EP0659237B1 - Flügelzellenmaschine - Google Patents

Flügelzellenmaschine Download PDF

Info

Publication number
EP0659237B1
EP0659237B1 EP93919192A EP93919192A EP0659237B1 EP 0659237 B1 EP0659237 B1 EP 0659237B1 EP 93919192 A EP93919192 A EP 93919192A EP 93919192 A EP93919192 A EP 93919192A EP 0659237 B1 EP0659237 B1 EP 0659237B1
Authority
EP
European Patent Office
Prior art keywords
rotor
stator
vane
vanes
machine 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.)
Expired - Lifetime
Application number
EP93919192A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0659237A1 (de
Inventor
Bernt Lorentz
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0659237A1 publication Critical patent/EP0659237A1/de
Application granted granted Critical
Publication of EP0659237B1 publication Critical patent/EP0659237B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • 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
    • F04C2/3441—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 inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation

Definitions

  • the invention relates to a vane machine for liquids, consisting of a rotor mounted in a stator with radially extending guide slots in which radially displaceable vanes are slidably arranged, which can be pressed against an inner wall of the stator under centrifugal force, with crescent-shaped expanding or narrowing feed cells during a rotor revolution are formed and the liquid entry through a tubular inner stator and the filling of the vane cells from the inside out.
  • Vane cell machines are built as constant pumps or motors or as variable pumps or motors. Vane machines are also used as volumetric counters. The advantages of vane cell machines are their even flow rate and their quiet running. Problems arise from the respective hydraulic radial and axial bearing loads.
  • the hydraulic radial bearing loads in vane cell machines with rotor lengths equal to the working area of the vanes result from the product of the projection area, formed from the rotor and protruding vane and the hydraulic pressure, ie the differential pressure acting on the rotor. Smaller radial loads result from the wing friction on the stator and in the Rotor slots and the weight of the rotor.
  • the rotor shafts and bearings are either dimensioned to a great extent or an attempt is made to compensate for them by complex and fluidically disadvantageous multi-stroke pump or motor designs.
  • the hydraulic axial bearing loads can be avoided by symmetrical formation of the axial hydraulic active surfaces of the rotor, the hydraulic pressures exerted on the active surfaces having to be the same.
  • axially movable rotor which is preferred for manufacturing and cost reasons, it rests on one side in the area of the stator, the hydraulic pressure becoming more effective on the opposite side, so that there is no axial force compensation. This would be remedied by an axially immovable design of the rotor bearing with a precisely identical setting of the end rotor gaps, which, however, is complex.
  • pneumatic cushions are provided in some recesses in the end faces of the rotor according to DE-A-21 33 455, which lie between the impeller blades and are fed with compressed air through channels which are in the form of a circular arc are incorporated in the side covers of the housing, so that when the rotor is axially displaced, pressure differences occur between the pneumatic cushions located on both sides of the rotor, which exert pushing forces in the direction of a central position.
  • a comparatively complex solution is also in the DE-A-31 20 350 proposed for a vane machine, in which the shaft rotor is designed with two large axially displaceable liners, which are acted upon in axially displaceable bearing bushes on the back and end faces by the delivery pressure in pressure-loaded columns, in order to bring about a pressure compensation on the shaft rotor , so that the bearing loads and friction losses are minimized.
  • Disadvantages are the large and costly number of precision parts in the hydraulic work area, the relatively large gap lengths required between the high-pressure and low-pressure areas and the resulting poor efficiency of the vane machine.
  • the shaft emerging for the input or output from a rotary piston machine causes axial bearing loads due to the pressure difference at the shaft seal and, in the case of constant-ring seals, also due to the spring force of the same, unless a compensation is made on the opposite side by a symmetrical design.
  • rotary piston pumps are known for example from DE-A-12 36 641.
  • a stator cavity of constant cross section a cylindrical rotating rotor with a plurality of essentially radial slots, in which vanes slide, is supported, with several conveyor cells being formed between the stator and the rotor by means of a correspondingly wavy design of the cross-sectional contour of the stator cavity
