WO2004088141A2 - Pompe - Google Patents

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Publication number
WO2004088141A2
WO2004088141A2 PCT/EP2004/050435 EP2004050435W WO2004088141A2 WO 2004088141 A2 WO2004088141 A2 WO 2004088141A2 EP 2004050435 W EP2004050435 W EP 2004050435W WO 2004088141 A2 WO2004088141 A2 WO 2004088141A2
Authority
WO
WIPO (PCT)
Prior art keywords
pump
housing
particular according
valve
piston
Prior art date
Application number
PCT/EP2004/050435
Other languages
German (de)
English (en)
Other versions
WO2004088141A3 (fr
Inventor
Sabine Meier
Sven Engelbrecht
Uwe Drewes
Rudolf Bahnen
Original Assignee
Gebr. Becker Gmbh & Co. Kg
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
Priority claimed from DE10319671A external-priority patent/DE10319671A1/de
Application filed by Gebr. Becker Gmbh & Co. Kg filed Critical Gebr. Becker Gmbh & Co. Kg
Priority to US10/549,968 priority Critical patent/US20070104600A1/en
Priority to JP2006505520A priority patent/JP2006522265A/ja
Priority to EP04725395A priority patent/EP1608874A2/fr
Publication of WO2004088141A2 publication Critical patent/WO2004088141A2/fr
Publication of WO2004088141A3 publication Critical patent/WO2004088141A3/fr

Links

Classifications

    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F04C21/00—Oscillating-piston pumps specially adapted for elastic fluids
    • 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
    • F04C21/00—Oscillating-piston pumps specially adapted for elastic fluids
    • F04C21/002—Oscillating-piston pumps specially adapted for elastic fluids the piston oscillating around a fixed axis
    • 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
    • F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C2220/00—Application
    • F04C2220/10—Vacuum

