EP2634426A1 - Pompe à deux étages - Google Patents

Pompe à deux étages Download PDF

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Publication number
EP2634426A1
EP2634426A1 EP12157913.0A EP12157913A EP2634426A1 EP 2634426 A1 EP2634426 A1 EP 2634426A1 EP 12157913 A EP12157913 A EP 12157913A EP 2634426 A1 EP2634426 A1 EP 2634426A1
Authority
EP
European Patent Office
Prior art keywords
pressure
stage pump
valve
chamber
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.)
Granted
Application number
EP12157913.0A
Other languages
German (de)
English (en)
Other versions
EP2634426B1 (fr
Inventor
Georg Neumair
Johannes Glaser
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.)
Hawe Hydraulik SE
Original Assignee
Hawe Hydraulik SE
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 Hawe Hydraulik SE filed Critical Hawe Hydraulik SE
Priority to EP20120157913 priority Critical patent/EP2634426B1/fr
Publication of EP2634426A1 publication Critical patent/EP2634426A1/fr
Application granted granted Critical
Publication of EP2634426B1 publication Critical patent/EP2634426B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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.
  • 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 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.
  • the pressure valves are connected to one another via a housing channel connected to the pressure outlet.
  • the housing channel leads into the chamber containing the switching valve.
  • 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 can be 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP20120157913 2012-03-02 2012-03-02 Pompe à deux étages Active EP2634426B1 (fr)

Priority Applications (1)

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

Applications Claiming Priority (1)

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

Publications (2)

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

Family

ID=45841236

Family Applications (1)

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

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EP (1) EP2634426B1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180195510A1 (en) * 2017-01-09 2018-07-12 Hawe Hydraulik Se Dual-stage pump with switching valve
DE102017012400B3 (de) 2017-01-09 2022-06-09 Hawe Hydraulik Se Zweistufenpumpe mit Umschaltventil

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4778350A (en) * 1986-02-27 1988-10-18 Aisin Seiki Kabushiki Kaisha Hydraulic pump assemblies
US4840544A (en) * 1985-02-06 1989-06-20 Aisin Seiki Kabushiki Kaisha Hydraulic pump assembly associated with accumulator
US4850828A (en) * 1986-11-21 1989-07-25 Kabushiki Kaisha Kosmek Plunger pump of quick pressure-rise type
DE19743747A1 (de) 1997-07-19 1999-01-21 Klauke Gmbh Gustav Kolbenpumpe

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4840544A (en) * 1985-02-06 1989-06-20 Aisin Seiki Kabushiki Kaisha Hydraulic pump assembly associated with accumulator
US4778350A (en) * 1986-02-27 1988-10-18 Aisin Seiki Kabushiki Kaisha Hydraulic pump assemblies
US4850828A (en) * 1986-11-21 1989-07-25 Kabushiki Kaisha Kosmek Plunger pump of quick pressure-rise type
DE19743747A1 (de) 1997-07-19 1999-01-21 Klauke Gmbh Gustav Kolbenpumpe

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180195510A1 (en) * 2017-01-09 2018-07-12 Hawe Hydraulik Se Dual-stage pump with switching valve
DE102017200212A1 (de) 2017-01-09 2018-07-12 Hawe Hydraulik Se Zweistufenpumpe mit Umschaltventil
ES2685458A1 (es) * 2017-01-09 2018-10-09 Hawe Hydraulik Se Bomba de dos etapas con válvula de conmutación.
US10851909B2 (en) * 2017-01-09 2020-12-01 Hawe Hydraulik Se Dual-stage pump with switching valve
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

Also Published As

Publication number Publication date
EP2634426B1 (fr) 2014-05-14

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