EP1813812B1 - Progressive cavity pump - Google Patents
Progressive cavity pump Download PDFInfo
- Publication number
- EP1813812B1 EP1813812B1 EP06001518A EP06001518A EP1813812B1 EP 1813812 B1 EP1813812 B1 EP 1813812B1 EP 06001518 A EP06001518 A EP 06001518A EP 06001518 A EP06001518 A EP 06001518A EP 1813812 B1 EP1813812 B1 EP 1813812B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- inner part
- pressure
- rotor
- progressive cavity
- cavity pump
- 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.)
- Not-in-force
Links
- 230000000750 progressive effect Effects 0.000 title claims 20
- 229920001971 elastomer Polymers 0.000 claims abstract description 9
- 239000000806 elastomer Substances 0.000 claims abstract description 6
- 230000033001 locomotion Effects 0.000 claims description 41
- 238000004891 communication Methods 0.000 claims description 8
- 229910010293 ceramic material Inorganic materials 0.000 claims description 4
- 239000000919 ceramic Substances 0.000 abstract description 2
- 239000012530 fluid Substances 0.000 description 17
- 230000008878 coupling Effects 0.000 description 10
- 238000010168 coupling process Methods 0.000 description 10
- 238000005859 coupling reaction Methods 0.000 description 10
- 239000013536 elastomeric material Substances 0.000 description 5
- 230000001419 dependent effect Effects 0.000 description 4
- 238000005192 partition Methods 0.000 description 4
- 239000011248 coating agent Substances 0.000 description 3
- 238000000576 coating method Methods 0.000 description 3
- 238000005086 pumping Methods 0.000 description 3
- 239000002184 metal Substances 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 230000002250 progressing effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
- F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
-
- 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
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0007—Radial sealings for working fluid
- F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
-
- 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
- F04C2250/00—Geometry
- F04C2250/20—Geometry of the rotor
- F04C2250/201—Geometry of the rotor conical shape
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2203/00—Non-metallic inorganic materials
- F05C2203/08—Ceramics; Oxides
Definitions
- the invention relates to an eccentric screw pump.
- Eccentric screw pumps which are also known under the name Moineau pumps, have a helical rotor. softer on a rotation eccentric running in a surrounding stator. Pumps are known in which the stator and the rotor have a constant cross section over their axial length.
- a sufficient pressure force between the stator and rotor is important to ensure the tightness of the pump at high pressures. At the same time, the fit should not be too tight to keep the friction in the pump low.
- the eccentric screw pump according to the invention has an annular outer part with an inner part arranged therein.
- the inner part and the outer part move in a known manner relative to each other, wherein the pumping movement is achieved.
- the inner part may be formed as a rotor which rotates in the outer part, which forms a stationary stator.
- the rotor and the stator perform an eccentric movement relative to each other, whereby this eccentric movement can be carried out either by the rotor and / or by the stator.
- the outer part rotates as a rotor around the fixed inner part, which then serves as a stator. Again, the eccentric motion can be either from the rotating outer part or the fixed, d. H. non-rotating inner part are executed.
- both the inner part and the outer part rotate to each other to perform the relative movement to each other.
- the eccentric movement occurring during operation can also be realized simultaneously by the inner part and outer part, instead of only one of the two parts executing the eccentric movement.
- all conceivable drive combinations which are known from such pumps, can be used in the eccentric screw pump according to the invention.
- the interior of the outer part and the exterior of the inner part are designed such that they taper in a manner corresponding to one another towards an axial side, ie they are preferably conical in the axial direction.
- This arrangement makes it possible that when the inner part in the direction of tapered end is further pressed into the surrounding outer part, the fit between the inner part and outer part is reduced and the contact pressure is increased at the contact surfaces between the inner and outer part. In this way, the fit or the contact pressure at the contact surfaces between the inner and outer part can be adjusted by axial relative movement between the inner and outer part.
- the inner and outer parts are mounted movably in the axial direction relative to each other and in such a way that the mobility is also given during operation of the pump, ie for example upon rotation of the inner part.
- the inner and / or the outer part are formed such that increases the contact pressure between the inner and outer part at a higher pressure in the pump or increasing pressure on the pressure side of the pump. That is, in the pump according to the invention, the fit or the contact pressure between inner and outer part automatically sets during operation, which is ensured by the higher contact pressure at higher pressure on the pressure side of the pump, even at high pump pressure sufficient tightness of the pump. Further, it is possible that at lower pressure on the pressure side of the contact pressure at the contact surfaces between the inner and outer part is reduced, so that the friction is reduced. In this way, it is possible to keep the friction as low as possible and at the same time the contact pressure between the inner and outer part as large as necessary at different pump pressures.
- This operation is inventively realized in that inner and / or outer part are formed such that a voltage applied to the pressure side of the eccentric screw pump and / or in the cavities of the eccentric screw between the inner and outer part pressure is used to generate a force which in the axial direction inner and outer parts pressed into each other. That is, this force produced by the pressure on the pressure side or in the cavities acts in the axial direction, in which the inner and outer parts taper on the inner part or in the direction in which the inner and outer parts expand on the outer part.
- Embodiments are also conceivable in which the pressure acts both on the outer part and in the opposite direction on the inner part.
- the eccentric screw pump is designed such that the pressure applied to the pressure side acts on a side facing away from the tapered end of the inner part surface of the inner part.
- an axial force acting in the direction of the tapered end of the inner part is generated, which presses the inner part towards the tapered end of the outer part.
- the magnitude of the acting force can also be influenced, so that by adjusting the surface, the force relationships and in particular the range in which the contact pressure between the inner and outer part can vary, can be preset.
- the surface in relation to the other end faces or end faces of the inner part, on which acts on the pressure applied to the suction or pressure side designed to preset the desired balance of power, which act on the inner part, can.
- the inner part and the outer part are arranged according to a first embodiment such that the axial side, to which the inside of the outer part and the exterior of the inner part taper, is the pressure side of the eccentric screw pump.
- the pressure on the pressure side acts on the small end face of the inner part. This force would thus push apart the inner and outer parts, if no opposite force acts on the inner and / or outer part.
- a channel is formed in the interior of the inner part, which is open to the pressure side or to a cavity inside the eccentric screw pump and with a side facing away from the pressure side of the inner part is in communication.
- the pressure prevailing on the pressure side or in the interior of the pump pressure is directed to a side facing away from the pressure side, there to generate a force which is directed axially opposite to the force acting on the pressure side of the inner part on this force and the inner part in the External part holds in abutment or pushes into the outer part.
- a pressure chamber is arranged on the axial side facing away from the pressure side of the inner part, which is in communication with said channel.
- the pressure chamber has a variable length in the axial direction and has a side facing away from the pressure side, connected to the inner part inner surface.
- the over the channel in the pressure chamber conducted pressure, which prevails on the pressure side of the pump, leads to an expansion of the pressure chamber and thus to a change in length of the pressure chamber.
- the pressure acts on an inner surface of the pressure chamber, which faces away from the pressure side and thus generates an axially directed pressure force on the inner part, which presses this towards the tapered end of the inner part in the outer part and ensures that a sufficiently high contact pressure between inner and outdoor part is maintained even at higher pressure on the pressure side of the pump.
- the pressure chamber is preferably sealed from the environment. This is particularly necessary if the pressure chamber is arranged on the suction side of the pump in the axial extension of the inner part. In this preferred embodiment it is achieved that also acts on the suction side of the pressure applied to the pressure side on an end face or facing the axial end surface of the inner part.
- the inner surface of the pressure chamber, on which this pressure acts, is preferably fixedly connected to the inner part or movement-coupled in the axial direction with the inner part in order to transmit the axially acting pressure force from the inner surface to the inner part.
- the pressure chamber is formed in the interior of a shaft driving the inner part, wherein the shaft with the pressure chamber in its length is variable.
- the shaft connects a drive motor, preferably an electric drive motor with the réelleteil.
- Das inner part forms a rotor which rotates relative to the outer part, which preferably acts as a stator.
- the drive takes place while on the shaft, which thus forms a rotor shaft.
- the pressure chamber via a piston-cylinder arrangement and / or by an elastic in the axial direction outer wall in its length is variable.
- the elastic outer wall may be formed, for example, in the manner of a bellows made of metal, an elastomer or rubber. Due to the elasticity can be realized at the same time a bias.
- the piston-cylinder arrangement can also be realized the multi-part design of the outer wall of the pressure chamber, wherein the parts of the outer wall of the pressure chamber telescopically engage each other.
- a throttle point may be formed in the channel or in the pressure space communicating with the channel.
- This throttle point is used to dampen pressure fluctuations that occur during operation of the pump to prevent a change in the contact pressure between the inner and outer part in short-term pressure fluctuations.
- the throttle point is arranged so that the transmission of the pressure from the pressure side of the inner part to the side facing away from the pressure side of the inner part or the inner surface of the pressure chamber is only attenuated via the throttle point, so that pressure changes in the pressure chamber are much slower than at the Pressure side of the pump.
- the side facing away from the pressure side ie the remote projected surface, with which the channel is in communication is preferred larger than the pressure side facing end face of the inner part. If the surface which communicates with the channel and which faces away from the pressure side, for example the inner surface of the pressure chamber, has the same pressure as the end surface of the inner part on the pressure side of the pump, the axial direction is due to the larger surface Pressure side towards the inner part acting force is greater than the force acting from the pressure side to the suction side in the axial direction force.
- the inner part is always acted upon in the direction of the pressure side with a larger force and is pressed into or against the outer part when the pressure side on the side of the tapered end of the inner and outside part.
- the force pressing the inner part into the outer part is thus dependent on the area difference between the end face of the inner part on the pressure side and the surface facing away from the pressure side and proportional to the pressure on the pressure side of the pump or to the pressure difference between the suction side and pressure side.
- the inner and outer parts are arranged such that the axial side, to which the interior of the outer part and the exterior of the inner part taper, is the suction side of the eccentric screw pump. That is, the inner part and the inside of the outer part expand toward the pressure side of the pump. Since in this embodiment, the large end face of the inner part is located to the pressure side, it is easily possible that the pressure applied to the pressure side acts on this surface and so presses the inner part in the outer part and always for a sufficient pressure force at the points of contact between inside - and outer part provides. The pressure acting on the suction side on the inner part is lower, so that a smaller force acts on the inner part on this side.
- a pressure channel which connects the pressure side or a cavity in the interior of the eccentric screw pump with a side facing away from the pressure side surface of the outer part.
- This is actually a suction side of the pump-facing surface which is acted upon via the pressure channel with the voltage applied to the pressure side or in the interior between the inner and outer part, so that from this side, on which the tapered end of the outer part is located the outer part is pressed onto the inner part.
- a throttle point may be arranged in the pressure channel.
- the tapered end of the inner part is located on the pressure side, so that the shaft driving the inner part acts on that end side of the inner part, on which the largest Querterrorismsfizze the inner part located is.
- at least one pressure surface which faces away from the suction side in the axial direction, is preferably arranged on the inner part and / or on the shaft connected to the inner part on the axial side. H. facing the pressure side, and on which acts on the pressure side of the eccentric screw pump applied pressure. By applying this pressure surface, a compressive force is generated which acts in the axial direction to the suction side and thus to the tapered end of the inner part and the inner space of the outer part and thus pushes the inner against the outer part.
- At least one biasing element is provided, which acts on the inner part with a biasing force in the axial direction in which it tapers, and / or which acts on the outer part with a biasing force in the opposite axial direction.
- a biasing element can in both of the above-described basic embodiments of the invention, ie regardless of whether the pressure side is located on the tapered or extended end of the inner part, are used.
- Such a biasing element or more such biasing elements cause the inner and outer parts are pressed against each other in the axial direction, so that the serving as sealing surfaces touch points or lines of contact between the inner and outer part are held in abutment.
- the biasing elements cause even at low pressure on the pressure side or less or no pressure difference between suction and pressure side between a sufficient pressure force between the inner and outer part is given, so that even when starting the pump, the pump chambers formed inside are tight and the function is guaranteed.
- the inner part is preferably connected via a shaft or rotor shaft with a drive motor, in particular an electric drive motor, wherein the shaft at a hinge point, for. B. at the articulation point on the output shaft of the drive motor, is articulated and the hinge point is preferably purely rotationally movable.
- a drive motor in particular an electric drive motor
- the shaft at a hinge point, for. B. at the articulation point on the output shaft of the drive motor is articulated and the hinge point is preferably purely rotationally movable.