Definitions

  • the invention relates to a pump with at least two pump pistons moving on a common circular path.
  • the invention is concerned with a novel pump with at least one pump piston moving on a circular path and a pump housing, the pump piston, possibly rigidly coupled with one or more further pump pistons, oscillating about an axis of rotation on a movement path having two reversing positions , whereby medium is discharged further via an outlet valve and an inlet valve is opened in the course of a movement from one reversal position into the other reversal position, after which a discharge is discharged on a respective pressure side of the pump piston in the course of a pressure build-up and on a suction side of the Pump piston suction of the medium takes place.
  • the pump is comparatively simple
  • the inlet valve is overflowed during the movement from one reversing position to the other reversing position.
  • the pump pistons move in a pump room.
  • the pump chamber is formed radially on the inside by an inner wall which is preferably designed to be rotationally fixed with the pump pistons. As far as several pump pistons are provided, it is preferably also the connecting wall between two or more pump pistons.
  • the housing wall which delimits the pump space radially on the outside is suitably designed to be fixed.
  • the inlet valve can be formed in the pump chamber floor and / or in the pump chamber ceiling and / or in the outer housing wall and / or in the housing partition.
  • the pump chamber is limited in the direction of movement of a pump piston - on both sides - by a fixed housing partition.
  • the housing partition walls separate the two pump chambers. This housing partition allows the pressure to be built up - to a desired extent - when the pump piston is moved into the reverse position.
  • the outlet valve is preferably designed as a check valve.
  • the outlet valve can be formed in the housing partition and / or in the pump chamber floor and / or in the pump chamber ceiling and / or in the outer housing wall.
  • the pump can be driven, for example, by an electric motor. But also by another engine. In detail, as explained below, it is advisable to carry out the power transmission by means of a crankshaft. It can also be an electric motor that directly generates the back and forth movement. In more detail, the electric motor can be a conventional universal motor. But it can also be a so-called reluctance motor. For the immediate generation of the back and forth movement, for example, is suitable. a stepper motor. In addition, an electrical or electromagnetic spring / mass system can be provided for the drive. Mass balancing must be ensured.
  • the arrangement of the axes of the drive and pumps is important here, for example if two pumps are connected with a central drive.
  • the reverse positions of the pistons of both pumps are in phase. In the intermediate positions, however, there are different angular positions and a phase deviation dependent on the position of the center points. This can be minimized by targeted height adjustments between the drive axis and the pump axis.
  • crankshaft When the drive force is transmitted to the pump by means of a crankshaft, it is also advisable to drive two or more such pumps at the same time.
  • the crankshaft enables the engine, in particular the electric motor, to move continuously.
  • the angle-limited back and forth movement of the pump or the pump pistons is generated by means of connecting rods acting on the crankshaft in a manner known per se, comparable to an Otto engine or a diesel engine in the automotive field.
  • the two such pumps which are preferably driven via the same crankshaft, then suitably move in opposite directions.
  • sealing lips can also be used on one of the several of the sealingly interacting surfaces and / or in the course of operation of the pump a coating is applied to one of the surfaces that interact with one another.
  • the reciprocating movement, oscillating movement, of the piston is carried out in such a way that the housing partition is preferably not touched.
  • the housing partition wall can be designed such that the distance to the associated piston surface is constant in the circumferential angle range of greatest approximation via a radial. However, it can also be selected (straight surface) so that there is a wedge-shaped, (radially) outwardly widening gap between the assigned surfaces in the position mentioned.
  • the range of rotation of a piston is preferably approximately 90 °. However, it can also go beyond this, for example up to + / - 30 °, in which case corresponding intermediate stages such as 95 °, 100 °, 105 °, 110 ° etc., as well as angle ranges still in between, must also be included. The same applies to values below 90 °. In this way you can achieve a coordination between the respective loading volume and the piston size.
  • the pump pistons themselves preferably consist of a light material such as aluminum. It is more preferably an extruded profile (although this is not bound to the material aluminum).
  • the construction is designed in such a way that the large masses are pushed radially outwards as far as possible with respect to the axis of rotation of the pump pistons. Overall, the moving masses should be as small as possible due to the moments of inertia, which is why a lightweight material such as aluminum is recommended for the moving masses.
  • the pump pistons When designed as an extrusion profile, the pump pistons have corresponding cavities. These can be closed with a lid at the top and bottom.
  • the height of the pump pistons or their extension in the axial direction of the common axis of rotation preferably corresponds approximately to a diameter from the axis of rotation to the outer circumferential wall of a pump piston. The aim is to minimize the column.
