EP1736666B1 - Pumpengetriebe - Google Patents

Pumpengetriebe Download PDF

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Publication number
EP1736666B1
EP1736666B1 EP06011681A EP06011681A EP1736666B1 EP 1736666 B1 EP1736666 B1 EP 1736666B1 EP 06011681 A EP06011681 A EP 06011681A EP 06011681 A EP06011681 A EP 06011681A EP 1736666 B1 EP1736666 B1 EP 1736666B1
Authority
EP
European Patent Office
Prior art keywords
crankshaft
pump
mechanism according
pump mechanism
connecting rod
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.)
Active
Application number
EP06011681A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1736666A1 (de
Inventor
Dirk Petersen
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.)
SPX Flow Technology Germany GmbH
Original Assignee
Bran und Luebbe 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 Bran und Luebbe GmbH filed Critical Bran und Luebbe GmbH
Priority to DE202006020806U priority Critical patent/DE202006020806U1/de
Publication of EP1736666A1 publication Critical patent/EP1736666A1/de
Application granted granted Critical
Publication of EP1736666B1 publication Critical patent/EP1736666B1/de
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
    • 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
    • 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
    • F04B1/0413—Cams
    • 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
    • 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
    • F04B53/006—Crankshafts

Definitions

  • the invention relates to a pump gearbox having a plurality of cylinders, the axes of which are arranged with predetermined angles enclosing a crankshaft, and whose pistons or diaphragms are each operatively connected to a connecting rod mounted on a separate crankshaft on the crankshaft, the crankshafts having a predetermined angular offset from each other, and this angular offset, in agreement with the angles which enclose the cylinder axes, is chosen such that the phase shifts between every two pistons of the cylinders successively actuated during one revolution of the crankshaft are the same.
  • Multi-cylinder pump transmissions are used in process pumps for conveying large flow rates or at high pressures.
  • pumpheads usually diaphragm pump heads are used. Since the membranes used in it are only limited deflection, diaphragm pump heads with very large diameter are required for large volumes. If such large diaphragm pump heads are to be operated with a multi-cylindrical gear, therefore, the distances between the pump head holder and the cylinder must be large enough.
  • the individual cylinders are usually arranged in parallel and horizontally mounted on a likewise horizontal crankshaft. In this case, a large cylinder spacing in the connection area for the pump heads also means a large bearing clearance on the crankshaft.
  • crankshaft With several cylinders and large pump heads, the crankshaft must be designed accordingly long. This in turn requires special properties of the crankshaft, in particular with regard to stability and flexural rigidity. This and the high space requirements result in high costs for production and warehousing. This is followed by efforts to develop efficient pump transmissions, which have a smaller footprint.
  • the DE 199 18 161 A1 discloses a compressor of a refrigerant compressor plant, wherein the cylinders are arranged at a V-shaped angle less than 90 ° to each other.
  • the compressor shaft is mounted at its two ends in corresponding bearings.
  • Eccentric are arranged between the bearing sections of the compressor shaft, wherein for each individual piston in each case an eccentric is provided, which is arranged at a distance from the other individual eccentric for the respective other piston.
  • a pump gearbox having a plurality of cylinders, the axes of which are arranged predetermined angles enclosing a crankshaft, and whose pistons are each articulated by a crankshaft mounted on a crankshaft connecting rod, each connecting rod is mounted on its own Kurbelkröpfung, and the crankshafts have a predetermined angular offset from each other.
  • the angular offset of these crankcases is according to the invention in vote to the angles which include the cylinder axes, chosen so that the phase shifts between each two successive actuated at a revolution of the crankshaft piston of the cylinder are the same size.
  • the sum of all angles which enclose the cylinder axes is inventively less than or equal to 180 ° and the cylinder axes are all in a plane perpendicular to the crankshaft or their mutual height offset in the direction of the crankshaft axis corresponds to a maximum of Pleueldicke.
  • the angles which enclose the cylinder axes are to be seen in projection on a plane perpendicular to the longitudinal axis of the crankshaft.
  • the cylinder axes do not intersect, as the points of engagement of the connecting rods are offset at the respective crankshafts along the longitudinal axis of the crankshaft.
  • the cylinder axes intersect in the crankshaft and radiate from this.
  • the angular distribution between the cylinder axes can be chosen almost arbitrarily around the crankshaft. Only the minimum angle between two adjacent cylinder axes is given by the dimensions of the cylinder and the pump heads to be connected and the sum of all included angles must not exceed 180 °. Both symmetrical arrangements with regular angular distances of the cylinders and asymmetric arrangements are possible.
  • the multiple possibilities of geometric arrangement have the advantage that the pump can be adapted to many different structural conditions, for example when it is to be integrated into a more complex system.
  • the cylinders are arranged so that the sum of the included by the cylinder axes angle is less than or equal to 180 °.
  • the cylinder axes are therefore not distributed around the crankshaft, but protrude from the crankshaft only in a half-space. That is, there are preferably two outermost cylinders whose axes enclose an angle smaller than 180 ° with each other, or which extend in parallel in opposite directions from the crankshaft. In the event that the pump gear has more than these two outermost cylinders, they are fan-shaped distributed between the two outermost cylinders, while in the second half space no cylinder axes protrude.