  • Working medium is supplied and discharged via tangential opening channels, of which the suction or low pressure side, located on one side of a wing, bores leading to a central rotor cavity are connected, while the high-pressure-side channels located on the other side of each vane are each connected in a continuous longitudinal channel of the rotor assigned to each vane.
  • the longitudinal channels are in turn connected to an annular groove embedded in a stator side wall, which is connected to the high-pressure connection opening of the pump or the motor.
  • DE-A-12 36 941 further proposed that as pressure-side channels on the relevant side of each wing a plurality of grooves running in the wing sliding direction are provided, which are incorporated in the corresponding wall of the associated rotor slot, an annular groove also being arranged on both sides of the rotor in the side walls of the stator facing the rotor end walls, into which the pressure-side longitudinal channels of the rotor open, the annular grooves are connected to the pressure connections of the pump or motor.
  • the rotor cavity in which the low-pressure side bores of the rotor lead, is part of a central longitudinal bore of a shaft connected to the rotor.
  • this rotary piston machine is expensive to construct.
  • US-A-3,361,076 describes a vane motor with a rotor mounted in a stator and slotted in the working area, which is screwed together and consists of a receptacle for the vanes, an end piece and a flow bushing.
  • the receptacle for the vanes contains an end flange which, like the end piece, projects radially beyond the outer diameter of the slotted rotor part and the inner diameter of the stator element and thus laterally limits the hydraulic working area.
  • the receptacle for the vanes is designed as a shaft in the axial direction, is roller-mounted and sealed in the stator, and is led out of the vane cell motor to receive a drive element.
  • the end piece has only a short shaft shoulder to accommodate the rolling bearing.
  • the vane cells are filled from the inside to the outside, with a rotor which is extended over the slotted area on both sides and has a larger outside diameter for positive axial centering of a movable cam ring.
  • Both extensions are on tapered roller bearings, too for absorbing radial and axial hydraulic forces, mounted in the housing, the one extension being guided out of the machine as a rotation-sealed shaft for the drive connection.
  • Pressure-adjustable overflow valves limit the gap pressure in the gap areas resulting from leakage from the operating pressure, which causes an axial pressure equalization at the same pressure across these gap areas up to the seal diameter. The axial hydraulic forces over the non-pressure-balanced surface below the seal diameter are absorbed by the bearings.
  • the vanes in this vane motor are spring-loaded, which makes them highly susceptible to the fact that when the spring pressure is released it is no longer guaranteed that the vanes can be guided to the inner wall of the stator in the operating state.
  • a rotation of the rotor to the stator must be ensured so that the blades can be moved into their receiving slots in the rotor against spring pressure.
  • the three-part rotor is neither shaftless nor tubular, which has no wing slot that runs from the inside to the outside diameter, since the inside diameter is formed by the flow bushing.
  • the pressurized space of the stator does not contribute to the compensation of radial forces in the area of the rotor extensions, which can only act on the rotor part due to the operating pressure.
  • US-A-3 361 076 discloses a non-shaftless tubular rotor with axial extensions, but which have a larger diameter than that of the rotor in the wing working area.
  • a vane pump in which two rotors separated by a spacer, two on a common shaft and axially firmly clamped Support rotors, two spacers and two shims are arranged.
  • the support rotors are slidably supported in a housing in bearing bushes, in which corresponding recesses, which are acted upon by operating pressure, are made to compensate for radial hydraulic forces.
  • the operating pressure is routed through external pipes from the pressure side to the recesses in the bearing bushes.
  • operating surfaces which are acted upon by operating pressure and are directed against the rotor are provided in the stator.
  • a vane machine in which a shaft-bearing rotor rotates in a stator, the inner circumferential surface of the stator having three part-circular recesses, the wall surfaces of which are guided so that the merging area of two wall surfaces in the outer circumferential area of the Rotors comes to rest.
