EP2334935A2 - Pompe rotative - Google Patents

Pompe rotative

Info

Publication number
EP2334935A2
EP2334935A2 EP09778231A EP09778231A EP2334935A2 EP 2334935 A2 EP2334935 A2 EP 2334935A2 EP 09778231 A EP09778231 A EP 09778231A EP 09778231 A EP09778231 A EP 09778231A EP 2334935 A2 EP2334935 A2 EP 2334935A2
Authority
EP
European Patent Office
Prior art keywords
valve
chamber
rotor
wall
pump according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP09778231A
Other languages
German (de)
English (en)
Inventor
Herbert Hüttlin
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 EP2334935A2 publication Critical patent/EP2334935A2/fr
Withdrawn legal-status Critical Current

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
    • 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
    • F04C18/3441—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 the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C18/3445—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 the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the vanes having the form of rollers, slippers or the like
    • 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
    • F01C21/0809—Construction of vanes or vane holders
    • 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
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors

Definitions

  • the invention relates to a pump, comprising a housing in which a rotor is arranged, which is rotatable in the housing about a rotational axis fixed to the housing, wherein the rotor has at least one recess in which at least one displacement body is accommodated, the axis of rotation when the rotor is rotating revolves while running along a housing inner wall of the housing, wherein the displacement body is radially movable in the recess between a position retracted into the recess and a position extended from the recess, wherein the housing inner wall in the circumferential direction around the axis of rotation has a region in which the Housing inner wall is spaced from an outer side of the rotor, so that in this area between the outside of the rotor and the housing inner wall, a first chamber is provided, wherein the displacement body in Circumferentially about the axis of rotation, the first chamber divided into a leading first partial chamber and a trailing second partial chamber.
  • Such a pump is generally known by its use.
  • a pump of the type mentioned is often referred to as a rotary vane pump.
  • a rotary vane pump has a usually hollow cylindrical housing, in which a rotor is arranged, which likewise usually has the shape of a cylinder.
  • the axis of rotation of the rotor is arranged eccentrically in the housing, so that the housing inner wall is spaced in a peripheral region of the rotor from the outside of the rotor.
  • the rotor contacts the housing inner wall between an inlet and outlet opening in the housing. The contact point forms the separation point between the suction and pressure chamber within the housing.
  • one or more, usually radially arranged recesses are or are incorporated in the rotor.
  • one or more displacement body which are designed in the form of rotary valves.
  • the rotary valves subdivide the chamber between the outside of the rotor and the housing inner wall into a plurality of sub-chambers.
  • the rotary valves are received radially movable in the recesses. Often they are pressed by a mounted in the bottom of the recess spring against the housing inner wall.
  • the classic rotary vane pumps are used as vacuum pumps, only a large vacuum range of 1.0 to 0.001 bar can be generated with them.
  • the corresponding achievable pressure is also limited.
  • the invention has for its object to form a pump of the type mentioned in that with the pump higher pump powers, whether as a vacuum pump or as a high-pressure pump or as a feed pump for gaseous and / or liquid media can be achieved.
  • this object is achieved with regard to the aforementioned pump in that the first sub-chamber is connected by a second channel in the rotor to a further chamber which is formed between the displacement body and an inner wall of the recess. and which, in accordance with the radial movements of the displacement body resulting from the rotation of the rotor around the axis of rotation, are alternately increased in volume, whereby an additional negative pressure is created or reduced in the further chamber and in the second partial chamber, whereby in the further chamber and in the first chamber Partial chamber creates an additional overpressure.
  • the achievable pump power is increased by not only the first chamber between the outside of the rotor and the housing inner wall is used as a suction and pressure chamber, but it is another chamber on the housing inner wall facing away from the displacement body between this and the inner wall of the recess is present, which is also used as a suction and pressure chamber, whereby the total volume of the suction and pressure chamber of the pump according to the invention over the classic rotary slide pumping is increased.
  • the displacement body moves from its retracted into the recess position in the extended position of the recess, creates a negative pressure or suction in the other chamber, and when the displacement body moves back from the extended position to the retracted position, arises in the another chamber overpressure.