  • An inlet valve can be designed as a simple permanent opening. For example in the form of a hole or in the form of a groove. In addition, it can also be designed as a check valve (e.g. ball valve). In the pump with two pump pistons, four outlet valves and two inlet valves are provided. However, four inlet valves can also be provided if, for example, the other two are each activated.
  • inlet valve and the outlet valve can be assigned to the same end region of the movement path, that is to say in detail to a respective retracting position.
  • Inlet valve and outlet valve can be provided adjacent to each other. In this regard, it proves to be advantageous if the inlet valve and the outlet valve are arranged in the same housing partition.
  • the inlet valve and / or the outlet valve can in this case be formed from a stamped or bent sheet metal part, with a closure plate assigned to a valve opening and an adjoining bend section.
  • a sheet steel part in particular formed from spring steel, can be provided.
  • the inlet valve and / or the outlet valve further preferably has closure plates and bending sections which merge into one another at the same level. Accordingly, these are preferably arranged offset from one another with respect to a plane.
  • an inlet valve and / or an outlet valve has a mounting foot, which is, for example, clamped, in particular clamped in the area of the housing partition. This bracket foot also merges, at least partially, preferably at the same level into the bending section.
  • the closure plate preferably lies on a sealing support which is clamped between the valve and the associated housing part. It can also be glued on. In the case of the clamp bracket, this is preferred achieved by means of a clamping part or a pressure part.
  • the support can be formed from a plastic part, for example an elastomer.
  • the longitudinal extension of the inlet valve and / or the outlet valve extends in the direction of the axis of rotation of the pump pistons, in particular in the configuration of the valves in the form of stamped or bent sheet metal parts, which essentially consist of a mounting foot, a bending section and a locking plate.
  • a plurality of outlet valves can also be arranged next to one another in the direction of the axis of rotation. It is also conceivable here to arrange a plurality of inlet valves side by side in the direction of the axis of rotation.
  • a parallel positioning of a spring-loaded inlet valve to the outlet valve in the housing partition proves itself in relation to a reduction in the power consumption during suction, i. H. when refilling the pressure chamber, as advantageous. This reduces the pressure difference.
  • the valve - both the inlet valve and the outlet valve - is designed as a lubricant-free spring valve, in further detail preferably as a tongue valve with a seal made of an elastomer.
  • valves in an easily replaceable or. also implementable valve bar are formed. This also means that simply turning the outer edge arrangement from inlet valve to outlet valve or. can be exchanged in reverse. This is important for the possible interconnection of several pumps in series or in parallel. Depending on the situation, the required valve can then be arranged (by turning the valve bar) in such a way that no long gas flow ducts are required.
  • the valve bar is therefore a mirror image of a longitudinal axis educated. Inlet valves and outlet valves are located opposite one another in relation to a central longitudinal axis of the valve bar.
  • valve tongues of the tongue valves are symmetrical.
  • Spring steel is a suitable material, but also Viton, for example. Due to the fact that the valves are flat, a very minimized dead space associated with a reversed position of a piston can be realized.
  • the inlet valves are flush with the surface of the valve rail.
  • a thin wall thickness is realized in the valve strip and / or, on the pump piston, a molded part can additionally be formed to avoid the dead space in front of the valve element.
  • the pump piston can have an opening projection associated with the outlet valve, for the purpose of triggering the outlet valve.
  • an opening projection associated with the outlet valve for the purpose of triggering the outlet valve.
  • a corresponding number of opening projections is provided on the pump piston section.
  • a pump has three, four or more pump pistons, two of which in any case move on a common circular path. If different circular paths are provided, on which two pump pistons each move, these different circular paths are preferably implemented in different pump housings.
  • Each pump housing can have two oscillatingly movable pump pistons, the pump spaces of which are decoupled from one another in the respective pump housing by the housing partition walls ,
  • a common drive is preferably provided for the four pump pistons then given in the example mentioned above, the drive being arranged in one of the then two pump housings, preferably a separate third housing, a drive housing. It is more preferably then a drive housing, to which the two pump housings are assigned adjacent on both sides.
  • the housing - both the drive housing and the pump housing - can be designed as extruded parts. But they can also be castings, for example.
  • a (first) assignment and fixing of the housings to one another can be achieved by joining them together by means of corresponding longitudinal grooves and longitudinal projections (in the direction of the axes of rotation of the pump pistons), which can be provided in a simple manner in the case of extruded parts.
  • these longitudinal grooves and associated projections are generally only to be regarded as assembly aids.