  • the rotor is provided with radially extending guide slots for four blades, the arrangement of the guide slots being such that two opposite guide slots form an imaginary radius line are offset from one another with the result that only one wing comes to rest in each individual part-circular recess.
  • a slide bearing lubrication of the rotor shaft that is lubricated by the conveying liquid is not provided.
  • DE-A-2 022 841 describes a valve-less rotary piston pump with circular, rotating vanes which take over the conveyance and which consist of a housing, two or more vanes designed as rotary pistons, which are mounted in a hollow drive shaft, and a fixed profile axis, which determines the position of the vanes in the individual work phases, the drive hollow shaft being mounted eccentrically in the pump housing in such a way that a sufficient conveying cross section remains between the hollow shaft and the housing in the working area and the hollow shaft lies sealingly against the housing in the separating area and thus the separation between pressure and suction side takes over.
  • the vanes, which cause the medium to be sucked in and conveyed, project so far out of the hollow shaft in the work area that they reach the housing wall.
  • the drive shaft is designed as a hollow shaft in which the vanes are mounted so as to be radially displaceable and are supported on a profile axis which is permanently displaced in the interior of the hollow shaft, the hollow shaft being mounted in the pump housing. Shaftless storage is therefore not provided.
  • the holding pressure which increases rapidly with the speed, means that they operate at economical drive speeds of, for example, 1450 rpm 1 and higher no longer possible.
  • the volumetric efficiency and the dry suction capacity (with an empty pump) of vane pumps is determined by the gap losses, the size of which - assuming the same product to be conveyed, the same manufacturing accuracy and pressure difference - depends on the gap lengths. Therefore, with a comparable flow rate, low-speed pumps with a correspondingly large cyclical pump volume and gap have poorer volumetric efficiencies and a lower dry suction capacity than fast-rotating pumps with correspondingly smaller cyclical pump volume and gap lengths. These technical relationships mentioned also limit the possibilities for constructively improving the volumetric efficiency and the dry suction capacity due to the necessary speed limitation by the holding pressure.
  • rotary piston machines for liquids require strongly dimensioned shafts and bearings due to the large projection surface, which is made up of the rotor and protruding vanes and is subjected to the differential pressure, unless the rotary piston machines are designed as double-stroke vane pumps or motors, each with two inlet and outlet openings for the liquids have a measure that is technically complex to manufacture and leads to an increase and thus deterioration of the holding pressure in pumps.
  • vane cell machines are addressed as volumetric counters, the measuring accuracy should be improved in the same way.
  • the vane machine consists in that the rotor is shaftless and tubular and extends both sides beyond the working area determined by the vanes and is mounted with the extensions in the outer stator and has continuous vane slots from the inside to the outside diameter, the jacket of the stator in Has area of the rotor extensions on the surface from the operating pressure and / or relieved hydraulic active surfaces directed against the rotor for at least partial compensation or avoidance of radially occurring forces.
  • the operating pressure becomes effective in the rotor / outer stator bearing gaps located there, which leads to further bearing loads.
  • recesses (effective surfaces) in the stator casing which are relieved of the operating pressure make this radial load part considerable reduced.
  • the vane cell machine is provided with a liquid entry through a hollow, centric stator, the channels for filling the enlarging vane cells being formed by radial recesses in the vanes and / or in the vane slots, and the surface of the centric stator being subjected to operating pressure has active surfaces directed against the rotor for at least partial compensation of radial forces, the hydraulically loadable recesses being able to be replaced by small bores subjected to operating pressure, which produce larger pressure active surfaces directed against the rotor in the rotor / outer stator bearing gaps.
  • This measure is easier to manufacture, causes comparatively lower gap losses and thus improves the volumetric efficiency.
  • This vane machine is advantageously of simple construction, with a comparatively complex additional shaft bearing and the resulting frictional forces being avoided from the outset, as well as minimizing axial and radial hydraulic forces.