  • the other chamber acts in the suction phase thus as an additional suction chamber and in the printing phase as an additional pressure chamber.
  • the further chamber is connected via at least one channel in the rotor with the first sub-chamber and the second sub-chamber, so that a corresponding pressure equalization between the two sub-chambers and the other chamber takes place depending on the suction or pressure phase.
  • the first channel and / or the second channel may be formed as holes in the rotor when this is formed as a solid body, or in the case of a hollow rotor as lines in the interior of the rotor.
  • the pump according to the invention can be used to generate a vacuum, to generate a high pressure, as a hydraulic pump, as a pump for gaseous and / or liquid media, etc.
  • the displacement body on its side facing the inner wall of the recess has a surface contour which corresponds to the inner contour of the inner wall of this recess.
  • the advantage of this measure is that the further chamber has a vanishingly small volume at completely retracted into the recess displacement body, whereby in the suction phase, a particularly high suction pressure can be generated, and in the printing phase, the medium located in the other chamber completely from the can be displaced further chamber, whereby particularly high pressures can be achieved.
  • the housing inner wall, along which the displacement body runs, has a surface contour which corresponds to the surface contour of the housing inner wall facing side of the displacement body corresponds.
  • the displacement body alone effects a sufficient sealing effect for sealing the first partial chamber from the second partial chamber without further sealing measures.
  • the displacement body is designed as a rotational body, which can rotate in the recess at least about an axis parallel to the axis of rotation.
  • This measure which is also considered without the characteristics of the plate as an independent invention, has the advantage that the friction between the displacement body and the housing inner wall is greatly reduced when running along the displacement body on the housing inner wall, because the displacement body can roll on the housing inner wall.
  • a film of the medium gas or liquid
  • the occurring in the classic rotary vane pumps, especially at high speeds of the rotor high friction forces are advantageously reduced to a minimum in this embodiment, whereby the pump according to the invention is much less wear than the classic rotary vane pumps and requires less energy for their drive.
  • the displacement body is a ball.
  • the advantage of a ball as a displacement body is that the ball can rotate in the recess to any endogenous axes, whereby a rolling of the displacement body on the housing inner wall even then is possible if the axis of rotation of the rotor is not exactly parallel to the housing center axis due to tolerances.
  • the ball is a hollow sphere.
  • the displacement body has a lower mass, which on the one hand reduces the forces acting on the displacer centrifugal forces when rotating the rotor, and also reduces the required for the operation of the pump drive energy.
  • the inner wall of the recess has the shape of a partial spherical surface.
  • the displacement body is a cylinder whose cylinder axis is parallel to the axis of rotation.
  • the displacement body is designed as a rotational body, wherein the cylinder rolls when running along the inner wall of the housing at this by rotation about the cylinder axis on the housing inner wall, which in turn greatly reduces the friction.
  • a cylinder has the further advantage that the further chamber and the first chamber can be made larger by a correspondingly long-lasting configuration of the cylinder in the direction of the cylinder axis to achieve even higher pump powers.
  • the rotor While in one embodiment of the displacement body as a ball, the rotor has a spherical basic shape, the rotor has a cylindrical basic shape in a configuration of the displacement body as a cylinder, which has the further advantage that the rotor axially in the direction of the cylinder axis of two or more sections Screwing can be assembled, whereby the introduction of the at least one first and the at least one second channel is simplified.
  • this in turn is preferably designed as a hollow cylinder, and according to a further preferred embodiment, the inner wall of the recess in the form of a partial cylinder jacket surface.
  • a first valve is arranged in the first channel, which closes the first channel when the displacement body moves from the retracted position to the extended position, and which releases the first channel, when the displacer from the extended position moved to the retracted position.
  • the first valve is used to control the pressure equalization between the other chamber and the first sub-chamber, which forms the pressure chamber during circulation of the displacement body.
  • the first valve which is then in its closed position, prevents the first partial chamber (pressure chamber) from communicating with the further chamber.
  • the first valve releases the first channel when the displacer moves from the extended position to the retracted position whereby, in the then occurring pressure phase, the further chamber communicates with the first subchamber to additionally increase the pressure in the first subchamber.
