CN102597517A - Vibrating armature pump - Google Patents
Vibrating armature pump Download PDFInfo
- Publication number
- CN102597517A CN102597517A CN201080050415XA CN201080050415A CN102597517A CN 102597517 A CN102597517 A CN 102597517A CN 201080050415X A CN201080050415X A CN 201080050415XA CN 201080050415 A CN201080050415 A CN 201080050415A CN 102597517 A CN102597517 A CN 102597517A
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- China
- Prior art keywords
- pump
- piston
- fro motion
- parts
- driver part
- Prior art date
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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
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
- F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
- F04B17/046—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the fluid flowing through the moving part of the motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Electromagnetic Pumps, Or The Like (AREA)
Abstract
The invention relates to a vibrating armature pump having a pump housing, which comprises a cylinder for receiving a substantially linearly displaceable pump piston unit (10). The pump piston unit (10) comprises at least one pump element (11) for pumping the pumping fluid and a drive element (12) for driving the pump element (11). Both elements are designed separately and arranged loosely one behind the other.
Description
Technical field
The present invention relates to like the claim 1 to-and-fro motion pump with pump casing as described in the preamble, it comprises the cylinder of the pump piston unit that is used to hold basic line shifting.
Background technique
The to-and-fro motion pump is characterised in that the piston of reciprocally swinging on axis of movement, and this piston is made up of material magnetic or magnetizable at least in part, and drives through electromagnetic coil.
The piston of to-and-fro motion pump is extruded fluid, the especially water that is arranged in cylinder when being immersed in cylinder interior.When piston stretched out cylinder, cylinder was full of by fluid or water once more, can during the pump swing process, realize the circuit pump action thus.
Because this working principle need make cylinder chamber have fluid seal structure.Must guarantee this sealing in each position of piston, so the sealing surface ordinary construction is slip surface, this slip surface is also carried out the sealing function in the axial motion of piston.
This to-and-fro motion pump has for example been described in document EP 0288216B1, DE 102005048765A1 or DE 60016905T2.These to-and-fro motion pumps disclose composite piston, and this composite piston has part of being made up of ferromagnetic metallic material and the part of being made up of nonmetal non-ferromagnetic material, these partial shapes sealed with force closure interconnect so that move.For example can be through squeezing folder, ca(u)lk, rolling, clamping, extruding, bonding, welding, shrink or realize the connection of two parts through other processing mode.In this example, for example in a part, be provided with and cut, when two parts linked together, the respective bump of another part was inserted this and is hited.
But its defective is that processing is cut or carried out accordingly the connection process step and takes a lot of trouble, and is that cost is disadvantageous from economic angle therefore.
Summary of the invention
Therefore, the objective of the invention is to propose a kind of to-and-fro motion pump with pump case, it comprises cylinder, and cylinder is used to hold the pump piston unit of basic line shifting, and said to-and-fro motion pump can more advantageously be processed than existing technology economically.
The to-and-fro motion pump of above-mentioned form is realized this purpose through having the described characteristic of claim 1 characteristic.Can realize favourable expansion structure of the present invention and improvement project through the measure of enumerating in the dependent claims.
Therefore, to-and-fro motion pump according to the present invention is characterised in that said pump piston unit has at least one pump parts that independently are used for pumping pump fluid and independently is used for the driver part of driven pump parts with at least one.This means that according to the present invention, at run duration, two independently perhaps separable parts form the pump piston unit of reciprocally swinging.Therefore, these two are independently or separable pump piston assembly of elements is in operation side by side or front and back ground is provided with, do not exist between two parts, be the pump parts with driver part between (material is sealed or force closure or inseparable) be connected.
Make the connection process step or the bothersome structural adjustment that are used to be connected two parts become unnecessary by means of two parts (pump parts and driver part in other words) independently of being in operation; Therefore; Save these steps or adjustment according to the present invention, therefore saved corresponding cost.Therefore, can advantageously process especially economically according to to-and-fro motion pump of the present invention.
