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
  • F04B1/047—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 outer 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
  • 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
  • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2/00—Rotary-piston machines or pumps
  • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
  • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
  • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
  • F04C2/348—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the vanes positively engaging, with circumferential play, an outer rotatable member

Definitions

• the invention relates to a positive displacement pump - in particular an oscillating positive displacement pump - with at least one piston which is relatively movable in a pump housing while changing the shape of a working space.
• Piston machines offer a work space that changes periodically and is filled with a fluid; its pressure changes with compression, decreases with expansion.
• the essential geometric size is the stroke volume as the change in the working space caused by the displacer during a cycle.
• Pumps of this type are generally driven in the classic unit design, ie the pump and motor are connected on a base plate or via a lantern in the alignment of both shaft axes by a coupling element which transmits the necessary drive power.
• the direct coupling of the motor is an exception;
• the pump shaft is designed as a hollow shaft on the drive side in such a way that the motor shaft is inserted and a torque can then be transmitted.
• a pump body is mounted in a rotor sleeve and is provided with longitudinal grooves extending from its circumferential surface for receiving pistons therein — associated with energy stores;
• Each piston is assigned a bolt-like or needle-like body on its head surface facing the 5 rotor sleeve, on the outer surface of which the inner surface of the rotor sleeve rests.
• the latter should advantageously be rotatably mounted around the pump body.
• the pump body runs eccentrically in cross section in the rotor sleeve; in a particularly favorable embodiment, the inner bore of the rotor sleeve is arranged eccentrically in this. In any case, there is an existing between these two parts
• the pump body is arranged with two or more longitudinal grooves - arranged radially and evenly distributed on the circumference - centrally to the pivot point of the drive motor so that the pistons inserted into the longitudinal grooves are guided by the rotating one
• the longitudinal grooves in the pump body are advantageously arranged at an angle to the cross-section of the diameter; the cross-sectional longitudinal axis of the longitudinal groove delimits an angle of approximately 20 ° to 40 °, in particular approximately 25 °, with one of the diameter lines of the pump body.
• a preferred positive displacement pump is characterized by two 35 pairs of longitudinal grooves, the orifices of which are offset from one another by 90 ° on the circumferential surface of the pump body; because two such longitudinal grooves are approximately opposite each other on a straight line in diameter. associated mouths, the mouth centers according to the invention being located on different sides of the assigned diameter straight line at a distance from it, that is to say they are offset from one another.
• the invention is not limited to the configuration described with two pairs of longitudinal grooves; a larger number of such pairings can also be provided.
• a channel-like longitudinal indentation in the head surface of the cross-sectionally flat piston as a bearing for the bolt-like or needle-like body formed by a bearing needle; approximately at right angles to the longitudinal indentation or the top surface of the flat piston should run in this recesses for receiving a force accumulator.
• Each of these recesses is preferably located next to the cross-sectional longitudinal axis of the longitudinal groove; The purpose of this offset is to increase the ridge surface on the bearing pressure side.
• the energy storage device which is designed as a coil spring and is supported on the groove base of the longitudinal groove, the flat piston is held at a variable distance from the groove base. The energy accumulator ensures that the piston is fixed without play via the head needle bearings to the eccentric rotor sleeve.
• the underside of the flat piston and the bottom of the groove determine the height of a conveying or working space which is delimited on both sides by groove walls. This should be connected to the needle bearing by at least one bore provided between the underside of the flat piston and its longitudinal molding.
• the rotor sleeve in the displacement pump has ball bearings on both ends and is closed on both ends by a pump cover.
• these pump covers which are arranged on the right and left of the pump body, have corresponding valves in order to generate a delivery process of the delivery medium from the suction to the pressure side of the pump according to the invention from the stroke movement of each flat piston.
• the Individual delivery rooms or delivery chambers - equal to the number of flat pistons selected in each case - are combined in the pump covers and form the connections for the suction and pressure lines via the motor covers.
• this structural design can be represented both in a direct current and in an alternating current motor version.
• the choice of the number of flat pistons and the choice of a relatively wide range of changed strokes - changing the eccentricity of the inner bore of the rotor sleeve - for a "size” means the delivery quantities "quantity” and "pressure” in changed a wide range.
• a particular advantage over conventional positive displacement pumps is improved security against "seizing" of the delivery elements, since the delivery pressure always decreases on both sides in the lubrication gap between the pump body and the flat piston, whereby the pressure component from the delivery chamber does not act in the direction of the slide bearing surfaces, as is the case with for example, the case with a screw pump.
• the hydrostatic pressure in the lubricating gap increases to the same extent with increasing delivery pressure.
• the classic design of the rotor of a three-phase motor consists of the laminated core of the cage rotor on a drive shaft with the cast-out cage grooves as a short-circuit rotor. If you replace the drive shaft - within the framework of the necessary minimum dimensions of the cage bars - with the rotor sleeve according to the invention and change the motor housing cover in the manner described, then the complete motor / pump / unit is formed. With such a design, there is no shaft seal, which is commonly known as the weakest link in pumps with an emerging shaft end. At the same time, the "hermetically sealed" pump can be achieved without additional additions at a cost which corresponds approximately to that of a simple unit structure. The alignment of the motor and pump which is usually necessary in the case of the classic assembly structure in order to ensure the proper functioning of the intermediate clutch is also eliminated in the present invention.