  • a second valve is preferably provided which releases the second passage when the displacer moves from the retracted position to the extended position and closes the second passage when the displacer moves from the extended position in FIG moves the retracted position.
  • the operation of the second valve is substantially inverse to the operation of the first valve and advantageously controls the communication between the further chamber and the second sub-chamber (suction chamber) in the suction phase, in which the additional chamber communicates with the second sub-chamber to produce an additional suction effect. and in the printing phase, the second valve interrupts the communication of the further chamber with the second sub-chamber.
  • first valve and / or the second valve are controlled automatically by the prevailing in the first and / or second channel on both sides of the first valve and / or on both sides of the second valve instantaneous pressures.
  • the advantage of this measure is that can be dispensed with measures of active control, such as an electromotive control of the valves, whereby the manufacturing cost of the pump and the cost of maintenance on the pump are reduced.
  • active control such as an electromotive control of the valves
  • the pressure which changes around the axis of rotation when the displacement body rotates is advantageously utilized in the first and / or second channel.
  • the first Valve opens automatically and the second valve is automatically closed.
  • the first valve has a first valve disk and a first valve seat, the first valve disk closing in the direction of the first sub-chamber against the first valve disk, wherein the first valve disk is preferably biased into its closed position.
  • the second valve preferably has a second valve disk and a second valve seat, wherein the second valve disk closes in the direction of the second partial chamber towards the first valve disk, wherein the second valve disk is preferably biased into its closed position.
  • the design of the first and / or second valve in a design with valve disk and valve seat is structurally very simple, and the bias of the first and / or second valve disk in the closed position allows advantageously and easily control of the opening and closing of the first and / or. or second valve by means of the prevailing in the first and / or second channel instantaneous pressure, as described above.
  • the first and second valves are arranged relative to each other so that their opening and closing movement are opposite to each other, which is particularly advantageous in a passive control of the valves by means of the prevailing instantaneous pressure.
  • the first valve in the first channel is arranged so that the first valve disk and the first valve seat are oriented substantially in the circumferential direction about the axis of rotation, and / or the second valve is arranged in the second channel, that the second valve plate and the second valve seat are oriented substantially in the circumferential direction about the axis of rotation.
  • This measure has the advantage that the forces acting on the two valves during rotation of the rotor in the circumferential direction about the axis of inertia acting forces the control of the two valves by means of the in the first and / or second channel prevailing instantaneous pressure additionally support. For example, these forces in the suction phase of the pump cause a safe closing of the first valve in the first channel (pressure channel).
  • a plurality of first channels and a plurality of second channels is present in the rotor.
  • This embodiment is particularly advantageous in connection with the design of the displacement body as a cylinder, because depending on the selected length of the cylinder by providing a plurality of first and second channels a sufficient pressure equalization cross section between the first sub-chamber and the second sub-chamber and the other chamber is created.
  • the pump according to the invention requires only one displacement body, even if the rotor of the pump according to the invention can be configured such that there are a plurality of displacement bodies in a plurality of recesses.
  • Figure 1 is a pump in a partially broken perspective view.
  • Fig. 2a shows a section along the line A-A in Fig. 2b) and Fig. 2b) shows a section along the line B-B in Fig. 2a);
  • Fig. 3a shows a section along the line A-A in Fig. 3b) and Fig. 3b) shows a section along the line B-B in Fig. 3a);
  • Fig. 4a shows a section along the line A-A in Fig. 4b) and Fig. 4b) shows a section along the line B-B in Fig. 4a);
  • FIG. 5a shows a section along the line AA in Fig. 5b) and Fig. 5b) shows a section along the line BB in Fig. 5a); 6 shows a further embodiment of a pump in a partially broken, perspective view;
  • Fig. 7a shows a section along the line A-A in Fig. 7b) and Fig. 7b) shows a section along the line B-B in Fig. 7a);
  • FIG. 8a shows a section along the line A-A in Fig. 8b) and Fig. 8b) shows a section along the line B-B in Fig. 8a).
  • a pump provided with the general reference numeral 10 is shown.
  • the pump 10 can be used as a vacuum pump, as a high-pressure pump, as a feed pump for gaseous and / or liquid media, etc.
  • FIGS. 2a) to 5b) show details of the pump 10 as well as various operating positions of the pump 10.