Confirm in surprise that it is essential for the to-and-fro motion pump suitably moves, to be not necessarily being connected of two parts (that is, independently pump parts and driver part independently).Therefore can save according to the crowded clip process of EP 0288216B1 or according to the extrusion process of DE 60016905T2, this means and saved corresponding process time.Owing to save corresponding breach or cut or similar structure, thereby realized main advantage economically compared with prior art.
According to the present invention, be in operation independently the pump parts be in operation independently driver part in an advantageous manner discretely side by side or front and back be provided with, promptly especially during the to-and-fro motion of pump piston unit.For this purpose, for example independently the pump parts and/or independently the flat contact surface of driver part be favourable.
Advantageously, these pump parts have first stop member that is used for this driver part, and this driver part has second stop member that is used for these pump parts.What realize thus is that the contact that existence is confirmed or definite surface of contact (being corresponding stop member) are realized accurate in size pump piston unit thus.For example, stop member is designed to plane surface, can be in operation thus independently or transmit between two parts that separate relatively large, mainly from the active force that is used for the driven pump parts of driver part.In addition, the active force of pump parts can be delivered to independently driver part, for example favourable reposition force or similar effect power.
Preferably, be provided with at least one first spring members so that power is loaded on pump piston unit and/or pump parts.For example construct first spring members like this: make and hinder drive movement slightly.Preferably, can pass through at least one electric driver, especially produce drive movement through electromagnetic coil.The pump motion favourable or that confirm or the drive movement of the pump parts of realizing thus being used to drive independently or separating.
Advantageously, first spring members guarantee two separation or independently parts in restricted portion, be held or link together, especially in state of rest and at pumping process or pump between moving period.
In favourable modification of the present invention; Be provided with at least one second spring members so that power is loaded on pump piston unit and/or the driver part and/or first spring members, wherein the spring force of second spring members is advantageously in the opposite direction with the spring force of first spring members.Advantageously, utilize drive unit or driver element tension or compress second spring members.
Advantageously, compression of second spring members or pumping fluid, that is, the spring travel of second spring members corresponds essentially to the pump stroke according to to-and-fro motion pump of the present invention.Second spring members can be configured to make pump piston unit or two to be in operation Returnning spring that parts (i.e. independently pump parts and independently driver part) independently reset thus.At this, the spring force of second spring members advantageously as reposition force so that the pump piston unit is resetted, advantageously carry out pumping simultaneously at reseting movement.
Advantageously, said driver part is made up of ferromagnetic material basically.The pump parts that can make at least one Electromagnetic Drive coil or like advantageously transmit pumping force or pumping energy to pump piston unit thus perhaps act on said pump parts thus.Verified, the to-and-fro motion pump of straight reciprocating motion or the driving of its pump piston unit can advantageously produce and move by means of electromagnetic coil especially economically.
Preferably, driver part basically by magnetic or magnetizable material, especially magnetic or magnetizable metal, be preferably magnetic or magnetizable special steel is formed.When using special steel as the material of driver part, advantageous particularly ground, this material generally also is rustless or non-oxidizing in the water for example at liquid medium.Thus, advantageously prolong working life according to to-and-fro motion pump of the present invention.
And also can use magnetic or magnetizable material originally like (getting rusty) steel, it for example has surface coating and correspondingly is configured to corrosion-resistant.But verified, because the vibration of to-and-fro motion or pump piston unit can grind off corresponding coating or coating etc., this causes disadvantageous wearing and tearing and possibly expose the material of corrosion.To realize about 400,000 times or multiple-pass and do not have disadvantageous damage more according to to-and-fro motion pump of the present invention.This mainly comes advantageously to realize through the material of stainless steel as driver part.
In special improvement project of the present invention, wall member is made up of plastics basically, wherein mainly considers thermoplastic and/or thermosetting plastic, especially also considers the mixture of these two kinds of plastics.Verified, corresponding plastics have good especially sliding properties and are cheap.Accurately and very effectively realize the sealing function of pump parts through favourable plastics.For example, thermoplastic can be polyoxymethylene, PEEK, Vespel or analog, and/or thermosetting plastic can be BMC or analog.These plastics resistances to chemical attack and/or cost are favourable and/or have a favourable sliding properties.
