EP 12157913A EP 2634426 B1 EP2634426 B1 EP 2634426B1
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EP
European Patent Office
Prior art keywords
pressure
valve
housing
chamber
stage pump
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Active
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EP20120157913
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German (de)
English (en)
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EP2634426A1 (fr
Inventor
Georg Neumair
Johannes Glaser
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Hawe Hydraulik SE
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Hawe Hydraulik SE
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Priority to EP20120157913 priority Critical patent/EP2634426B1/fr
Publication of EP2634426A1 publication Critical patent/EP2634426A1/fr
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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
    • F04B3/00—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage
    • 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
    • F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two 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
    • F04B25/00—Multi-stage pumps
    • F04B25/005—Multi-stage pumps with two cylinders

Definitions

  • the invention relates to a two-stage pump according to the preamble of patent claim 1.
  • Such two-stage pumps are used, for example, in manual or motor-driven hand tools, for example for pressing cable lugs, cable connectors, press fitting systems, also for shears such as cable shears and the like .
  • the two pumping elements deliver up to a certain limit pressure, which is a fraction of the maximum pressure of for example 700 bar can be, together a much higher flow rate than when the limit pressure is exceeded to the maximum pressure, for example, to cover an idle stroke of a tool quickly before the actual work process with high power requirements, ie high working pressure occurs.
  • the low-pressure and high-pressure conveying spaces are not separated from each other, but connected to each other via the suction valve of the high pressure delivery chamber, so that the flow from the Niederdruc delivery chamber to the pressure outlet takes the flow path through the high-pressure delivery chamber and the pressure valve of the high-pressure delivery chamber.
  • the high-pressure and low-pressure pumping elements share a common pressure valve, which must be designed inordinately large, now also with the combined flow rates of high-pressure and low-pressure pumping elements to cope.
  • the chamber of the changeover valve communicates with the pressure outlet downstream of the single pressure valve via a housing channel.
  • the low pressure reciprocating piston is connected to the high pressure reciprocating piston. Both reciprocating pistons are biased together via a return spring of a pneumatic drive in each case in the suction direction.
  • a two-stage pump in which the two pumping elements have reciprocating piston, which operate linearly and reciprocally in a common delivery chamber with only one suction valve and only one pressure valve, the reciprocating piston of the low-pressure pumping element dividing the delivery chamber, and the high-pressure piston is driven.
  • a check valve is included, which opens in the flow direction to the high-pressure delivery chamber part dependent on pressure or positively controlled. The volumetric efficiency is low.
  • the reciprocating piston are subject to heavy wear.
  • the invention has for its object to provide a two-stage pump of the type mentioned, which is structurally simple, reliable and easy to drive, works with high volumetric efficiency, and allows accurate adjustment of the limit pressure.
  • the two reciprocating pump elements with their separate reciprocating pistons, separate delivery chambers, and their own pressure and suction valves, work completely independently of each other and with high partial efficiencies. Their different flow rates are combined up to the limit pressure before the working pressure at the pressure port actuates the switching valve, so that from then on the flow of the low-pressure pump element loss is passed to the tank, the pressure in the pressure outlet, the pressure valve of the low-pressure pump element keeps closed, so that no portion of the delivery flow of the high-pressure pump element is lost via the pressure valve of the low-pressure pump element and then subsequently via the actuated changeover valve to the tank.
  • the pressure valves are connected to each other via a housing channel connected to the pressure outlet. The housing channel leads into the chamber containing the switching valve.
  • the pressure valves are placed laterally of the delivery chambers and the suction valves in the reciprocating stroke direction in extension of the pumping chambers, which can be achieved with compact housing dimensions low-loss and short pressure-side flow paths, and the switching valve can be integrated to save space.
  • the switching valve a spring-loaded seat valve.
  • the spring preload which determines the limit pressure for the low-pressure pumping element or the control pressure of the changeover valve, should be adjustable in order to select the limit pressure as needed.