  • a screw connection and / or gluing or other connection between the housings is indicated.
  • a transfer channel can be easily integrated into the housing. It can namely be included in the housing as a cavity which extends in the direction of the axes of rotation of the pump pistons and is subsequently closed on one or both sides by appropriate covers.
  • the pump piston and / or the pump housing can be flocked in the area of an assigned movement gap.
  • This flocking forms a running-in layer, which grinds off in the first working cycles to create a minimum gap.
  • the flakes create an advantageous labyrinth effect.
  • others can also alternative declarations (which also do not have the advantage of a labyrinth seal) can be applied alternatively.
  • a shrunk-in steel shaft can be provided in the pump piston, which is made of aluminum, for example, to form the physical axis of rotation.
  • the geometry of the pump chamber is preferably square, which means that the free path of the pump pistons between the reversed positions corresponds approximately to the extension of the pump chamber in the direction of the axis of rotation.
  • the goal is to minimize the gap lengths. According to the formula, this prefers that the sum of twice the gap length and twice the difference between the outer and inner radius of the pump chamber is minimized.
  • Pump chamber geometries can also be implemented in which the free path of the pump piston between the reversal positions is less than the extension of the pump chamber in the direction of the axis of rotation, and in which the free path of the pump piston is larger than the extension of the pump chamber in the direction the axis of rotation.
  • FIG. 1 shows a schematic plan view of the pumps in a first embodiment
  • Fig. 2 is a schematic perspective view of two interconnected pump pistons 3 shows a schematic view of two pumps driven at the same time by means of a drive;
  • FIG. 3a shows a schematic representation of a crankshaft flanged to the drive
  • Figures 4 to 6 details regarding the sealing and valve actuation of the pump piston against the housing.
  • FIG. 9 is a perspective view of a housing partition with inlet and outlet valves arranged therein;
  • FIG. 10 shows an explosion perspective view of the housing partition according to FIG. 9;
  • FIG. 11 shows a longitudinal section through a pump housing with a view of a further alternative embodiment of housing partitions having outlet valves;
  • FIG. 12 shows a perspective detailed illustration of the area of a pump chamber with outlet valves arranged in a housing partition;
  • Fig. 13 is a representation corresponding to FIG. 12, but an alternative
  • FIG. 14 shows a detailed illustration according to the illustration in FIG. 4, but an alternative embodiment with regard to the gap sealing
  • Kg. 15 a representation corresponding to FIG. 5, but relating to the sealing design according to FIG. 14;
  • FIG. 17 shows the pump according to FIG. 16 in a rear view
  • FIG. 18 shows a perspective view of a drive housing with separate pump housings arranged on both sides;
  • FIGS. 19 to 21 are sectional views relating to FIGS. 19 to 21;
  • FIG. 25 shows a representation according to FIG. 17, but with a separate design
  • Fig. 26 is a further view of the object of FIG. 25, with the
  • FIG. 1 Shown and described first with reference to FIG. 1 is a pump 1 with two pump pistons 2, 3, which are connected to one another via a common entrance area 4, which in the exemplary embodiment has a circular cross section. In the central area 4 there is also the 5 axis of rotation 5, about which the pump pistons 2, 3 oscillate back and forth.
  • the pump pistons covering an angular range ⁇ of approximately 60 ° in the exemplary embodiment each move accordingly over an angular range of
  • an outlet valve 8 is formed in the direction of rotation of a pump piston 2, 3 in front of the housing partition 6 or 7, for example, in the 90 ° range of the 180 ° pumping space in which a pump piston 2 or 3 is located.
  • the pump pistons are designed over an angular range of approximately 90 °, so that they also each move over an angular range of 90 °. Sealing advantages result from the larger sealing lengths. Another advantage is that the inlet valve is not open for too long and the gas is not partially pushed out again (on the way back).
  • angular extensions of more than 90 ° with respect to the piston are also possible. For example 110 °, 120 ° or 130 ° or intermediate degrees. You can then do without the compression on the back.
  • the inlet valve is then suitably arranged close to the pump piston at the start of compression.
  • an inlet valve 9 is designed as a simple opening.
  • a double piston is shown alone in perspective.
  • a height h of a piston 2 or 3 can correspond to a radius r from the axis of rotation 5 to a piston outer wall 10.
  • a diameter D of the central region 4 preferably corresponds to approximately one third of the total diameter d of the two pump pistons 2 and 3 formed as a unit together with the central region 4.
  • FIG. 3 schematically shows a drive of two pumps 1 driven together by means of an electric motor 11.
  • a crankshaft 12, schematically indicated in FIG. 3a, is flanged to the electric motor 11, by means of which the pump pistons 2, 3 are driven in opposite directions via connecting rods 13.
  • the crankshaft 12 can have a counterweight or a flywheel 14.
  • the arrangement shown is also advantageous in that an arrangement in a space-saving manner while maintaining a horizontal position of the shafts It is possible in such a way that the entire unit can stand on only one pump as a standing surface, so that the motor and the further pump then extend in a tower-like manner, as mentioned, with horizontal waves.
