CN101484703B - Moineau type pump - Google Patents
Moineau type pump Download PDFInfo
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- CN101484703B CN101484703B CN2007800249440A CN200780024944A CN101484703B CN 101484703 B CN101484703 B CN 101484703B CN 2007800249440 A CN2007800249440 A CN 2007800249440A CN 200780024944 A CN200780024944 A CN 200780024944A CN 101484703 B CN101484703 B CN 101484703B
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- 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
- F04C2/1073—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 where one member is stationary while the other member rotates and orbits
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- 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
- F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
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- 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
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C15/0069—Magnetic couplings
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- 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
- F04C2/1076—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 where one member orbits or wobbles relative to the other member which rotates around a fixed axis
Abstract
The invention refers to a Moineau type pump having at least one outer part (4; 44, 76) and one inner part (2; 42; 78) arranged inside the outer part (4; 44; 76), wherein at least one of the inner (2; 42; 78) and outer part (4; 44; 76) acts as a rotor and is driven by a magnetic field, wherein the rotor is movable in axial direction and does not comprise an axial bearing.
Description
Technical field
The present invention relates to a kind of screw pump (Moineau type pump), promptly a kind of screw rod boost pump (progressive cavity pump).
Background technique
The screw rod boost pump is because the eccentric motion of its rotary component is very complicated usually.Generally speaking, need flexible coupling or universal joint to connect the rotor and the motor of pump, so that motor can eccentric motion.So just increased the total length and the weight of pump, and the price of pump is improved.In addition, the precision of having relatively high expectations when the parts of processing and assembling pump is to allow complicated eccentric motion.
In addition,, must make constituting one of at least in rotor or the stator, touch to guarantee that liquid between rotor and stator connects airtight by elastic material even if close for guaranteeing that under high pressure pump chamber is still liquid.Yet this has caused higher friction and wear, has reduced the reliability and the serviceability of pump simultaneously.
Summary of the invention.
In view of this, the purpose of this invention is to provide a kind of simple screw pump, its easier manufacturing and price are more cheap, and have high abrasiveness, reliability and serviceability.
This purpose realizes by a kind of screw pump as described below,, the invention discloses a kind of screw pump that is, has: at least one external pump parts; And at least one internal pump parts, described internal pump parts are arranged on the inside of described external pump parts, in wherein said internal pump parts and the described external pump parts one of at least as rotor and by field drives, it is characterized in that, the inside of described external pump parts and described internal pump parts are tapered, this rotor can move vertically, and does not comprise the thrust supporting.
A plurality of preferred embodiments are limited in the following explanation and accompanying drawing.
Screw pump simplicity of design of the present invention, it is low to wear and tear, and especially, has the Sealing of simplification in the pump.
A design of the present invention is to obtain a kind of driving with other type of use by magneto drive to compare simpler and compacter pump.In addition, this magneto drive does not need complicated Sealing.
Screw pump according to the present invention has at least one external pump parts (external pump member) and at least one internal pump parts (internal pump member), and the internal pump parts are arranged on the inside of external pump parts.The external pump parts have circular structure, and its inside has the cavity of ccontaining internal pump parts.Usually for screw pump, internal pump parts and external pump parts carry out eccentric toward each other rotatablely moving, and wherein the internal pump parts externally roll on the inner ring surface of pump parts.Further, all have helical structure on the internal surface of the outer surface of internal pump parts and external pump parts, described helical structure forms gradual cavity with pumping fluid between internal pump parts and external pump parts.Relative movement between internal pump parts and the external pump parts can realize by rotation internal pump parts or rotation external pump parts, also can be by rotating the internal pump parts in the lump and the external pump parts are realized.Therefore, according to the present invention, drive as rotor and by magnetic field to major general's internal pump parts or external pump parts.This means between rotor and driving component or drive system and exist magnetic coupling.Therefore, between these members, promptly between rotor and drive system, no longer need mechanical connection.Thus, simplified the structure of screw pump.If flexible coupling or universal joint required when connecting both by axle need be set between drive system and rotor.Another advantage is that magneto drive can make the design of entire pump compacter.In addition, because this design concept need not mechanical drive components is incorporated into the inside of the pump that is full of the fluid for the treatment of pumping or medium, so can more easily realize sealing.Therefore, this pump does not need shaft seal, and makes the dangerous minimum of leakage.
In addition, according to the present invention, rotor (being internal pump parts and/or external pump parts) is removable vertically and do not comprise thrust bearing.The manufacturing and the assembling of pump have so just further been simplified.Because rotor does not have thrust bearing, so it can move freely in the axial direction.Preferably, rotor is only by magnetic force and/or be pumped and act on the pressure of this epitrochanterian fluid or medium and remain on the appropriate location.Preferably, this rotor (be internal pump parts and/or the external pump parts or the member of pump, depend on which parts is driven) is designed to make and acts on the axial force balance that this epitrochanterian pressure produces.
Preferably, by coming at least in part along the pressure of axial action at the lip-deep effluent fluid of rotor, preferably compensate fully by in pump chamber between internal pump parts and the external pump parts or the pump chamber hydrodynamic pressure produced acts on epitrochanterian axial force.On the outlet side of rotor specific surface can be set, be preferably end face, the pressure of effluent fluid acts on this end face, with the axial force of compensation by the generation of the pressure in the pump chamber between internal pump parts and the external pump parts (being gradual cavity).
Particularly preferably, the inside of external pump parts and internal pump parts are all tapered.This means that the cavity in the external pump parts has the internal pump parts of corresponding taper with ccontaining taper.The helical structure of internal pump parts and external pump parts is separately positioned on the tapered annular internal surface of the cavity in the conical outer surface of internal pump parts and the external pump parts.
