CN109072904A - Eccentrie helical totorpump - Google Patents
Eccentrie helical totorpump Download PDFInfo
- Publication number
- CN109072904A CN109072904A CN201780025644.8A CN201780025644A CN109072904A CN 109072904 A CN109072904 A CN 109072904A CN 201780025644 A CN201780025644 A CN 201780025644A CN 109072904 A CN109072904 A CN 109072904A
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- China
- Prior art keywords
- driving wheel
- eccentrie helical
- pump
- helical totorpump
- rotor
- 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.)
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Classifications
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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
- F04C15/0057—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
- F04C15/0065—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
Abstract
The present invention relates to a kind of eccentrie helical totorpump (100), it is with pump rotor (107) and pump stator (109), wherein, pump stator (109) limits hollow cavity, at least part of pump rotor (107) is revolvably arranged in the hollow cavity, and pump rotor (107) is configured to through driving wheel (103,203) rotation is with trandfer fluid, wherein, pump rotor (107) is eccentrically mounted on driving wheel (103,203).
Description
Technical field
The present invention relates to a kind of eccentrie helical totorpump, particularly for household appliance, such as washing machine dosing system it is inclined
Heart screw pump.
Background technique
Focused in household appliance, particularly washing machine simple structure and it is low-cost for fluid, especially
It is the proportioning pump for liquid detergent, so that the part as dosing system uses in household appliance.It is known herein
Following dosing systems, the dosing system have the proportioning pump in different variants, for example in gear pump, peristaltic pump or piston
The positive displacement pump of pump form.
Same known so-called eccentrie helical totorpump.It is for example well known that by publication DE 10212184A1, eccentric screw
Use is pumped in commercial laundry machine, so as to the unguinosus detergent concentrate of container transport from commercial laundry machine.
Because eccentrie helical totorpump only has a unique motion parts in principle, the eccentric screw is cost phase
To cheap and robust and be therefore highly suitable in principle especially as proportioning pump using in household appliance.
However the simplicity of eccentrie helical totorpump is using relative complex driving device as prerequisite, because eccentrie helical totorpump must be realized
The two dimensional motion of rotor, the two dimensional motion are reversed on cylindrical outer cover with identical frequency by the rotation and armature spindle of rotor
It rotates and is superimposed to realize.The driving of well known eccentrie helical totorpump is not suitable at all due to its complexity and cost related to this
It is used in household appliance, particularly washing machine in the part as proportioning pump.
Summary of the invention
The object of the present invention is to provide the eccentric screws with simple structure and low-cost drive system
Pump, wherein eccentrie helical totorpump (not considering drive system) has the unique motion parts of only one for trandfer fluid, and
And the drive system is adapted to carry out the two dimensional motion of the rotor of eccentrie helical totorpump.
The task is solved by having according to the theme of the feature of independent claims.Advantageous embodiment party of the invention
Formula is the content of attached drawing, specification and dependent claims.
According to the first aspect of the invention, which solves by a kind of eccentrie helical totorpump, the eccentrie helical totorpump tool
There are pump rotor and pump stator, wherein pump stator limits hollow cavity, and at least part of pump rotor is revolvably arranged in the sky
In the chambers of the heart, and pump rotor is configured to rotate by driving wheel with trandfer fluid, wherein pump rotor is eccentrically mounted in driving wheel
On.Thus the eccentrie helical totorpump with the driving device of simple structure is provided, the driving device is configured in eccentric screw
The complicated two dimensional motion of the needs of pump rotor is realized in pump.
According to a preferred embodiment, eccentrie helical totorpump is configured to 2:1 hypocycloid-eccentrie helical totorpump, wherein described
2:1 hypocycloid is determined as follows, with radius R first circle do not slip with radius 2R second circle inside
Upper rolling.
According to an other preferred embodiment, pump rotor is eccentrically mounted on driving wheel, so that pump rotor
Longitudinal axis relative to driving wheel center with spacing R extension.
According to an other preferred embodiment, driving wheel is gear, and eccentrie helical totorpump further includes driving spiral shell
Bar, the driving screw configuration is for driving the driving wheel.
According to an other preferred embodiment, driving wheel has circular periphery.
According to an other preferred embodiment, driving wheel is the crown gear with tooth or cylindrical pin.