  • the asymmetric cylinder distribution is taken into account by the angular offset of the crankshafts, so that nevertheless a uniform flow rate is achieved.
  • the restriction of the space for cylinder connections to 180 ° has the advantage that all cylinders, for example for maintenance, are accessible from one side.
  • the phase difference is 90 ° for two consecutively actuated cylinders. In this way it is ensured that the partial flow rates of the individual cylinders overlap uniformly and no excessive pressure pulsations occur. Due to the angular offset of the crankshafts can therefore be a uniform flow with any angular positions of the cylinder axes.
  • the inventive pump transmission is particularly suitable for the cultivation of piston diaphragm pump heads.
  • piston diaphragm pump heads For trouble-free operation of piston diaphragm pump heads, horizontally located piston axes with vertically aligned superimposed valve connections are to be preferred.
  • the crankshaft is therefore expediently mounted vertically standing, wherein the cylinder axes point horizontally radially away from this.
  • the articulation of the piston through the connecting rods is preferably carried out via a crosshead, which receives the transverse portions of the outgoing from the crankshaft rotational movement of the connecting rod.
  • crankshafts for the individual connecting rods and cylinders are distributed along the longitudinal axis of the crankshaft.
  • the crankshafts are so close together that the connecting rods slide on each other without appreciable spatial separation. If the connections from the connecting rod to the crosshead and from the crosshead to the cylinder piston are centered, this also results in a corresponding height offset of the cylinder axes by one connecting rod thickness.
  • the cylinder axes are then, in fact, fan-like or similar to the steps of a spiral staircase from the crankshaft.
  • the pump gear according to the invention has three cylinders. In a distribution of the cylinder axes to 180 °, these can each be at an angle of 90 ° to each other.
  • the three cylinder axes are distributed only over an angular range of 90 ° and the individual cylinders are then at an angle of 45 ° to each other.
  • This arrangement allows an even more compact design of the pump.
  • the accessibility from one side is further improved.
  • the pump gearbox can be driven, for example, with a worm gear or an external geared motor which can be coupled directly to the crankshaft. Therefore, in a preferred development, the crankshaft has both a clutch for such an external transmission and a connecting device for a worm gear. If the pump gear is surrounded by a housing, both drive options are expediently possible with the same base variant of a housing.
  • the worm gear can then be integrated into the housing, while the external gear can be mounted in extension of the crankshaft outside of the housing.
  • the drive motor is then either mounted to the drive via the worm gear directly to the side of the housing, or to the drive via the external gear following it. With both types of drive, a stroke frequency suitable for diaphragm pumps can be generated.
  • Such a frequency is usually less than 250 strokes per minute.
  • the drive of the pump gear via a worm gear has the advantage that a plurality of pump gear can be chained horizontally via a compound of the screw shafts. A vertical linking of several pump transmissions is possible with both types of drive.
  • the crankshafts of several pumps can be coupled to each other. Both an equal and a mutual arrangement of the pump heads is possible.
  • the crankshaft is driven by a worm gear.
  • the drive motor whose axis is naturally perpendicular to the crankshaft, mounted so that its axis with the axis of the middle cylinder forms an angle of less than or equal to 135 °.
  • Cylinder and drive motor are then arranged fan-shaped around the crankshaft. If the worm engages in the vicinity of the crankshaft crankshaft, the crankshaft can be designed correspondingly short, and a particularly compact flat design of the pump is possible.
  • the cylinders are each offset by a connecting rod thickness, in the direction of the longitudinal axis of the crankshaft, and are not in one plane. This may require an increased effort when connecting the pump, for example in the piping.
  • This constructive disadvantage can be avoided in a preferred embodiment by one or more connecting rods are angled so that the crankshaft remote from the outer ends of all connecting rods lie in one plane, while the other ends naturally next to each other or, for a vertical crankshaft, one above the other on the crankshaft are stored.
  • at least two such angled connecting rods are necessary so that all connecting rod ends facing away from the crankshaft can lie in one plane.
  • the height offset of the cylinder axes is circumvented by the fact that either the connecting rods on the crossheads or the crossheads on the pistons engage eccentrically. In this way, the crosshead tracks, or at least the cylinder pistons, can already be brought into a plane. It is also appropriate to combine both measures.
  • crankshaft For the assembly of the connecting rod on the crankshaft, this is preferably composed lengthwise of at least two parts. The division is expediently in the range of crankcases.
  • the torque transmission is then ensured by a positive shaft-hub connection. Possible embodiments include a multi-tooth or polygonal profile or a feather key.
  • a split crankshaft allows the use of several similar connecting rods, but at least of connecting rods with the same shaped closed main bearings, for all cylinders. As a result, warehousing and production costs can be reduced or kept low.
  • the crankshaft For three- or four-cylinder pump transmissions, the crankshaft must be composed of at least two parts. With a larger number of cylinders correspondingly more parts are necessary.
  • an undivided crankshaft for a pump transmission having at least three cylinders, preferably at least one main bearing of a connecting rod on a split bearing shell.