  • the radial channels for filling the feed cells are formed by radial recesses in the vanes and / or in the vane slots, which extend continuously from the outside diameter to the longitudinal rotor bore as the inside diameter of a working area that extends on both sides beyond the working area determined by the vanes shaftless rotor run, the liquid entering axially through the hollow rotor axis and the filling of the enlarging feed cells in the radial direction through a window in the rotor axis and in the further course through recesses in the rotor slots and / or in the wings.
  • the radial filling of the vane cells from the inside via the rotor slots also has the advantage that the stroke volume of the vanes in the rotor slots is included in the cyclical working volume of the pump or motor without a special filling process for this stroke volume against the centrifugal force, as is the case with the tangential or axial filling of the vane cells known from the prior art is required.
  • the rotor axis which also serves as a liquid inlet and as a bearing for the rotor, advantageously makes it possible for pumps and motors to carry out the hydraulic, in particular radial, pressure compensation in a cost-saving manner by means of hydraulic support against the rotor axis.
  • the recesses are preferably acted upon by the operating pressure given by the liquid, so that no further pressure sources or controls are necessary.
  • the recesses in the stator casing outside the wing working area are arranged opposite the rotor outer casing, that is to say symmetrically with respect to a vertical surface passing through the wing working area.
  • the recesses are located in the jacket of a stator pin, which passes through the central opening of a rotor tube and lies sealingly against it.
  • the latter embodiment has the advantage that the recesses can also be at the same height as the wing working area, which may result in a reduction in the overall height. Combinations of the mentioned embodiment are equally possible.
  • the rotor part projecting beyond the wing working area has the same or a reduced outer diameter compared to a diameter in the wing working area.
  • a reduced diameter outside the wing working area has the advantage that the rotor is axially centered when the vane machine is running.
  • the required centering of the rotor relative to the working space takes place through the blades.
  • the space in the guide slots below the blades is connected to the blade cell in front of it in the direction of rotation, for example by radial recesses in the blade and / or in the rotor.
  • the vanes which are moved outwards by centrifugal force can be immersed in the rotor and the freely movable rotor can be axially displaced on one side against an end-face stator and this can prevent the vanes from coming out or even tilt when the vane machine starts up,
  • the stator parts that laterally delimit the working area towards the axis of rotation slightly widening the working area.
  • bevels are slightly wider on both sides than it corresponds to the axial mobility of the rotor in the stator, so that when the vane machine begins to rotate, the vanes that come out by centrifugal force immediately center the rotor to the working area and, due to the lack of axial forces, do so without additional friction the wings is maintained.
  • the rotor is tubular and has a longitudinal bore in which an even number of vane slots ends openly and in which diametrically opposite vanes are firmly connected to one another or are formed in one piece.
  • the rotor can also accommodate a stator pin in the tube opening, which is hollow on the inside and has a window in the area of the slots for the displaceable vanes which pass radially through the rotor and the vanes and / or the rotor slots have radial recesses .
  • This arrangement enables a partial compensation of the radial hydraulic forces on the rotor.
  • the rotor is preferably coupled on one of its end faces to an axially fixed shaft as an input or output connection, the shaft being received in the stator housing.
  • the stator bore is made radially outward in a pitch circle over the area going through the maximum radial deflection of the vanes, so that a connection between two or more feed cells exists via the cutout thereby created. This measure makes it easier to fill the feed cells.
  • stator casing transition area between the enlarging and the reducing feed cells or the guiding of the blades in the area between two feed cells is preferred with regard to the
  • the axis of rotation is arranged centrally, so that the blades do not execute any radial movement when rotating in this area which is loaded with differential pressure.