  • the seat valve construction also guarantees in the locked position leakage.
  • a seat for a poppet-closing member of the switching valve exhibiting sleeve insert is mounted sealed. This has a multiple function, since it separates entrances into the chamber from each other without leakage, and at the same time can form an abutment for a biasing spring of the seat valve closing member.
  • the biasing spring is a threaded onto a shaft of the seat valve closing member disc spring package.
  • a spring abutment nut can be screwed onto the shaft.
  • the spring preload is not changed uncontrollably, can be arranged, preferably, in the internal thread of the spring abutment nut against the free shaft end tensionable counter-Madenhohlschraube.
  • a sleeve insert in the Chamber-positioning screw be used, which at the same time has a flow connection to the tank-forming passages, for example, open directly to a housing outside.
  • the high pressure pressure valve preferably centric, placed in lying on a housing outside pressure outlet.
  • the high-pressure pressure valve has lateral valve openings to the pressure outlet, where appropriate, where the housing channel opens into the pressure outlet and the low-pressure pressure valve connects to the pressure outlet.
  • the pressure outlet is, for example, a circular recess in the outside of the housing, so that there an O-ring can be mounted, which provides the necessary seal to the other hydraulic system at this interface.
  • the seat valve closure member is expediently pressure-balanced with respect to the pressure from the low-pressure delivery chamber and acted upon exclusively by the pressure from the housing channel or the working pressure at the pressure outlet against the spring preload.
  • the reciprocating pistons are arranged parallel next to one another. They are available with their operating ends on the same outside of the housing, and are, for example, by a common eccentric or phase-shifted in the direction of rotation eccentrics, optionally even eccentrics of different eccentricity, one drive shaft or two drive shafts, actuated, in the latter case, not only the strokes out of phase, but also the speeds can be chosen either the same or different.
  • the former case allows a simple drive with a common drive shaft whose torque substantially only after exceeding the limit pressure more is removed from the high-pressure pumping element, since the low-pressure pumping element runs "empty", so to speak.
  • the lifting pistons are arranged parallel next to one another. However, their actuating ends are on opposite sides of the housing to each eccentric on its own of two drive shafts. With this design, not only different strokes or stroke frequencies, but also any phase displacements between the strokes can be adjusted to achieve the highest possible degree of uniformity.
  • the diameter of the reciprocating piston of the low-pressure pump element is greater than the diameter of the piston of the high-pressure pump element.
  • Such a two-stage pump with housing dimensions of about 32 x 32 x 36 mm, piston diameters ⁇ 10.0 mm and strokes, for example, about 5 mm generated before exceeding the arbitrarily high selectable limit pressure, a flow rate, depending on the drive speed of about 0.35 to 1 , 4l / min, and after exceeding the limit pressure only a flow of about 0.2 to 0.5 l / min, in order to achieve a maximum working pressure at the pressure outlet, for example, 700 bar relatively quickly.
  • a low-pressure pumping element N with a larger flow rate and a high-pressure pumping element H with a smaller flow rate, for example, are accommodated parallel to one another.
  • the housing 1 has a pressure outlet 2 to a hydraulic system connectable there and outlets 20 to a tank T, which may be formed by a housing containing the two-stage pump P (not shown) itself.
  • the high-pressure pump element H is a piston pump element with its own delivery chamber 3, own pressure and suction valves 4, 5 and a reciprocating piston 16, the actuating end 18 protrudes on a housing outside.
  • the low-pressure pumping element N is a piston pump element with a reciprocating piston 17 in its own low-pressure delivery chamber 6, the own suction and pressure valves 8, 7 are assigned, and a portion 15 a of a housing channel 12 to a in the housing 1 (in a chamber 27, for example Fig. 1 ) integrated switching valve 9 is connected, which in turn can open to the tank T.
  • a section 14 of the housing channel 12 leads to the low-pressure pressure valve 7, which is connected via a portion 15 b with the low-pressure delivery chamber 6 or inserted directly into this.