  • the pump 10 has a housing 12, which has a substantially spherical shape in the embodiment shown.
  • the housing 12 is constructed of two housing parts 14 and 16 (see Fig. 2a)) which are secured together along flanges 18 and 20, for example by screws (not shown).
  • the housing 12 has an inlet 22, through which a medium can be introduced into the housing 12, and an outlet 24, through which the medium is discharged again.
  • a rotor 26 is arranged in the housing 12 about an axis of rotation 28 in the direction of an arrow 30 in Fig. 2a) and an arrow 32 in Fig. 2b).
  • the rotor 26 in the direction of the axis of rotation 28 axial projections 34 and 36, which are rotatably mounted in the housing 12 by means of bearings 38, 40.
  • the axial extension 36 has a further extension 42, which protrudes from the housing 12 and serves as a drive shaft for the rotor 26.
  • the housing-fixed axis of rotation 28 is arranged in the housing 12 eccentrically to the housing center, as shown in Fig. 2a).
  • a housing inner wall 44 between a location 46 and a location 48 has a region in which the housing inner wall 44 is spaced from an outer side 50 of the rotor 26.
  • the medium gas or liquid
  • a first chamber 52 is thus seen in the region between the points 46 and 48 in the direction of rotation as indicated by arrow 30 about the axis of rotation 28, which is completely flooded by the medium admitted through the inlet 22 , as will be described below.
  • the outer side 50 of the rotor 26 substantially corresponds to the surface of a ball.
  • the rotor 26 has a recess 54, in which at least one, in the embodiment shown exact displacement body 56 is added.
  • the displacement body 56 is formed in the embodiment shown as a ball 58.
  • the ball 58 is a hollow sphere.
  • the ball 58 is rotatably received in the recess 54 around any endogenous axes.
  • the ball 58 is arranged radially movable in the recess 54 with respect to the axis of rotation 28.
  • the ball 58 When rotating the rotor 26 about the axis of rotation 28, the ball 58 always runs along the housing inner wall 44 of the housing 12, wherein the centrifugal forces acting on the ball 58 during rotation of the rotor 26 cause the ball 58 always abuts against the housing inner wall 44.
  • the ball 58 is movable in the recess 54 between a radially retracted position, which is shown in Fig. 2a) and b), and a maximum extended position, which is shown in Fig. 4a) and b) in the recess 54 movable.
  • the extent of the recess 54 in the direction perpendicular to the axis of rotation 28 is shown in FIG. 4a) and b) chosen so that the ball 58 is still taken in the maximum extended position with at least half a diameter in the recess 54 of the rotor 26.
  • the recess 54 in the rotor 26 is formed such that an inner wall 60 of the recess 54 facing the ball 58 corresponds to the surface contour of the ball 58, i. the inner wall 60 has the shape of a partial spherical surface.
  • the ball 58 is completely over half its circumference on the inner wall 60 of the recess 54 at.
  • the housing inner wall 44 of the housing 12, along which the ball 58 runs when rotating about the axis of rotation 28, has a surface contour which is also adapted to the surface contour of the ball 58, which here so in section according to FIG. 2b) partially circular, in particular semicircular is trained.
  • the ball 58 rotates about the axis of rotation 28, the ball 58 divides the first chamber 52 into a leading first sub-chamber 62 and a trailing second sub-chamber 64.
  • the first sub-chamber 62 forms a pressure space and the second sub-chamber 64 forms a suction space.
  • the first sub-chamber 62 and the second sub-chamber 64 change in circulation of the ball 58 along the housing inner wall 44 correspondingly relative to each other in terms of their volumes.
  • a further chamber 66 is formed, which is circulating around the ball 58 about the rotation axis 28 due to the radial movement of the ball 58 between its retracted into the recess 54 and position Recess 54 extended position in the volume periodically increased and decreased.
  • the ball 58 always seals the further chamber 66 against the first and second sub-chambers 62, 64, i. regardless of their radial position in the recess 54th
  • a first channel 68 is present, which connects the first sub-chamber 62 with the further chamber 66, and a second channel 70, which connects the second sub-chamber 64 with the further chamber 66.
  • the further chamber 66 can thus communicate with the first sub-chamber 62 and with the second sub-chamber 64 in a pressure-compensating manner, wherein the communication of the further chamber 66 with the first sub-chamber 62 and the second sub-chamber 64 takes place substantially alternately when the ball 58 about the rotational axis 28th circulates.
  • the first channel 68 and the second channel 70 open into the further chamber 66 via a common section 71.
  • the first channel 68 and the second channel 70 are formed in the embodiment shown as bores in the rotor 26.
  • the first channel 68 and the second channel 70 open into the first sub-chamber 62 and into the second sub-chamber 64 in the immediate vicinity of the opening of the recess 54.
  • a first valve 72 and in the second channel 70, a second valve 74 is arranged in the first channel 68.