  • the inner stator outer casing has depressions which can be acted upon hydraulically with the pump delivery pressure or the inlet pressure of the motor for at least partial compensation of the radial hydraulic bearing load.
  • the rotor parts projecting beyond the wing working area preferably have a reduced outer diameter compared to the rotor diameter in the wing working area. As a result, the rotor is axially centered during operation.
  • the stator jacket laterally delimiting the wing working area is conical in the area of the non-pressurized blades, so that the blades are positively guided when starting slide into the axially centered position.
  • the rotor is connected directly or via a coupling on the end face opposite the inlet opening to a shaft as an input or output device, the shaft being guided in a sealed manner into the stator housing.
  • the vane machine which is preferably designed as a single-stroke vane machine, which is designed as a pump in the embodiment shown in FIGS. 1 and 2, has a shaftless rotor 1, which in the axial direction has either an outer diameter 2 with a constant circumference, as in the vane working area 15 , or a reduced circumference 3.
  • the rotor 1 is fitted in a stator 4 in a sealed manner.
  • the stator has recesses 5, which are designed according to their position and size such that the the operating pressure of the liquid acting here leads to a partial or complete hydraulic force balance, also taking into account the friction and weight forces.
  • the recesses 5 are located in the axial direction in front of or behind the wing working area 15 and are arranged symmetrically thereto.
  • the vertical end faces or diameter jumps 6 in the case of a diameter jump of the rotor 1 present in the upper half of FIG. 2 serve at the same time for rotor centering, which results in gaps 7 of equal size between the rotor end face and the respective opposite stator end face during running operation.
  • these jumps in diameter 6 serve to center the rotor to the working space, the disadvantage described above of the effectiveness of the hydraulic pressure being stronger on one side being able to be accepted by contacting the opposite side, since the end face 6 as an effective area is kept small by a small difference in diameter.
  • This rotor centering to the work area between the end faces of the rotor 1 and the bilateral stators 4 ensures the gaps 7 for hydrostatic force compensation at the same pressure.
  • the rotor 1 has radially extending slots 8, in which the vanes 9 are slidably guided.
  • the space in the guide slots 8 below the wings 9 is connected to the wing cell in front of it in the direction of rotation, in the present case by radial recesses 10 in the wing and / or recesses 11 in the rotor. Since, when the vane machine is at a standstill, as shown in FIG.
  • the vanes 9 which are moved outwards by centrifugal force can be immersed in the rotor and the freely movable rotor 1, which is not reduced in diameter, can be axially displaced on one side against an end face of the stator 4, as a result of which When the vane machine starts up, the vanes 9 are prevented from coming out, which can lead to the vane canting on the relevant stator inner wall expanding conical or slightly beveled.
  • stator inner shell parts 12, 12a extend slightly further on both sides than corresponds to the axial mobility of the rotor 1 in the stator, so that when the vane machine begins to rotate, the vanes which come out by centrifugal force immediately center the rotor 1 to the working space 15 and do so in the absence of them axial forces is maintained even without additional friction on the wings 9.
  • the input and output connection of the vane cell machine takes place via a shaft 13 protruding into the stator housing 4 and sealed there, which shaft is connected to the rotor axially without reaction via a coupling 14.
  • the - 1 ', 1 "- rotor 1 which is extended on both sides over the working area determined by the vanes 9, is tubular, with a central opening in the tube opening Stator pin 16 protrudes, the stator pin 16 being fixedly connected to the other stator parts.
  • FIGS. 8 and 9 While in the previously described embodiments the filling of the expanding vane cells takes place essentially tangentially from the outside, in the embodiment shown in FIGS. 8 and 9 an inlet connection is provided on the stator journal 16 which is hollow up to the end of the working space width 20.
  • This stator has a window 21 in the working area 15 of the expanding vanes 9, radial recesses 10 and 11 being provided in the vanes 9 and / or in the rotor 1, through which the expanding vane cells are filled with the assistance of the centrifugal force.
  • the recesses 10 and 11 are arranged in the direction of rotation on the back of the blades and / or in the rotor directly behind the blades.