Especially, owing to have a shape of taper, be preferably along the directive effect that external pump parts and internal pump parts are pressed together on the surface of rotor according to the pressure of the effluent fluid of screw pump of the present invention.That rotor (be internal pump parts and/or external pump parts, depend on the design of pump) has is enough, pump head or pumping pressure effect surface thereon.Preferably, this Surface Vertical is extended in the direction of rotor longitudinal axis so that this pressure produce along this direction and act on epitrochanterian axial force.This surface can be that rotor is at the outlet end place, promptly at the end face of the pressure side of pump.By the axial force that is produced by pumping pressure, the internal pump parts and the external pump parts of pump are pressed together.Can allow like this to be designed to make the contact pressure between internal pump parts and the external pump parts to raise pump along with the rising of pumping pressure.Ideally, be zero (0) as pumping pressure, then contact pressure or contact force are zero (0).This makes friction and detent torque in the pump reduce, and has reduced wearing and tearing.Along with pumping pressure raises, contact force or pressure between internal pump parts and the external pump parts also raise, thereby connect airtight and touch even under high pressure still can obtain liquid between internal pump parts and the external pump parts.Contact force is along with the proportional rising of pumping pressure.
In addition, rotor can contacting by rotor and miscellaneous part or member on axially at one, can keep in position by the pumping pressure that acts on vertically on the rotor surface on another is axial, therefore this design does not need the thrust bearing of rotor.Therefore, rotor is fixed on the miscellaneous part of pump vertically.If the internal pump parts are as rotor, then the internal pump parts are pressed against on the external pump parts.If the external pump parts are as rotor, then the external pump parts are pressed against on the internal pump parts.
In addition, owing to do not need to be arranged on the mechanical coupling that axial motion takes place in the drive system, therefore by using magneto drive can easily realize the being axially moveable property of rotor.
Magnetic driving equipment preferably includes: at least one first magnet, and it is fixed on this rotor; And at least one and interactional second magnet of first magnet, second magnet is fixed on the rotatable driving component.Preferably, a plurality of first magnets and a plurality of second magnet distribute equably around the side face of rotor and driving component.Rotatable driving component can be equipped with thrust bearing or radial bearing, moves so that can be rotated along running shaft.This driving component can be driven by for example electric motor or other suitable drive mechanism.The torque of rotatable driving component can be delivered on the rotor of screw pump by first magnet and second magnet, and described first magnet and second magnet are set to: second magnet that is fixed on the rotatable driving component drives first magnet and causes the rotor rotation.Preferably, the rotation of driving component axle is identical with the running shaft of rotor, that is, driving component and rotor rotate with coaxial manner.Yet, also can be that rotor carries out eccentric motion, and driving component be rotated around himself spin axis.If have enough spaces diametrically between first magnet and second magnet, then the tolerable rotor carries out certain eccentric motion with respect to driving component.Yet if the spacing between first magnet and second magnet is excessive, the efficient of magneto drive can reduce.Therefore, the degree of eccentricity of rotor motion is limited in certain amount.Yet for the amount of this permissible degree of eccentricity, it is much simpler than the mechanical coupling that needs flexible coupling to use magnet to drive rotor.
Use magnet will rotatablely move to be delivered to and have such advantage on the rotor: between driving component and rotor, need not mechanical coupling.In addition, because magnetic coupling can easily make between rotor and the preferred fixing vertically driving component certain moving axially arranged, so the axial motion of rotor is also out of question under this magnetic coupling situation.In addition, because magnetic field can see through the wall (being full of fluid or the medium for the treatment of pumping in this pump) of the inside that limits pump, therefore seal with respect to the external world than the inside that is easier to pump.Therefore, according to preferred embodiment, can between rotor and driving component, Rotor can be set.So encapsulated the inside of the pump that is full of the fluid for the treatment of pumping or medium fully.Therefore, need not live axle is introduced the inside of pump.Driving component can be arranged on the outside of Rotor can or housing, and second magnet is in the rotation of the outside of Rotor can.Rotor with first magnet is arranged on Rotor can inside, and is driven by second magnet in the outside rotation of this Rotor can at least.
Preferably, first magnet and/or second magnet are permanent magnet.This makes the simple and reliable for structure of magneto drive.
According to another embodiment of the invention, along the longitudinal 2 observation of this pump, first magnet and second magnet are set to be preferably zero position near the degree of eccentricity minimum between internal pump parts and the external pump parts.
In common screw pump, internal pump parts and external pump parts relative to each other carry out off-centre and rotatablely move.This means that when for example the internal pump parts also centered on the longitudinal axis rotation of himself as rotor, this longitudinal axis self also rotated round the longitudinal axis of external pump parts (being stator).Preferably, in the screw pump of internal pump parts with above-mentioned conical design and external pump parts, the degree of eccentricity of the motion of internal pump parts and external pump parts is not constant, but from thinner end the reducing linearly than butt end to pump of pump.This means that the longitudinal axis of internal pump parts and the longitudinal axis of external pump parts are place, the point of intersection intersection of zero (0) in the degree of eccentricity.According to the preferred embodiment, pump vertically on magnet be set to close, be preferably the position that is set directly at this minimum degree of eccentricity.This optimum seeking site is the intersection point of two longitudinal axis or two running shafts.Magnet can extend longitudinally, and can extend across the position of the minimum degree of eccentricity in the direction.In this position, the eccentric motion of magnet will be very limited, improve the efficient of magneto drive thus.In addition, magnet is arranged in the zone of the position of the minimum degree of eccentricity or the minimum degree of eccentricity and can makes pump have bigger maximum eccentricity.Usually, by using magneto drive, (being the spacing between the magnet of the magnet of rotor and driving component) do not allow to exceed a certain maximum value because the spacing between first magnet and second magnet, so eccentric motion is very limited.In addition, preferably, during rotation this spacing is constant basically, with the rotation of guaranteeing this rotor with to act on this epitrochanterian torque evenly constant.This situation occurs in minimum degree of eccentricity place.