Perhaps, also can select to use the material of stainless steel as the pump parts.The major character of this material as the pump parts time is that it is a wear-resistant and corrosion resistant and anti-dry running and/or resistant to elevated temperatures.
Description of drawings
Embodiments of the invention shown in the drawings and below by means of the accompanying drawing illustrated in detail.During accompanying drawing shows:
Fig. 1 illustrates the longitudinal section according to to-and-fro motion pump of the present invention,
Fig. 2 illustrates the longitudinal section according to to-and-fro motion pump of the present invention unit, and it is arranged between two spring members.
Embodiment
Comprise the pump case 2 of two parts according to the to-and-fro motion pump 1 of Fig. 1, it is fixed on the yoke 3 of electromagnetic coil 4.
Pump case 2 comprises that the armature of tubulose holds body 6 and cylinder part 7, and armature holds body and extends in the inside of coil 4, and cylinder part leans on yoke 3 through flange 8.
Pump piston unit or pump piston 10 enter into pump case 2 the insides, and comprise pump parts or piston element 11 and driver part or magnet assembly 12.Piston element 11 is designed to tubulose and has axial hole, and is immersed in cylinder 13 the insides, and cylinder 13 is configured in the cylinder part 7.
Pump piston 10 and therefore piston element 11 be in operation and on double-head arrow A direction, carry out circuit and move axially, be i.e. pump piston double vibrations in the axial direction periodically.
On a side relative with magnet assembly 12, by means of transverse arm 16 sealing cylinders 13, transverse arm has central through bore 17.Stage clip 18 towards the piston side surface bearing on transverse arm 16, stage clip 18 with seal 19 roof pressures in the outlet of tubular piston parts 11.
On the side with transverse arm 16 on piston 11 opposites, cylinder part 7 tubulose ground prolong and on its outer end, form the connection of the outlet side of to-and-fro motion pump 1 and take over 20.Support ring 21 linings are gone into the stop member of taking over 20 the insides and being formed for another stage clip 22 to connecting, and this stage clip on transverse arm 16, seals through hole 17 with seal 23 roof pressures simultaneously.
Pump piston 10 has the cross section expansion of two-stage in magnet assembly 12 directions from piston element 11 beginnings.Therefore, the piston element 11 that has a little cross section is connecting intermediate member 24 with middle iso-cross-section and the magnet assembly 12 with big cross section.In intermediate member 24, be formed with cross-drilled hole 25, an end of cross-drilled hole 25 is connected with the axial hole 26 of piston element 11, and the other end is connected with the axial hole 27 of magnet assembly 12.
On a relative side, stage clip 28 is bearing on the backstop dish 29, and backstop dish 29 is inserted between the cylinder part 7 that armature holds body 6 and pump case 2.
On a side relative with piston element 11, magnet assembly 12 has space 32, forms galianconism 15 thus.Second stage clip 31 is bearing on the space 32, wherein stage clip 31 radially fixing or centering by means of galianconism 15.
On a side relative with stage clip 31, stage clip 31 leans at armature and holds on the step 33 of body 6.Armature holds that body 6 comprises stop member 30 and prolongs the connecting tube 34 that comes out and be formed for connecting supplying tube in its end from coil 4.
The operation of to-and-fro motion pump 1 is following.
Through with alternating voltage, or advantageously with the immovable alternating voltage of voltage sign pulse or intermittently, for example half-wave (promptly only to comprise one (positive or negative); Each other half-wave " conceals " by means of diode or like in case of necessity) alternating voltage loading coil 4, pump piston 10 is axially being vibrated on the A.At this pump piston periodically around vibrating in stage clip 28,31 and also limits stage clip 18 in case of necessity neutral position.
According to the present invention, two independently parts 11,12 be in operation and only be separated from each other, do not have fixing or dissoluble connection.Only two springs 28,31 guarantee two leaning each other reliably of pump piston parts 11,12 and do not have additional connection measure.