According to an other preferred embodiment, driving wheel is bevel gear.
According to an other preferred embodiment, driving wheel includes the teeth portion of interior rounding of angle formula.
According to an other preferred embodiment, driving wheel has the periphery of kidney shape, and eccentrie helical totorpump also wraps
The driving wheel of motor-side is included, the driving wheel of the motor-side is configured to drive the driving wheel.
According to an other preferred embodiment, pump rotor and driving wheel are integrally constructed.
According to an other preferred embodiment, pump stator includes bearing, and the bearing construction is for supportedly connecing
Receive driving wheel and/or pump rotor.
According to an other preferred embodiment, pump stator limits the outlet for conveyed fluid to be discharged.
According to an other preferred embodiment, pump stator includes row's leak.
According to an other preferred embodiment, pump rotor and pump stator have corresponding shape, corresponding
Shape determines the periodicity of the longitudinal axis along pump rotor, wherein the length of pump rotor and pump stator corresponds to fixed along pump
At least one period of the longitudinal axis of son.
A kind of household appliance, particularly washing machine are provided according to the second aspect of the invention, with according to the present invention
The eccentrie helical totorpump of first aspect.
Detailed description of the invention
In attached drawing:
Fig. 1 shows the schematic diagram for illustrating the kinematic principle of eccentrie helical totorpump according to one embodiment,
Fig. 2 shows the kinematics models for the movement for illustrating the pump rotor of eccentrie helical totorpump according to one embodiment
Schematic diagram,
Fig. 3 shows eccentrie helical totorpump according to one embodiment, kinematics model based on Fig. 2 driving device
Schematic diagram,
Fig. 4 shows the schematic diagram for illustrating the motion process in the driving device of Fig. 3,
Fig. 5 shows the pump stator of eccentrie helical totorpump according to one embodiment and the cross-sectional view of pump rotor,
Fig. 6 shows the perspective view of eccentrie helical totorpump according to one embodiment,
Fig. 7 shows the top view of the eccentrie helical totorpump of Fig. 6,
Fig. 8 shows the longitudinal section of the eccentrie helical totorpump of Fig. 6,
Fig. 9 shows the perspective, cut-away view of the rotor of the eccentrie helical totorpump of Fig. 6,
Figure 10 shows the schematic diagram of the driving device of eccentrie helical totorpump according to one embodiment.
Specific embodiment
Fig. 1 illustrates kinematic principle of the rotor 107 relative to stator 109, such as the kinematic principle according to following detailed
It carefully, particularly in the eccentrie helical totorpump 100 of the embodiment of the present invention in conjunction with described in Fig. 6 to 9 realizes, the eccentrie helical totorpump
It is 2:1 hypocycloid-eccentrie helical totorpump.In the eccentrie helical totorpump 100 so constructed, the movement of rotor 107 can be by having
The first of radius R justifies 10 to describe, and first circle does not roll with not slipping in the second circle 20, and second circle is the first circle 10
Twice big (there is radius 2R；Therefore ratio is 2:1).Here, the eccentricity of the movement of rotor 107 is corresponding to the rolled
The radius R of one circle 10.
Central point (or the rotor in the top view of Fig. 1 to 3 of the central point of the first circle 10 rolled, i.e. rotor 107
The intersection point of 107 longitudinal axis) draw an other circle in its movement, the other circle it is concentric with the second circle 20 and
By showing one section by curved arrow in Fig. 1.The other diameter of a circle drawn by the first circle 10 is it may be said that corresponding to inclined
" piston stroke " of heart screw pump 100, as being in conjunction with as further implementing Fig. 5 particularly below.