  • the vane cell machine shown in FIGS. 10 and 11 essentially consists of a rotor 111, which is mounted on a hollow shaft 110 as an inner stator 100 and which is arranged in its stator 112 so as to be rotatable and surrounded by it is.
  • the stator 112 can be formed in two parts, in particular with a component 113 integrated with the hollow shaft 110.
  • the rotor 111 has a reduced diameter to the side thereof in each case and lies with its outer lateral surface in a sealed manner against the inner stator jacket.
  • a gap 116 and 117 is formed to the opposite end face of the stator, which is pressurized.
  • an axial bore 118 and a radial bore 118 'ensure pressure equalization between the columns 116 and 117.
  • the rotor is connected directly or via a coupling (not shown) to a shaft 119, which is rotatably mounted in a sealed manner in the stator housing or in the input or output machine.
  • the hollow shaft 110 is designed as an inlet opening in the direction of the arrow 120, which is connected via a window opening 121 of the hollow shaft via corresponding recesses in the rotor to radially extending groove-shaped recesses 122 in the rotor and recesses 123 in the wing.
  • the blades 124 are located in radial slots 125 of the rotor 111.
  • the inner stator 100 is provided on its running surface with depressions 126 which are hydraulically acted upon by the pump delivery pressure or the input pressure of the motor and are arranged in size and position in such a way that the radial hydraulic bearing load is partially or is fully balanced.
  • the space between the rotor 111 and the stator 112 with the sickle-shaped feed cells 127 is in each case divided by wings 124, which run in the area represented by the arc 128 with the respective wing end.
  • the inner stator jacket has additional recesses 129 which protrude in a crescent shape beyond the maximum radial deflection (curve 128).
  • a transmission area 130 is provided, in which the vanes 124 do not execute any radial movement when rotating in the direction of the arrow 131.
  • the liquid flowing in in the direction of the arrow 120 is guided through the window opening 121 into the groove-shaped radial recesses 122, 123 radially outward into the feed cells 127 and is discharged essentially tangentially in the direction of the arrow 132.
  • the ingress of liquid through the hollow axis and the filling of the enlarging vane cells from the inside to the outside is largely due to the energy input from the drive and leads to low holding pressures even at high speeds.
  • hydraulic pressure equalization can be created by simple design measures.
  • the tubular rotor 201 is slidably supported in the two bearings 202 and 203.
  • the single-stroke cam ring 204 forms the working space 205 and is firmly connected to the bearings 202 and 203.
  • This 3-part outer cylindrical stator is inserted into the pump housing 207 with a liquid-carrying or flowable gap 206 and is connected at both ends to the pump housing e.g. sealed by O-rings 208.
  • the pressure outlet 209 located in the cam ring acts upon the gap 206 with the respective operating pressure of the pump when it is transferred to the corresponding outlet port 218 of the housing 207.
  • one or more radial bores 210 are arranged in the bearings 202 and 203, which have opposite pressure forces acting on the rotor within the bearing areas and for partial or full pressure equalization.
  • the inner stator 213 is fitted in a contactless manner but with a narrow gap in the inner diameter of the rotor 201.
  • the filling of the same takes place via the inlet bore 214 of the inner stator 213 which runs through to the drive side and the window 215 in the region of the expanding vane cells.
  • the inlet pressure is effective on both end faces of the rotor.
  • the bearings in the circumferential effective range of the hydraulic radial pressure forces are provided with recesses 211, which pass through the gaps 217 and the bores 214 and 218 are connected to the low-pressure side, so that only a small bearing length 212 sufficient for sealing and storage remains in the area of the recesses 211.
  • the hydraulic operating pressure acts directly on the inner stator without loading the rotor and, in addition, the gaps between the rotor and the inner stator are pressurized via the rotor slots, which contributes to a further partial pressure equalization.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Centrifugal Separators (AREA)
  • Soil Working Implements (AREA)
EP93919192A 1992-09-02 1993-08-26 Flügelzellenmaschine Expired - Lifetime EP0659237B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE9211768U DE9211768U1 (de) 1992-09-02 1992-09-02 Flügelzellenmaschine
DE9211768U 1992-09-02
PCT/EP1993/002311 WO1994005912A1 (de) 1992-09-02 1993-08-26 Flügelzellenmaschine