, extrudes piston element 11 fluid that is positioned at cylinder 13 the insides when entering into cylinder 13 the insides.The outlet of the axial hole 26 in these seal 19 closed piston parts 11.Therefore, the fluid of cylinder 13 the insides is attempted to get into connection adapter 20 through the through hole 17 of transverse arm 16, reacts on the pressure of stage clip 22, by means of the fluid that is under the pressure seal 23 is extruded from through hole 17.
When pump piston 10 returns when shaking in the opposite direction, retract piston element 11 from cylinder 13.Residual fluid in these cylinder 13 the insides expands and the result is under the negative pressure.Utilize stage clip 22 and seal 23 sealing through holes 17 thus.Stage clip 22 forms safety check with seal 23, suppresses just to have entered into the backflow that connects the fluid of taking over 20 zones through this safety check.
During retracting piston element 11, in cylinder 13, form negative pressure, this causes seal 19 to lift from the outlet of axial hole 26, and fluid is flow in the cylinder 13 through through hole 26.The fluid of liquid state or gaseous state enters into the inside that armature holds body 6 through adding pipe 34, and enters into the axial hole 26 of piston element 11 through the axial hole 27 of magnet assembly 12.
Backward in the movement process, after cylinder 13 had been filled, the fluid in the cylinder 13 was extruded from cylinder 13 through through hole 17 in piston element 11 travels forward process once more at piston element.
In an illustrated embodiment, the magnet assembly 12 that has a big cross section holds the inwall of body 6 near armature.But the oscillating movement of pump piston 10 need be full of the inner chamber that holds body 6 with emptying armature circularly in the both sides of magnet assembly 12.This be because; In this expansion structure of magnet assembly 12; Hold at magnet assembly 12 and armature between the inwall of body 6 and only have very little gap; Cross-drilled hole 25 is positioned at zone line 24 in this embodiment, therefore guarantee fluid unhinderedly from a side flow of magnet assembly 12 to opposite side, vice versa.
But the function of cross-drilled hole 25 also can other mode realize, for example through vertical hole or cutting in the magnet assembly 12.But the advantage of present embodiment is, the big quantity of magnetism in the action range of coil 4.
By means of stage clip 28,31, pump piston 10 by spring-loaded, in axial motion, is realized the reversing motion of buffering in both sides on each stop, do not have hard backstop thus.Obtain very low noise pump running thus.In addition, this arranges the vibration system that constitutes machinery, and coil 4 needs energy still less so that the mechanical part of to-and-fro motion pump keeps vibration thus.
Because stage clip 31,28 is bearing on each step of pump piston 10, the centering parts that stage clip 28,31 and the intermediate member 24 of the shaft shoulder 32 or middle iso-cross-sections combine and be formed for pump piston 10 simultaneously.
In the multipart embodiment of pump piston 10, the possibility that between magnet assembly 12 and piston element 11, also exists different materials to select.Therefore it is less important or unimportant can aspect sealing function, selecting piston element 11 materials, magnetic property.Therefore, for these parts of pump piston 10, can use magnetic or nonmagnetic substance as required.
Advantageous particularly ground is provided with enough a large amount of magnetic materials in the direct action range of coil 4 in magnet assembly 12.Therefore the material of magnet assembly 12 need not reach the preferable characteristic of the sealing aspect of pump, for example can select material aspect the efficient of pump or the power.
In addition; Two parts or multipart pump piston 10 structures provide the possibility of simple processing in magnet assembly 12 zones, for example constitute axial hole 27 through the magnet assembly 12 of intercepting certain-length from the pipeline section with respective diameters and by the magnetic or the magnetizable material that are fit to.
Therefore, be plunger pump 1 according to pump of the present invention with electromagnetic actuator device 4.For the operation of pump 1, the one way rectifier that is not shown specifically is particularly advantageous.Preferably, favourable rectifier, especially diode or like have been integrated in the pump 1, can on coil connectors, apply general common alternating voltage thus in an advantageous manner.By means of rectifier, by 50 voltage half-waves of alternating voltage per second generation of favourable frequency (for example f=50Hz).