• the - mentioned - design as a DC or single-phase machine is also possible;
• the rotor winding is replaced by a package of permanent magnets - known from the magnetic couplings. This enables small designs (here the system diameter) and opens up a wide field of application for the large-scale production of small pumps with high pressure ranges.
• the drive takes place by means of a toothed or V-belt engaging on that outer rotor.
• This makes it possible to use it as a flange-mounted auxiliary unit on all types of engines. If one replaces the outer rotor with magnets, including the toothed or V-belt elements, for example by a DC or commutatorless three-phase stator, the use of the pump generally described above can be seen; Because of the dimensions, this pump is particularly suitable for mobile use.
• Fig. 2 a partially sectioned side view of the tangential piston pump
• FIG. 3 shows a partially sectioned side view of the tangential piston pump as a three-phase short-circuit machine
• FIG. 4 the longitudinal section through the tangential piston pump, enlarged compared to FIG. 3;
• FIG. 5 shows an enlarged cross section through a central part of FIG. 1 and its section line V - V;
• FIG. 6 a detail from FIG. 5;
• a rotor sleeve 20 of the inner diameter d which surrounds a pump body 22 of circular cross-section of the diameter e, is mounted in a tubular housing 16 - closed on both ends by fastening strips 12 having housing covers 14 - in the region of ball bearings 18.
• the longitudinal axis of the pump body 22 is denoted by A, and four longitudinal grooves 24 are arranged in it with a groove base 26 which is rounded in the form of a partially circular circle in such a way that, in the example shown, their cross-sectional longitudinal axes Q with the central cross-sectional axis M, which defines a straight line, or the transverse axis perpendicular to this B of the pump body 22 limit an angle w of approximately 25 °.
• the center of the mouth 25 of the longitudinal grooves 24 on the body circumference is offset laterally by a dimension i to the corresponding cross-sectional central axis M or the transverse axis B, and the cross-sectional longitudinal axes Q of the two longitudinal grooves 24 on the cross-sectional central axis M run parallel to one another as well as the cross-sectional longitudinal axes Q of the two longitudinal grooves 24 assigned to the transverse axis B.
• Each longitudinal groove 24 of cross-sectional width a receives a flat piston 30, in the outwardly directed head surface 32 of which a bearing needle 36 rests in an indentation 34 extending in its longitudinal direction - the width b of its part-circular cross-section;
• a minimum stroke is sufficient for the representation of the delivery volume - with a corresponding selection of the number of pistons.
• the maximum stroke is in the range of 2 to 6.5 mm. The consequence of this is that the known disadvantages of oscillating displacement pumps with regard to the pulsating flow can be reduced to a minimum. If there is more than one flat piston 30, the pressure pulsation which forms at the pressure port of the pump 10 is thus also greatly reduced.
• the piston movement during the suction stroke ie the running of the flat piston 30 in the area of the diameter increase or the positive eccentricity of the inside diameter d of the rotor sleeve 20 takes place through the pretensioning force of springs inserted into the recesses 38 of the flat piston 30 as a force accumulator 40 and the lubrication of the needle bearing on Piston head 32 of the flat piston 30 through the medium through the arrangement of holes 46 or the like. Connections of the delivery chamber 28 remaining in the longitudinal groove 24 to the bearing recess or longitudinal indentation 34 in the piston head 32.
• a wide range of the lubricating properties of the delivery medium (also v ⁇ 1 mm ⁇ 2 / sec.) Can be achieved by appropriate choice of material and surface of the needle bearing parts hydrostatic lubrication can be maintained since the lubrication pressure always increases with the delivery pressure.
• the motor stator is not sealed off from the pumped medium. If required, the stator can be given a thin-walled tube made of the classic materials of this application, as in the known "canned motor". For aggressive media - e.g. in chemistry - due to the negligible lubrication limit due to the lack of plain bearing conditions, a wide range can be covered by appropriate choice of materials for pump body parts and the flat pistons.
• the stator housing Since no classic fan can be arranged on the motor shaft in this construction, the stator housing must be provided with appropriate surface cooling. In any case, however, a certain amount of the magnetic heat loss is absorbed by the circuit of the leakage currents that flow through the bearings on the stator to the suction side and by the heat conduction of the squirrel-cage rotor / rotor sleeve.
• the rotor sleeve 20 can also be driven via a magnetic coupling.
• the rotor sleeve 20 of the tangential piston pump 10 a according to FIGS. 7, 8 carries at least one sleeve-like magnetic element 50 on its axially parallel outer contour.
• the inner magnet element 50 runs in a gap 56 parallel to the longitudinal axis A.
• the outer rotor 54 on the magnetic coupling 52 formed by the magnetic elements 50, 51 is driven by a toothed or V-belt 64.
• the drive torque - coming from an outer shaft - is supplied to the pump body 22 on the inside via the magnetic coupling 52, which in particular detects the two rotors 20, 54.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Reciprocating Pumps (AREA)
• Polysaccharides And Polysaccharide Derivatives (AREA)
• Electrically Driven Valve-Operating Means (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)

Applications Claiming Priority (3)

Publications (2)

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• 2001
  • 2001-07-06 EP EP01971753A patent/EP1299643B1/fr not_active Expired - Lifetime
  • 2001-07-06 AU AU2001291662A patent/AU2001291662A1/en not_active Abandoned
  • 2001-07-06 AT AT01971753T patent/ATE306019T1/de active
  • 2001-07-06 DE DE50107621T patent/DE50107621D1/de not_active Expired - Lifetime
  • 2001-07-06 WO PCT/EP2001/007776 patent/WO2002004812A1/fr not_active Ceased
  • 2001-07-06 DE DE10132298A patent/DE10132298A1/de not_active Withdrawn

Non-Patent Citations (1)

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