  • the first valve 72 closes the first channel 68, so that the first sub-chamber 62 does not communicate with the other chamber 66 in this state, when the ball 58 moves from the retracted position to the extended position.
  • the first valve 72 releases the first channel 68 when the ball 58 moves from the extended position to the retracted position, so that in the open position of the first valve 72, the first sub-chamber 62 communicates with the further chamber 66, whereby in the first Part chamber 62 and the other chamber 66, the same pressure prevails.
  • the second valve 74 releases the second channel 70 as the ball 58 moves from the radially retracted position to the radially extended position such that the same pressure prevails in the second subchamber 64 and the further chamber 66 and closes the second channel 70, when the ball 58 moves from the extended position to the retracted position.
  • the first valve 72 and the second valve 74 are controlled automatically by the prevailing in the first channel 68 and the second channel 70 on both sides of the first and second valves 72 and 74 instantaneous pressures.
  • the first valve 72 has a first valve disk 76 which cooperates with a first valve seat 78, the first valve disk 76 closing in the closed position of the first valve 72 in the direction of the first partial chamber 62 against the first valve seat 78.
  • the second valve 74 has a second valve disk 80 which cooperates with a second valve seat 82, the second valve disk 80 closing in the closed position of the second valve 74 in the direction of the second partial chamber 64 against the second valve seat 82.
  • Both the first valve 72 and the second valve 74 are biased by a spring 84 and 86 in their closed position.
  • the bias of the valves 72, 74 is also a parameter of the control of the valves 72, 74 in addition to the above-mentioned instantaneous pressures in the channels 68, 70.
  • the valves 72 and 74 are arranged in the first channel 68 and the second channel 70, respectively, such that the first valve disk 76 and the first valve seat 78 or the second valve disk 80 and the second valve seat 82 are oriented around the rotation axis 28 in the circumferential direction.
  • the pump 10 has a seal 88 disposed in a central web 90 of the housing 12 that separates the inlet 22 from the outlet 24.
  • the seal 88 is shown in FIG. 2b) in the plane of the rotation axis 28 is approximately semicircular and biased by a wave spring 92 radially elastically against the rotor 26, so that the seal 88 abuts the rotor 26.
  • the rotor 26 In the operating position shown in Fig. 2a) and b), the rotor 26 is in the rotational position referred to here as the O ° position with respect to the rotation axis 28. In this position, the ball 58 is maximally retracted into the recess 54, so that the volume the further chamber 66 is minimal or even zero. The ball 58 is in this position approximately at the level of the central web 90 between the inlet 22 and the outlet 24th
  • first valve 72 and the second valve 74 are both closed, because on neither of the two valves 72, 74 acts an opening force.
  • the pump 10 is shown in an operating position in which the rotor 26 has rotated about the axis of rotation 28 by slightly less than 90 ° relative to the 0 ° position in Fig. 2a) and b).
  • the ball 58 has been under constant running something on the housing inner wall 44 is moved out of the recess 54 radially, whereby the volume of the further chamber 66 has increased.
  • an additional negative pressure is created in the further chamber 66, which causes the second valve 74 to open.
  • an additional suction effect arises at the inlet 22, through which medium flows through the inlet 22 through the second channel 70 into the further chamber 66, as indicated by arrows 94, 96.
  • the ball 58 begins to divide about the rotation axis 28, the first chamber 52 in the first sub-chamber 62 and the second sub-chamber 64 approximately in this orbital position. This results in the first chamber 52, a pressure chamber (first sub-chamber 62) and a suction chamber (second sub-chamber 64). By investing the ball 58 on the housing inner wall 44, both sub-chambers 62, 64 are sealed from each other.
  • the first valve 72 is still closed. Due to the fact that the first valve disk 76 closes against the first valve seat 78 against the direction of rotation of the rotor 26 about the axis of rotation 28, the first valve disk 76 is further pressed against the first valve seat 78 by the inertia and under the action of the spring 84, so that the In the further chamber 66 resulting suction or negative pressure, the first valve 72 does not open.
  • the second valve disc 80 closes against the second valve seat 82 in the direction of rotation, so that due to the rotational movement of the rotor 26 about the rotation axis 28, the inertia of the first valve disc 80 against the action of the spring 86 in cooperation with the Negative pressure in the further chamber 66 lifts off from the second valve seat 82, whereby the second valve 74 is opened.
  • the rotor 26 has rotated about the axis of rotation 28 by 180 °, starting from FIGS. 2 a) and b).
  • the ball 58 is extended in this position, maximum radially out of the recess 54.
  • the volume of the others Chamber 66 is now maximum and corresponds to about half the volume of the ball 58.
  • the second valve 74 is still in its open position, while the first valve 72 is still closed.