Favourable voltage half-wave mainly causes following processes in pump 1:
A) magnetic action on the pump piston 10:
When applying the voltage half-wave, the electric current that flows through coil 4 produces magnetic field in coil 4, and this magnetic field acts on the piston (major diameter) 10 with electromagnetic force and reacts on piston spring 31.
In order to reach big as far as possible magnetic force, preferably, surround coil 4 by ferromagnetic ring.This ferromagnetic ring is advantageously interrupted by the air gap of several mm lengths in the piston lateral side regions, and piston spring 31 acts on this zone.Above-mentioned two iron parts that possibly form air gap are for example as utmost point cover, and all the other iron hoops are as box yoke plate.
In case electric current begins the magnetic action of mobile and coil magnetic field greater than making piston 10 remain on the power of position of rest, then piston 10 moves on air gap direction.In advantageous embodiments, this piston stroke for example is about 6 to 7mm on the piston spring direction.In case electric current (half-wave) reduces with the relevant therewith magnetic force on piston 10 or piston 10 overlaps air gap to a great extent, then piston spring 31 is also by tensioning farthest.
After the magnetic force of coil 4 reduced largely, piston 10 was owing to the power effect of piston spring 31 is moved on the direction of piston position of rest once more.The kinetic energy of piston 10 is very big, makes piston 10 cross position of rest and continues motion and then advantageously be cushioned spring 28 brakings.For example, this cushion stroke is about 3 to 4mm.Then, damping spring 28 makes piston 10 reversing motions remain on position of rest to the piston position of rest and by means of friction and liquid damping.
B) for example there is not the pumping process of back pressure
Piston 10 has major diameter and minor diameter.Major diameter is used for causing the power effect on air gap direction by means of magnetic field.Minor diameter is as hydraulic pressure piston 11.
In position of rest, hydraulic pressure piston 11 puts in the about 8mm of pressing chamber.Advantageously, this hydraulic pressure piston 11 is hollow 26 at the center or holes.This hole 26 is again by means of valve 19 and stage clip 18 (length) sealing.
When piston 10 moved owing to electromagnetic force, the water of piston 10 back (homonymy of piston spring) advantageously was extruded through excessive piston hole 27 and subsequently through too small piston hole 26.In this process, open the valve 19 in sealing small piston hole 26 and be full of pressing chamber with water.
The power of piston spring 31 begins again to move in the opposite direction in case piston stroke has reached its maximum value and piston 10; The valve 19 that then is positioned on the piston 10 is closed, and makes the pressure piston 11 that is immersed in the pressing chamber the inside extrude the water that is positioned in the pressing chamber through its volume that becomes bigger thus.Because this extrusion process, be arranged in that valve 23 on the pump delivery outlet is opened and from pump 1 discharge water.
Because piston 10 for example can be crossed position of rest by means of damping spring 28 and continues motion owing to its kinetic energy, be immersed in the further expressed water of piston volume of pressing chamber the inside.
In case damping spring 28 moves piston 10 again on the position of rest direction; Valve 23 in the outlet (short spring 22) is closed; And the valve on the piston 10 19 (long spring 18) is opened; Make pressing chamber be full of water once more thus, and the same this process that repeats for a long time with the voltage half-wave that on coil 4, applies.
C) the pump process when the back pressure of for example p=12bar:
As long as on the pump outlet side, for example reduce flow, on the pump delivery outlet, set up corresponding back pressure through throttle valve.The effect of this back pressure is the position of rest when making piston 10 move away p=0bar.
The surface that moves through pressure piston 11 of piston 10, the reaction force that acts on lip-deep pressure of pressure piston and piston spring 31 are confirmed.Back pressure is big more, and the position of rest of piston 10 during from p=0bar is many more movably.Thus, reduced air gap and strengthened the prestressing force (active force of spring 31 in position of rest) of piston spring 31.Because it is littler that air gap has become, spring force strengthens simultaneously, and when applying electric half-wave, piston stroke is not more than the for example 6mm to 7mm when p=0bar, but much little.
The consequence of less piston stroke is that the water of from the pressure chamber, extruding still less.If throttle valve cuts out fully, then piston 10 continues to move from position of rest in each pump stroke, no longer can make piston spring 31 tensions up to electromagnetic force, and piston 10 stops finally.