- the inner part serving as a rotor to perform an eccentric movement during its rotation, wherein the pivot point itself preferably rotates only about a longitudinal axis and does not perform any eccentric or axial movement in the direction of the longitudinal axis. That is, there is no eccentricity of movement at the hinge point itself.
- the rotor shaft may be made flexible or provided with a hinge, so that an eccentric movement about a fictitious pivot point is possible.
- the inner part is connected via a shaft with a drive motor and the shaft with the inner part together eccentrically movable, wherein inner part and shaft are arranged such that the eccentricity of their movement starting from a hinge point, z. B. the articulation point on the drive motor, increases, preferably increases linearly.
- no eccentricity is given in addition to the rotary motion of the shaft.
- Starting from this point perform inner part and shaft in addition to its rotation about its longitudinal axis an eccentric movement about the hinge point, while the longitudinal axis of the shaft preferably moves along a conical surface, the tip of the cone is located in the hinge point. That is, the shaft rolls over the conical surface.
- the longitudinal axis of the inner part and the longitudinal axis of the shaft form a straight line, which perform about the pivot point described eccentric movement over the conical surface crevices. In this way, an eccentric movement of the inner part is achieved in the interior of the outer part, so that the inner part rolls on the inner surface of the outer part.
- the inner part is preferably formed at least on its surface of a ceramic material, while the outer part is preferably formed at least on the inner part facing surface of an elastomer.
- the inner part is made entirely of a ceramic material and the outer part is made entirely of an elastomer material. That is, the inner part has a hard surface, while the outer part has an elastic surface facing the inner part.
- the following embodiments relate to ⁇ ntriebsan elevenen in which the inner part of the pump is designed as a rotor and is driven in rotation. Accordingly, the outer part of the eccentric screw pump is designed as a non-rotating stator. Ie. the relative movement between rotor and stator is generated solely by rotation of the rotor.
- the principle underlying the invention of adjusting the fit between the rotor and the stator can also be used in arrangements in which the outer part described below as a stator rotates relative to the inner part.
- eccentric screw pump is designed as a submersible pump, which has at its lower end an electric drive motor 2, on which axially the actual pump unit 4 is flanged.
- the pump unit 4 has circumferential inlet openings 6 and at its upper axial end in the direction of the longitudinal axis X a discharge nozzle 8.
- the eccentric screw pump arranged in the interior of the pump unit 4 has an annular stator 10 and a helical rotor 12 arranged in its interior.
- the stator inside is coated with an elastomeric material 14, which comes into contact with the outer surface of the rotor 12 at the contact points.
- the rotor 12 is preferably made of steel, in particular stainless steel or ceramic.
- Rotor 12 and stator 10 form a known eccentric screw or Moineau pump, in which the rotor 12 rotates in the interior of the stator 10 about its longitudinal axis.
- the longitudinal axis simultaneously describes a circular movement about the stator longitudinal axis, ie the rotor rotates eccentrically in the stator 10.
- the pumping effect is due to the fact that the Statorinnenwandung and the Rotorau fieldwandung have a different number of helical turns.
- the eccentric screw pump is conical, ie, the stator 10 and the interior of the stator 10 and the rotor 12 taper toward an axial end face 16 back.
- the end face 16 forms the pressure side of the pump, while the opposite end face 18 of the stator 10 is located on the suction side of the pump.
- the rotor 12 is connected to the wear shaft 24 of the drive motor 2 via a rotor shaft 20 adjoining the end face 18 at an articulation point 22.
- the rotor shaft 20 is articulated so that the rotor shaft 20 can additionally perform an eccentric movement during its rotation.
- the articulation of the rotor shaft 20 will be described later Bellows 30 realized at the end of the rotor shaft 20 facing the drive motor 2.
- This eccentric movement takes place in such a way that a fictitious pivot point 23 on the longitudinal axis of the bellows 30 forms the tip of a cone, on the surface of which the rotor shaft 20 moves eccentrically with the rotor 12, while the rotor shaft 20 and the rotor 12 driven by Turn the drive motor 2 about its longitudinal axis.
- the rotor 12 performs together with the rotor shaft 20 in the interior of the stator 14 an eccentric movement, which takes place conically around the longitudinal axis X and the pivot point 23 in the bellows 30.
- the eccentricity results from the design of stator 10 and rotor 12, so that the rotor 12 automatically performs the described eccentric movement upon rotation of the rotor about its own axis.
- the eccentric movement is such that on the end face 16, the eccentricity is greatest, ie the diameter of the circle on which moves the central axis of the rotor during rotation is greatest.
- the pivot point 23 in the bellows 30 no eccentricity is given.
- At the end face 18 of the rotor moves with a lower eccentricity than at the end face 16, that is, the diameter of the circle on which the central axis of the rotor moves during its rotation, is smaller.
- the eccentric screw pump according to the invention is designed so that the fit between the rotor 12 and the stator 10 automatically adjusts as a function of the pressure conditions on the pressure side and the suction side of the eccentric screw pump and in particular the pressure difference between the pressure and suction side. That is, the contact pressure at the contact surfaces between the rotor 12 and stator 10 is adjusted automatically depending on the fluid pressure.
- the rotor 12 has a centrally disposed channel which extends in the longitudinal direction from the end face 16 to the pressure surface 26, which here forms the opposite end face of the rotor 12.
- the channel 28 opens into the interior of the hollow rotor shaft 20.
- Fig. 4 This leads to a balance of power, as essentially in Fig. 4 is shown by a detailed view.
- a force F z which is caused by the fluid pressure at the pressure side of the pump.
- This force F z is dependent on the size, ie, the diameter B of the front side of the rotor 12. Since the fluid pressure is conducted from the suction side through the channel 28 into the interior of the rotor shaft 20, is on the rotor 12 facing inner surface, which Pressure surface 26 forms, generated by the voltage applied to the pressure side of the rotor 12 fluid pressure F a .
- This force is furthermore dependent on the size of the pressure surface 26, ie on the inner diameter A of the rotor shaft 20, which corresponds to the diameter of the pressure surface 26.
- the pressure surface 26 is larger than the frontal surface of the rotor 12 at the end face 16. This results in that, since the same pressure is applied to both sides, the force F a is always greater than the force F z , so as to ensure in that the rotor 12 is pressed into the stator 10 in the direction of the end face 16. The acting in the axial direction.
- Pressure force is the difference of the forces F a and F z , ie, the force which results from the area difference of the two end faces of the rotor 12 multiplied by the voltage applied to the pressure side fluid pressure, and the contributions from the pressure conditions in the cavities between the rotor 12 and the stator 10. It follows that with increasing fluid pressure on the pressure side and the contact pressure between the rotor and stator increases.
- the rotor shaft 20 is formed so that an axial displaceability of the rotor 12 in the direction of the longitudinal axis W of the rotor 12 and the rotor shaft 20 is given.
- This Löngsverschieb harshness also realized by the bellows 30, which forms an elastic wall of the rotor shaft 20.
- the bellows 30 may be formed of metal or plastic, in particular an elastomer. He must in addition to the elasticity in the axial direction W and a torsional stiffness for transmitting the torque which acts on the rotor shaft 20, as well as a flexibility for the eccentric movement of the rotor 12 have.
- the rotor shaft 20 with the bellows 30 is hollow, so that in the interior of a pressure chamber 32 and 34 is formed.
- the pressure chamber 32 lies in the rigid part of the rotor shaft 20, the pressure chamber 34 is located in the part of the rotor shaft 20 formed by the bellows 30.
- the pressure chambers 32 and 34 are separated by a partition wall 36.
- the partition wall 36 is disposed at the axial end of the rigid part of the rotor shaft 20 adjacent to the part formed by the bellows 30.
- the partition wall 38 has a channel which extends between the two end faces and connects the pressure chambers 32 and 34 adjacent to the two end faces.
- the channel 38 forms a throttle point, through which the fluid passed from the pressure side of the rotor 12 through the channel 28 can flow from the pressure chamber 32 into the pressure chamber 34 and back. This throttle point damps periodically occurring pressure fluctuations, which occur due to the design of the operation of the eccentric screw pump. In this way, fluctuations of the pressing force F a due to these pressure fluctuations are eliminated. Only larger pressure fluctuations with a larger period lead to a change in the force F a .
- the bellows 30 acts due to its elasticity in the axial direction further as a spring element which generates a bias between the rotor 12 and stator 40. Due to the elasticity of the bellows 30, the rotor 12 is pressed in the direction of the longitudinal axis W in the stator interior.
- eccentric screw pump has a stator 40 in which a rotor 42 is arranged, wherein the stator 40 and rotor 42 have the usual in eccentric screw pumps helical surface design.
- the stator 40 is disposed in a housing 44 having at a first axial end a suction port 46 through which the fluid to be delivered penetrates into the pump.
- the suction opening 46 faces the end face 48 of the stator 40 and the rotor 42, which have the smallest diameter.
- the rotor 42 and the interior of the stator 40 has a larger diameter.
- the interior of the stator 40 and the outer periphery of the rotor 42 are thus conical.
- the end face 50 faces the pressure side of the eccentric screw pump formed by the stator 40 and the rotor 42.
- the rotor 42 merges into a rotor shaft 52 on the axial side, in which case the rotor 42 and the rotor shaft 52 are designed as an integral component.
- the rotor shaft 52 is connected at its end remote from the rotor 42 axial end 54 with a motor shaft of a drive motor, not shown here.
- the rotor shaft 52 lead to the rotor 42 an eccentric movement in the interior of the stator 40, wherein the rotor shaft 52 on the one hand rotates about its longitudinal axis W and on the other performs an eccentric movement about the longitudinal axis X of the stator 40.
- the rotor 42 performs here, as described in the first embodiment, due to the conical configuration of the rotor 42 and stator 40 from a movement in which the longitudinal axis W runs on a conical surface.
- the tip of this cone is located in the point of articulation of the rotor shaft 52 on the motor shaft. That is, the end of the rotor 42 located at the end face 48 performs an eccentric movement with a larger diameter about the longitudinal axis X than the end region of the rotor 42 at the end face 50.
- the rotor shaft 52 has a seal 56 which seals the space 58, which adjoins the stator 40 on the pressure side, to the engine.
- shoulder surfaces 60 are formed, which are facing away from the rotor 42 and thus the suction side on the front side 48. Since these shoulder surfaces 60 are located in the interior of the space 58, in which the pressure-side fluid pressure acts, the fluid pressure acts on these shoulder surfaces 60 and generates a force in the direction of the longitudinal axis W of the rotor shaft 52, which the rotor shaft 52 with the rotor 42 to the front side 48th towards the stator 40. In this way, a pressure force between rotor 42 and stator 40 is generated by the fluid pressure on the pressure side, which increases with increasing fluid pressure at the pressure side of the pump and decreases with decreasing fluid pressure. Thus, an automatic adjustment of the fit and thus the pressure force between the rotor 42 and stator 40 is ensured during operation of the pump in this embodiment.
- the rotor shaft with the rotor 42 is integrally formed of a ceramic material and has a cavity 62 in its interior.
- the cavity 62 has a polygonal cross-sectional shape and is at its end facing away from the rotor 42 with a coupling element 64 in engagement, which has a corresponding polygonal outer cross-sectional shape.
- the coupling element 64 forms the axial end 54 of the rotor shaft 52.
- the coupling element 64 is axially displaceable in the direction of the longitudinal axis W in the interior of the cavity 62. In this way, axial displacement of the rotor shaft 52 is achieved with the rotor 42 relative to the stator 40.
- the coupling element 64 allows the eccentric movement of the rotor shaft 52 about a fictitious hinge point 65 on the central axis of the coupling element 64.
- the coupling element 64 is formed of an elastomeric material, preferably rubber or at least on its inner rotor shaft 52 facing region of a coating an elastomeric material or rubber. This leads to an articulated mounting of the coupling element 64 in the cavity 62 in the interior of the rotor shaft 52.
- the rotor shaft about the coupling member 64 and the pivot point 65 perform an eccentric movement due to the articulation of the connection between the rotor shaft 52 and coupling member 64.
- the pressing force with which the rotor 42 is pressed into the stator 40 thereby automatically adjusts itself due to the pressures on the suction and pressure side of the rotor 42 and the ambient pressure and in particular based on the balance of forces between the on the shoulder surfaces 60 and the end face of the Rotor 42 on the axial side 48 acting compressive forces and the force acting on the axial end 54 ambient pressure.
- a spring element 66 is provided, which generates a bias of the rotor in the direction of the stator 40.
- the stator 40 has on its rotor 42 facing inner surface on a coating 68 of an elastomeric material.