Must be noted that first magnet and second magnet be arranged near the degree of eccentricity between internal pump parts and the external pump parts and can't form limitation to the axially displaceable design of rotor for minimum position.This set of magnet also can be applicable to the pump that rotor can not move vertically.
In another preferred embodiment, the magnetic field that drives this rotor also produces except producing rotating force and acts on the internal pump parts of pump and the axial force between the external pump parts.Thus, the axial force that magnetic field produced that is used to drive rotor can be used to realize more benefit.
Axial magnetic force can produce by first magnet and second magnet, and wherein at least one first magnet is fixed on the rotor, and at least one second magnet is fixed on the driving component.Axial magnetic force can be fixed on the axial dipole field that this epitrochanterian first magnet and at least one be fixed on second magnet on the rotatable driving component by at least one and produce.
According to the direction of axial dipole field, axial magnetic can act on opposite direction.This means that for example, if second magnet is displaced to first axle head of pump with respect to first magnet, then act on epitrochanterian axial force towards this first end, that is, axial magnetic is attempted rotor is moved to this first end.If second magnet is displaced to opposite second end, then axial force will be along the opposite direction effect towards this second end.
According to the action direction of axial magnetic, this power can be used as different functions.
When the inside of external pump parts and internal pump parts were taper, the axial force that is produced by magnetic force will be towards the direction that internal pump parts and external pump parts are pressed together, or towards the direction that forces internal pump parts and external pump parts to separate.Under the situation that axial magnetic is pressed together internal pump parts and external pump parts, this power can be used for compensating at least in part by the internal pump parts of pump and the axial force that hydrodynamic pressure produced in the pump chamber between the external pump parts.Another advantage is, when pump do not turn round and the internal pump parts of pump and/or external pump parts on when not having fluid pressure action, the internal pump parts can remain with the external pump parts and contact.When axial magnetic force during towards direction that internal pump parts and external pump parts are separated, can obtain reverse effect, that is, under the non-operating state of pump, keep certain spacing between internal pump parts and the external pump parts.Therefore, when pump does not turn round, be preferably contactless power and friction between internal pump parts and the external pump parts.So just reduce the startup dynamic torque of pump and reduced the wearing and tearing of pump.
Description of drawings
Below describe the preferred embodiments of the present invention with reference to the accompanying drawings, in the accompanying drawings:
Fig. 1 is the schematic cross sectional views according to the screw pump of first embodiment of the invention;
Fig. 2 is the schematic cross sectional views according to the screw pump of second embodiment of the invention;
Fig. 3 is the schematic cross sectional views according to the screw pump of third embodiment of the invention;
Fig. 4 is the schematic cross sectional views according to the 4th embodiment of screw pump of the present invention;
Fig. 5 shows the angle of swing of several screw pump designs and the chart of axial force relation;
Fig. 6 is the schematic cross sectional views according to another embodiment of screw pump of the present invention;
Fig. 7 is the schematic cross sectional views according to another embodiment of screw pump of the present invention;
Fig. 8 is the schematic representation according to the magnet setting that is used for magneto drive of screw pump of the present invention;
Fig. 9 is the schematic cross sectional views of another embodiment's the screw pump according to the present invention; And
Figure 10 is the schematic cross sectional views of another embodiment's the screw pump according to the present invention.
Embodiment
Described a kind of improved screw pump or transmission device (gears) in the preferred embodiment, wherein, be delivered to the influence that epitrochanterian torque is subjected to preferably the magnetic field that produced by permanent magnet, and wherein this rotor has been taper.
Because driver is the part of pumping installations, therefore this pump is very compact in the axial direction.In addition, this pump is made up of very small amount of parts, and no longer needs to cause the coupling that is used for rotor and rotor shaft, shaft seal, the nothing supporting bellows (bellow no-bearing) of fault.In addition, the use of magnetic coupler or magnetic drives can make pump keep the close property of liquid with respect to the external world, and leak free danger.
Fig. 1 shows the first kind of design of the present invention or first preferred embodiment.Actual pump comprises internal pump parts or member 2 and external pump parts or member 4.External pump parts 4 are for having the ring part of conical cavity 6, and the inside of conical cavity 6 is equipped with internal pump parts 2.Normally, the inside of the conical cavity 6 of screw pump has helical structure, and the outside of internal pump parts 2 has corresponding helical structure, and wherein the screw thread of the helical structure of external pump parts 4 or tooth are Duoed one than the screw thread or the tooth of the helical structure of internal pump parts 2.
In the embodiment according to Fig. 1, internal pump parts 2 are used as stator and are fixed in the pump case 8.The external pump parts are as rotor and can center on 2 rotations of internal pump parts, thereby form the eccentric motion with respect to internal pump parts 2.External pump parts 4 are driven by magnetic drives.Externally be fixed with first magnet 10 on the outer circumferential face of pump parts 4, on the driving component 14 of surrounding external pump parts 4, be fixed with second magnet 12.Driving component 14 links to each other with the drive motor (not shown in figure 1), and can be around the longitudinal axis rotation of this driving component 14 self.Preferably, the longitudinal axis of the spin axis of driving component 14 and internal pump parts 2 is same axis.