The kinematic principle of eccentrie helical totorpump 100 illustrated in fig. 1 can be real by kinematics model shown in Figure 2
It is existing.The kinematics model is made of connecting rod 101, and the connecting rod has fixed length 2R, and at two ends of the connecting rod
Each a sliding members 102a, 102b are hingedly connect with connecting rod 101 in portion.First sliding members 102a is herein along y-axis quilt
Guidance, and the second sliding members 102b is guided along the x-axis perpendicular to y-axis of cartesian coordinate system.Shown in Fig. 2
In kinematics model, connecting rod 101 has the length of 2R corresponding to the diameter of the first circle 10 of Fig. 1.Similar to the first of Fig. 1
Justify 10, the central point of connecting rod 101 is implemented with radius R around the circus movement of the origin of coordinate system, and the origin and second justifies 20
Central point is overlapped.During the circus movement of the central point of connecting rod 101, the first and second sliding members 102a, 102b are real respectively
Amplitude 2R is imposed along the vibration of the straight line of y-axis or x-axis, wherein the vibration of the first sliding members 102a is relative to the second sliding
The vibration of element 102b carries out with being staggered 90 ° of phases.This is for example it is meant that in the kinematics model of Fig. 2, when the second sliding member
When part 102b is in its peak excursion, then the first sliding members 102a is on the origin of coordinate system, and vice versa.
According to one embodiment, eccentrie helical totorpump 100 constructs in this way, so that the connecting rod 101 of the kinematics model of Fig. 2
Central point be overlapped with the longitudinal axis (the definitely intersection point of longitudinal axis) of the rotor 107 of eccentrie helical totorpump 100.As by scheming
5 it can be seen that as, show according to the transversal of the pump stator 109 of the eccentrie helical totorpump 100 of the embodiment and pump rotor 107
Face figure, the circle in stator cross section for being given at long hole shape in the cross section of each longitudinal axis perpendicular to pump rotor 107
The rotor cross-section of shape.The cross-sectional view in following height of the longitudinal axis along rotor 107, the height is shown here in Fig. 5
For degree corresponding to by the guidance to rotor 107 in the x direction of stator 109, which is similar to the second sliding members to Fig. 2
The guidance of 102b.Correspondingly, it is right by stator 109 to limit respectively in the other height of the longitudinal axis along rotor 107
The guidance of rotor 107, the guidance is for example perpendicular to guidance extension, the guidance i.e. with the first sliding members 102a to Fig. 1 of Fig. 5
The guidance of similar guidance in y-direction or the guidance relative to Fig. 5 at other angles.
Three point P1, P2 and P3 marked of eccentrie helical totorpump 100 according to one embodiment are shown in FIG. 5.
Point P1 is the central point of pump stator 109.Each cross section of stator 109 has the point P1 as system centre.
Point P3 with pump stator 109 central point, i.e. the spacing 2R of point P1, more precisely the phase shown in, i.e. in institute
It is located in x-axis in the height shown.The ginseng of the stator 109 for the cross section that this point P3 on rotor 107 is illustrated herein
Examine be middle implementation along x-axis with the vibration of amplitude 2R, i.e. " piston stroke " of 4R in total.Point P3 corresponds to the circle of rotor cross-section
The heart.According to one embodiment, the coordinate of the center of circle of driving wheel 103 is on this point P3, that is to say, that driving wheel axis extends logical
Cross this point.Therefore, driving wheel 103 implements vibration in the x direction in the referential of stator 109.
In illustratively positioning in Fig. 5, rotor axis extends through point P2, which is located between stator center point P1
At R.When rotor 107 rotates, this point P2 is in the referential of stator 109 around stator center point P1 with radius R
Circle on move.In the referential of rotor 107, point P2 around the center of circle of rotor cross-section, i.e. around point P3 with radius R
Circle on move.In an embodiment of eccentrie helical totorpump 100, below in association with pivot pin described in Fig. 7 in this point
It is mounted on P2 on driving wheel 103, the driving wheel 103 is for generating the axial force being applied on rotor 107.In this installation
In, pivot pin implements circus movement (the movement circle that pivot pin central point is shown in FIG. 7) in the referential of stator 109.
The point P1, P2 and P3 marked in Fig. 5 correspond in Fig. 2 central point (P1) the i.e. stator center point of great circle 20,
What the central point (P2) of connecting rod 101 rotated on the circle with radius R i.e. in the referential of stator 109 around stator center point
The central point of hinge joint (P3) the i.e. rotor cross-section of rotor axis and the second sliding members 102b vibrated along x-axis, so
And Fig. 2 is corresponding to the other orientation of rotor 107 (i.e. corresponding to the orientation of the angle [alpha] with about 60 °).