- the pressure side 70 of the pump is located at the axial end of the conical rotor 72 with the small diameter, ie according to the first of the FIGS. 1 to 4 described embodiment.
- the rotor 72 is as in the embodiment according to FIG FIGS. 1 to 4 arranged inside a stator 74.
- the stator 74 is movably guided in a housing 76 in the axial direction X, ie in the direction of the longitudinal axis of the stator 72.
- the stator 74 is formed such that an end face 78 facing the pressure side 70 is formed, on which the fluid pressure of the pump acting on the pressure side 70 acts. This pressure generates a pressure force F b on the stator, which presses it against the rotor. In this way, a self-adjusting pressure force between the rotor 72 and stator 74 is generated as a function of the fluid pressure in the pump.
- the arrangement may alternatively be used in such a way that the suction side of the pump is located at the axial end of the conical rotor 72 with the small diameter.
- the output side pressure of the Exzenfierschneckenpumpe is applied to the axial-side end face 80, wherein the rotor 72 is fixed by a thrust bearing, not shown.
- the pressure-side pressure through a channel or gap 82 between the housing 76 and the stator 74 on one of the suction side of the pump facing end face 84 of the stator 74 are passed.
- a compressive force is generated at this end face 84, which presses the stator 72 on the rotor.
- Fig. 7 shows an embodiment in which the rotor 86 driven by the rotor shaft 88 can perform a purely rotational movement.
- the occurring eccentricity between the rotor 86 and stator 90 upon rotation of the rotor 86 is compensated in this embodiment by a mobility of the stator 90.
- the stator 90 is part of a stator housing, which is extended beyond the axial end face 92 of the rotor 86 addition.
- the extension 94 of the stator housing is tubular and passes at its end remote from the rotor 86 in a bellows 96, which is connected to the discharge port 98 of the surrounding pump housing 100.
- the pressure side of the pump is on the side of rotor 86 and stator 90, which has the larger cross-section.
- the end 102 of the rotor 86 and stator 90th formed eccentric screw pump forms the suction side of the pump, which is in communication with the inner of the surrounding pump housing 100 and a suction port 104 which opens into this pump housing.
- the rotor 86 rotates about its longitudinal axis.
- the stator 90 with the subsequent extension 94 simultaneously performs an eccentric movement with respect to the longitudinal axis X, wherein the eccentric movement is made possible by the bellows 96, which forms a hinge.
- a fictitious pivot point 106 is located on the longitudinal side X, around which the eccentric movement of the stator 90 takes place.
- the eccentric motion describes a path along a conical surface, wherein the articulation point 106 forms the conical tip. Ie. the eccentricity is greatest at the front end 102 of the stator 90 and zero at the pivot point 106.
- the interior of the extension 94 forms a pressure chamber in which the pressure-side pumping pressure of the eccentric screw pump acts.
- the pressure-side pressure acts on the one hand on the end face 92 of the rotor 86 and at the same time on the surrounding the bellows 96 annular surface 108, which is arranged in the interior of the pressure chamber formed by the extension 94.
- the rotor 86 is fixed by a thrust bearing, not shown.
- the annular surface 108 is in this case on the end face 92 of the rotor 86 facing away from the extension. 94 arranged and the rotor 86, ie facing the suction side of the pump.
- the suction-side pressure prevails inside the pump housing 100
- the suction-side pressure which is lower than the pressure in the interior of the extension 94
- the suction-side pressure is also present at the outer wall of the extension 94 opposite the annular surface 108.
- an automatic adjustment of the fit between rotor 86 and stator 90 can be effected as a function of the pressure difference between the suction and pressure sides of the eccentric screw pump.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Superconductors And Manufacturing Methods Therefor (AREA)
- Jet Pumps And Other Pumps (AREA)
- Pulleys (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Die Erfindung betrifft eine Exzenterschneckenpumpe. Exzenterschneckenpumpen, welche auch unter der Bezeichnung Moineau-Pumpen bekannt sind, weisen einen schneckenförmigen Rotor auf. weicher bei einer Rotation exzentrisch in einem umgebenden Stator läuft. Dabei sind Pumpen bekannt, bei welchen der Stator und der Rotor über ihre axiale Länge einen konstanten Querschnitt aufweisen.The invention relates to an eccentric screw pump. Eccentric screw pumps, which are also known under the name Moineau pumps, have a helical rotor. softer on a rotation eccentric running in a surrounding stator. Pumps are known in which the stator and the rotor have a constant cross section over their axial length.
Beispielsweise aus
Eine ausreichende Andruckkraft zwischen Stator und Rotor ist wichtig, um die Dichtigkeit der Pumpe bei hohen Drücken zu gewährleisten. Gleichzeitig soll die Passung nicht zu eng sein, um die Reibung in der Pumpe gering zu halten.A sufficient pressure force between the stator and rotor is important to ensure the tightness of the pump at high pressures. At the same time, the fit should not be too tight to keep the friction in the pump low.
Aus
Es ist Aufgabe der Erfindung, eine Exzenterschneckenpumpe zu schaffen, welche eine verbesserte Einstellung der Passung zwischen Rotor und Stator ermöglicht, so dass immer eine ausreichende Dichtigkeit an den Kontaktflächen zwischen Rotor und Stator gegeben ist und gleichzeitig die Reibung zwischen Rotor und Stator möglichst gering gehalten werden kann.It is an object of the invention to provide an eccentric screw pump, which allows an improved adjustment of the fit between the rotor and stator, so that always a sufficient tightness the contact surfaces between the rotor and stator is given while the friction between the rotor and stator can be kept as low as possible.
Diese Aufgabe wird durch eine Exzenterschneckenpumpe mit den im Anspruch 1 angegebenen Merkmalen gelöst. Bevorzugte Ausführungsformen ergeben sich aus den Unteransprüchen, der nachfolgenden Beschreibung sowie den Zeichnungen.This object is achieved by an eccentric screw pump having the features specified in claim 1. Preferred embodiments will become apparent from the dependent claims, the following description and the drawings.
Die erfindungsgemäße Exzenterschneckenpumpe weist ein ringförmiges Außenteil mit einem darin angeordneten Innenteil auf. Das Innenteil und das Außenteil bewegen sich in bekannter Weise relativ zueinander, wobei die Pumpbewegung erreicht wird. So kann das Innenteil als Rotor ausgebildet sein, welcher in dem Außenteil, welches einen feststehenden Stator bildet, rotiert. Dabei führen Rotor und Stator gleichzeitig eine exzentrische Bewegung zueinander aus, wobei diese exzentrische Bewegung entweder von dem Rotor und/oder von dem Stator ausgeführt werden kann. Alternativ ist es auch möglich, dass das Außenteil als Rotor sich um das feststehende Innenteil, welches dann als Stator dient, dreht. Dabei kann wiederum die exzentrische Bewegung entweder von dem rotierenden Außenteil oder dem feststehenden, d. h. nicht rotierenden Innenteil ausgeführt werden. Alternativ ist es ferner auch möglich, dass sich sowohl das Innenteil als auch das Außenteil zueinander drehen, um die Relativbewegung zueinander auszuführen. Die beim Betrieb auftretende exzentrische Bewegung kann auch von Innenteil und Außenteil gleichzeitig realisiert werden, anstatt dass nur eines der beiden Teile die exzentrische Bewegung ausführt. Insofern sind bei der erfindungsgemäßen Exzenterschneckenpumpe alle denkbaren Antriebskombinationen, welche von derartigen Pumpen bekannt sind, verwendbar.The eccentric screw pump according to the invention has an annular outer part with an inner part arranged therein. The inner part and the outer part move in a known manner relative to each other, wherein the pumping movement is achieved. Thus, the inner part may be formed as a rotor which rotates in the outer part, which forms a stationary stator. At the same time, the rotor and the stator perform an eccentric movement relative to each other, whereby this eccentric movement can be carried out either by the rotor and / or by the stator. Alternatively, it is also possible that the outer part rotates as a rotor around the fixed inner part, which then serves as a stator. Again, the eccentric motion can be either from the rotating outer part or the fixed, d. H. non-rotating inner part are executed. Alternatively, it is also possible that both the inner part and the outer part rotate to each other to perform the relative movement to each other. The eccentric movement occurring during operation can also be realized simultaneously by the inner part and outer part, instead of only one of the two parts executing the eccentric movement. In this respect, all conceivable drive combinations, which are known from such pumps, can be used in the eccentric screw pump according to the invention.
Bei der erfindungsgemäßen Exzenterschneckenpumpe sind das Innere des Außenteils und das Äußere des Innenteils derart ausgebildet, das sie sich korrespondierend zueinander zu einer Axialseite hin verjüngen, d. h. vorzugsweise in axialer Richtung konisch ausgebildet sind. Diese Anordnung ermöglicht es, dass wenn das Innenteil in der Richtung des verjüngten Endes weiter in das umgebende Außenteil gedrückt wird, die Passung zwischen Innenteil und Außenteil verkleinert wird und der Anpressdruck an den Kontaktflächen zwischen Innen- und Außenteil erhöht wird. Auf diese Weise kann durch axiale Relativbewegung zwischen Innen- und Außenteil die Passung bzw. der Anpressdruck an den Kontaktflächen zwischen Innen- und Außenteil eingestellt werden. Dazu sind Innen- und Außenteil in axialer Richtung relativ zueinander beweglich gelagert und zwar so, das die Beweglichkeit auch im Betrieb der Pumpe, d. h. z. B. bei Rotation des Innenteils gegeben ist.In the case of the eccentric screw pump according to the invention, the interior of the outer part and the exterior of the inner part are designed such that they taper in a manner corresponding to one another towards an axial side, ie they are preferably conical in the axial direction. This arrangement makes it possible that when the inner part in the direction of tapered end is further pressed into the surrounding outer part, the fit between the inner part and outer part is reduced and the contact pressure is increased at the contact surfaces between the inner and outer part. In this way, the fit or the contact pressure at the contact surfaces between the inner and outer part can be adjusted by axial relative movement between the inner and outer part. For this purpose, the inner and outer parts are mounted movably in the axial direction relative to each other and in such a way that the mobility is also given during operation of the pump, ie for example upon rotation of the inner part.
Ferner sind erfindungsgemäß das Innen- und/oder das Außenteil derart ausgebildet, das sich der Anpressdruck zwischen Innen- und Außenteil bei höherem Druck in der Pumpe bzw. steigendem Druck an der Druckseite der Pumpe erhöht. Das heißt, bei der erfindungsgemäßen Pumpe stellt sich die Passung bzw. der Anpressdruck zwischen Innen- und Außenteil im Betrieb selbsttätig ein, wobei durch den höheren Anpressdruck bei höherem Druck an der Druckseite der Pumpe auch bei hohem Pumpendruck eine ausreichende Dichtigkeit der Pumpe sichergestellt wird. Ferner wird ermöglicht, dass bei niedrigerem Druck an der Druckseite der Anpressdruck an den Kontaktflächen zwischen Innen-und Außenteil reduziert wird, so dass die Reibung verringert wird. Auf diese Weise ist es möglich, bei unterschiedlichen Pumpendrücken die Reibung so gering wie möglich und gleichzeitig den Anpressdruck zwischen Innen- und Außenteil so groß wie nötig zu halten.Further, according to the invention, the inner and / or the outer part are formed such that increases the contact pressure between the inner and outer part at a higher pressure in the pump or increasing pressure on the pressure side of the pump. That is, in the pump according to the invention, the fit or the contact pressure between inner and outer part automatically sets during operation, which is ensured by the higher contact pressure at higher pressure on the pressure side of the pump, even at high pump pressure sufficient tightness of the pump. Further, it is possible that at lower pressure on the pressure side of the contact pressure at the contact surfaces between the inner and outer part is reduced, so that the friction is reduced. In this way, it is possible to keep the friction as low as possible and at the same time the contact pressure between the inner and outer part as large as necessary at different pump pressures.