When driving component 14 during around its longitudinal axis rotation, magnet 12 is around 4 rotations of external pump parts, and is fixed on first magnet 10 on the external pump parts 4 by the field drives that second magnet 12 produces, so that external pump parts 4 are with driving component 14 rotations.Magnet 10,12 is a permanent magnet.Preferably, Rotor can 16 is made of plastics, so that this magnetic field is not subjected to the influence of this Rotor can.
Fluid or the medium for the treatment of pumping enter in the pump through inlet 18.This inlet is the inlet duct that extends longitudinally internal pump parts 2 inside.Inlet 18 is arranged on the thicker end face of internal pump parts 2 of taper.Inlet duct is in the thinner end face upper shed of internal pump parts 2, and from the thinner end of the internal pump parts 2 of taper and external pump parts 4 enters pump chamber between these internal pump parts 2 and the external pump parts 4.When external pump parts 4 were driven by driving component 14, pump chamber was progressive towards its relative the other end vertically from the thinner end of external pump parts 4.Externally the thicker end of pump parts 4 is located, and fluid leaves the pump chamber between internal pump parts 2 and the external pump parts 4, and subsequently, fluid enters the space 20 between external pump parts 4 and the Rotor can 16 and is directed to outlet 22.
In space 20, act on the outside of external pump parts 4 by the pumping pressure of pump accumulation or pump head (pump head) along the direction A among Fig. 1, this direction A is parallel to the longitudinal axis of internal pump parts 2.Thus, the axial force that produces by the pumping pressure that acts on external pump parts 4 outsides of external pump parts 4 and by being pressed on the internal pump parts 2.
In this embodiment, because the pumping pressure that external pump parts 4 produce by pump and by being pressed on the internal pump parts 2, so external pump parts 4 do not need the thrust supporting.External pump parts 4 are kept by the pressure balance between the pump chamber pressure inside between space 20 pressure inside and internal pump parts 2 and the external pump parts 4 in the axial direction.
Fig. 2 shows second embodiment or the second kind of design according to screw pump of the present invention.In a second embodiment, internal pump parts 2 ' externally pump parts 4 ' interior rotation, this external pump parts 4 ' be fixed in pump case 8 ' on.As previously mentioned, external pump parts 4 ' inner chamber and internal pump parts 2 ' be taper, and external pump parts 4 ' surface of internal cavity and internal pump parts 2 ' the surface on all have helical structure.
Internal pump parts 2 ' by driving component 14 ' driving, this driving component 14 ' be arranged in the space or cavity of internal pump parts 2 ' inside.Internal pump parts 2 ' be cup-shaped, and internal pump parts 2 ' inner peripheral surface be provided with first magnet 10 ', and described first magnet face is inside.Be similarly cup-shaped Rotor can 16 ' extend into internal pump parts 2 ' cavity in.Driving component 14 ' be arranged on Rotor can 16 ' in.This driving component can be around the rotation of its longitudinal axis, and carry on its outer circumferential face second magnet 12 ', so that this second magnet 12 ' in the face of first magnet 10 '.Driving component 14 ' link to each other with drive motor (not shown among Fig. 2).
Rotation 14 ' time of driving component, because magnet 10 ' and 12 ' between the effect in magnetic field, the magnet 12 in driving component 14 ' outside ' to being fixed on the first magnet 10 ' effect on internal pump parts 2 ' inboard, so that these internal pump parts 2 ' along with this driving component 14 ' rotation together.Thus, internal pump parts 2 ' externally pump parts or member 4 ' interior rotation.Thus, treat the fluid of pumping or medium be sucked into inlet 18 ' in and by 24 pumpings of longitudinally progressive pump chamber.Fluid or medium leave internal pump parts 2 ' and external pump parts 4 ' between pump chamber 24 after, fluid or medium by Rotor can 16 ' the outside and internal pump parts 2 ' the inboard between the space flow into internal pump parts 2 ', and flow to outlet 22 '.Therefore, the pumping pressure of pump head is in internal pump parts 2 ' interior accumulation, with the internal pump parts are pushed against externally pump parts 4 ' on.Because second embodiment compares with the embodiment shown in Fig. 1 and has bigger diameter, so second embodiment shown in Fig. 2 can obtain bigger flow.
The 3rd embodiment has been shown among Fig. 3.Similar with the embodiment shown in Fig. 1, in the embodiment shown in Fig. 3, external pump parts 4 " are driven by driving component (not shown among Fig. 3).For this purpose, on the outer circumferential face that first magnet 10 " is fixed on external pump parts 4 ".Fig. 1 is illustrated as reference, during external pump parts 4 " are contained in Rotor can 16 "., Rotor can 16 similar with the embodiment among Fig. 1 " the outside driving component can be set.
The embodiment of Fig. 3 is the layout that enters the mouth than the difference of the embodiment shown in Fig. 1.According to the embodiment among Fig. 3, longitudinally to observe, the inlet that fluid enters pump chamber is arranged on internal pump parts 2 centre of " with external pump parts 4 ".In this example, internal pump parts 2 " and external pump parts 4 " are made up of two-part 2 " a and 2 " b and 4 " a and 4 " b respectively.Described part 2 " a and the 4 " screw thread of a is opposite with the thread rotary orientation of other part 2 " b and 4 " b, the screw thread of described other part 2 " b and 4 " b starts from centre gangway 26, and this centre gangway 26 " radially extends to internal pump parts 2 " and external pump parts 4 from inlet channel 18 " between the pump space.Internal pump parts 2 " first portion 2 " a and external pump parts 4 " first portion 4 " a extends to a longitudinal end of pump, and internal pump parts 2 " second portion 2 " b and external pump parts 4 " second portion 4 " b extends to relative the other end.Described part 2 " a and 4 " a has left-handed thread, and other part 2 " b, 4 " b has right-handed thread, thereby the fluid that enters into the space between the internal pump parts 2 " with external pump parts 4 " in two directions is pumped into two relative longitudinal ends of pump from passage 26.Yet, internal pump parts and the external pump parts part that also can form as one, wherein the screw thread that rotation direction is opposite starts from the neutral position respectively, and extends to relative end.