  • This can advantageously be implemented in that the housing is at once rectangular in the sense that it offers at least two installation surfaces. Firstly, one installation surface that corresponds to the arrangement in FIG. 3 and another installation surface for an arrangement as described above.
  • Figures 4 to 6 show details of the gap seals required for a high performance pump.
  • FIG. 4 schematically shows the gap seal radially on the outside on the pump piston 3.
  • the gap piston 3 can have such sealing lips 15 as a result of the gap dimension, which are firmly connected to the pump piston 3 and against an inner wall 16 of the pump housing. It can be, for example, plastic lips, for example made of PVC, PP or PE.
  • FIG. 5 schematically shows a seal between the housing web 7 and the central area 4.
  • a sealing lip 17 is firmly connected to the housing web 6 and acts with the inner wall of the central area 4, which is designed to be non-rotatable with the pump pistons 2, 3 Pump housing sealing together.
  • FIG. 7 shows a cross section of the housing bridge 6 in an alternative embodiment.
  • One, two or more outlet valves 8 are formed in each of the two housing webs 6, 7.
  • the outlet valves 8 exist from valve disks 19, 20 which in the exemplary embodiment are connected to one another in a U-shaped cross section and bear against the bores 21, 22 under spring preload.
  • a seal 23, 24 is arranged, each of which has corresponding openings corresponding to the bores 21, 22.
  • a forced opening of the exhaust valves can also be provided, in particular when the exhaust valves are arranged in the housing webs as shown in FIG. 7, as illustrated in FIG. 6. Through an opening part firmly connected to each pump piston, which then pushes the valve plate into the open position. This is particularly advantageous with regard to the control times to be achieved.
  • the associated side walls of the pump pistons 2, 3 just touch the respective walls of a housing web 6, 7 in the reversed position. It is also advantageous here to have a soft, flexible coating, such as, for example, on the housing web and / or the associated wall of a pump piston 2, 3. realized by a rubber part, to be provided.
  • FIG. 8 schematically shows an alternative arrangement of outlet valves 8 and inlet valves 9. These are both arranged here in the area of a housing partition 6 separating the two pumping chambers 25 from one another.
  • the diametrically opposed housing partition 7 is designed in the same way as the housing partition 6 shown.
  • the housing partition 6 is initially designed as a hollow part with a parallel to the Axis of rotation 5 of the pump piston 2 and 3 extending orientation.
  • the cavity formed is interrupted approximately in the middle by a transverse wall 26.
  • the outlet valves 8 and the inlet valves 9 are formed on both sides of this transverse wall 26, for which purpose the walls of the housing partition 6 facing the pumping chambers 25 are first provided with bores 21, 22.
  • Each with a hole 21 or. 22 side of the housing partition 6 is assigned an inlet valve 9 and an outlet valve 8, which, regardless of the function of the valve, initially has a closure actuator 27 to which a bending section 28 is connected.
  • the locking plate 27 and the bending section 28 are in one piece formed, these merge into one another at the same level and are formed from a stamped or bent sheet metal part, in particular from a spring steel part.
  • the bending sections 28 extend approximately in Langser's stretching of the housing partition 6, that is to say parallel to the axis of rotation 5.
  • the bending section 28 forms a mounting foot 29.
  • the spring part of the inlet valve 9 formed by the locking plate 27, the bending-out section 28 and the mounting foot 29 is shaped like a key with respect to a plan view of the same. But it can also be shaped as a continuous, straight tongue.
  • the spring part 30 of the outlet valve 8 has two support feet 29 arranged opposite one another at the end of the bending section 28, whereby the latter and the bending section 28 are arranged in a T-shape with respect to one another.
  • a membrane-like support 31 is provided between the spring part 30 and the associated wall of the housing partition 6, which inlet valve 9 is adapted in terms of floor plan to the floor plan of the associated spring part 30, cf. 10, in particular, here too, a stem-like section 32 is provided, at one end of which a mounting foot 33 is arranged approximately at right angles thereto, and the other end of which carries - in the specific exemplary embodiment: circular - sealing section 34 with an outer diameter that fits on the outer diameter of the locking plate 27 and with an inner diameter which is adapted to the diameter of the associated bore 22 in the housing partition 6
  • the support 31 of the outlet valve 8 is elongated in rectangular plan with an integrated sealing section 34 assigned to the locking plate 27 of the spring part 30, the passage opening of which also corresponds to the diameter of the assigned bore 21 in the housing partition 7.
  • valves 9 and outlet valves 8 are provided for each housing partition wall 6 and 7, each directed towards the pumping chamber 25 which is sealed off from one another by the housing partition walls 6, 7. Accordingly, the valves lie in pairs opposite one another.
  • the outlet valves 8 or the spring parts 30 and supports 31 forming the outlet valves 8 are arranged on the inside of the housing of the housing partition 6, a support 31 being clamped between the spring part 30 and the associated housing part.
  • a pressure part 35 is provided. This is positioned in the area of the spaced-apart mounting feet 29 of the two spring parts 30 in the hollow-chamber-like housing partition.