As described below, embodiment according to the present invention of the invention have driving mechanism, the driving mechanism by
The rotation at center generates rotor 107 and in Fig. 1 and by the movement shown in the kinematics model of Fig. 2 or is transmitted to rotor 107
On.Fig. 3 shows the kinematics model of Fig. 2 in the frame of the driving mechanism of eccentrie helical totorpump 100 according to one embodiment
Implementation.Driving mechanism includes the circular driving wheel and cylindrical driving screw rod 105 in 103 form of gear, described
Drive screw configuration be in known manner with the such phase interaction of the tooth (furthermore illustrative tooth 103a) of method and gear 103
With so that the rotary motion for the driving screw rod 105 for example realized by drive motor causes gear 103 to rotate.
As can be seen according to Fig. 3, placement of the circular gear 103 at following centers Dian Chu leads to gear
103 implement the vibration with the amplitude of 2R in y-direction, kinematics model of this in Fig. 2 when rotating around its center simultaneously
In corresponding to the first sliding members 102a position (that is, the center of gear 103 is located at the hinge of the first sliding members 102a
On contact), wherein gear 103 is not moved in the x direction.Those skilled in the art can be seen that and be shown in FIG. 3
Compare, the length of connecting rod 101 is more much smaller than the radius of driving wheel 103 in embodiments of the present invention.In addition, Fig. 3 is shown
Spacing m between the longitudinal axis and y-axis of driving screw rod 105 with a semidiameter d/2.In one embodiment, eccentric
Screw pump 100 can have following sizes: the pitch circle diameter d of driving screw rod 105 is 8.8mm, the gear section of gear 103
Circular diameter is 27.2mm, and radius R is 1mm, this corresponds to " piston stroke " of 4mm, distance between axles m=(27.2mm+8.8mm)/2=
18mm。
In the embodiment of eccentrie helical totorpump 100, thus driving wheel 103 is centrally fixed at following points, which exists
The position of the first sliding members 102a is corresponded in the kinematics model of Fig. 2, and pump rotor 107 connects with driving wheel 103 in this way
It connects, so that connecting rod 101 is overlapped with the diameter of pump rotor 107 or the longitudinal axis of the central point of connecting rod 101 and pump rotor 107
Line is overlapped.In other words: pump rotor is eccentrically mounted on the driving wheel with the spacing R at the center with driving wheel 103.At this
In configuration, rotation of the gear 103 around its center is directly delivered on the pump rotor 107 with gear 103, and gear 103 is implemented
Vibration in y-direction, the center of the gear are overlapped with the first sliding members 102a.
As above-cited, be parallel to y-axis with the cylindrical driving screw rod 105 of suitable spacing m arrangement as
Like that by rotating the rotation to realize gear 103 around its axis in the case where traditional screw drive, and gear 103 is same
When longitudinally to driving screw rod 105 moved back and forth in a manner of the vibration with amplitude 2R.This is shown in FIG. 4, this illustrates root
Driving spiral shell according to an embodiment in one of gear 103 complete revolution middle gear 103 relative to eccentrie helical totorpump 100
The relative position of bar 105.Connecting rod and sliding members be not in the view of figure 4 be truly present in eccentrie helical totorpump 100, and
It is to be merely illustrative the kinematics model realized by Fig. 2.For example, the movement of the pump rotor 107 of eccentrie helical totorpump 100 can be set
Want for circus movement, the circus movement diameter is determined as above-cited by connecting rod.The different views of Fig. 4
Show again, in a complete revolution of gear 103, the center of the gear with only in y-direction, i.e. in vertical direction
On vibration move back and forth, however without movement in the x direction, i.e. in the horizontal direction, that is to say, that especially gear
Spacing between 103 center and the longitudinal axis for driving screw rod 105 does not change.
Fig. 6 to 9 shows different views, the i.e. perspective view of an embodiment of eccentrie helical totorpump 100, top view, indulges
To sectional view and perspective, cut-away view.In the embodiment shown in Fig. 6 to 9 of eccentrie helical totorpump 100, driving wheel 103 is constructed
For the spur gear 103 with helical teeth, such as tooth 103a, which is driven by the driving screw rod 105 for being configured to cylindrical screw.