Diese Funktionsweise wird erfindungsgemäß dadurch realisiert, dass Innen- und/oder Außenteil derart ausgebildet sind, dass ein an der Druckseite der Exzenterschneckenpumpe und/oder in den Kavitäten der Exzenterschneckenpumpe zwischen Innen- und Außenteil anliegender Druck dazu verwendet wird, eine Kraft zu erzeugen, welcher in axialer Richtung Innen- und Außenteil ineinander drückt. Das heißt, diese von dem Druck an der Druckseite oder in den Kavitäten erzeugte Kraft wirkt in der Axialrichtung, in welcher sich innen- und Außenteil verjüngen auf das Innenteil oder in der Richtung, in welcher sich Innen- und Außenteil erweitern auf das Außenteil. Es sind auch Ausgestaltungen denkbar, bei welchen der Druck sowohl auf das Außenteil als auch in entgegengesetzter Richtung auf das Innenteil wirkt. Bei jeder dieser Anordnungen wird sichergestellt, dass durch den an der Druckseite oder den Kavitäten im Inneren der Pumpe anliegenden Druck Kräfte erzeugt werden, welche auf das Innen- und/oder das Außenteil wirken und diese ineinander drücken, um in Abhängigkeit des Drucks an der Druckseite oder im Inneren den Anpressdruck zwischen Innen- und Außenteil einzustellen. So wird der Differenzdruck zwischen Saug- und Druckseite der Exzenterschneckenpumpen, d. h. zwischen den beiden Axialenden von Innen- und Außenteil bzw. zwischen der Saugseite und den Kavitäten im inneren dazu genutzt, Innen- und Außenteil zusammenzudrücken. Bei Verringerung des Druckes bewegen sich Innen- und Außenteil vorzugsweise selbsttätig aufgrund des in der Pumpe herrschenden Druckes wieder auseinander bzw. der in der Pumpe herrschende Druck verringert selbsttätig den Anpressdruck zwischen Innen- und Außenteil, wenn er den von außen wirkenden Kräften entgegen wirkt.This operation is inventively realized in that inner and / or outer part are formed such that a voltage applied to the pressure side of the eccentric screw pump and / or in the cavities of the eccentric screw between the inner and outer part pressure is used to generate a force which in the axial direction inner and outer parts pressed into each other. That is, this force produced by the pressure on the pressure side or in the cavities acts in the axial direction, in which the inner and outer parts taper on the inner part or in the direction in which the inner and outer parts expand on the outer part. Embodiments are also conceivable in which the pressure acts both on the outer part and in the opposite direction on the inner part. In each of these arrangements it is ensured that forces are applied by the pressure applied to the pressure side or the cavities inside the pump, which act on the inner and / or the outer part and press them into each other, depending on the pressure on the pressure side or to adjust the contact pressure between the inner and outer part inside. Thus, the differential pressure between the suction and pressure side of the eccentric screw, ie between the two axial ends of the inner and outer part or between the suction side and the cavities used inside to compress the inner and outer parts. When reducing the pressure, the inner and outer parts preferably move apart automatically due to the pressure prevailing in the pump again or the pressure prevailing in the pump automatically reduces the contact pressure between the inner and outer part, when it counteracts the forces acting from the outside.
Vorzugsweise ist die Exzenterschneckenpumpe derart ausgebildet, das der an der Druckseite anliegende Druck auf eine dem verjüngten Ende des Innenteils abgewandte Fläche des innenteils wirkt. Durch die Druckbeaufschlagung dieser Fläche wird eine in Richtung des verjüngten Endes des Innenteils wirkende axiale Kraft erzeugt, welche das Innenteil zum verjüngten Ende des Außenteils drückt. Über die Größe der Fläche, auf welcher der Druck in axialer Richtung wirkt, kann ferner die Größe der wirkenden Kraft beeinflusst werden, so dass durch Anpassung der Fläche die Kräfteverhältnisse und insbesondere der Bereich, in weichem der Anpressdruck zwischen Innen- und Außenteil variieren kann, voreingestellt werden kann. Insbesondere wird die Fläche im Verhältnis zu den übrigen Stirnflächen bzw. Stirnseiten des Innenteils, auf welche der an der Saug- oder Druckseite anliegende Druck wirkt, ausgelegt, um die gewünschten Kräfteverhältnisse, welche auf das Innenteil wirken, voreinstellen zu können.Preferably, the eccentric screw pump is designed such that the pressure applied to the pressure side acts on a side facing away from the tapered end of the inner part surface of the inner part. By the pressurization of this surface, an axial force acting in the direction of the tapered end of the inner part is generated, which presses the inner part towards the tapered end of the outer part. On the size of the surface on which the pressure acts in the axial direction, the magnitude of the acting force can also be influenced, so that by adjusting the surface, the force relationships and in particular the range in which the contact pressure between the inner and outer part can vary, can be preset. In particular, the surface in relation to the other end faces or end faces of the inner part, on which acts on the pressure applied to the suction or pressure side, designed to preset the desired balance of power, which act on the inner part, can.
Das Innenteil und das Außenteil sind gemäß einer ersten Ausführungsform derart angeordnet, dass die Axialseite, zu welcher sich das Innere des Außenteils und das Äußere des Innenteils verjüngen, die Druckseite der Exzenterschneckenpumpe ist. Der große Querschnitt von Innen- und Außenteil am entgegengesetzten Axialende bildet entsprechend die Saugseite der Pumpe. Bei dieser Ausgestaltung wirkt der Druck an der Druckseite auf die kleine Stirnfläche des Innenteils. Diese Kraft würde somit das Innen- und das Außenteil auseinanderdrücken, wenn keine entgegengesetzte Kraft auf Innen- und/oder Außenteil wirkt. Wenn nun der an der Druckseite anliegende Druck gleichzeitig auf eine der Druckseite abgewandte Fläche des Innenteils oder aber auf eine der Druckseite zugewandte Fläche des Außenteils wirkt, kann der auf die kleine Stirnfläche des Innenteils wirkenden Kraft entgegengewirkt werden, um Innen- und Außenteil auch bei größerer Druckdifferenz zwischen Saug-und Druckseite in Anlage zu halten.The inner part and the outer part are arranged according to a first embodiment such that the axial side, to which the inside of the outer part and the exterior of the inner part taper, is the pressure side of the eccentric screw pump. The large cross-section of inner and outer part at the opposite end of the axial corresponding to the suction side of the pump. In this embodiment, the pressure on the pressure side acts on the small end face of the inner part. This force would thus push apart the inner and outer parts, if no opposite force acts on the inner and / or outer part. Now, if the voltage applied to the pressure side simultaneously acts on a side facing away from the pressure side of the inner part or on a side facing the pressure side of the outer part, acting on the small end face of the inner part force can be counteracted to inner and outer part even with larger Pressure difference between suction and pressure side to keep in plant.
Bei der Exzenterschneckenpumpe, bei welcher das verjüngte Ende von Innen- und Außenteil die Druckseite der Pumpe bildet, ist im Inneren des Innenteils ein Kanal ausgebildet, welcher zu der Druckseite oder zu einer Kavität im Inneren der Exzenterschneckenpumpe geöffnet ist und mit einer der Druckseite abgewandten Fläche des Innenteils in Verbindung steht. Auf diese Weise wird der an der Druckseite oder der im Inneren der Pumpe herrschende Druck auf eine der Druckseite abgewandte Fläche geleitet, um dort eine Kraft zu erzeugen, welche der an der Druckseite des Innenteils auf diesen wirkenden Kraft axial entgegengesetzt gerichtet ist und das Innenteil im Außenteil in Anlage hält bzw. in das Außenteil drückt.In the eccentric screw pump, in which the tapered end of inner and outer part forms the pressure side of the pump, a channel is formed in the interior of the inner part, which is open to the pressure side or to a cavity inside the eccentric screw pump and with a side facing away from the pressure side of the inner part is in communication. In this way, the pressure prevailing on the pressure side or in the interior of the pump pressure is directed to a side facing away from the pressure side, there to generate a force which is directed axially opposite to the force acting on the pressure side of the inner part on this force and the inner part in the External part holds in abutment or pushes into the outer part.
Weiter bevorzugt ist dazu an der der Druckseite abgewandten Axialseite des Innenteils ein Druckraum angeordnet, welcher mit dem genannten Kanal in Verbindung steht. Der Druckraum weist eine in axialer Richtung veränderbare Länge auf und hat eine der Druckseite abgewandte, mit dem Innenteil verbundene Innenfläche. Der über den Kanal in den Druckraum geleitete Druck, welcher an der Druckseite der Pumpe herrscht, führt zu einer Ausdehnung des Druckraumes und damit zu einer Längenänderung des Druckraumes. Der Druck wirkt dabei auf eine Innenfläche des Druckraumes, welche der Druckseite abgewandt ist und erzeugt so eine axial gerichtete Druckkraft auf das Innenteil, welche diesen zum verjüngten Ende des Innenteils hin in das Außenteil drückt und dafür sorgt, das ein ausreichend hoher Anpressdruck zwischen Innen- und Außenteil auch bei höherem Druck an der Druckseite der Pumpe aufrechterhalten wird. Der Druckraum ist vorzugsweise gegenüber der Umgebung abgedichtet. Dies ist insbesondere dann erforderiich, wenn der Druckraum auf der Saugseite der Pumpe in axialer Verlängerung des Innenteils angeordnet ist. Bei dieser bevorzugten Ausführungsform wird erreicht, dass auch von der Saugseite her der an der Druckseite anliegende Druck auf eine Stirnfläche bzw. eine zur axialen Stirnseite gewandte Fläche des Innenteils wirkt. Die Innenfläche des Druckraumes, auf welche dieser Druck wirkt, ist vorzugsweise fest mit dem Innenteil verbunden bzw. in axialer Richtung mit dem Innenteil bewegungsgekoppelt, um die axial wirkende Druckkraft von der Innenfläche auf das Innenteil zu übertragen.More preferably, a pressure chamber is arranged on the axial side facing away from the pressure side of the inner part, which is in communication with said channel. The pressure chamber has a variable length in the axial direction and has a side facing away from the pressure side, connected to the inner part inner surface. The over the channel in the pressure chamber conducted pressure, which prevails on the pressure side of the pump, leads to an expansion of the pressure chamber and thus to a change in length of the pressure chamber. The pressure acts on an inner surface of the pressure chamber, which faces away from the pressure side and thus generates an axially directed pressure force on the inner part, which presses this towards the tapered end of the inner part in the outer part and ensures that a sufficiently high contact pressure between inner and outdoor part is maintained even at higher pressure on the pressure side of the pump. The pressure chamber is preferably sealed from the environment. This is particularly necessary if the pressure chamber is arranged on the suction side of the pump in the axial extension of the inner part. In this preferred embodiment it is achieved that also acts on the suction side of the pressure applied to the pressure side on an end face or facing the axial end surface of the inner part. The inner surface of the pressure chamber, on which this pressure acts, is preferably fixedly connected to the inner part or movement-coupled in the axial direction with the inner part in order to transmit the axially acting pressure force from the inner surface to the inner part.
Besonders bevorzugt ist der Druckraum im Inneren einer das Innenteil antreibenden Welle ausgebildet, wobei die Welle mit dem Druckraum in ihrer Länge veränderbar ist. Die Welle verbindet einen Antriebsmotor, vorzugsweise einen elektrischen Antriebsmotor mit dem Innenteil.Das Innenteil bildet dabei einen Rotor, welcher sich relativ zu dem Außenteil, welches vorzugsweise als Stator fungiert, dreht. Der Antrieb erfolgt dabei über die Welle, welche somit eine Rotorwelle bildet. Wenn die Welle über den Druckraum in ihrer Länge veränderlich ist, kann die Andruckkraft zwischen dem zu einer Seite verjüngten, insbesondere konischen Innenteil und der entsprechend geformten Innenfläche des Au-ßenteils durch die Längenänderung eingestellt werden.Particularly preferably, the pressure chamber is formed in the interior of a shaft driving the inner part, wherein the shaft with the pressure chamber in its length is variable. The shaft connects a drive motor, preferably an electric drive motor with the Innenteil.Das inner part forms a rotor which rotates relative to the outer part, which preferably acts as a stator. The drive takes place while on the shaft, which thus forms a rotor shaft. When the shaft is variable in length over the pressure space, the pressing force between the tapered to one side, in particular conical inner part and the correspondingly shaped inner surface of the Au-ßenteils can be adjusted by the change in length.
Gemäß besonders bevorzugter Ausführungsformen ist der Druckraum über eine Kolben-Zylinder-Anordnung und/oder durch eine in axialer Richtung elastische Außenwandung in seiner Länge veränderbar. Die elastische Außenwandung kann beispielsweise nach Art eines Faltenbalges aus Metall, einem Elastomer oder Gummi ausgebildet sein. Durch die Elastizität kann gleichzeitig eine Vorspannung realisiert werden. Die Kolben-Zylinder-Anordnung kann auch die mehrteilige Ausgestaltung der Außenwandung des Druckraumes realisiert werden, wobei die Teile der Außenwandung des Druckraumes teleskopartig ineinander greifen.According to particularly preferred embodiments, the pressure chamber via a piston-cylinder arrangement and / or by an elastic in the axial direction outer wall in its length is variable. The elastic outer wall may be formed, for example, in the manner of a bellows made of metal, an elastomer or rubber. Due to the elasticity can be realized at the same time a bias. The piston-cylinder arrangement can also be realized the multi-part design of the outer wall of the pressure chamber, wherein the parts of the outer wall of the pressure chamber telescopically engage each other.