  • a foot-side bearing is formed for the outlet valves 8 designed as spring valves.
  • an adhesive bond can also be provided.
  • the supports 31 and spring parts 30 of the inlet valves 9 are in contour-adapted recesses 36 of the outer walls of the housing partition wall 6 and 7 facing the pumping chambers 25, the supports 31 being clamped between the spring part 30 and the associated housing wall by means of a clamping part 37.
  • This clamping part 37 engages over the housing partition 6 or 7 in the region of a recess on the ceiling. In the clamped position, the two legs of the clamping part 37 with a C-shaped cross-section overlap the mounting feet 33 and 29 of the supports 31 and spring parts 30, as a result of which the tongue valves are also supported at the ends.
  • outlet valves such as the inlet valves in the housing partition
  • the valve control is preferably pressure-dependent. Starting from a reversed position, a vacuum is generated by the pump piston 2 or 3 migrating from the housing partition 6 or 7, which causes the inlet valves 9 to open if a preselected threshold value is exceeded. When the pump piston 2 or 3 compresses the medium in the direction of the housing partition 6 or 7, a pressure increase is achieved which causes the outlet valves 8 to open.
  • the spring parts 30 of the outlet valves 8 are prestressed in the direction of the assigned pumping chambers 25, accordingly open when the pressure is exceeded inwards in the direction of the hollow chamber of the housing partition 6 or 7.
  • the spring parts 30 of the inlet valves 9, however, are in the direction of the assigned hollow chamber in the housing partition 6 or 7 biased and open by bending in the direction of the pump chambers 25 when a predetermined vacuum value is exceeded.
  • a plurality of outlet valves 8 provided in a side-by-side arrangement can also be provided in the housing partition walls 6 and 7.
  • three outlet valves 8 are provided here for each housing partition 6 and 7.
  • These exhaust valves 8 are designed similarly to the previously described exhaust valves 8, and accordingly have tongue-type spring parts 30.
  • These spring parts 30 of all three outlet valves 8 of a housing partition 6 or 7 are formed in one piece, the respective mounting feet 29 opening into a common base 38.
  • the respective inlet valves 9 of each pump chamber 25 are designed as a permanent opening 39, thus in the form of a bore in the bottom region of the pump chamber 25 (cf. FIG. 12).
  • the inlet valve 9 designed in this way overflows when moving from one reversing position to the other reversing position.
  • FIG. 13 shows an alternative embodiment, in which the pump piston 2 or 3, assigned to the outlet valves 8 arranged side by side in the housing partition 6, 7, each has an opening projection 40 for triggering the outlet valves 8 by acting in the one reversed position.
  • the closure plates 37 of the outlet valves 8 are mechanically pushed into their valve opening position via these opening projections 40
  • Pump piston 2 or 3 is like this Provided on the outside radially in the area of the movement gap with a flocking 41, which serves as a finishing layer, which grinds off in the first working cycles to produce a minimum gap.
  • a flocking 41 which serves as a finishing layer, which grinds off in the first working cycles to produce a minimum gap.
  • the same is also possible radially on the inside.
  • 15 schematically shows a seal with a flocking 41 between the housing web 7 and the central region 4.
  • flocking is also provided on the end side of the pump piston 2, 3, which is not shown in detail.
  • the flocking is only a preferred coating to achieve the desired tightness. Other coatings are also possible.
  • FIG. 16 shows a cross section through the pump housing G. This is made as an extruded part, for example made of aluminum, and has a central section for receiving the electric motor 11.
  • Pump chambers, each with two pump pistons 2, 3, are provided on both sides of the electric motor 11, each moving on a common circular path.
  • Each pump piston 2, 3 is assigned to a pump chamber 25, which are separated from one another by diametrically opposed housing partition walls 6, 7, in which outlet valves 8 are also arranged.
  • the inlet valves 9 are formed on the front side of the pump chambers 25.
  • FIG. 17 shows a rear view against the pump 1. It can be seen that the two pairs of pump pistons arranged on the side are driven by a crank mechanism via the centrally arranged electric motor 11. For this purpose, arms 43 rotatably mounted on the electric motor 11 or on its output shaft 42 are provided, via which a connecting rod length 13 can be driven in each case, for driving the pump piston pairs in opposite directions. Alternatively, what is not shown in detail, a stepper motor drive of each pump piston pair is also possible here. Another alternative is an electro-mechanical swing arm.
  • FIG. 18 shows a further embodiment of the pump housing G, which is constructed in three parts.
  • a drive housing 44 and two pump housings 18 each designed to receive a pair of pump pistons are provided.
  • These housings are formed from extruded parts, so preferably from aluminum.
  • the drive housing 44 is designed to receive the electric motor 11 accordingly
  • the two pump housings 18 are designed to be interchangeably identical and can be arranged symmetrically to the drive housing 44. Accordingly, the two pump housings 18 can be formed from one and the same extruded profile.
  • the two pump housings are fixed to the drive housing 44 by means of extruded longitudinal grooves 45 and corresponding, cross-section-adapted projections 46.
  • pinning, screwing or gluing is preferably provided.