The installation eccentric on driving wheel 103 of pump rotor 107 can for example be found out by the top view of Fig. 7.Herein it is noted that
, the central point of the pivot pin projected upwards on gear 103 is not following point of rotation, and gear 103 is (inclined around the point of rotation
Heart) rotation, because as implemented circus movement above in conjunction with pivot pin as described in Fig. 5, and driving wheel 103 is around its geometry
Center rotation.In one embodiment, pivot pin can be used for that pump rotor 107 is axially pressed onto pump stator 109 by pressing plate
In.Here, pivot pin is slided on pressing plate with movement above-mentioned.The longitudinal section of eccentrie helical totorpump 100 shown in fig. 8 of dissecting illustrates
Pump rotor 107 in following orientations out, in the orientation, the maximum eccentricity of driving wheel 103 is located exactly at view plane
In.
As for example as can be seen that longitudinal section shown in fig. 8, pump rotor 107 and driving wheel 103 are integrally
Construction.In addition, the part that the section (top section of pump stator 109 in fig. 8) of pump stator 109 is for example configured to shell is used as
For driving wheel 103 and/or the bearing of pump rotor 107, the bearing realizes the vibration motion above-mentioned of driving wheel 103.Pump is fixed
Son 109 further includes for the outlet 113 of conveyed fluid and row's leak 111 to be discharged.Arranging leak 111 will be by bias for energy
Fluid discharge that screw pump 100 conveys, being overflowed from the sealing station of 103 lower section of driving wheel.
Not only the shape of pump rotor 107 but also the corresponding shape of pump stator 109 have the longitudinal axis along pump rotor 107
The periodicity of line, wherein rotor cycle is big usually as the half of sub-period.Such as pump rotor 107 and pump stator 109
Length in the embodiment shown in Fig. 6 to 9 of eccentrie helical totorpump 100 corresponding to along pump rotor 107 longitudinal axis
About 3.8 rotor cycles of line, 3.8 rotor cycles are equal to 1.9 sub-periods.According to eccentrie helical totorpump 100
The length of embodiment, pump rotor 107 and pump stator 109 should be corresponding at least one of the longitudinal axis along pump stator 109
A period, i.e. sub-period.
For the eccentrie helical totorpump 100 as household appliance, particularly the dosage of washing machine shown in Fig. 6 to Fig. 9
The typical specification of embodiment be following specifications being partly mentioned above: eccentrie helical totorpump 100 it is inclined
The heart is 1 away from (i.e. the spacing of the central point of the longitudinal axis of pump rotor 107 and driving wheel 103) R=2mm, the revolving speed of pump rotor 107
Revolutions per second.It realizes total movement in practice by described value, in total movement, for example turns as caused by the vibration of gear 103
The fluctuation of square or rotor speed is relatively small and can take into account running about peace and quiet without practical limitation.
In the driving screw rod 105 for being configured to cylindrical screw, embodiment according to the present invention can be used gear 103 and
The other shapes of its teeth portion, driving wheel 103 can also for example be configured with the crown gear of tooth or cylindrical pin, particularly in balls
The bevel gear of face type or Hindley worm gear.In the case where 103 spherical gear of driving wheel, such as it is configured to the driving of spur gear
The teeth portion of wheel 103 can form to interior rounding of angle formula.Spherical surface variant also can be used on other gear shapes.
According to embodiment of the present invention, substituting cylindrical driving screw rod for example also can be used spur gear for horse
Up to the driving of side.This embodiment is shown in FIG. 10, the embodiment show circular motor-side driving wheel 205 and partially
The schematical top view of the driving wheel 203 of the pump rotor 107 of heart screw pump 100.In order to pass through the driving of circular motor-side
Wheel 205 realizes the movement above-mentioned of the driving wheel 203 of pump rotor 107, i.e. with the rotation of reversal of vibrations, the drive of pump rotor 107
The periphery of driving wheel 203 substantially constructs to kidney shape.This causes, the two driving wheels 203,205 substitute on straight line (as preceding
In the embodiment with circular driving wheel 103 and driving screw rod 105 stated like that) and along the driving wheel for surrounding motor-side
The circular motion of 205 central point.
As front partly illustrates, eccentrie helical totorpump 100 according to the present invention, which also has, to be had the advantage that.
Only one is only with (not considering to drive screw rod 105 or driving wheel 205) for eccentrie helical totorpump 100 according to the present invention
One moving component can also be constructed integrally together with the pump rotor 107 of driving wheel 103, the driving wheel and pump rotor.?