Gemäß einer weiteren bevorzugten Ausführungsform kann in dem Kanal oder dem mit dem Kanal in Verbindung stehenden Druckraum eine Drosselstelle ausgebildet sein. Diese Drosselstelle dient dazu, Druckschwankungen, welche während des Betriebes der Pumpe auftreten zu dämpfen, um eine Änderung des Anpressdruckes zwischen Innen-und Außenteil bei kurzzeitigen Druckschwankungen zu unterbinden. Dazu ist die Drosselstelle so angeordnet, das die Übertragung des Druckes von der Druckseite des Innenteils zu der der Druckseite abgewandten Fläche des innenteils bzw. der Innenfläche des Druckraumes nur gedämpft über die Drosselstelle erfolgt, so dass Druckänderungen in dem Druckraum deutlich langsamer erfolgen als an der Druckseite der Pumpe.According to a further preferred embodiment, a throttle point may be formed in the channel or in the pressure space communicating with the channel. This throttle point is used to dampen pressure fluctuations that occur during operation of the pump to prevent a change in the contact pressure between the inner and outer part in short-term pressure fluctuations. For this purpose, the throttle point is arranged so that the transmission of the pressure from the pressure side of the inner part to the side facing away from the pressure side of the inner part or the inner surface of the pressure chamber is only attenuated via the throttle point, so that pressure changes in the pressure chamber are much slower than at the Pressure side of the pump.
Die der Druckseite abgewandten Fläche, d.h. die abgewandte projizierte Fläche, mit welcher der Kanal in Verbindung steht, ist bevorzugt größer als die der Druckseite zugewandte Stirnfläche des Innenteils. Wenn auf die Fläche, welche mit dem Kanal in Verbindung steht und welcher der Druckseite abgewandt ist, beispielsweise die innenfläche des Druckraumes, derselbe Druck wirkt wie auf die Stirnfläche des Innenteils an der Druckseite der Pumpe, ist aufgrund der größeren Fläche die in axialer Richtung zur Druckseite hin auf das Innenteil wirkende Kraft größer ist als die von der Druckseite zur Saugseite in axialer Richtung wirkende Kraft. Auf diese Weise wird sichergestellt, das unabhängig von dem an der Druckseite anliegenden Druck das Innenteil immer in Richtung der Druckseite mit einer größeren Kraft beaufschlagt wird und in bzw. gegen das Außenteil gedrückt wird, wenn die Druckseite an der Seite des verjüngten Endes des Innen- und Außenteils gelegen ist. Die das Innenteil in das Außenteil drückende Kraft ist somit abhängig von der Flächendifferenz zwischen der Stirnfläche des Innenteils an der Druckseite und der der Druckseite abgewandten Fläche und proportional zum Druck an der Druckseite der Pumpe bzw. zur Druckdifferenz zwischen Saugseite und Druckseite.The side facing away from the pressure side, ie the remote projected surface, with which the channel is in communication is preferred larger than the pressure side facing end face of the inner part. If the surface which communicates with the channel and which faces away from the pressure side, for example the inner surface of the pressure chamber, has the same pressure as the end surface of the inner part on the pressure side of the pump, the axial direction is due to the larger surface Pressure side towards the inner part acting force is greater than the force acting from the pressure side to the suction side in the axial direction force. In this way it is ensured that regardless of the pressure applied to the pressure side, the inner part is always acted upon in the direction of the pressure side with a larger force and is pressed into or against the outer part when the pressure side on the side of the tapered end of the inner and outside part. The force pressing the inner part into the outer part is thus dependent on the area difference between the end face of the inner part on the pressure side and the surface facing away from the pressure side and proportional to the pressure on the pressure side of the pump or to the pressure difference between the suction side and pressure side.
Gemäß einer alternativen Ausführungsform der Erfindung sind innen-und Außenteil derart angeordnet, das diejenige Axialseite, zu welcher sich das Innere des Außenteils und das Äußere des Innenteils verjüngen, die Saugseite der Exzenterschneckenpumpe ist. Das heißt, Innenteil und das Innere des Außenteils erweitern sich zur Druckseite der Pumpe hin. Da bei dieser Ausführungsform die große Stirnfläche des Innenteils zur Druckseite hin gelegen ist, ist es leicht möglich, dass der an der Druckseite anliegende Druck auf diese Fläche wirkt und so das Innenteil in das Außenteil drückt und stets für eine ausreichende Andruckkraft an den Berührungspunkten zwischen Innen- und Außenteil sorgt. Der an der Saugseite auf das Innenteil wirkende Druck ist geringer, so dass an dieser Seite eine geringere Kraft auf das Innenteil wirkt.According to an alternative embodiment of the invention, the inner and outer parts are arranged such that the axial side, to which the interior of the outer part and the exterior of the inner part taper, is the suction side of the eccentric screw pump. That is, the inner part and the inside of the outer part expand toward the pressure side of the pump. Since in this embodiment, the large end face of the inner part is located to the pressure side, it is easily possible that the pressure applied to the pressure side acts on this surface and so presses the inner part in the outer part and always for a sufficient pressure force at the points of contact between inside - and outer part provides. The pressure acting on the suction side on the inner part is lower, so that a smaller force acts on the inner part on this side.
Bei der alternativen Ausführungsform ist ein Druckkanal vorgesehen, welcher die Druckseite oder eine Kavität im Inneren der Exzenterschneckenpumpe mit einer der Druckseite abgewandten Fläche des Außenteils verbindet. Dies ist eine eigentlich der Saugseite der Pumpe zugewandte Fläche, welche über den Druckkanal mit dem an der Druckseite oder im Inneren zwischen Innen- und Außenteil anliegenden Druck beaufschlagt wird, so dass von dieser Seite her, an welcher das verjüngte Ende des Außenteils gelegen ist, das Außenteil auf das Innenteil gedrückt wird. In dem Druckkanal kann eine Drosselstelle angeordnet sein.In the alternative embodiment, a pressure channel is provided, which connects the pressure side or a cavity in the interior of the eccentric screw pump with a side facing away from the pressure side surface of the outer part. This is actually a suction side of the pump-facing surface which is acted upon via the pressure channel with the voltage applied to the pressure side or in the interior between the inner and outer part, so that from this side, on which the tapered end of the outer part is located the outer part is pressed onto the inner part. In the pressure channel, a throttle point may be arranged.
Vorzugsweise ist es bei dieser Ausführungsform wie auch bei der vorangehend beschriebenen Ausführungsform, bei welcher das verjüngte Ende des Innenteils an der Druckseite gelegen ist, so, dass die das Innenteil antreibende Welle an derjenigen Stirnseite des Innenteils angreift, an welcher die größte Querschnittsfiäche des Innenteils gelegen ist. Dabei ist bei der Ausführungsform, bei welcher das Innenteil sich zur Druckseite hin erweitert, an dem Innenteil und/oder an der axialseitig mit dem Innenteil verbundenen Welle vorzugsweise zumindest eine Druckfläche angeordnet, welche in axialer Richtung der Saugseite abgewandt, d. h. der Druckseite zugewandt ist, und auf welche der an der Druckseite der Exzenterschneckenpumpe anliegende Druck wirkt. Durch Beaufschlagung dieser Druckfläche wird eine Druckkraft erzeugt, welche in axialer Richtung zur Saugseite und damit zum verjüngten Ende des Innenteils und des Innenraumes des Außenteils hin wirkt und so das Innen- gegen das Außenteil drückt.Preferably, in this embodiment as well as in the embodiment described above, in which the tapered end of the inner part is located on the pressure side, so that the shaft driving the inner part acts on that end side of the inner part, on which the largest Querschnittsfiäche the inner part located is. In the embodiment in which the inner part widens toward the pressure side, at least one pressure surface, which faces away from the suction side in the axial direction, is preferably arranged on the inner part and / or on the shaft connected to the inner part on the axial side. H. facing the pressure side, and on which acts on the pressure side of the eccentric screw pump applied pressure. By applying this pressure surface, a compressive force is generated which acts in the axial direction to the suction side and thus to the tapered end of the inner part and the inner space of the outer part and thus pushes the inner against the outer part.
Weiter bevorzugt ist zumindest ein Vorspannelement vorgesehen, welches das Innenteil mit einer Vorspannkraft in der axialen Richtung, in welcher er sich verjüngt, beaufschlagt und/oder welches das Außenteil mit einer Vorspannkraft in entgegengesetzter axialer Richtung beaufschlagt. Ein solches Vorspannelement kann bei beiden vorangehend beschriebenen grundsätzlichen Ausführungsformen der Erfindung, d. h. unabhängig davon, ob die Druckseite am verjüngten oder am erweiterten Ende des Innenteils gelegen ist, zum Einsatz kommen. Ein solches Vorspannelement oder mehrere solche Vorspannelemente bewirken, dass Innen- und Außenteil in axialer Richtung gegeneinander gedrückt werden, so dass die als Dichtflächen dienenden Berührungspunkte bzw. Berührungslinien zwischen Innen- und Außenteil in Anlage gehalten werden. Die Vorspannelemente bewirken, dass auch bei nur geringem Druck an der Druckseite bzw geringer oder nicht vorhandener Druckdifferenz zwischen Saug- und Druckseite eine ausreichende Andruckkraft zwischen Innen- und Außenteil gegeben ist, so dass auch beim Anlaufen der Pumpe die im Inneren ausgebildeten Pumpenräume dicht sind und die Funktion gewährleistet ist.More preferably, at least one biasing element is provided, which acts on the inner part with a biasing force in the axial direction in which it tapers, and / or which acts on the outer part with a biasing force in the opposite axial direction. Such a biasing element can in both of the above-described basic embodiments of the invention, ie regardless of whether the pressure side is located on the tapered or extended end of the inner part, are used. Such a biasing element or more such biasing elements cause the inner and outer parts are pressed against each other in the axial direction, so that the serving as sealing surfaces touch points or lines of contact between the inner and outer part are held in abutment. The biasing elements cause even at low pressure on the pressure side or less or no pressure difference between suction and pressure side between a sufficient pressure force between the inner and outer part is given, so that even when starting the pump, the pump chambers formed inside are tight and the function is guaranteed.
Das Innenteil ist vorzugsweise über eine Welle bzw. Rotorwelle mit einem Antriebsmotor, insbesondere einem elektrischen Antriebsmotor verbunden, wobei die Welle an einem Gelenkpunkt, z. B. am Anlenkungspunkt an der Abtriebswelle des Antriebsmotors, gelenkig gelagert ist und der Gelenkpunkt vorzugsweise rein rotatorisch bewegbar ist. Dies ermöglicht, dass das als Rotor dienende Innenteil während seiner Drehung eine exzentrische Bewegung vollführt, wobei der Gelenkpunkt selber sich vorzugsweise nur um eine Längsachse dreht und keine exzentrische oder axiale Bewegung in Richtung der Längsachse vollführt. Das heißt, es ist keine Exzentrizität der Bewegung am Gelenkpunkt selber gegeben. Durch die gelenkige Ausgestaltung des Anlenkungspunktes kann auf zusätzliche Gelenkelemente in der Welle zur Ermöglichung der exzentrischen Bewegung verzichtet werden. Alternativ kann die Rotorwelle biegsam ausgebildet oder mit einem Gelenk versehen sein, so dass eine exzentrische Bewegung um einen fiktiven Gelenkpunkt möglich ist.The inner part is preferably connected via a shaft or rotor shaft with a drive motor, in particular an electric drive motor, wherein the shaft at a hinge point, for. B. at the articulation point on the output shaft of the drive motor, is articulated and the hinge point is preferably purely rotationally movable. This allows the inner part serving as a rotor to perform an eccentric movement during its rotation, wherein the pivot point itself preferably rotates only about a longitudinal axis and does not perform any eccentric or axial movement in the direction of the longitudinal axis. That is, there is no eccentricity of movement at the hinge point itself. Due to the articulated design of the articulation point can be dispensed with additional joint elements in the shaft to allow the eccentric movement. Alternatively, the rotor shaft may be made flexible or provided with a hinge, so that an eccentric movement about a fictitious pivot point is possible.