List of numerals
1 to-and-fro motion pump
2 pump cases
3 yokes
4 coils
5 contacts
6 armature hold body
7 cylinder parts
8 flanges
9 ring shoulders
10 pump pistons
11 piston elements
12 magnet assemblies
13 cylinders
14 galianconism
15 galianconism
16 transverse arms
17 through holes
18 stage clips
19 seals
20 connect adapter
21 support rings
22 stage clips
23 seals
24 intermediate members
25 cross-drilled holes
26 axial holes
27 axial holes
28 stage clips
29 backstop dishes
30 stop members
31 stage clips
32 spaces
33 steps
34 connecting tubes
Claims (9)
1. to-and-fro motion pump; It has pump casing (2); Said to-and-fro motion pump comprises the cylinder (13) of the pump piston unit (10) that is used to hold basic line shifting; It is characterized in that said pump piston unit (10) has at least one and independently is used for the pump parts (11) of pumping pump fluid and the driver part (12) that at least one independently is used for driven pump parts (11).
2. to-and-fro motion pump as claimed in claim 1; It is characterized in that; Said pump parts (11) have first stop member (5) that is used for said driver part (12), and said driver part (12) has second stop member (5) that is used for said pump parts (11).
3. like each described to-and-fro motion pump in the above-mentioned claim, it is characterized in that, be provided with at least one first spring members (28) so that power is loaded on pump piston unit (10) and/or pump parts (11).
4. like each described to-and-fro motion pump in the above-mentioned claim; It is characterized in that; Be provided with at least one second spring members (31) so that power is loaded on pump piston unit (10) and/or driver part (12), wherein the spring force of the spring force of second spring members (31) and first spring members (28) is in the opposite direction.
5. like each described to-and-fro motion pump in the above-mentioned claim, it is characterized in that driver part (12) is made up of ferromagnetic material basically at least.
6. like each described to-and-fro motion pump in the above-mentioned claim, it is characterized in that driver part (12) is made up of special steel basically at least.
7. like each described to-and-fro motion pump in the above-mentioned claim, it is characterized in that pump parts (11) are made up of plastics basically at least.
8. like each described to-and-fro motion pump in the above-mentioned claim, it is characterized in that, be provided with at least one coil that is used to adjust driver part (12) (4).
9. like each described to-and-fro motion pump in the above-mentioned claim, it is characterized in that, be provided with a voltage pulse or intermittence.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102009040698 | 2009-09-09 | ||
| DE102009040698.0 | 2009-09-09 | ||
| PCT/EP2010/005499 WO2011029577A1 (en) | 2009-09-09 | 2010-09-08 | Vibrating armature pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102597517A true CN102597517A (en) | 2012-07-18 |
Family
ID=43063924
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080050415XA Pending CN102597517A (en) | 2009-09-09 | 2010-09-08 | Vibrating armature pump |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20120230847A1 (en) |
| EP (1) | EP2475887A1 (en) |
| CN (1) | CN102597517A (en) |
| DE (1) | DE102010044775A1 (en) |
| WO (1) | WO2011029577A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103615366A (en) * | 2013-10-30 | 2014-03-05 | 江南大学 | Linear driving reciprocating type plunger pump |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20130133909A1 (en) * | 2010-05-25 | 2013-05-30 | Roland Greenwood | Enhanced vibrational or hammering apparatus |
| DE102013107481A1 (en) * | 2013-07-15 | 2015-01-15 | Sysko AG Systeme und Komponenten | Piston for a vibration tank pump |