  • the section 15a forms a branch of the housing channel 12, from which also a further branch 13 leads to a control side of the changeover valve 9, for example, contains a against a biasing spring 10 from the shutoff position shown in the open position to the tank T adjustable closing member 11.
  • the switching valve 9 is a seat valve with leak-free shut-off (see Fig. 6a ).
  • the housing channel 12 leads from the portion 14 of the low-pressure pressure valve 7 to the pressure outlet 2 at or downstream of the high-pressure pressure valve 4.
  • a diaphragm 28 may be included, for example, in FIG Fig. 4 is shown.
  • the two reciprocating pistons 16, 17 can be driven together or separately to and fro (not shown), for example via a common eccentric or separate eccentric drive shaft (in Fig. 3 indicated), or two drive shafts (not shown).
  • both piston pump elements When operating record both piston pump elements suck first on the suction valves 5, 8 hydraulic medium from the tank into their delivery chambers 3, 6, compress the sucked hydraulic medium, and promote this via their pressure valves 7, 4 with the larger flow of the low-pressure pumping element N and the added smaller flow of the high pressure pumping element H to the pressure outlet 2, wherein the switching valve 9 is in the leak-tight dense shut-off position. If, for example, at the pressure outlet 2, a set on the biasing spring 10 limit pressure reached, then the switching valve 9 is opened via the branch 13, which connects the low-pressure delivery chamber 6 via the branch or the section 15a directly to the tank T.
  • the low-pressure pressure valve 7 is kept closed by the working pressure, so that the low-pressure pumping element N sucks on the low-pressure suction valve 8, but low-loss directly into the tank T promotes, while the smaller flow of the high-pressure pumping element H via the high pressure Pressure valve 4 is conveyed from the high-pressure delivery chamber 3 to the pressure outlet 2 until the maximum system pressure is reached.
  • the basis Fig. 6 explained components of the two-stage pump P can also be found in the Fig. 1 to 5 ,
  • the switching valve 9 is located in a chamber 27 of the housing 1, which in Fig. 1 better to see.
  • Fig. 1 and Fig. 3 are the reciprocating piston 16, 17 shown with the same effective length, but the low-pressure piston 17 and the delivery chamber 6 have a larger diameter than the high-pressure piston 16 and the delivery chamber 3.
  • the stroke directions of the two reciprocating pistons 16, 17 are here, for example approximately perpendicular to the axis of the chamber 27, in which the switching valve 9 is mounted.
  • the high-pressure suction valve 5, for example a spring-loaded platelet valve is mounted directly in the end region of the high-pressure delivery chamber 3, while the high-pressure pressure valve 4, for example visible on a housing outside, can be mounted in the pressure outlet 2.
  • the low-pressure pressure valve 7 is according to Fig.
  • the high pressure suction valve 5 is in Fig. 3 positioned with a continuous ring insert, which is fixed by a continuous locking screw, so that suck both suction valves 5, 8 on the same outside of the housing.
  • Both reciprocating pistons 16, 17 are acted upon in the suction direction of springs 19 and have approximately equal and aligned actuating ends 18, which in the embodiment of Fig. 1, 2 and 3 projecting on the same outside of the housing, and facing away from the outside of the housing, to suck the suction valves 8, 5.
  • Fig. 1 From the housing channel 12 and its portions 15 a, 15 b, 14, 13 are in the Fig. 1 . 3 and 4 in each case the courses are recognizable. So shows Fig. 1 combined with Fig. 4 the branch 13 as a blind bore, which opens into an inner end of the chamber 27, shows Fig. 3 the portions 15a, 15b in the low-pressure suction valve 8, of which in Fig. 6 the section 15b to the low pressure pressure valve 7 and section 15a lead to another inlet in the chamber 27 (see also Fig. 4). Fig. 4 also illustrates how the low-pressure pressure valve 7 is connected via the portion 14 with the housing channel 12, the in Fig. 3 leads to the region of the pressure outlet 2 and is connected to this via a connection 24.