Weiter bevorzugt ist das Innenteil über eine Welle mit einem Antriebsmotor verbunden und die Welle mit dem Innenteil gemeinsam exzentrisch bewegbar, wobei Innenteil und Welle derart angeordnet sind, dass die Exzentrizität ihrer Bewegung ausgehend von einem Gelenkpunkt, z. B. dem Anlenkungspunkt an dem Antriebsmotor, zunimmt, vorzugsweise linear zunimmt. Wie oben beschrieben ist am Gelenkpunkt, vorzugsweise keine Exzentrizität zusätzlich zu der Drehbewegung der Welle gegeben. Ausgehend von diesem Punkt vollführen Innenteil und Welle neben ihrer Rotation um ihre Längsachse eine exzentrische Bewegung um den Gelenkpunkt, dabei bewegt sich die Längsachse der Welle vorzugsweise entlang einer Kegelmantelfläche, wobei die Spitze des Kegels im Gelenkpunkt gelegen ist. Das heißt, die Welle rollt über die Kegelmantelfläche ab. Besonders bevorzugt bilden die Längsachse des Innenteils und die Längsachse der Welle eine gerade Linie, welche um den Gelenkpunkt die beschriebene exzentrische Bewegung über die Kegelmantelflüchen vollführen. Auf diese Weise wird eine exzentrische Bewegung des Innenteils im Inneren des Außenteils erreicht, so dass das Innenteil auf der Innenfläche des Außenteils abrollt.More preferably, the inner part is connected via a shaft with a drive motor and the shaft with the inner part together eccentrically movable, wherein inner part and shaft are arranged such that the eccentricity of their movement starting from a hinge point, z. B. the articulation point on the drive motor, increases, preferably increases linearly. As described above, at the hinge point, preferably, no eccentricity is given in addition to the rotary motion of the shaft. Starting from this point perform inner part and shaft in addition to its rotation about its longitudinal axis an eccentric movement about the hinge point, while the longitudinal axis of the shaft preferably moves along a conical surface, the tip of the cone is located in the hinge point. That is, the shaft rolls over the conical surface. Particularly preferably, the longitudinal axis of the inner part and the longitudinal axis of the shaft form a straight line, which perform about the pivot point described eccentric movement over the conical surface crevices. In this way, an eccentric movement of the inner part is achieved in the interior of the outer part, so that the inner part rolls on the inner surface of the outer part.
Das Innenteil ist vorzugsweise zumindest an seiner Oberfläche aus einem keramischen Material ausgebildet, während das Außenteil zumindest an der dem innenteil zugewandten Oberfläche vorzugsweise aus einem Elastomer ausgebildet ist. Besonders bevorzugt ist das innenteil vollständig aus einem keramischen Material und das Außenteil vollständig aus einem Elastomermaterial ausgebildet. Das heißt, das innenteil weist eine harte Oberfläche auf, während das Außenteil eine elastische dem Innenteil zugewandte Oberfläche aufweist.The inner part is preferably formed at least on its surface of a ceramic material, while the outer part is preferably formed at least on the inner part facing surface of an elastomer. Particularly preferably, the inner part is made entirely of a ceramic material and the outer part is made entirely of an elastomer material. That is, the inner part has a hard surface, while the outer part has an elastic surface facing the inner part.
Nachfolgend wird die Erfindung beispielhaft anhand der beigefügten Figuren beschrieben. In diesen zeigt:
- Fig. 1
- eine geschnittene Gesamtansicht eines erfindungsgemäßen Pumpenaggregats,
- Fig. 2
- eine geschnittene Ansicht des Rotors und des Stators eines Pumpenaggregates gemäß
Fig. 1 , - Fig. 3
- eine perspektivische Ansicht des Rotors in teilweise geschnittener Darstellung
- Fig. 4
- eine schematische Darstellung der Druckverhältnisse an Stator und Rotor,
- Fig. 5
- eine Schnittansicht einer Exzenterschneckenpumpe gemäß einer zweiten Ausführungsform der Erfindung,
- Fig. 6
- eine Schnittansicht von Rotor und Stator gemäß einer dritten Ausführungsform der Erfindung und
- Fig. 7
- eine perspektivisch geschnittene Ansicht einer vierten Ausführungsform der Erfindung.
- Fig. 1
- a sectional overall view of a pump unit according to the invention,
- Fig. 2
- a sectional view of the rotor and the stator of a pump assembly according to
Fig. 1 . - Fig. 3
- a perspective view of the rotor in a partially sectioned view
- Fig. 4
- a schematic representation of the pressure conditions on stator and rotor,
- Fig. 5
- a sectional view of a progressing cavity pump according to a second embodiment of the invention,
- Fig. 6
- a sectional view of the rotor and stator according to a third embodiment of the invention and
- Fig. 7
- a perspective sectional view of a fourth embodiment of the invention.
Die nachfolgenden Ausführungsbeispiele betreffen Äntriebsanordnungen, bei welchem das Innenteil der Pumpe als Rotor ausgebildet ist und rotatorisch angetrieben wird. Entsprechend ist das Außenteil der Exzenterschneckenpumpe als nicht rotierender Stator ausgebildet. D. h. die Relativbewegung zwischen Rotor und Stator wird allein durch Rotation des Rotors erzeugt. Es ist jedoch zu verstehen, dass das der Erfindung zugrunde liegende Prinzip der Einstellung der Passung zwischen Rotor und Stator auch bei Anordnungen zur Anwendung gelangen kann, bei welcher das nachfolgend als Stator beschriebene Außenteil relativ zu dem Innenteil rotiert.The following embodiments relate to Äntriebsanordnungen in which the inner part of the pump is designed as a rotor and is driven in rotation. Accordingly, the outer part of the eccentric screw pump is designed as a non-rotating stator. Ie. the relative movement between rotor and stator is generated solely by rotation of the rotor. However, it should be understood that the principle underlying the invention of adjusting the fit between the rotor and the stator can also be used in arrangements in which the outer part described below as a stator rotates relative to the inner part.
Die in
Bei dem in
Der Rotor 12 ist über eine sich an der Stirnseite 18 anschließende Rotorwelle 20 an einem Anlenkungspunkt 22 mit der Abriebswelle 24 des Antriebsmotors 2 verbunden.The
Die Rotorwelle 20 ist derart gelenkig ausgebildet, das die Rotorwelle 20 bei ihrer Rotation zusätzlich eine exzentrische Bewegung ausführen kann. Die Gelenkigkeit der Rotorwelle 20 wird durch den später beschriebenen Faltenbalg 30 an dem dem Antriebsmotor 2 zugewandten Ende der Rotorwelle 20 realisiert. Diese exzentrische Bewegung erfolgt in der Weise, dass ein fiktiver Gelenkpunkt 23 auf der Längsachse des Faltenbalges 30 die Spitze eines Kegels bildet, auf dessen Oberfläche sich die Rotorwelle 20 mit dem Rotor 12 exzentrisch bewegt, während die Rotorwelle 20 und der Rotor 12 sich angetrieben durch die Antriebsmotor 2 um ihre Längsachse drehen. Das heißt, der Rotor 12 führt gemeinsam mit der Rotorwelle 20 im Inneren des Stators 14 eine exzentrische Bewegung aus, welche kegelförmig um die Längsachse X und den Gelenkpunkt 23 im Falenbalg 30 erfolgt. Die Exzentrizität ergibt sich durch die Gestaltung von Stator 10 und Rotor 12, so dass der Rotor 12 bei Rotation des Rotors um seine eigene Achse automatisch die beschriebene exzentrische Bewegung ausführt. Die exzentrische Bewegung erfolgt so, dass an der Stirnseite 16 die Exzentrizität am größten ist, d. h. der Durchmesser des Kreises, auf welchem sich die Mittelachse des Rotors bei der Rotation bewegt am größten ist. Am Gelenkpunkt 23 im Faltenbalg 30 ist keine Exzentrizität mehr gegeben. An der Stirnseite 18 bewegt sich der Rotor mit einer geringeren Exzentrizität als an der Stirnseite 16, d. h. der Durchmesser des Kreises auf welchem sich die Mittelachse des Rotors bei dessen Rotation bewegt, ist kleiner.The
Die erfindungsgemäße Exzenterschneckenpumpe ist so ausgebildet, dass sich die Passung zwischen Rotor 12 und Stator 10 selbsttätig in Abhängigkeit der Druckverhältnisse an der Druckseite und der Saugseite der Exzenterschneckenpumpe und insbesondere der Druckdifferenz zwischen Druck- und Saugseite einstellt. Das heißt, der Anpressdruck an den Kontaktflächen zwischen Rotor 12 und Stator 10 wird in Abhängigkeit des Fluiddruckes selbsttätig angepasst.The eccentric screw pump according to the invention is designed so that the fit between the
Bei dem in
Der Rotor 12 weist einen zentral angeordneten Kanal auf, welcher sich in Längsrichtung von der Stirnseite 16 bis zu der Druckfläche 26, welche hier die entgegengesetzte Stirnseite des Rotors 12 bildet, erstreckt. An der Druckfläche 26 öffnet sich der Kanal 28 in das Innere der hohl ausgebildeten Rotorwelle 20. So kann der an der Stirnseite 16, d. h. der Druckseite der Exzenterschneckenpumpe anliegende, Fluiddruck durch den Kanal 28 auf die der Stirnseite 16, d. h. der Druckseite abgewandte Druckfläche 26 geleitet werden.The
Dies führt zu einem Kräfteverhältnis, wie es im Wesentlichen in
Die Rotorwelle 20 ist so ausgebildet, das eine axiale Verschiebbarkeit des Rotors 12 in Richtung der Längsachse W von Rotor 12 und Rotorwelle 20 gegeben ist. Diese Löngsverschiebbarkeit ebenfalls durch den Faltenbalg 30 realisiert, welcher eine elastische Wandung der Rotorwelle 20 bildet. Der Faltenbalg 30 kann aus Metall oder Kunststoff, insbesondere einem Elastomer ausgebildet sein. Er muss neben der Elastizität in axialer Richtung W auch eine Torsionssteifigkeit zur Übertragung des Drehmomentes, welches auf die Rotorwelle 20 wirkt, sowie eine Gelenkigkeit für die exzentrische Bewegung des Rotors 12 aufweisen. Die Rotorwelle 20 mit dem Faltenbalg 30 ist hohl ausgebildet, so dass im Inneren ein Druckraum 32 und 34 gebildet wird. Der Druckraum 32 liegt dabei in dem starren Teil der Rotorwelle 20, der Druckraum 34 liegt in dem von dem Faltenbalg 30 gebildeten Teil der Rotorwelle 20. Die Druckräume 32 und 34 sind durch eine Trennwand 36 voneinander getrennt. Die Trennwand 36 ist am axialen Ende des starren Teils der Rotorwelle 20 angrenzend an den durch den Faltenbalg 30 gebildeten Teil angeordnet. Die Trennwand 38 weist einen Kanal auf, welcher sich zwischen den beiden Stirnseiten erstreckt und die an die beiden Stirnseiten angrenzenden Druckräume 32 und 34 miteinander verbindet. Der Kanal 38 bildet eine Drosselstelle, durch weiche das von der Druckseite des Rotors 12 durch den Kanal 28 geleitete Fluid von dem Druckraum 32 in den Druckraum 34 und zurück strömen kann. Diese Drosselstelle dämpft periodisch auftretende Druckschwankungen, weiche konstruktionsbedingt beim Betrieb der Exzenterschneckenpumpe auftreten. Auf diese Weise werden Schwankungen der Andruckkraft Fa aufgrund dieser Druckschwankungen eliminiert. Lediglich größere Druckschwankungen mit größerer Periode führen zu einer Änderung der Kraft Fa.The
Der Faltenbalg 30 wirkt aufgrund seiner Elastizität in axialer Richtung ferner als Federelement, welches eine Vorspannung zwischen Rotor 12 und Stator 40 erzeugt. Aufgrund der Elastizität des Faltenbalges 30 wird der Rotor 12 in Richtung der Längsachse W in das Statorinnere gedrückt.The bellows 30 acts due to its elasticity in the axial direction further as a spring element which generates a bias between the
Anhand von
Die in