In addition, in this embodiment, as described in according to the embodiment of Fig. 1, the pressure that pump produces acts on external pump parts 4, and " outside is so that on " being pressed into internal pump parts 2 " with these external pump parts 4.Compare with the aforementioned concepts shown in Fig. 2 with Fig. 1, angle, diameter, length and the degree of eccentricity etc. of the various piece by optimizing internal pump parts 2 " and external pump parts 4 " can reduce axial force.In addition, high pump pressure can only not be applied to as aforementioned concepts on the surface, but is applied to side, end face and bottom surface.Can reduce to bear the gross area of high pump pressure like this, thereby reduce axial force.
Axial force from two parts 4 of two parts 2 " a and the 2 " b and the external pump parts of internal pump parts " a and, 4 " b will increase, and by between two parts, angle being set, can make the frequency of pulse of axial force higher, amplitude is littler, (line 38) will be discussed this hereinafter as shown in Figure 5.
Another major advantage of the 3rd embodiment is: owing in entire pump, all circulate, and have the dead angle in first and second embodiments, and therefore, according to the easier cleaning of the 3rd embodiment's pump.According to the embodiment shown in Fig. 1 and Fig. 2, because bigger area is exposed under the high pumping pressure, thereby its application is limited to, and compare with the embodiment shown in Fig. 2 with this Fig. 1, pump according to the 3rd embodiment has axial force optimization, balance, and can be mainly used in the situation of high pump head or pumping pressure.
Fig. 4 shows the similar embodiment with Fig. 3.In this embodiment according to Fig. 4, internal pump parts 2 " ' and external pump parts 4 " ' also have two parts 2 " ' a, 4 " ' a and 2 " ' b, 4 " ' b respectively, wherein, fluid enters two middle parts between the part.Internal pump parts 2 " ' first portion 2 " ' a and external pump parts 4 " ' first portion 4 " ' a extends to a longitudinal end that is provided with outlet 30 of pump from the middle part that is provided with inlet channel 28 of pump.And internal pump parts 2 " ' second portion 2 " ' b and external pump parts 4 " ' second portion 4 " ' b extends to relative longitudinal end along opposite direction.Equally, in this embodiment because internal pump parts 2 " ' and external pump parts 4 " ' the screw thread of two parts reverse each other, so fluid from inlet channel 28 begin to be pumped into internal pump parts 2 " ' with external pump parts 4 " ' two relative ends.Different with the embodiment of Fig. 3 is, in the embodiment of Fig. 4, and internal pump parts 2 " ' be driven, and external pump parts 4 " ' be fixed on the pump case.For this reason, similar with the embodiment shown in Fig. 2, on first magnet 10 " ' be fixed on internal pump the parts 2 " ' inner space or the inner peripheral surface of cavity.In the space of Rotor can 16 " ' extend to internal pump parts 2 " ' inner, and can be ccontaining with Fig. 2 in the similar driving component of embodiment (not shown among Fig. 4).
Fig. 5 shows angle of swing among aforesaid several embodiment
Chart with the relation of axial force F.Dotted line 32 shows the pulse axial force that occurs among the embodiment according to Fig. 1.Line 34 shows the angle of swing of internal pump parts 2 according to Fig. 3 " bottom part 2 " b and external pump parts 4 " bottom part 4 " b (promptly extending to the part than thick end of pump)
Relation with the pulse axial force.Line 36 shows the pulse axial force of the other parts (being the part of the thinner end portion that extends to pump of internal pump parts 2 " and external pump parts 4 ") among Fig. 3.Line 38 shows the power that the axial force according to line 34 and 36 produces, the i.e. total axial force that produces among the embodiment according to Fig. 3.As seen, compare, can reduce total axial force according to the third design of Fig. 3 with first embodiment.Embodiment according to Fig. 4 also has identical effect.
Fig. 6 shows another and the similar embodiment of embodiment shown in Figure 3.Unique difference is that in the embodiment according to Fig. 6, " b constitutes internal pump parts 2 " by two parts 2 " a and 2.Correspondingly, " b constitutes external pump parts 4 " by two independent parts 4 " a and 4." b is designed to independently that member makes design have offers additional possibilities to the part 2 of internal pump parts " a and 2 " b and external pump parts 4 " part 4 " a and 4, and can distribute axial force better.
In the embodiment show in figure 3, internal pump parts 2 " and external pump parts 4 " are fabricated to the integral piece with two parts, as expect constant flow, and then the product of the degree of eccentricity and diameter (product) preferably keeps constant.In this embodiment according to Fig. 6, externally the middle part between pump parts and internal pump parts part 4 " a and 2 " a that forms and part 4 " b and the 2 " b that is formed by external pump parts and internal pump parts has a diameter and suddenlys change.This means the diameter that to select two parts or part independently, i.e. the diameter of an end of first portion and second portion.Therefore, axial force can almost entirely be balanced.