  • the pressure outlet 2 (interface) is in Fig. 3
  • a circular recess 22 in a housing outside, where there may be an O-ring 23 may be arranged.
  • the high-pressure pressure valve 4 has a spring-loaded plate 26 and lateral valve outlets 25 in the recess 22 of the pressure outlet 2.
  • Fig. 4 shows the in the housing channel 12, for example, upstream of the branch 13 to the chamber 27, inserted aperture 28th
  • Fig. 3 indicates two different drive principles of the reciprocating piston 17, 16 via a here preferably common drive shaft 46, although separate drive shafts would also be possible.
  • the two eccentrics 47, 45 could be phase-shifted in the direction of rotation of the drive shaft 46 (not shown).
  • the actuator ends 18 could protrude from two opposite sides of the housing, and be driven by a respective drive shaft, wherein also the stroke of each reciprocating piston 16, 17 could be selected individually, as well as the phase offset between the strokes. Also in Fig. 3 For example, the two eccentrics 45, 47 could be different from each other to produce different strokes.
  • Fig. 5 That in the Fig. 1, 2 and 4 indicated switching valve 9 is based Fig. 5 explained. It is for example a seat valve according to Fig. 6a , which is mounted with a sleeve insert 29 in the chamber 27 of the common housing 1.
  • the sleeve insert 29 is sealed on the outside in the chamber 27 twice (see Fig. 1 ), on the one hand to separate inlets into the chamber 27 from each other, ie the separation of the working pressure to the pressure in the low-pressure chamber 6, and on the other hand to separate the branch 15a from the tank T, ie the sealing of the pressure in the low-pressure delivery chamber 6 against escape into the Tank T.
  • the sleeve insert 29 has there a circumferential groove, where the inlet of the branch 15a lies in the chamber 27, and transverse passages 30 from the circumferential groove to the sleeve insert 29 limited Inner space. Furthermore, the sleeve insert 29 forms a valve seat 31 for a seat valve closing member 33, for example, with the in Fig. 6a indicated valve member 11 corresponds.
  • the seat valve closure member 33 is here e.g. formed as a cone and has a shaft 34 which protrudes from the sleeve insert 29, and on which the biasing spring 10 is threaded in the form of a plate spring package 36.
  • the shaft can serve as centering of the biasing spring.
  • a biasing spring 10 may also serve any other spring.
  • the sleeve insert 29 forms a spring abutment 37 for the biasing spring 10.
  • a spring abutment nut 38 is screwed, which adjusts the bias of the biasing spring 10, and may have a rotary handle 41 for adjustment.
  • In the other end of the seat valve closing member 33 may also be formed a rotary handle 42 to be able to counteract when setting the spring preload can.
  • the spring abutment nut 38 may be further secured by a counter-serrate hollow screw 39 which has an internal rotary handle 40 and is tightened against the free end of the shaft 34.
  • the seat valve closing member 33 has a sealing surface 43 which cooperates with the valve seat 31 in the sleeve insert 29, wherein the effective diameter D of the poppet valve closing member 33 with the diameter of the valve seat 31 almost coincides, so that the poppet valve closure member 33 with respect to the pressure is pressure-balanced in the branch or the portion 15a, and on the effective diameter D exclusively from the pressure in the branch 13 in the direction of control, ie Lifting direction of the sealing surface 43 is acted upon by the valve seat 31 against the biasing spring 10.
  • the sleeve insert 29 is positioned in the chamber 27 by a closure screw 32 which includes flow passages 20 to the tank T, which may also be used, for example, in FIG Fig. 2 you can see. Furthermore, the closure screw 32 limit the poppet valve in its stroke to achieve a defined maximum opening cross-section, and also limit the stroke of the plate spring package to a predefined stroke, which positively affects its life.
  • the bias of the biasing spring 10 can be adjusted only after removing the switching valve 9 from the chamber 27.