Eccentrie helical totorpump 100 according to the present invention does not need additional component for compensating eccentric motion.That is, herein relating to skill
The solution that can be simply implemented in art, especially unique moving component, the driving wheel for combining eccentrie helical totorpump 100
103 pump rotor 107 can be constructed rigidly (non-resiliently).
Eccentrie helical totorpump 100 according to the present invention can construct very compactly, because can cancel in traditional pump
The required eccentricity compensation for example in the form of universal shaft, the universal shaft usually require big structure length.In given structure
In space, the structure length saved in eccentrie helical totorpump 100 according to the present invention can be implemented as the additional length of pump chamber.
Because the length of contact line of the length of pump chamber usually between the rotor 107 of eccentrie helical totorpump 100 and stator 109 is proportional,
The length of the pump chamber is also referred to as sealing configuration, so eccentrie helical totorpump according to the present invention 100 can correspondingly more fluid
Hermetically construction and thus more accurately dosage, that is to say, that actual volume flow preferably corresponds to nominal volume stream
It measures (minimum slippage generally can not be avoided in practice).On the contrary, passing through the bigger of pump chamber under predetermined dosing accuracy
Length, i.e. bigger sealing configuration can be used between the rotor 107 and stator 109 of eccentrie helical totorpump 100 according to the present invention
Bigger gap size, this leads to the precision for the needs for reducing component under given dosing accuracy and thus eventually leads to
Reduce the cost of eccentrie helical totorpump 100.
In eccentrie helical totorpump 100 according to the present invention, with flexible coupling device, such as spring leaf coupling device
Or the eccentrie helical totorpump of the universal shaft with elastic joint differently only generates small additional bearing load, because not generating
Cross force.Therefore, it is tired to be not subjected to the component as caused by alternating bending load for the component of eccentrie helical totorpump 100 according to the present invention
Labor.
As previously mentioned, the combination being made of the rotor 107 of eccentrie helical totorpump 100 according to the present invention and stator 109 is quasi-
Really realize movement described in the kinematics model of front according to fig. 2.Because driving wheel 103 carries out the movement herein,
Additional bearing is not needed in eccentrie helical totorpump 100 according to the present invention.In eccentrie helical totorpump 100 according to the present invention,
This region is solely for sealing in the fluid guidance correspondingly selected.
In the embodiment shown in Fig. 6 to 9, driving wheel 103 can in the form of gear in arbitrary phase, i.e.
It is connect in arbitrary angle orientation with driving screw rod 105.In assembly thus without pay attention to by driving wheel 103 relative to drive
Dynamic screw rod 105 is positioned with special angle, this simplify significantly assembly and with must phase accurately assemble the pump of driving wheel
Structure, which is compared, reduces assembly cost.
Described in all combinations each embodiment of the invention and shown in feature can be with different combination settings
In theme according to the present invention, to realize its advantageous effect simultaneously.
Reference signs list
10 first circles
20 second circles
100 eccentrie helical totorpumps
101 connecting rods
The first sliding members of 102a
The second sliding members of 102b
103 driving wheels
103a tooth
105 driving screw rods
107 pump rotors
109 pump stators
203 pump driving wheels
205 driving wheels.
Claims (15)
1. a kind of eccentrie helical totorpump (100), with pump rotor (107) and pump stator (109), wherein the pump stator (109)
Hollow cavity is limited, at least part of the pump rotor (107) is revolvably arranged in the hollow cavity, and the pump turns
Sub (107) are configured to rotate by driving wheel (103,203) with trandfer fluid, which is characterized in that the pump rotor (107) is eccentric
Ground is mounted on the driving wheel (103,203).
2. eccentrie helical totorpump (100) according to claim 1, which is characterized in that the eccentrie helical totorpump (100) is configured to
2:1 hypocycloid-eccentrie helical totorpump (100), wherein the 2:1 hypocycloid is determined as follows, first with radius R
Circle (10) rolls with not slipping on the inside of the second circle (20) with radius 2R.
3. eccentrie helical totorpump (100) according to claim 1 or 2, which is characterized in that the pump rotor (107) is prejudicially
It is mounted on the driving wheel (103,203), so that the longitudinal axis of the pump rotor (107) is relative to the driving wheel
The center of (103,203) is with spacing R extension.