Fig. 7 shows the further modification of the embodiment shown in Fig. 6.Pump according to Fig. 7 is a multistage pump.This pump has four layers and is similar to arranging shown in Fig. 6.In this embodiment according to Fig. 7, the driving mode and the embodiment shown in Fig. 2 of internal pump parts 42 are similar.Be provided with Rotor can 46 in the inside of internal pump parts 42.Be provided with the driving component 48 that supports first magnet 50 in Rotor can 46 inside.When this driving component 48 of rotation, magnet 50 rotations also drive second magnet 52 that is fixed on these internal pump parts 42.The pump-unit of Fig. 7 has 54 and two outlets 56 of two inlets.Flowing of fluid indicated by the arrow among Fig. 7.Flowing to of the level II of the level I of one side and the flow direction of III and opposite side and IV is different.In level II and IV, fluid flows to the relative two ends of internal pump parts 42 and external pump parts 44 from the middle part.In level I and III, fluid flows to the middle part of the level that is formed by internal pump parts 42 and external pump parts 44 from relative longitudinal end.Design according to Fig. 7 can be transmitted higher pressure.The structure of Fig. 7 N two internal pump parts 42 of group and two external pump parts 44 can be set, so that can provide N doubly to the pressure of a group or a hierarchy structure.
When considering possible degree of eccentricity problem, all there is limitation in aforesaid all embodiments.Preferably, the degree of eccentricity of the screw pump of taper or screw rod boost pump is not constant.In the above-described embodiments, maximum eccentricity is restricted, so that keep the efficient of magnetic drives.The efficient of magnetic drives can descend along with the increase of distance between the first relative magnet and second magnet.
Fig. 8 shows preferred principle, according to this principle, can drive by using magnetic force under the higher degree of eccentricity.Fig. 8 schematically show eccentric cone 58 and magnet 60 and 62 along two of longitudinal axis X possible positions.Magnet 60 is arranged in the zone that has than the large eccentricity degree in a conventional manner.The maximum eccentricity and the extreme length of the pump shown in braces I have so just been limited.
According to a preferred embodiment of the invention or design, observe along longitudinal axis X, magnet 62 be set near or be located immediately at without acceptance of persons 63 places, position.Therefore, for a pair of internal magnets and external magnets, when magnet 62 therein was in this position, this internal magnets and this external magnets can be set to close to each other, thereby have good magnetic drives efficient.In addition, this structure can make the overall degree of eccentricity of helical structure bigger, shown in the braces II among Fig. 8.The degree of eccentricity of helical structure directly influences flow, causes flow to increase.
Fig. 9 shows an alternative embodiment of the invention, this embodiment is preferably used for the example of the medium that for example density is bigger, for example be used for food service industry, require this moment interval between flow velocity between tooth or the screw thread lower and tooth or the screw thread can reduce shearing force (shear) in the fluid.The degree of eccentricity of present embodiment is bigger than aforesaid each embodiment.This means that the vibration meeting that causes limited speed is bigger.
Similar with the embodiment according to Fig. 2, the embodiment shown in Fig. 9 has driven internal pump parts 66, and it is arranged in the fixing external pump parts 64.And in this embodiment, internal pump parts 66 and external pump parts 64 all are tapers.As can be seen from Figure 9, in the present embodiment, first magnet 68 is fixed on the internal pump parts 66 as rotor, and along the longitudinal axis (with external pump parts 64) the partition distance c of internal pump parts 66.This is because first magnet 68 and second magnet 70 all are set near the position without acceptance of persons 63 (consulting Fig. 8) in the earlier figures 8.Second magnet 70 is fixed on the driving component 72 that links to each other with motor (not shown among Fig. 9).In this embodiment, Rotor can 74 also is arranged between first internal magnets 68 and second external magnets 70.
Figure 10 shows another embodiment, uses shaft seal among this embodiment but not the Rotor can that uses in the previous embodiment.Other aspects and the embodiment shown in Fig. 2 according to the embodiment of Figure 10 are similar.In embodiment, also be provided with fixing external pump parts 76 and rotatable and as the internal pump parts 78 of rotor according to Figure 10.Above-mentioned external pump parts and internal pump parts are taper.In addition, in this embodiment, the rotor that is formed by internal pump parts 78 is a jar shape, and driving component 84 is arranged on the inside of these internal pump parts 78.On the inner peripheral surface of internal pump parts 78, be fixed with first magnet 80, so that first magnet 80 is relative with second magnet 82 on the outer circumferential face that is fixed on driving component 84.Rotor can is not set in this embodiment, and replaces the shaft seal 86 on the longitudinal end that is arranged on internal pump parts 78, this shaft seal contacts with the surface 88 of pump case.Shaft seal is flexible, with the axial motion of compensation internal pump parts 78.This embodiment's a advantage is that fluid does not enter this internal pump parts 78.Can there be the dead angle when therefore, cleaning this pump.In addition, because magnet 80,82 contacts with fluid, therefore need not to encapsulate magnet 80,82 unlike previous embodiment.
In aforesaid all embodiments, form the parts of rotor, comprise external pump parts 4 among Fig. 1, the internal pump parts 2 among Fig. 2 ', the external pump parts 4 among Fig. 3 ", internal pump parts 2 in Fig. 4 " ', the external pump parts 4 among Fig. 6 ", internal pump parts 42, the internal pump parts 66 among Fig. 9 and the internal pump parts 78 among Figure 10 among Fig. 7, be not provided with the thrust supporting.As previously mentioned, in all embodiments, rotor can move vertically, and can only locate with respect to the stator that is formed by other pumping parts or member by acting on this epitrochanterian pressure balance.In all embodiments, the outflow pressure that is produced by pump is used for the internal pump parts and the external pump parts of taper are pressed together, so that these internal pump parts remain in these external pump parts.
In addition, need be understood that, can utilize according to Fig. 1,2,3,4,6, each embodiment of 9 and 10 to make up and similarly many group pumps of the pump-unit shown in Fig. 7 or multistage pumps.