Publications (2)

Publication Number Publication Date
EP0659237A1 EP0659237A1 (de) 1995-06-28
EP0659237B1 true EP0659237B1 (de) 1996-04-24

Family

ID=6883305

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93919192A Expired - Lifetime EP0659237B1 (de) 1992-09-02 1993-08-26 Flügelzellenmaschine

Country Status (10)

Country Link
EP (1) EP0659237B1 (ko)
JP (1) JP3129737B2 (ko)
KR (1) KR950703124A (ko)
CN (1) CN1040786C (ko)
AT (1) ATE137306T1 (ko)
AU (1) AU684725B2 (ko)
CA (1) CA2143719C (ko)
DE (2) DE9211768U1 (ko)
DK (1) DK0659237T3 (ko)
WO (1) WO1994005912A1 (ko)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100398824C (zh) * 2004-06-25 2008-07-02 丁桂秋 一种容积式叶片泵

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5545014A (en) * 1993-08-30 1996-08-13 Coltec Industries Inc. Variable displacement vane pump, component parts and method
EP0650801A1 (de) * 1993-10-29 1995-05-03 Ing. Büro H. Schellenberg Pneumatische Positioniereinrichtung
AUPO580397A0 (en) * 1997-03-24 1997-04-17 Baker Medical Research Institute Positive displacement pump
SE9804317D0 (sv) * 1998-12-15 1998-12-15 Gunnar Bjoerk Pulspump
JP4780154B2 (ja) * 2008-07-18 2011-09-28 パナソニック電工株式会社 ベーンポンプ
DE102010022677B4 (de) 2010-06-04 2016-06-30 Nidec Gpm Gmbh Flügelzellenpumpe
CN103080554B (zh) * 2010-08-18 2016-08-17 三菱电机株式会社 叶片式压缩机
CN103001344A (zh) * 2012-10-29 2013-03-27 无锡金阳电机有限公司 无轴电机
RU2554691C1 (ru) * 2014-02-03 2015-06-27 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Казанский национальный исследовательский технический университет им. А.Н. Туполева-КАИ" Устройство генерации колебаний
FR3033370B1 (fr) * 2015-03-02 2017-03-24 Peugeot Citroen Automobiles Sa Pompe a palettes
CN105545744B (zh) * 2015-12-22 2017-12-26 重庆市高新技术产业开发区潞翔能源技术有限公司 吸附式天然气系统内的压缩机
CN106017199B (zh) * 2016-07-27 2017-11-17 广州市昕恒泵业制造有限公司 用于管壳式换热器的泵
RU172054U1 (ru) * 2016-11-02 2017-06-28 Виктор Иванович Чудин Камерный объемный счетчик жидкости
CN106640515B (zh) * 2016-11-29 2018-06-29 河南科技大学 一种链子式转子液压马达

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3153384A (en) * 1961-06-12 1964-10-20 Pacific Ind Mfg Co Vane type pump
FR1395435A (fr) * 1964-05-22 1965-04-09 Dispositif actionné par un fluide
US3361076A (en) * 1966-05-06 1968-01-02 William B Pritchett Jr Expansible chamber device
DE2022841A1 (de) * 1970-05-11 1971-11-25 Adolf Kresin Ventillose Rotationskolbenpumpe
DE3120350A1 (de) * 1981-05-22 1983-01-27 Albert Wagner Fluegelzellen-pumpen und -motoren mit druck-spalt-ausgleich
CN2045031U (zh) * 1989-03-15 1989-09-27 浙江省仙居液压件厂 双作用变量叶片泵