4. eccentrie helical totorpump (100) according to any one of the preceding claims, which is characterized in that the driving wheel
It (103) is gear, and the eccentrie helical totorpump (100) further includes driving screw rod (105), the driving screw configuration is for driving
Move the driving wheel (103).
5. eccentrie helical totorpump (100) according to claim 4, which is characterized in that the driving wheel (103) has circular
Periphery.
6. eccentrie helical totorpump (100) according to any one of the preceding claims, which is characterized in that the driving wheel
It (103) is the crown gear with tooth or cylindrical pin.
7. eccentrie helical totorpump (100) according to any one of the preceding claims, which is characterized in that the driving wheel
It (103) is bevel gear.
8. eccentrie helical totorpump (100) according to claim 7, which is characterized in that the driving wheel includes interior rounding of angle formula
Teeth portion.
9. eccentrie helical totorpump (100) according to any one of claim 1 to 3, which is characterized in that the driving wheel
(203) with the periphery of kidney shape, and the eccentrie helical totorpump (100) further includes the driving wheel (205) of motor-side, the motor
The driving wheel of side is configured to drive the driving wheel (203).
10. eccentrie helical totorpump (100) according to any one of the preceding claims, which is characterized in that the pump rotor
(107) it is integrally constructed with the driving wheel (103,203).
11. eccentrie helical totorpump (100) according to any one of the preceding claims, which is characterized in that the pump stator
It (109) include bearing, the bearing construction is for supportedly receiving the driving wheel (103,203) and/or the pump rotor
(107)。
12. eccentrie helical totorpump (100) according to any one of the preceding claims, which is characterized in that the pump stator
(109) outlet for conveyed fluid to be discharged is limited.
13. eccentrie helical totorpump (100) according to any one of the preceding claims, which is characterized in that the pump stator
It (109) include row's leak.
14. eccentrie helical totorpump (100) according to any one of the preceding claims, which is characterized in that the pump rotor
(107) and the pump stator (109) has corresponding shape, and corresponding shape is determined along the pump rotor (107)
The periodicity of longitudinal axis, wherein the length of the pump rotor (107) and the pump stator (109) is corresponded to along the pump
At least one period of the longitudinal axis of stator (109).
15. a kind of household appliance, particularly washing machine, with eccentric screw according to any one of the preceding claims
It pumps (100).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102016207247.1 | 2016-04-28 | ||
| DE102016207247.1A DE102016207247A1 (en) | 2016-04-28 | 2016-04-28 | Cavity Pump |
| PCT/EP2017/058807 WO2017186497A1 (en) | 2016-04-28 | 2017-04-12 | Eccentric screw pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109072904A true CN109072904A (en) | 2018-12-21 |
| CN109072904B CN109072904B (en) | 2020-01-10 |
Family
ID=58548694
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201780025644.8A Active CN109072904B (en) | 2016-04-28 | 2017-04-12 | Eccentric screw pump |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP3449128B1 (en) |
| CN (1) | CN109072904B (en) |
| DE (1) | DE102016207247A1 (en) |
| PL (1) | PL3449128T3 (en) |
| WO (1) | WO2017186497A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111120298A (en) * | 2019-12-16 | 2020-05-08 | 徐海英 | Pump based on eccentric transmission |
Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2483370A (en) * | 1946-06-18 | 1949-09-27 | Robbins & Myers | Helical multiple pump |
| US4273521A (en) * | 1978-02-10 | 1981-06-16 | E. T. Oakes Limited | Drive arrangement |