Der Rotor 42 geht axialseitig in eine Rotorwelle 52 über, wobei hier Rotor 42 und Rotorwelle 52 als ein integrales Bauteil ausgebildet sind. Die Rotorwelle 52 wird an ihrem dem Rotor 42 abgewandten Axialende 54 mit einer hier nicht gezeigten Motorwelle eines Antriebesmotors verbunden. Auch bei dieser Ausführungsform führen die Rotorwelle 52 mit dem Rotor 42 eine exzentrische Bewegung im Inneren des Stator 40 aus, wobei sich die Rotorwelle 52 zum einen um ihre Längsachse W dreht und zum anderen eine exzentrische Bewegung um die Längsachse X des Stators 40 ausführt. Dabei führt der Rotor 42 hier, wie bei der ersten Ausführungsform beschrieben, aufgrund der konischen Ausgestaltung von Rotor 42 und Stator 40 eine Bewegung aus, bei welcher die Längsachse W auf einer Kegelmantelfläche abläuft. Dabei ist die Spitze diese Kegels im Anlenkungspunkt der Rotorwelle 52 an der Motorwelle gelegen. Das heißt, das an der Stirnseite 48 gelegene Ende des Rotors 42 führt um die Längsachse X eine exzentrische Bewegung mit größerem Durchmesser aus als der Endbereich des Rotors 42 an der Stirnseite 50. Am axialen Ende 54 der Rotorwelle, welches mit der Motorwelle verbunden wird, ist vorzugsweise keine Exzentrizität der Bewegung mehr gegeben. An ihrem dem Rotor 42 abgewandten Ende weist die Rotorwelle 52 eine Dichtung 56 auf, weiche den Raum 58, welcher sich druckseitig an den Stator 40 anschließt zum Motor hin abdichtet.The
An der Dichtung 56 sind Absatzflächen 60 ausgebildet, welche dem Rotor 42 und somit der Saugseite an der Stirnseite 48 abgewandt sind. Da diese Absatzflächen 60 im Inneren des Raumes 58 gelegen sind, in welchem der druckseitige Fluiddruck wirkt, wirkt der Fluiddruck auf diese Absatzflächen 60 und erzeugt eine Kraft in Richtung der Längsachse W der Rotorwelle 52, welche die Rotorwelle 52 mit der Rotor 42 zur Stirnseite 48 hin in den Stator 40 drückt. Auf diese Weise wird durch den Fluiddruck an der Druckseite eine Andruckkraft zwischen Rotor 42 und Stator 40 erzeugt, weiche mit zunehmendem Fluiddruck an der Druckseite der Pumpe zunimmt und mit abnehmendem Fluiddruck abnimmt. So wird auch bei dieser Ausführungsform eine selbsttätige Einstellung der Passung und damit der Andruckkraft zwischen Rotor 42 und Stator 40 im Betrieb der Pumpe gewährleistet.At the
im gezeigten Beispiel ist die Rotorwelle mit dem Rotor 42 einstückig aus einem keramischen Material ausgebildet und weist in ihrem inneren einen Hohlraum 62 auf. Der Hohlraum 62 weist eine polygonale Querschnittsform auf und ist an seinem dem Rotor 42 abgewandten Stirnende mit einem Kupplungselement 64 in Eingriff, welches eine korrespondierende polygonale äußere Querschnittsform aufweist. Das Kupplungselement 64 bildet das Axialende 54 der Rotorwelle 52. Das Kupplungselement 64 ist in Richtung der Längsachse W axial im Inneren des Hohlraumes 62 verschiebbar. Auf diese Weise wird eine Axialverschiebbarkeit der Rotorwelle 52 dem Rotor 42 relativ zu dem Stator 40 erreicht. Ferner ermöglicht das Kupplungselement 64 die exzentrische Bewegung der Rotorwelle 52 um einen fiktiven Gelenkpunkt 65 auf der Mittelachse des Kupplungselementes 64. Dazu ist das Kupplungselement 64 aus einem Elastomermaterial, vorzugsweise Gummi ausgebildet oder weist zumindest an seiner dem inneren der Rotorwelle 52 zugewandte Bereich eine Beschichtung aus einem Elastomermaterial oder Gummi auf. Dies führt zu einer gelenkigen Lagerung des Kupplungselementes 64 in dem Hohlraum 62 im Inneren der Rotorwelle 52. So kann die Rotorwelle um das Kupplungselement 64 und den Gelenkpunkt 65 eine exzentrische Bewegung aufgrund der Gelenkigkeit der Verbindung zwischen Rotorwelle 52 und Kupplungsteil 64 ausführen.In the example shown, the rotor shaft with the
Die Andruckkraft, mit welcher der Rotor 42 in den Stator 40 gedrückt wird, stellt sich dabei selbsttätig aufgrund der Drücke an Saug- und Druckseite des Rotors 42 sowie des Umgebungsdruckes ein und insbesondere auf Grundlage des Kräfteverhältnisses zwischen den auf die Absatzflächen 60 sowie die Stirnfläche des Rotors 42 an der Axialseite 48 wirkenden Druckkräfte und den auf das Axialende 54 wirkenden Umgebungsdruck ein. Zusätzlich ist hier im Bereich der Dichtung 56 ein Federelement 66 vorgesehen, welches eine Vorspannung des Rotors in Richtung auf den Stator 40 erzeugt.The pressing force with which the
Der Stator 40 weist an seiner dem Rotor 42 zugewandten Innenoberfläche eine Beschichtung 68 aus einem Elastomermaterial auf.The
Anhand von
Bei der in
Die Anordnung, wie sie schematisch in
Es ist zu verstehen, dass es zur Einstellung der Passung bzw. der Andruckkraft zwischen Rotor und Stator lediglich auf die Relativbewegung zwischen Rotor und Stator ankommt. So lassen sich die Ausführungsformen gemäß
Bei dem in
Beim Betrieb der Pumpe führt der Rotor 86 eine Drehbewegung um seine Längsachse aus. Der Stator 90 mit der anschließenden Verlängerung 94 führt gleichzeitig eine exzentrische Bewegung bezüglich der Längsachse X aus, wobei die exzentrische Bewegung durch den Faltenbalg 96 ermöglicht wird, welcher ein Gelenk bildet. Im Inneren des Faltenbalgs 96 ist auf der Längsseite X ein fiktiver Gelenkpunkt 106 gelegen, um welchen die exzentrische Bewegung des Stators 90 erfolgt. Dabei beschreibt auch hier die exzentrische Bewegung eine Bahn entlang einer Kegeloberfläche, wobei der Gelenkpunkt 106 die Kegelspitze bildet. D. h. die Exzentrizität ist am Stirnende 102 des Stators 90 am größten und im Gelenkpunkt 106 gleich Null.During operation of the pump, the
Das Innere der Verlängerung 94 bildet eine Druckkammer, in welcher der druckseitige Pumpdruck der Exzenterschneckenpumpe wirkt. Dabei wirkt der druckseitige Druck zum einen auf die Stirnfläche 92 des Rotors 86 und gleichzeitig auf die den Faltenbalg 96 umgebende Ringfläche 108, welche im Inneren des von der Verlängerung 94 gebildeten Druckraumes angeordnet ist. Der Rotor 86 ist dabei durch ein nicht gezeigtes Axiallager fixiert. Die Ringfläche 108 ist dabei an dem der Stirnseite 92 des Rotors 86 abgewandten Seite der Verlängerung. 94 angeordnet und dem Rotor 86, d. h. der Saugseite der Pumpe zugewandt. Da im Inneren des Pumpengehäuses 100 der saugseitige Druck herrscht, liegt an der der Ringfläche 108 entgegengesetzte Außenwandung der Verlängerung 94 auch der saugseitige Druck an, welcher geringer als der Druck im inneren der Verlängerung 94 ist. Auf diese Weise wird aufgrund des Druckes im Inneren der Verlängerung 94 der Stator 90 zum Druckstutzen 86 hin gedrückt, wobei der Längenausgleich durch den Faltenbalg 96 erfolgt. So kann auch bei dieser Ausführungsform eine selbsttätige Einstellung der Passung zwischen Rotor 86 und Stator 90 in Abhängigkeit der Druckdifferenz zwischen Saug- und Druckseite der Exzenterschneckenpumpe erfolgen.The interior of the
- 2 -2 -
- Antriebsmotordrive motor
- 4 -4 -
- Pumpeneinheitpump unit
- 6 -6 -
- Eintrittsöffnunginlet opening
- 8 -8th -
- Druckstutzenpressure port
- 10 -10 -
- Statorstator
- 12 -12 -
- Rotorrotor
- 14 -14 -
- Elastomermaterialelastomeric material
- 16, 18 -16, 18 -
- Stirnseitenfront sides
- 20 -20 -
- Rotorwellerotor shaft
- 22 -22 -
- Anlenkungspunktarticulation point
- 2323
- Gelenkpunktfulcrum
- 24 -24 -
- Abtriebswelleoutput shaft
- 26 -26 -
- Druckflächeprint area
- 28 -28 -
- Kanalchannel
- 30 -30 -
- Faltenbalgbellow
- 32, 34 -32, 34 -
- Druckraumpressure chamber
- 36 -36 -
- Trennwandpartition wall
- 38 -38 -
- Kanalchannel
- 40 -40 -
- Statorstator
- 42 -42 -
- Rotorrotor
- 44 -44 -
- Gehäusecasing
- 46 -46 -
- Ansaugöffnungsuction
- 48,50 -48.50 -
- Stirnseitenfront sides
- 52 -52 -
- Rotorwellerotor shaft
- 54 -54 -
- Axialendeaxial
- 56 -56 -
- Dichtungpoetry
- 58 -58 -
- Raumroom
- 60 -60 -
- Absatzflächenshoulder surfaces
- 62 -62 -
- Hohlraumcavity
- 64 -64 -
- Kupplungselementcoupling member
- 6565
- Gelenkpunktfulcrum
- 66 -66 -
- Federelementspring element
- 68 -68 -
- Beschichtungcoating
- 70 -70 -
- Druckseitepressure side
- 72 -72 -
- Rotorrotor
- 74 -74 -
- Statorstator
- 76 -76 -
- Gehäusecasing
- 78 -78 -
- Stirnflächeface
- 8080
- Stirnflächeface
- 8282
- Spaltecolumn
- 8484
- Stirnflächeface
- 8686
- Rotorrotor
- 8888
- Rotorwellerotor shaft
- 9090
- Statorstator
- 9292
- Stirnseitefront
- 9494
- Verlängerungrenewal
- 9696
- Faltenbalgbellow
- 9898
- Druckstutzenpressure port
- 100100
- Pumpengehäusepump housing
- 102102
- Stirnendefront end
- 104104
- Sauganschlusssuction
- 106106
- Gelenkpunktfulcrum
- 108108
- Ringflächering surface
- X -X -
- Längsachse des StatorsLongitudinal axis of the stator
- W -W -
- Längsachse des RotorsLongitudinal axis of the rotor
Claims (11)
- A progressive cavity pump comprising an annular outer part (10; 40; 74) and an inner part (12; 42; 72) disposed therein, wherein the inside of the outer part (10; 40; 74) and the outside of the inner part (12; 42; 72) taper towards an axial side (16; 46; 70) in a manner corresponding to one another and the inner part (12; 42; 72) and the outer part (10; 40; 74) are mounted so that they are movable relative to one another in the axial direction (X, W),
characterised in that either
the axial side towards which the inside of the outer part (10; 74) and the outside of the inner part (12; 72) taper, is the delivery side of the progressive cavity pump and the inner part (12) has a channel (28) in its interior which is open towards the delivery side or a cavity in the interior of the progressive cavity pump and is in communication with a face (26) of the inner part (12) facing away from the delivery side, whereby a pressure present at the delivery side of the progressive cavity pump or in the interior of the progressive cavity pump between inner and outer part (10, 40, 74) produces a force acting axially on the inner part (12; 42; 72) in the direction in which the inner part (12; 42; 72) tapers,
or
the axial side to which the inside of the outer part (40) and the outside of the inner part (42) taper, is the intake side (46) of the progressive cavity pump and a pressure channel (82) is provided, which connects the delivery side or a cavity between inner part (42) and outer part (40) of the progressive cavity pump to a face (84) of the outer part facing away from the delivery side, whereby a pressure present at the delivery side of the progressive cavity pump or in the interior of the progressive cavity pump between inner and outer part (10, 40, 74) produces a force acting axially on the outer part (10; 40; 74) in the direction opposite to that in which the inner part (12; 42; 72) tapers. - The progressive cavity pump according to claim 1, characterised in that this is configured in such a manner that the pressure present at the delivery side acts on a face of the inner part (12; 42) facing away from the tapering end of the inner part (12; 42).
- The progressive cavity pump according to claim 1 or 2, characterised in that a pressure chamber (32, 34) is disposed on the axial side of the inner part (12) facing away from the delivery side, which pressure chamber is in communication with the channel (28) and has a variable length in the axial direction (W) and an inner face facing away from the delivery side, which is connected to the rotor (12).