In addition, in all embodiments, for each pump group or pump stage of being made up of rotary component and fixed component, can use a row or multi-row magnet, the quantity of every row's magnet is preferably four or more.
Preferably, rotary component and driver part have the magnet of equal number all the time.Magnet both can be fixed on the yoke shape spare shown in Figure 10, also can directly be fixed on the rotary component, and for example shown in Fig. 1, wherein magnet 10 directly is fixed on the external pump parts 4.
Preferably, the encapsulation magnet, to avoid magnet to be subjected to treating the influence of the fluid of pumping, for example, because described magnet ferromagnet normally, so need avoid these magnets to get rusty or corrode.Only in according to the embodiment of Figure 10 not needs encapsulate magnet as previously mentioned.
In addition, for example shown in Figure 10, can have small axial displacement d between internal magnets 82 and the external magnets 80.Because magnet 80 and 82 has the trend of alignment, therefore, in the embodiment shown in fig. 10, internal pump parts 78 are pushed into external pump parts 76 by axial magnetic force.Like this, when pumping pressure mentioned above acted on the internal pump parts 78, internal pump parts 78 also can remain in the external pump parts 76.As shown in Figure 10, by magnet 80 and 82 this side-play amount d in the vertical, can during the quitting work of pump, obtain little closing force.In addition, this axial magnetic force also can be used for partly compensating or offset the axial force that pumping pressure produced by in the pump chamber between internal pump parts 78 and the external pump parts 76.
Selectively, magnet 80 and 82 can be along opposite direction displacement, internal magnets 82 is set to than external magnets 80 more close shaft seals 86.In this was provided with, magnet 80 and 82 had the trend of alignment equally, thereby rotatable parts (being internal pump parts 78) are pushed away fixed component (being external pump parts 76).Thus, when not having pumping pressure in the pumping system, still can open pumping installations.
Even in all embodiments, the geometrical shape of internal pump parts and external pump parts can be fully different, and still, if flow must be constant, then the product of the degree of eccentricity and diameter must keep constant.
Be applicable to that all embodiments' material, the material that especially is applicable to the internal pump parts of pump and external pump parts can be potteries (aluminium oxide, silicon carbide, silicon nitride) for example.Under the situation of using metallic material, can use materials such as hot compress coating (thermal spread coating), hard chromium, stainless steel.In addition, preferably can also use plastics, for example polymer (thermoplastic resin or contain the resin of filler), rubber or fluid silicone rubber.
Reference numerals list:
2,2 ', 2 ", 2 " ' internal pump parts
4,4 ', 4 ", 4 " ' outside pump parts
6,6 ' chamber
8,8 ' pump case
10,10 ', 10 ", 10 " ' first magnet
12,12 ' the second magnets
14,14 ' driving member
16,16 ', 16 ", 16 " ' rotor housing
18,18 ' entrance
20 spaces
22,22 ' outlet
24 pump chambers
26 passages
28 inlets
30 outlets
32,34,36,38 lines
40 Rotor cans
42 internal pump parts
44 external pump parts
46 Rotor cans
48 driving component
50 first magnets
52 second magnets
54 inlets
56 outlets
58 eccentric cones
60,62 magnets
63 points without acceptance of persons
64 external pump parts
66 internal pump parts
68 first magnets
70 second magnets
72 driving component
74 Rotor cans
76 external pump parts
78 internal pump parts
80 first magnets
82 second magnets
84 driving component
86 shaft seals
88 surfaces
A axial force direction
The displacement of d magnet axial
The c distance
Claims (12)
1. a screw pump has: at least one external pump parts (4; 44; 76); And at least one internal pump parts (2; 42; 78), described internal pump parts are arranged on described external pump parts (4; 44; 76) inside, wherein said internal pump parts (2; 42; 78) and described external pump parts (4; 44; 76) in one of at least as rotor and by field drives, it is characterized in that described external pump parts (4; 44; 76) inside and described internal pump parts (2; 42; 78) tapered, this rotor can move vertically, and does not comprise the thrust supporting.
2. screw pump according to claim 1 is characterized in that, by compensating at least in part because described internal pump parts (2 along the lip-deep fluid outflow pressure of axial action at this rotor; 42; 78) and described external pump parts (4; 44; 76) hydrodynamic pressure in the pump chamber between and act on this epitrochanterian axial force.
3. screw pump according to claim 2 is characterized in that, by compensating fully because described internal pump parts (2 along the lip-deep fluid outflow pressure of axial action at this rotor; 42; 78) and described external pump parts (4; 44; 76) hydrodynamic pressure in the pump chamber between and act on this epitrochanterian axial force.
4. screw pump according to claim 2 is characterized in that, this fluid outflow pressure is along with described external pump parts (4; 44; 76) and described internal pump parts (2; 42; 78) directive effect that is pressed together is in the surface of this rotor.
5. screw pump according to claim 1 is characterized in that, is fixed with at least one first magnet (10 on this rotor; 50; 80); And in revolvable driving component (14; 48; 84) be fixed with at least one and interactional second magnet (12 of described first magnet on; 52; 82).
6. screw pump according to claim 5 is characterized in that, in described rotor and described driving component (14; 48) be provided with Rotor can (16 between; 40).
7. screw pump according to claim 5 is characterized in that, described first magnet (10; 50; 80) and/or described second magnet (12; 52; 82) be permanent magnet.
8. screw pump according to claim 5, it is characterized in that, the degree of eccentricity of the motion of described internal pump parts and described external pump parts reducing linearly from the thinner end of pump to pump than butt end, along the longitudinal 2 observation of this pump, described first magnet and described second magnet (62; 68,70) be minimum position near the degree of eccentricity between described internal pump parts (66) and the described external pump parts (64).