  • the selected design, in particular of the pump housing 18, makes it possible to achieve different lengths of the pumping chambers 25 in a very simple manner, with reference to an axis of rotation of the pumping pistons, which further allows the geometry of the pumping chambers 25 to be preset in the simplest form so as to be adaptable to different needs.
  • the most square possible pump Chamber geometry preferred in which the diameter of the pump piston corresponds approximately to the extent of the pump chamber 25 in the direction of the axis of rotation 5.
  • Accessories such as suction or discharge ports, can also be provided at the front and rear, when viewed in the direction of the axes of rotation.
  • such accessories can also be integrated in terms of shape, for example in the sense that they fit into the gaps between the motor housing and the drive housing which result in the embodiment shown.
  • the pumps can also have separate housings with which they are then inserted into the overall housing shown.
  • the pump piston and the pump housing consist of the same material. If different materials are provided, it is provided that the pump piston consists of a material with a lower expansion coefficient compared to the material of the pump housing.
  • an outlet valve is formed which only consists of a valve tab 47 which is arranged on the inside of a housing web 6 and which - in this case special - opening in the housing web 6 or 7. It is essential that a multiplicity of individual openings 48 are formed in the region of the outlet, so that webs remain between them, which serve as a support for the valve tab 47. This can be very soft be formed without it squeezing into the outlet opening more than justifiable due to negative pressure.
  • the same design is also possible for an inlet valve. It may be advisable to form a recess in the outer wall, in which the valve flap lies, in order to maintain a smooth transition in the outer wall between the valve flap and the outer surface.
  • FIG. 22 The cross-sectional representation corresponding to FIG. 19 is shown in FIG. 22. It can be seen here that one valve tab 47 is in the outlet position, while the other valve tab 47 lies sealingly against the inner wall
  • a ball valve is implemented in the embodiment of FIG. 20, a ball valve is implemented.
  • the outlet and inlet valve is designed as a combined valve.
  • the inlet position of the inlet valve is immediately coupled to the sealing position of the outlet valve and vice versa.
  • a (numerical word) active body, here the closure ball 53, is both the inlet valve active body and the outlet valve active body.
  • a cage 49 which has openings 50 with respect to a gas supply line and gas discharge line (not shown in detail).
  • the cage 49 has, in association with the housing web 6 or 7, a circumferential sealing flange 51, 52. This can also be suitably covered with a sealing material such as a rubber or elastomer on the inside, on the ball side.
  • the cage 49 can also be made integrally from such a material.
  • a locking ball 53 is caught in the cage 49. Depending on the pressurization, this moves into its corresponding one Sealing position.
  • the cage extends between the housing webs 6, 7, connecting them transversely.
  • a valve which also functions as an outlet and inlet valve.
  • it consists of two valve disks 54, 55, which are preferably rigidly coupled to one another via a connection 56, rod-shaped in the exemplary embodiment.
  • the connection 56 in turn extends transversely to the housing webs 6, 7.
  • the connection 6 is suspended by means of a spring part 56. As a result, it can be aligned with a central position, which corresponds to an opening of both the inlet and the outlet valve. This can also pull it into a closed position of the inlet or outlet valve.
  • a tube-like guide can also be provided. This is particularly the case if, in deviation from the specific embodiment shown, one of the valve disks 54 or 55 comes into contact with the inside of a housing wall 6 or 7 in the sealing position.
  • FIGS. 25 and 26 show a pump in which the pump pistons are not only in a separate housing, referred to here as the first housing 57 run, which in turn is then still accommodated in the outer housing 58, but in which the housing 57 is also rotatably accommodated in the housing 58 and, by means of the crank mechanism shown in FIG. 26, preferably by the same drive that drives the pump pistons, is moved in opposite directions during a pump piston movement.
  • the absolute movement of a pump piston from one to the other reversed position can be halved, for example (with the same delivery rate).
  • the housing 58 can also be made in several parts in the same way as is described with reference to FIG. 18.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne une pompe (1), telle qu'une pompe à vide ou un compresseur, comportant au moins un piston (2, 3) effectuant un mouvement rotatif et un carter (18). L'invention vise à créer une pompe nouvelle de ce type. A cet effet, le piston (2, 3), qui est éventuellement couplé de manière fixe avec un ou plusieurs autres pistons (2, 3), oscille autour d'un axe de rotation (5) en suivant une trajectoire comportant deux points de renvoi. Un agent, éventuellement comprimé ou sous pression, est évacué par une soupape de décharge (8). Le mouvement passant d'un point de renvoi à l'autre point de renvoi fait ouvrir une soupape d'admission (9). L'agent est alors évacué lors de la montée en pression côté pression du piston (2, 3) et aspiré côté aspiration du piston (2,3).
PCT/EP2004/050435 2003-03-05 2004-04-02 Pompe WO2004088141A2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US10/549,968 US20070104600A1 (en) 2003-03-05 2004-04-02 Oscillating piston pump
JP2006505520A JP2006522265A (ja) 2003-04-02 2004-04-02 ポンプ
EP04725395A EP1608874A2 (fr) 2003-04-02 2004-04-02 Pompe