- The progressive cavity pump according to claim 3, characterised in that the pressure chamber (32, 34) is configured in the interior of a shaft (20) driving the inner part (12), wherein the shaft (20) with the pressure chamber (32, 34) is variable in its length.
- The progressive cavity pump according to claim 3 or 4, characterised in that the pressure chamber (32, 34) is variable in its length by means of a piston-cylinder arrangement and/or by means of an outer wall which is elastic in the axial direction (W).
- The progressive cavity pump according to one of the preceding claims, characterised in that a constriction point (38) is formed in the channel (28) or the pressure chamber (32, 34) in communication with the channel (28).
- The progressive cavity pump according to one of the preceding claims, characterised in that the face (26) facing away from the delivery side, with which the channel (28) is in communication, is larger than the front face (16) of the inner part (12) facing the delivery side.
- The progressive cavity pump according to one of the preceding claims, characterised in that at least one pre-tensioning element (30; 66) is provided, which acts upon the inner part (12; 42; 72) with a pre-tensioning force in the axial direction (W) in which it tapers and/or which acts upon the outer part (10; 40; 74) with a pre-tensioning force in the opposite axial direction (W).
- The progressive cavity pump according to one of the preceding claims, characterised in that the inner part (12; 42; 72) is connected to a drive motor (2) by means of a shaft (20; 52), wherein the shaft (20; 52) is mounted in an articulated manner at a hinge point (23) and the hinge point (23) is preferably purely rotationally movable.
- The progressive cavity pump according to one of the preceding claims, characterised in that the inner part (12; 42; 72) is connected to a drive motor (2) by means of a shaft (20; 52) and the shaft
(20; 52) is eccentrically movable with the inner part (12; 42; 72), wherein the inner part (12; 42; 72) and the shaft (20; 52) are disposed in such a manner that the eccentricity of their movement increases from a hinge point (23), preferably increases linearly. - The progressive cavity pump according to one of the preceding claims, characterised in that the inner part (12; 42; 72) is formed from a ceramic material at least on its surface and the outer part (10; 40; 74) is formed from an elastomer at least on the surface facing the inner part.
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE502006002188T DE502006002188D1 (en) | 2006-01-26 | 2006-01-26 | Cavity Pump |
AT06001518T ATE415560T1 (en) | 2006-01-26 | 2006-01-26 | PROCESSING SCREW PUMP |
EP06001518A EP1813812B1 (en) | 2006-01-26 | 2006-01-26 | Progressive cavity pump |
PL06001518T PL1813812T3 (en) | 2006-01-26 | 2006-01-26 | Progressive cavity pump |
CN2007800037165A CN101375061B (en) | 2006-01-26 | 2007-01-25 | Progressive cavity pump |
PCT/EP2007/000604 WO2007085437A1 (en) | 2006-01-26 | 2007-01-25 | Eccentric screw pump |
US12/162,150 US8152499B2 (en) | 2006-01-26 | 2007-01-25 | Eccentric screw pump |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP06001518A EP1813812B1 (en) | 2006-01-26 | 2006-01-26 | Progressive cavity pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1813812A1 EP1813812A1 (en) | 2007-08-01 |
EP1813812B1 true EP1813812B1 (en) | 2008-11-26 |
Family
ID=36581669
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06001518A Not-in-force EP1813812B1 (en) | 2006-01-26 | 2006-01-26 | Progressive cavity pump |
Country Status (7)
Country | Link |
---|---|
US (1) | US8152499B2 (en) |
EP (1) | EP1813812B1 (en) |
CN (1) | CN101375061B (en) |
AT (1) | ATE415560T1 (en) |
DE (1) | DE502006002188D1 (en) |
PL (1) | PL1813812T3 (en) |
WO (1) | WO2007085437A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AU2010240676B2 (en) * | 2009-04-21 | 2016-03-03 | Quantex Patents Limited | Pump with a resilient seal |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE202009002823U1 (en) * | 2009-03-02 | 2009-07-30 | Daunheimer, Ralf | Cavity Pump |
EP2610493B1 (en) * | 2010-08-25 | 2020-01-01 | Furukawa Industrial Machinery Systems Co., Ltd. | Stator seal structure for single-shaft eccentric screw pump |
WO2015124918A1 (en) | 2014-02-18 | 2015-08-27 | Vert Rotors Uk Limited | Rotary positive-displacement machine |
CN104047846B (en) * | 2014-06-09 | 2018-05-15 | 无锡市恒烽水煤浆有限公司 | Wear-resistant high-pressure single-screw pump |
JP5802914B1 (en) * | 2014-11-14 | 2015-11-04 | 兵神装備株式会社 | Fluid transfer device |
US9776739B2 (en) | 2015-08-27 | 2017-10-03 | Vert Rotors Uk Limited | Miniature low-vibration active cooling system with conical rotary compressor |
US10174973B2 (en) | 2015-08-27 | 2019-01-08 | Vert Rotors Uk Limited | Miniature low-vibration active cooling system with conical rotary compressor |
DE102016207249B3 (en) * | 2016-04-28 | 2017-08-24 | BSH Hausgeräte GmbH | household appliance |
CN106337806A (en) * | 2016-11-18 | 2017-01-18 | 天津泵业机械集团有限公司 | High-temperature molten aluminum conveying pump |
DE102017100715A1 (en) * | 2017-01-16 | 2018-07-19 | Hugo Vogelsang Maschinenbau Gmbh | Control of the gap geometry in an eccentric screw pump |
CN109723637A (en) * | 2019-01-25 | 2019-05-07 | 无锡恒信北石科技有限公司 | All-metal taper combined threaded rod suitable for oil field pumps |
CA3131941A1 (en) * | 2019-03-11 | 2020-09-17 | National Oilwell Varco, L.P. | Progressing cavity devices and assemblies for coupling multiple stages of progressing cavity devices |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2733854A (en) * | 1956-02-07 | chang | ||
US2401189A (en) * | 1944-05-12 | 1946-05-28 | Francisco A Quiroz | Rotary pump construction |
US2527673A (en) * | 1947-02-28 | 1950-10-31 | Robbins & Myers | Internal helical gear pump |
US2957427A (en) | 1956-12-28 | 1960-10-25 | Walter J O'connor | Self-regulating pumping mechanism |
FR1284388A (en) * | 1961-03-21 | 1962-02-09 | Machine for the transport under pressure of mortar, cement or similar products | |
DE1553197A1 (en) * | 1965-09-08 | 1970-08-06 | Schlecht Dipl Ing Karl | Eccentric screw pump with movable stator |
US3938744A (en) * | 1974-09-05 | 1976-02-17 | Allen Clifford H | Positive displacement rotary pump and drive coupling therefor |
DE2524741A1 (en) * | 1975-06-04 | 1976-12-16 | Hermann Kraemer | Rotary pump with helical housing or rotor - with seal strips having long resilient common sealing element in contact with housing wall |
DE2632716A1 (en) * | 1976-07-21 | 1978-01-26 | Martin Theodor Melchior | LIQUID PUMP, ESPECIALLY FOR PLASTER STARTING DEVICES |
US6354824B1 (en) * | 2000-03-09 | 2002-03-12 | Kudu Industries, Inc. | Ceramic hardfacing for progressing cavity pump rotors |
RU2214513C1 (en) * | 2002-04-24 | 2003-10-20 | Давыдов Владимир Всеволодович | Gyration machine |
-
2006
- 2006-01-26 DE DE502006002188T patent/DE502006002188D1/en active Active
- 2006-01-26 EP EP06001518A patent/EP1813812B1/en not_active Not-in-force
- 2006-01-26 AT AT06001518T patent/ATE415560T1/en not_active IP Right Cessation
- 2006-01-26 PL PL06001518T patent/PL1813812T3/en unknown
-
2007
- 2007-01-25 CN CN2007800037165A patent/CN101375061B/en not_active Expired - Fee Related
- 2007-01-25 WO PCT/EP2007/000604 patent/WO2007085437A1/en active Application Filing
- 2007-01-25 US US12/162,150 patent/US8152499B2/en not_active Expired - Fee Related
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AU2010240676B2 (en) * | 2009-04-21 | 2016-03-03 | Quantex Patents Limited | Pump with a resilient seal |
Also Published As
Publication number | Publication date |
---|---|
CN101375061A (en) | 2009-02-25 |
PL1813812T3 (en) | 2009-05-29 |
US20090214369A1 (en) | 2009-08-27 |
CN101375061B (en) | 2011-04-06 |
DE502006002188D1 (en) | 2009-01-08 |
EP1813812A1 (en) | 2007-08-01 |
WO2007085437A1 (en) | 2007-08-02 |
ATE415560T1 (en) | 2008-12-15 |
US8152499B2 (en) | 2012-04-10 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1813812B1 (en) | Progressive cavity pump | |
EP2406497B1 (en) | Hydraulic toothed wheel machine | |
DE10161131B4 (en) | Vane pump variable displacement | |
DE19942466A1 (en) | Adjustable displacement pump comprises pump body with inner chamber and suction and delivery paths connected to inner chamber, together with cam ring | |
EP1701038B1 (en) | Internal gear pump | |
DE102005056909A1 (en) | Hydraulic gearwheel machine e.g. reversible outer gear wheel motor, for mobile hydraulic system, has covers with front recesses, where one recess is coupled with leakage oil channel of support latches via grooves for forming oil flow path | |
EP0517014A1 (en) | Lubrication gear pump for internal combustion engines, especially for vehicles | |
EP1283971A1 (en) | Regulated pump | |
EP3610154B1 (en) | Eccentric screw pump | |
DE102005041579A1 (en) | Internal gear pump with filling piece | |
WO2016173800A1 (en) | Pump device | |
EP0666422B1 (en) | Bearings and drive connection for the rotors of a screw compressor | |
DE202015103751U1 (en) | pump device | |
DE102015213338B4 (en) | Actuator unit | |
DE10245306B4 (en) | Extruder / gear pump assembly | |
DE102004038477B3 (en) | Cavity Pump | |
EP0846861A1 (en) | Continuously variable annular gear pump | |
DE102006021815A1 (en) | Hydraulic gear wheel machine e.g. external gear pumps used in movable hydraulics, comprises external gear pump with gear wheel system in inner chamber and mesh supported in bearing support opposite to housing | |
EP2119869A2 (en) | Hydro transformer | |
EP1311762B1 (en) | Internal geared wheel pump | |
DE1653905A1 (en) | Displacement pump | |
WO2016173799A1 (en) | Pump device | |
EP2063126A2 (en) | Hydraulic cog wheel machine and method for sealing a hydraulic cog wheel machine | |
DE19962035B4 (en) | swing motor | |
DE102005033707A1 (en) | Compressor for the air conditioning unit of a vehicle comprises an axial sliding ring seal radially impinged with pressure prevailing in the compressor at the height of a gap arranged between a sliding ring and a counter ring |
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 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA HR MK YU |
|
17P | Request for examination filed |
Effective date: 20070807 |
|
AKX | Designation fees paid |
Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REF | Corresponds to: |
Ref document number: 502006002188 Country of ref document: DE Date of ref document: 20090108 Kind code of ref document: P |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LT 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: 20081126 Ref country code: ES 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: 20090308 |
|
NLV1 | Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act | ||
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI 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: 20081126 Ref country code: NL 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: 20081126 Ref country code: FI 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: 20081126 Ref country code: IS 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: 20090326 Ref country code: LV 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: 20081126 |
|
REG | Reference to a national code |
Ref country code: PL Ref legal event code: T3 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FD4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE 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: 20081126 Ref country code: EE 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: 20081126 Ref country code: RO 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: 20081126 Ref country code: DK 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: 20081126 Ref country code: BG 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: 20090226 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT 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: 20090427 Ref country code: SE 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: 20090226 Ref country code: CZ 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: 20081126 Ref country code: MC Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090131 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SK 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: 20081126 |
|
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 |
Effective date: 20090827 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090131 |
|
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: 20090126 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100131 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: 20090227 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100131 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090126 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU 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: 20090527 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR 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: 20081126 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY 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: 20081126 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 11 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 12 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 13 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20220125 Year of fee payment: 17 Ref country code: DE Payment date: 20220124 Year of fee payment: 17 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: PL Payment date: 20220114 Year of fee payment: 17 Ref country code: IT Payment date: 20220124 Year of fee payment: 17 Ref country code: FR Payment date: 20220120 Year of fee payment: 17 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R082 Ref document number: 502006002188 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 502006002188 Country of ref document: DE |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20230126 |
|
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: 20230126 Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230801 |
|
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: 20230131 |
|
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: 20230126 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PL Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230126 |