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100398824C (zh) * 2004-06-25 2008-07-02 丁桂秋 一种容积式叶片泵

Also Published As

Publication number Publication date
EP0659237A1 (de) 1995-06-28
CN1103931A (zh) 1995-06-21
CN1040786C (zh) 1998-11-18
AU684725B2 (en) 1998-01-08
AU4954393A (en) 1994-03-29
CA2143719A1 (en) 1994-03-17
WO1994005912A1 (de) 1994-03-17
DK0659237T3 (da) 1996-07-29
JP3129737B2 (ja) 2001-01-31
DE9211768U1 (de) 1992-11-12
KR950703124A (ko) 1995-08-23
CA2143719C (en) 2001-07-17
JPH08500877A (ja) 1996-01-30
DE59302390D1 (de) 1996-05-30
ATE137306T1 (de) 1996-05-15

Similar Documents

Publication Publication Date Title
EP0659237B1 (de) Flügelzellenmaschine
DE2324967A1 (de) Schraubenverdichter
EP2633194A2 (de) Flügelzellenpumpe
DE3018711C2 (de) Axialkolbenpumpe
DE2835340A1 (de) Oelgekuehlte antriebseinheit
EP2359005B1 (de) Flügelzellenpumpe
WO2013068531A2 (de) Regelbarer flügelkompressor
EP2510192B1 (de) Hydrostatische radialkolbenmaschine
DE1528940C3 (de) Rotationskolbenpumpe mit in Schlitzen eines zylindrischen Rotors radial be weglichen Arbeitsschiebern
DE4011671C2 (de) Regelbare Flügelzellenpumpe
WO1988003229A2 (en) Swivelling impeller pump
DE2143401C2 (de) Pumpe
DE102004021216B4 (de) Hochdruck-Innenzahnradmaschine mit mehrfacher hydrostatischer Lagerung pro Hohlrad
DE1653921B2 (de) Rotationskolbenpumpe
DE2533776A1 (de) Drehmotor
DE3423276A1 (de) Fluegelmotor oder -pumpe
DE3727281C2 (ko)
DE9207087U1 (de) Rotationskolbenmaschine
DE4425429A1 (de) Hydraulikmaschine
DE1236941B (de) Drehkolbenpumpe oder -motor
DE1528615A1 (de) Hydrostatische Radialkolbeneinheit
EP3020917A1 (de) Hydraulische Flügelzellenmaschine
DE726932C (de) Regelbare und umschaltbare Fluegelkolbenpumpe
WO2009019095A1 (de) Flügelzellenpumpe mit verringerter flächenpressung der flügel
DE2857227A1 (de) Fluessigkeitsringpumpe

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19950216

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE DE DK ES FR GB GR IT NL SE

17Q First examination report despatched

Effective date: 19950907

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

ITF It: translation for a ep patent filed
AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE DE DK ES FR GB GR IT NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19960424

Ref country code: ES

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19960424

REF Corresponds to:

Ref document number: 137306

Country of ref document: AT

Date of ref document: 19960515

Kind code of ref document: T

ET Fr: translation filed
REF Corresponds to:

Ref document number: 59302390

Country of ref document: DE

Date of ref document: 19960530

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19960514

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DK

Payment date: 20010824

Year of fee payment: 9

Ref country code: SE

Payment date: 20010824

Year of fee payment: 9

Ref country code: AT

Payment date: 20010824

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20010827

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20010829

Year of fee payment: 9

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020826

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020827

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020831

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020831

BERE Be: lapsed

Owner name: *LORENTZ BERNT

Effective date: 20020831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030301

EUG Se: european patent has lapsed
REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 20030301

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20030813

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20030819

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040826

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20040826

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050429

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050826

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20051026

Year of fee payment: 13

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070301