| GB2120729A (en) * | 1982-05-21 | 1983-12-07 | Mono Pumps Ltd | Helical gear pump |
| JPS6196193A (en) * | 1984-10-17 | 1986-05-14 | Heishin Sobi Kk | Driving gear of single-shaft eccentric screw pump |
| CN2345736Y (en) * | 1998-06-11 | 1999-10-27 | 中国科学院大连化学物理研究所 | Screw pump |
| EP1400694A2 (en) * | 2002-09-20 | 2004-03-24 | Netzsch-Mohnopumpen GmbH | Moineau-type pump with spare stator |
| US20100040498A1 (en) * | 2007-03-08 | 2010-02-18 | Heishin Sobi Kabushiki Kaisha | Rotor drive mechanism, eccentric shaft sealing structure, and pump apparatus |
| US20110129375A1 (en) * | 2007-11-15 | 2011-06-02 | Spyro Kotsonis | Work extraction from downhole progressive cavity devices |
| CN202560176U (en) * | 2012-05-14 | 2012-11-28 | 大庆永磁电机制造有限公司 | Screw pump direct driving device with leaking liquid overflow system |
| CN103711691A (en) * | 2014-01-06 | 2014-04-09 | 中国石油大学(华东) | Single-screw pump capable of balancing axial force and radial force |
| CN104564655A (en) * | 2013-10-24 | 2015-04-29 | 奈赤－泵和系统有限责任公司 | Eccentric screw pump, and use of eccentric screw pump |
| CN105247213A (en) * | 2013-05-21 | 2016-01-13 | 兵神装备株式会社 | Uniaxial eccentric screw pump |
| CN205135988U (en) * | 2015-11-23 | 2016-04-06 | 重庆高研泵业有限公司 | Safe screw pump |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10212184A1 (en) | 2002-03-20 | 2003-10-09 | Ecolab Gmbh & Co Ohg | Dosing solids-containing free-flowing detergent paste concentrates to industrial washing machines uses an eccentric screw pump |
-
2016
- 2016-04-28 DE DE102016207247.1A patent/DE102016207247A1/en not_active Ceased
-
2017
- 2017-04-12 CN CN201780025644.8A patent/CN109072904B/en active Active
- 2017-04-12 PL PL17717685T patent/PL3449128T3/en unknown
- 2017-04-12 EP EP17717685.6A patent/EP3449128B1/en active Active
- 2017-04-12 WO PCT/EP2017/058807 patent/WO2017186497A1/en active Application Filing
Patent Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2483370A (en) * | 1946-06-18 | 1949-09-27 | Robbins & Myers | Helical multiple pump |
| US4273521A (en) * | 1978-02-10 | 1981-06-16 | E. T. Oakes Limited | Drive arrangement |
| GB2120729A (en) * | 1982-05-21 | 1983-12-07 | Mono Pumps Ltd | Helical gear pump |
| JPS6196193A (en) * | 1984-10-17 | 1986-05-14 | Heishin Sobi Kk | Driving gear of single-shaft eccentric screw pump |
| CN2345736Y (en) * | 1998-06-11 | 1999-10-27 | 中国科学院大连化学物理研究所 | Screw pump |
| EP1400694A2 (en) * | 2002-09-20 | 2004-03-24 | Netzsch-Mohnopumpen GmbH | Moineau-type pump with spare stator |
| US20100040498A1 (en) * | 2007-03-08 | 2010-02-18 | Heishin Sobi Kabushiki Kaisha | Rotor drive mechanism, eccentric shaft sealing structure, and pump apparatus |
| US20110129375A1 (en) * | 2007-11-15 | 2011-06-02 | Spyro Kotsonis | Work extraction from downhole progressive cavity devices |
| CN202560176U (en) * | 2012-05-14 | 2012-11-28 | 大庆永磁电机制造有限公司 | Screw pump direct driving device with leaking liquid overflow system |
| CN105247213A (en) * | 2013-05-21 | 2016-01-13 | 兵神装备株式会社 | Uniaxial eccentric screw pump |
| CN104564655A (en) * | 2013-10-24 | 2015-04-29 | 奈赤－泵和系统有限责任公司 | Eccentric screw pump, and use of eccentric screw pump |
| CN103711691A (en) * | 2014-01-06 | 2014-04-09 | 中国石油大学(华东) | Single-screw pump capable of balancing axial force and radial force |
| CN205135988U (en) * | 2015-11-23 | 2016-04-06 | 重庆高研泵业有限公司 | Safe screw pump |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111120298A (en) * | 2019-12-16 | 2020-05-08 | 徐海英 | Pump based on eccentric transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| PL3449128T3 (en) | 2022-03-28 |
| CN109072904B (en) | 2020-01-10 |
| WO2017186497A1 (en) | 2017-11-02 |
| DE102016207247A1 (en) | 2017-11-02 |
| EP3449128B1 (en) | 2021-11-17 |
| EP3449128A1 (en) | 2019-03-06 |
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