  • a three-cylinder gearbox then expediently carried the middle Pleuelhauptlager divided.
  • the assembly of more than two connecting rods on an undivided crankshaft can alternatively also by different diameter of the connecting rod main bearings are made possible.
  • the crankshaft itself is preferably mounted at its ends, on both sides of the crank cranks, in at least two main bearings.
  • both sliding and rolling bearing technology can be used.
  • the pump gearbox is installed in a housing.
  • the housing is preferably made of one part and equipped for installation, each with a closable opening in the bottom and rear wall. Through these openings, the inner workings of the pump, so the one- or multi-part crankshaft and the connecting rods are mounted.
  • the crosshead lift tracks of the cylinder and the pump head holder are integrated into the housing.
  • the individual pump head holders can then be interconnected. This has the advantage that pressure differences in the housing, which arise from the oscillating movements of the crossheads and pistons, even with sealed housing openings can be compensated because the required air mass balance between the cylinders can take place.
  • the interconnected housing volumes can be used in special construction variants of diaphragm pump heads as a reservoir for hydraulic oil.
  • the object of the invention is also achieved by a pump with a pump transmission according to the invention.
  • diaphragm pump heads are connected to the pump head holders of the cylinder.
  • Fig. 1 shows a possible geometric arrangement of the pump gear 10 according to the invention with three cylinders 11 seen from above. These cylinders 11 point horizontally radially away from the vertically oriented crankshaft 12. They are arranged symmetrically in this embodiment and include in the projection shown on a plane perpendicular to the crankshaft 12 in each case an angle W Z with each other.
  • a pump transmission 10 is shown in more detail with the same geometry.
  • the sectional plane of the drawing passes through the uppermost mounted connecting rod 15.
  • the other two connecting rods 15 are mounted without a distance directly below the uppermost connecting rod 15 on the crankshaft 12.
  • the vertical crankshaft 12 is driven by a horizontal worm gear 18 with a drive motor 19.
  • the three connecting rods 15 are each mounted on a separate crank 14. At their other, the crankshaft 12 facing away from the end, they are hinged to a crosshead 16. This converts the rotational movement of the connecting rod 15 in a linear movement. This movement is transmitted via a piston rod to a piston 13. This in turn directs the membranes of the connected pump heads 22.
  • Fig. 3 shown in vertical section. Here, the distance from one another superimposed on the crankshaft 12 connecting rod 15 are visible.
  • the crankshaft 12 with the directly superimposed cranks 14 is in Fig. 4 again shown in detail in side view.
  • the cranes appear horizontally shifted in this view, but in fact they have an angular offset W K to each other, as in Fig.
  • one or more connecting rods 15 can be designed angled, so that the connecting rod ends facing away from the crankshaft 12 all lie in a horizontal plane.
  • Fig. 7 shows a vertical crankshaft 12 with three connecting rods mounted thereon, wherein the middle connecting rod is straight and both the upper and the lower connecting rod 15 are angled such that the ends are all on the plane AA of the central connecting rod 15.
  • Fig. 8 This is again shown in plan view of the vertical crankshaft 12.
  • the kinks in the two outer connecting rods are represented by lines 24.
  • FIG. 9 again shows a pump gear in vertical section.
  • a cross-head track 25 can be seen in section and behind perspective the opening to an adjacent cross-head track.
  • Both brutkopraufbahnen are at the same height despite superimposed on the crankshaft 12 mounted un-angled connecting rod 15.
  • the height offset b is here compensated by the fact that the connecting rods on the crosshead not centrally attack, but, depending on the position on the crankshaft, either below or above the center of the crosshead 16.
  • the bottom of the lowest crank 14 mounted connecting rod 15 then attacks below the center of the crosshead 16 at. This is in detail in Fig. 10 on the far left.
  • the middle connecting rod 15 which acts in the center of the crosshead 16 to see. Right attacks the uppermost connecting rod 15 accordingly above the center of the crosshead 16.
  • Fig. 11 shows another embodiment in which the Wienkopflaufbahnen 25 still have a height offset. This is compensated only in the transmission of the movement of the piston 13, in which this is articulated according to above or below the crosshead center.
  • Fig. 12 shows a pump gear according to the embodiments in Fig. 2 and 3 in vertical section, but here with an external gear 17. This is coupled to the upper end of the vertically mounted crankshaft 12. This is followed by the drive motor 19.
  • crankshaft 12 is designed to be divisible in a specific embodiment.
  • Fig. 13 shows such a crankshaft 12 in longitudinal section.
  • the pitch is in the range of crankcases 14.
  • the illustrated crankshaft 12 is composed of three parts 12.1, 12.2 and 12.3.
  • Fig. 14 shows a compact pump gear 10 in a housing 20.
  • the individual Kreuzkopflaufbahnen 25 are connected via housing openings 23 with each other.
  • This variant has, as well as in Fig. 1-3 shown, a symmetrical angular distribution of the cylinder over 90 °.
  • the drive motor is additionally arranged at an angle of 135 ° relative to the middle cylinder. This special arrangement allows a particularly compact design of the pump gear according to the invention. Depending on the size of the pump heads used, the angle between the cylinders and the drive motor can be chosen even lower.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Transmission Devices (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP06011681A 2005-06-24 2006-06-06 Pumpengetriebe Active EP1736666B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE202006020806U DE202006020806U1 (de) 2005-06-24 2006-06-06 Kurbelwelle einer Kolbenpumpe