  • the effective diameter D of the seat valve closing member 33 is for example about 4 mm, while its opening stroke may be about 0.5 mm.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (14)

  1. Pompe (P) à deux étages, comprenant un élément de pompe haute-pression (H) pouvant être entraîné et destiné à un débit plus faible, ainsi qu'un élément de pompe basse-pression (N) pouvant être entraîné et destiné à un débit plus élevé, une sortie de refoulement (2) commune, et une valve d'inversion (9), qui est agencée entre l'élément de pompe basse-pression (N) et un réservoir (T), et peut être commandée en ouverture vers le réservoir (T) en fonction de la pression dans la sortie de refoulement (2), pompe
    dans laquelle les deux éléments de pompe (H, N) sont des éléments de pompe à piston comprenant des pistons alternatifs (16, 17) précontraints par ressort dans la direction de l'aspiration, et comprenant des chambres de refoulement (6, 3) présentant leur propres soupapes d'aspiration (5, 8) et au moins une soupape de pression de refoulement (4, 7), et
    dans laquelle les pistons alternatifs (16, 17), les soupapes d'aspiration et de pression de refoulement (5, 8; 4, 7) et la valve d'inversion (9) agencée dans un compartiment (27), se partagent un carter (1) commun, caractérisée en ce que les chambres de refoulement haute-pression et basse-pression (3, 6) sont agencées de manière séparée dans le carter (1) et présentent chacune leur propre soupape de pression de refoulement (4, 7),
    et en ce que les soupapes de pression de refoulement (4, 7) sont mutuellement reliées, en aval, par l'intermédiaire d'un canal de carter (12) qui est relié à la sortie de refoulement (2) et est dérivé dans la chambre (27).
  2. Pompe à deux étages selon la revendication 1, caractérisée en ce que les soupapes de pression de refoulement (4, 7) sont placées latéralement aux chambres de refoulement (3, 6), et les soupapes d'aspiration (5, 8) dans la direction de la course des pistons, en prolongement des chambres de refoulement (3, 6), et en ce que le compartiment (27) renfermant la valve d'inversion (9) est placé dans la zone des soupapes d'aspiration (5, 8), et, de préférence, communique séparément avec la chambre de refoulement basse-pression (6) et la sortie de refoulement (2) respectivement le canal de carter (12).
  3. Pompe à deux étages selon la revendication 1, caractérisée en ce que la valve d'inversion (9) est une valve à siège précontrainte par ressort, et en ce que, de préférence, la précontrainte de ressort, qui détermine la pression de commande d'ouverture vers le réservoir (T) définissant la pression limite de la pompe à deux étages (P), est réglable.
  4. Pompe à deux étages selon la revendication 1, caractérisée en ce que dans au moins un chemin d'écoulement (13) vers le compartiment (27), qui est dérivé du canal de carter (12), est prévu un diaphragme (28).
  5. Pompe à deux étages selon la revendication 2, caractérisée en ce que dans le compartiment (27) est monté, de manière étanche, un insert en douille (29) présentant un siège (31) pour un organe d'obturation de valve à siège (11, 13) de la valve d'inversion (9), qui sépare mutuellement des entrées dans le compartiment (27) raccordées à des chemins d'écoulement séparés vers le compartiment (27), et, de préférence, forme une butée d'appui (37) pour un ressort de précontrainte (10).
  6. Pompe à deux étages selon la revendication 5, caractérisée en ce que le ressort de précontrainte (10) est un empilement de rondelles-ressorts (36) enfilées sur un corps allongé (34) de l'organe d'obturation de valve à siège (11, 33).
  7. Pompe à deux étages selon la revendication 6, caractérisée en ce que sur le corps allongé (34) peut être vissé un écrou de butée d'appui de ressort (38), et en ce que, de préférence, dans un filetage intérieur de l'écrou de butée d'appui de ressort (38) est agencée une vis creuse sans tête (39) formant contre-écrou, qui peut être serrée contre l'extrémité libre du corps allongé.