  • the further chamber 66 is now completely filled with the medium sucked through the inlet 22.
  • the first sub-chamber 62 and the second sub-chamber 64 have approximately the same volume.
  • the rotor 26 has in Fig. 5a) and b) about a little more than 90 ° further rotated about the axis of rotation 28 (about 270 ° position, wherein on this rotation, the ball 58th
  • the volume of the further chamber 66 decreases correspondingly, so that an overpressure is created therein, which closes the second valve 74 while the first valve 72 is open Force is generated by the now high overpressure in the first sub-chamber 62 and the portion of the first channel 58 which opens into the sub-chamber 62.
  • the further chamber 66 now communicates with the first sub-chamber 62 and the medium in the further sub-chamber 66 becomes via the first channel 68 in the first sub-chamber 62 and from there through the gap between the housing inner wall 44 and the outer side 50 of the rotor 26 in the area of the location 48 in the outlet 24 is pressed.
  • the second sub-chamber 64 which has steadily increased in volume starting from FIG. 4 a) and b), continues to suck, so that further medium is admitted through the inlet 22 into the second sub-chamber 64. At the operating position in Fig. 5a) and b) then closes again the state in Fig. 2a) and b).
  • the pump 10 As a vacuum pump or as a feed pump for a gas or liquid medium, medium is continuously drawn through the inlet 22 and continuously discharged through the outlet 24.
  • an outlet valve in particular a check valve may be arranged in the outlet 24, which releases the outlet 24 only when in the first sub-chamber 62, a correspondingly high pressure is present, the valve in the Outlet 24 opens.
  • FIG. 6 shows an embodiment of a pump 110 modified from FIG. 1. Further details of the pump 110 are shown in Fig. 7a) to 8b).
  • the same reference numerals as for the pump 10, increased by 100, are used for identical or comparable parts.
  • the pump 110 has a substantially cylindrical housing 112, in which a likewise substantially cylindrical rotor 126 is arranged, which rotates about a center of the housing eccentric fixed housing axis of rotation 128 in the housing.
  • a displacement body 156 is arranged, which is designed as a cylinder 158.
  • An inner wall 160 of the recess 154 has an inner contour, which is adapted to the surface contour of the cylinder 158.
  • a housing inner wall 144, along which the cylinder 158 runs when the rotor 126 rotates, is formed with a surface contour which is adapted to the cylinder surface of the cylinder 158.
  • the housing inner wall 144 has a substantially rectangular shape in a section parallel to the rotation axis 128, and seen in the circumferential direction about the rotation axis 128, the housing inner wall 144 is substantially the surface of a cylinder.
  • the cylinder 158 is arranged in the recess 154 so that its cylinder axis 159 extends parallel to the axis of rotation 128. Like the ball 58 of the pump 10, the cylinder 158 rolls on the housing inner wall 144 when it revolves around the rotation axis 128, whereby friction losses are minimal.
  • the cylinder 158 is formed as a hollow cylinder.
  • the inner wall 160 of the recess 154 is likewise adapted to the surface contour of the cylinder 158 and has the shape of a Operazylindermantel- surface, so that the cylinder 158 in its recess in the recess 154 maximum radially retracted position on the inner wall 160 along an approximately semicircular contact line is present, as shown in Fig. 7a).
  • the housing inner wall 144 has, in the circumferential direction about the rotation axis 128, a region in which the housing inner wall 144 is spaced from an outer side 150 of the rotor 126, so that a first chamber 152 is formed in this region between the outer side 150 of the rotor 126 and the inner housing wall 144 is.
  • the first chamber 152 is divided when rotating the cylinder 158 about the axis of rotation 128 in a first sub-chamber 162 and a second sub-chamber 164, as shown in Fig. 8a) can be seen.
  • a further chamber 166 is formed, wherein the further chamber 166 with the first partial chamber 162 is connected via a first channel 168 and with the second sub-chamber 164 via a second channel 170.
  • FIG. 6 shows three first channels 168 and correspondingly also three common sections 171 of the channels 168 and 170.
  • a first valve 172 and a second valve 174 are preferably arranged in each case.
  • the operation of the first valve or valves 172 and / or the second valve 174 is identical to the operation of the first valve 72 and the second valve 74 of the pump 10.
  • Fig. 7a) and b) show the pump 110 in an operating position corresponding to the operating position of the pump 10 in Fig. 2a) and b), and Fig. 8a) and b) show the pump 110 in an operating position, the operating position the pump 10 in Fig. 4a) and b) corresponds.
  • the length of the cylinder 58 and corresponding to the rotor 126 can be chosen more or less long to achieve a corresponding pumping power.
  • the rotor 126 may be designed in several parts in the direction of the axis of rotation 128 or the cylinder axis of the cylinder 158, which in particular also simplifies the introduction of the first and second channels 168, 170.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