9. screw pump according to claim 8 is characterized in that, the longitudinal axis of the longitudinal axis of described internal pump parts and described external pump parts is that zero place, point of intersection intersects described first magnet and described second magnet (62 in the degree of eccentricity; 68,70) be set near described point of intersection.
10. according to the described screw pump of aforementioned each claim, it is characterized in that the magnetic field that drives this rotor also produces axial force except producing rotating force, this responsive to axial force is between described internal pump parts (78) and described external pump parts (76).
11. screw pump according to claim 10, it is characterized in that the axial force that is produced by described magnetic field is by being fixed on this epitrochanterian at least one first magnet (80) and being fixed on the axial dipole field of at least one second magnet (82) on the revolvable driving component (84) and producing.
12. screw pump according to claim 10, it is characterized in that, the inside of described external pump parts (76) and described internal pump parts (78) are tapered, and the axial force that is produced by described magnetic field is towards the direction that described internal pump parts (78) and described external pump parts (76) are pressed together, perhaps towards the direction that forces described internal pump parts (78) and described external pump parts (76) to separate.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DKPA200600897 | 2006-06-30 | ||
| DKPA200600897 | 2006-06-30 | ||
| PCT/EP2007/005788 WO2008000506A1 (en) | 2006-06-30 | 2007-06-29 | Moineau type pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101484703A CN101484703A (en) | 2009-07-15 |
| CN101484703B true CN101484703B (en) | 2011-10-19 |
Family
ID=38520621
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007800249440A Active CN101484703B (en) | 2006-06-30 | 2007-06-29 | Moineau type pump |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2035709B1 (en) |
| CN (1) | CN101484703B (en) |
| PL (1) | PL2035709T3 (en) |
| WO (1) | WO2008000506A1 (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7553139B2 (en) | 2006-10-06 | 2009-06-30 | Moyno, Inc. | Progressing cavity pump with wobble stator and magnetic drive |
| DE102008039973A1 (en) * | 2008-08-27 | 2010-03-04 | Wmf Württembergische Metallwarenfabrik Ag | Cavity Pump |
| DE102010043391A1 (en) * | 2010-11-04 | 2012-05-10 | Robert Bosch Gmbh | feed pump |
| US8905728B2 (en) * | 2011-12-30 | 2014-12-09 | Peopleflo Manufacturing, Inc. | Rotodynamic pump with permanent magnet coupling inside the impeller |
| US8905729B2 (en) | 2011-12-30 | 2014-12-09 | Peopleflo Manufacturing, Inc. | Rotodynamic pump with electro-magnet coupling inside the impeller |
| CA2940158C (en) | 2014-02-18 | 2023-01-17 | Vert Rotors Uk Limited | Rotary positive-displacement machine |
| JP5802914B1 (en) | 2014-11-14 | 2015-11-04 | 兵神装備株式会社 | Fluid transfer device |
| US10174973B2 (en) | 2015-08-27 | 2019-01-08 | Vert Rotors Uk Limited | Miniature low-vibration active cooling system with conical rotary compressor |
| US9776739B2 (en) | 2015-08-27 | 2017-10-03 | Vert Rotors Uk Limited | Miniature low-vibration active cooling system with conical rotary compressor |
| BE1025570B1 (en) * | 2017-09-21 | 2019-04-17 | Atlas Copco Airpower Naamloze Vennootschap | Cylindrical symmetrical volumetric machine |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| USRE21374E (en) * | 1940-02-27 | Gear mechanism | ||
| GB1583582A (en) * | 1976-07-21 | 1981-01-28 | Melchior M T | Rotary liquid pump in particular for plastermixing apparatus |
| CN1030967A (en) * | 1987-07-31 | 1989-02-08 | 东芝有限公司 | Fluid compression engine |
| US5857842A (en) * | 1997-06-16 | 1999-01-12 | Sheehan; Kevin | Seamless pump with coaxial magnetic coupling including stator and rotor |
| US6361292B1 (en) * | 2000-04-12 | 2002-03-26 | Sheldon S. L. Chang | Linear flow blood pump |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ATE385289T1 (en) * | 1997-10-24 | 2008-02-15 | John Leishman Sneddon | PUMPING DEVICE |
| SE9803894D0 (en) * | 1998-11-12 | 1998-11-12 | Volvo Lastvagnar Ab | Rotary displacement pump |
-
2007
- 2007-06-29 EP EP07764955.6A patent/EP2035709B1/en active Active
- 2007-06-29 CN CN2007800249440A patent/CN101484703B/en active Active
- 2007-06-29 PL PL07764955.6T patent/PL2035709T3/en unknown
- 2007-06-29 WO PCT/EP2007/005788 patent/WO2008000506A1/en active Application Filing
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| USRE21374E (en) * | 1940-02-27 | Gear mechanism | ||
| GB1583582A (en) * | 1976-07-21 | 1981-01-28 | Melchior M T | Rotary liquid pump in particular for plastermixing apparatus |
| CN1030967A (en) * | 1987-07-31 | 1989-02-08 | 东芝有限公司 | Fluid compression engine |
| US5857842A (en) * | 1997-06-16 | 1999-01-12 | Sheehan; Kevin | Seamless pump with coaxial magnetic coupling including stator and rotor |
| US6361292B1 (en) * | 2000-04-12 | 2002-03-26 | Sheldon S. L. Chang | Linear flow blood pump |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2035709A1 (en) | 2009-03-18 |
| EP2035709B1 (en) | 2016-05-25 |
| PL2035709T3 (en) | 2016-11-30 |
| CN101484703A (en) | 2009-07-15 |
| WO2008000506A1 (en) | 2008-01-03 |
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