  8. Pompe à deux étages selon la revendication 5, caractérisée en ce que dans une extrémité ouverte du compartiment (27) est insérée une vis de fermeture (32), qui positionne l'insert en douille (29) dans le compartiment (27), et présente des passages (20) formant une liaison d'écoulement vers le réservoir (T), de préférence des passages (20) débouchant librement dans un côté extérieur de carter.
  9. Pompe à deux étages selon la revendication 1, caractérisée en ce que les soupapes de pression de refoulement et d'aspiration (4, 7, 5, 8) sont des soupapes à lamelle, chargées par ressort.
  10. Pompe à deux étages selon la revendication 1, caractérisée en ce que la soupape de pression de refoulement haute-pression (4) est placée, de préférence de manière centrée, dans une sortie de refoulement (2) située sur un côté extérieur de carter, et y présente des ouvertures de soupape latérales (25) vers la sortie de refoulement (2), où débouche également dans la sortie de refoulement (2), le canal de carter (12) raccordé à la chambre de refoulement basse-pression (6) par l'intermédiaire de la soupape de pression de refoulement basse-pression (7).
  11. Pompe à deux étages selon la revendication 10, caractérisée en ce que la sortie de refoulement (2) est un creux (22) de forme circulaire dans le côté extérieur du carter, et renferme un joint torique (23).
  12. Pompe à deux étages selon la revendication 5, caractérisée en ce que l'organe d'obturation de valve à siège (33) est équilibré en pression concernant la pression dans la chambre de refoulement basse-pression (6), et ne peut être actionné que par la pression dans le canal de carter (12) dans le sens de la commande d'ouverture, à l'encontre du ressort de précontrainte (10).
  13. Pompe à deux étages selon l'une au moins des revendications 1 à 12, caractérisée en ce que les pistons alternatifs (16, 17) sont agencés parallèlement côte à côte, font saillie, avec leurs extrémités d'actionnement (18), du même côté extérieur de carter, et peuvent être actionnés par un excentrique commun, ou par des excentriques séparés (45, 47) de même phase, ou encore par des excentriques décalés en phase dans le sens de rotation, d'un arbre d'entraînement (46) ou de deux arbres d'entraînement.
  14. Pompe à deux étages selon l'une au moins des revendications 1 à 12, caractérisée en ce que les pistons alternatifs (16, 17) sont agencés parallèlement côte à côte, et font saillie, avec leurs extrémités d'actionnement (18), de deux côtés de carter mutuellement opposés, vers un excentrique respectif sur l'un de deux arbres d'entraînement, qui leur est propre, les arbres d'entraînement étant agencés des deux côtés du carter (1).
EP20120157913 2012-03-02 2012-03-02 Pompe à deux étages Active EP2634426B1 (fr)

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EP20120157913 EP2634426B1 (fr) 2012-03-02 2012-03-02 Pompe à deux étages

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Application Number Priority Date Filing Date Title
EP20120157913 EP2634426B1 (fr) 2012-03-02 2012-03-02 Pompe à deux étages

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EP2634426A1 EP2634426A1 (fr) 2013-09-04
EP2634426B1 true EP2634426B1 (fr) 2014-05-14

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017200212B4 (de) * 2017-01-09 2021-12-16 Hawe Hydraulik Se Zweistufenpumpe mit Umschaltventil
DE102017012400B3 (de) 2017-01-09 2022-06-09 Hawe Hydraulik Se Zweistufenpumpe mit Umschaltventil

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2172665B (en) * 1985-02-06 1988-07-27 Aisin Seiki Hydraulic pump assemblies
JPH048318Y2 (fr) * 1986-02-27 1992-03-03
JPS63131873A (ja) * 1986-11-21 1988-06-03 Kosumetsuku:Kk 急速昇圧式プランジヤポンプ
DE19743747B4 (de) 1997-07-19 2013-07-18 Gustav Klauke Gmbh Kolbenpumpe

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