La présente invention concerne une pompe (10) présentant un boîtier (12) dans lequel se trouve un rotor (26) qui peut tourner dans le boîtier (12) sur un axe de rotation (28) solidaire du boîtier, le rotor (26) présentant au moins une cavité (54) dans laquelle est logé au moins un corps de refoulement (56) qui, lorsque le rotor (26) tourne, effectue des révolutions autour de l'axe de rotation (28) et se déplace ainsi le long d'une paroi intérieure (44) du boîtier (12), le corps de refoulement (50) pouvant effectuer un mouvement radial dans la cavité (54) entre une position rentrée dans la cavité (54) et une position sortie de la cavité (54). La paroi intérieure (44) du boîtier présente, lorsqu'on la considère en direction circonférentielle autour de l'axe de rotation (28), une zone dans laquelle ladite paroi intérieure (44) est espacée du côté extérieur (50) du rotor (26) de sorte que dans cette zone est formée une première chambre (52) entre le côté extérieur (50) du rotor (26) et la paroi intérieure (44) du boîtier, et le corps de refoulement (56), lorsqu'il effectue des révolutions autour de l'axe de rotation (28), subdivise la première chambre (52) en un premier compartiment (62) avant et un deuxième compartiment (64) arrière. Le premier compartiment (62) est relié à une autre chambre (68) par un premier canal (68) et le deuxième compartiment (64) est relié à l'autre chambre (68) par un deuxième canal (70) s'étendant dans le rotor (26), ladite autre chambre étant formée entre le corps de refoulement (56) et une paroi intérieure (60) de la cavité (54), et ayant un volume qui, en fonction des mouvements radiaux du corps de refoulement (56) lorsque le rotor (26) tourne sur l'axe de rotation (28), alternativement augmente, ce qui permet la formation d'une dépression supplémentaire dans l'autre chambre (68) et dans le deuxième compartiment (64), ou diminue, ce qui permet la formation d'une surpression supplémentaire dans l'autre chambre (66) et dans le premier compartiment (62).
EP09778231A 2008-09-12 2009-09-01 Pompe rotative Withdrawn EP2334935A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008047516A DE102008047516B4 (de) 2008-09-12 2008-09-12 Pumpe
PCT/EP2009/006305 WO2010028756A2 (fr) 2008-09-12 2009-09-01 Pompe