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10315104.4 2003-04-02
DE10315104 2003-04-02
DE10319671.4 2003-05-02
DE10319671A DE10319671A1 (de) 2003-04-02 2003-05-02 Pumpe

Publications (2)

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WO2004088141A2 true WO2004088141A2 (fr) 2004-10-14
WO2004088141A3 WO2004088141A3 (fr) 2005-01-06

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Country Link
US (1) US20070104600A1 (fr)
EP (1) EP1608874A2 (fr)
JP (1) JP2006522265A (fr)
KR (1) KR20050114270A (fr)
WO (1) WO2004088141A2 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010042967A2 (fr) * 2008-10-17 2010-04-22 Mahle König Kommanditgesellschaft Gmbh & Co Kg Étanchéité pour moteur à pistons rotatifs
WO2017186341A1 (fr) * 2016-04-28 2017-11-02 Linde Aktiengesellschaft Machine à énergie fluidique
US20180154869A1 (en) * 2016-12-01 2018-06-07 Fujitsu Ten Limited Air compressor and extraneous-matter removing apparatus
US20190145411A1 (en) * 2017-11-14 2019-05-16 Denso Ten Limited Gas ejection apparatus
RU2697779C1 (ru) * 2018-06-25 2019-08-19 Федеральное государственное автономное образовательное учреждение высшего образования "Южно-Уральский государственный университет (национальный исследовательский университет)" ФГАОУ ВО "ЮУрГУ (НИУ)" Лопастной двигатель

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JP2008202459A (ja) * 2007-02-19 2008-09-04 Hori Engineering Co Ltd 圧縮機
WO2008141361A1 (fr) * 2007-05-21 2008-11-27 Philip David Giles Pompe pour système de dessalement
US20160281712A1 (en) * 2013-03-20 2016-09-29 Magna Powertrain Inc. Tandem electric pump
JP7037335B2 (ja) * 2017-11-14 2022-03-16 株式会社デンソーテン 気体噴射装置および気体噴射システム

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US1951607A (en) * 1932-04-09 1934-03-20 Boyar Schults Corp Refrigerator pump
FR976094A (fr) * 1942-04-07 1951-03-13 Machine à pistons oscillants susceptible de fonctionner comme pompe ou comme moteur
FR1299714A (fr) * 1961-06-16 1962-07-27 Appareil pouvant constituer un compresseur ou une pompe, un moteur à vapeur, à air comprimé ou à explosion
AT325757B (de) * 1971-10-29 1975-11-10 Wyzsza Szkola Inzynierska Mehrkammer-arbeitsmaschine mit flügelmotor
GB1554358A (en) * 1976-09-01 1979-10-17 Doundoulakis G Rotary fluid-machine
DE2808769A1 (de) * 1978-03-01 1979-09-06 Werner Mayer Schwenkkolben-maschine
WO1989005918A1 (fr) * 1987-12-23 1989-06-29 3H Invent A/S Agencement de soupape pour pompe ou compresseur
WO2001053659A1 (fr) * 2000-01-21 2001-07-26 Free Energy Technology Ltd. Moteur

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010042967A2 (fr) * 2008-10-17 2010-04-22 Mahle König Kommanditgesellschaft Gmbh & Co Kg Étanchéité pour moteur à pistons rotatifs
WO2010042967A3 (fr) * 2008-10-17 2010-08-12 Mahle König Kommanditgesellschaft Gmbh & Co Kg Étanchéité pour moteur à pistons rotatifs
WO2017186341A1 (fr) * 2016-04-28 2017-11-02 Linde Aktiengesellschaft Machine à énergie fluidique
US20180154869A1 (en) * 2016-12-01 2018-06-07 Fujitsu Ten Limited Air compressor and extraneous-matter removing apparatus
US10717418B2 (en) * 2016-12-01 2020-07-21 Fujitsu Ten Limited Air compressor and extraneous-matter removing apparatus
US20190145411A1 (en) * 2017-11-14 2019-05-16 Denso Ten Limited Gas ejection apparatus
RU2697779C1 (ru) * 2018-06-25 2019-08-19 Федеральное государственное автономное образовательное учреждение высшего образования "Южно-Уральский государственный университет (национальный исследовательский университет)" ФГАОУ ВО "ЮУрГУ (НИУ)" Лопастной двигатель

Also Published As

Publication number Publication date
KR20050114270A (ko) 2005-12-05
JP2006522265A (ja) 2006-09-28
EP1608874A2 (fr) 2005-12-28
WO2004088141A3 (fr) 2005-01-06
US20070104600A1 (en) 2007-05-10

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