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005029481A DE102005029481B4 (de) 2005-06-24 2005-06-24 Pumpengetriebe

Publications (2)

Publication Number Publication Date
EP1736666A1 EP1736666A1 (de) 2006-12-27
EP1736666B1 true EP1736666B1 (de) 2009-12-09

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ID=36915746

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06011681A Active EP1736666B1 (de) 2005-06-24 2006-06-06 Pumpengetriebe

Country Status (7)

Country Link
US (2) US9097249B2 (zh)
EP (1) EP1736666B1 (zh)
JP (1) JP5060071B2 (zh)
CN (1) CN1932286A (zh)
AT (1) ATE451550T1 (zh)
DE (3) DE102005029481B4 (zh)
ES (1) ES2341179T3 (zh)

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RU2697590C2 (ru) * 2015-01-22 2019-08-16 ЭсПиИкс ФЛОУ ТЕКНОЛОДЖИ ДЖЕРМАНИ ГМБХ Технологический насос с кривошипным механизмом
US11310959B2 (en) 2018-06-22 2022-04-26 Andreas Stihl Ag & Co. Kg Tool head for a hand-guided implement and implement having a tool head

Also Published As

Publication number Publication date
DE502006005562D1 (de) 2010-01-21
CN1932286A (zh) 2007-03-21
DE202006020806U1 (de) 2010-04-15
DE102005029481B4 (de) 2008-04-10
US9097249B2 (en) 2015-08-04
JP5060071B2 (ja) 2012-10-31
ES2341179T3 (es) 2010-06-16
DE102005029481A1 (de) 2006-12-28
ATE451550T1 (de) 2009-12-15
US20150300331A1 (en) 2015-10-22
EP1736666A1 (de) 2006-12-27
US20070098580A1 (en) 2007-05-03
JP2007002848A (ja) 2007-01-11

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