Publications (1)

Publication Number Publication Date
EP2334935A2 true EP2334935A2 (fr) 2011-06-22

Family

ID=41693708

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09778231A Withdrawn EP2334935A2 (fr) 2008-09-12 2009-09-01 Pompe rotative

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US (1) US20110223041A1 (fr)
EP (1) EP2334935A2 (fr)
CN (1) CN102149922A (fr)
DE (1) DE102008047516B4 (fr)
WO (1) WO2010028756A2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106704182B (zh) 2015-08-07 2019-03-29 珠海格力电器股份有限公司 流体机械、换热设备和流体机械的运行方法
CN106826096B (zh) * 2017-04-17 2018-08-17 中国工程物理研究院激光聚变研究中心 一种金属空心微球制造方法

Family Cites Families (11)

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Publication number Priority date Publication date Assignee Title
GB647781A (en) * 1946-05-24 1950-12-20 Nicolas Barna Improvements in or relating to hydraulic pumps
GB654808A (en) * 1948-11-23 1951-06-27 Alfred George Langdon Improvements in or relating to rotary circulating pumps
US3447476A (en) * 1967-05-25 1969-06-03 Edward L Farris Rotary fluid device
FR2598746B1 (fr) * 1986-05-16 1990-02-09 Bitar Joseph Machine a piston rotatif.
EP0695870B1 (fr) * 1993-03-01 1999-12-15 Japan I.D. Tech. Inc. Pompe du type compresseur renforcee
CN1116277A (zh) * 1994-08-03 1996-02-07 肖茂如 双圆弧转子泵
DE29521598U1 (de) * 1995-07-31 1998-01-22 Voulgaris, Alexander, 83734 Hausham Hydraulische Maschine in Zahnring-Bauweise
US6099261A (en) * 1998-06-08 2000-08-08 Worden; Gary Roller vane stage for a fuel pump
US7371053B2 (en) * 2004-07-29 2008-05-13 General Motors Corporation Two-stage hydraulic pump
US8517705B2 (en) * 2005-03-09 2013-08-27 Merton W. Pekrul Rotary engine vane apparatus and method of operation therefor
DE102006007519A1 (de) * 2006-02-16 2007-08-30 Roland Eckgold Einstellbarer Segmentverdränger

Non-Patent Citations (1)

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Title
See references of WO2010028756A2 *

Also Published As

Publication number Publication date
WO2010028756A3 (fr) 2010-11-11
CN102149922A (zh) 2011-08-10
DE102008047516A1 (de) 2010-03-25
WO2010028756A2 (fr) 2010-03-18
DE102008047516B4 (de) 2010-11-25
US20110223041A1 (en) 2011-09-15

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