| DE102013107482A1 (en) * | 2013-07-15 | 2015-01-15 | Sysko AG Systeme und Komponenten | Piston for a vibration tank pump |
| DE102013112306A1 (en) | 2013-11-08 | 2015-05-13 | Pierburg Gmbh | Magnetic pump for an auxiliary unit of a vehicle and method for controlling a magnetic pump for an auxiliary unit |
| WO2016106310A1 (en) * | 2014-12-22 | 2016-06-30 | Eaton Corporation | In-line valve |
| DE102015107207A1 (en) * | 2015-05-08 | 2016-11-10 | Pierburg Gmbh | Magnetic pump for an auxiliary unit of a vehicle |
| DE102016114568A1 (en) | 2016-08-05 | 2018-02-08 | Sysko Ag | Oscillating piston pump device |
| IT201800003069A1 (en) * | 2018-02-27 | 2019-08-27 | Elbi Int Spa | Vibration pump with improved actuation |
| DE102022116097A1 (en) | 2022-06-28 | 2023-12-28 | Sysko AG Systeme & Komponenten | Swing armature pump |
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| DE3934494A1 (en) * | 1988-10-20 | 1990-04-26 | Autobrzdy Jablonec Np | Vehicle electromagnetically-actuated piston pump esp. for heater fuel - incorporates free intake in central aperture of annular pole piece carried on hollow cylindrical support |
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| DE102005048765A1 (en) * | 2005-10-10 | 2007-04-12 | Aweco Appliance Systems Gmbh & Co. Kg | Oscillating anchor pump used in household appliances, e.g. coffee machines comprises a sliding surface formed as a sealing surface for sealing the cylinder of a pump housing during axial displacement of a plunger using a sealing element |
| CN101275543A (en) * | 2007-03-27 | 2008-10-01 | 德昌电机股份有限公司 | Electromagnetic pump |
| CN101427025A (en) * | 2006-04-18 | 2009-05-06 | 惠而浦股份有限公司 | Linear compressor |
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|---|---|---|---|---|
| IT1130947B (en) * | 1980-03-10 | 1986-06-18 | De Dionigi Manlio | IMPROVEMENTS TO ALTERNATIVE ELECTROMAGNETIC PUMPS IN PARTICULAR FOR NON-VISCOUS FLUIDS |
| JPS5797188U (en) * | 1980-12-06 | 1982-06-15 | ||
| EP0605903B1 (en) * | 1993-01-07 | 1997-06-11 | TDK Corporation | Movable magnet type pump |
| DE19932416A1 (en) * | 1999-07-15 | 2001-01-18 | Huber Hans Gmbh Maschinen Und | Device for dewatering sludge |
| CN1133810C (en) * | 2001-02-16 | 2004-01-07 | 郗大光 | Electronic fuel oil jetter |
| ITUD20030162A1 (en) * | 2003-07-30 | 2005-01-31 | Invensys Controls Italy Srl | ELECTROMAGNETIC PUMP WITH OSCILLATING CORE. |
| US20060027097A1 (en) * | 2004-08-03 | 2006-02-09 | Lee Pao C | Composite piston for electromagnetic induction type reciprocating pump |
| US20070248475A1 (en) * | 2006-02-10 | 2007-10-25 | Defond Components Limited | Fluid pump |
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2010
- 2010-09-08 DE DE102010044775A patent/DE102010044775A1/en not_active Withdrawn
- 2010-09-08 CN CN201080050415XA patent/CN102597517A/en active Pending
- 2010-09-08 WO PCT/EP2010/005499 patent/WO2011029577A1/en active Application Filing
- 2010-09-08 US US13/261,210 patent/US20120230847A1/en not_active Abandoned
- 2010-09-08 EP EP10757026A patent/EP2475887A1/en not_active Withdrawn
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| EP0288216B1 (en) * | 1987-04-15 | 1992-04-15 | Eaton S.A.M. | Electrical fluid pump |
| DE3934494A1 (en) * | 1988-10-20 | 1990-04-26 | Autobrzdy Jablonec Np | Vehicle electromagnetically-actuated piston pump esp. for heater fuel - incorporates free intake in central aperture of annular pole piece carried on hollow cylindrical support |
| CN1342246A (en) * | 1999-04-09 | 2002-03-27 | 尤卡有限责任公司 | Composite piston for vibration pump |
| DE102005048765A1 (en) * | 2005-10-10 | 2007-04-12 | Aweco Appliance Systems Gmbh & Co. Kg | Oscillating anchor pump used in household appliances, e.g. coffee machines comprises a sliding surface formed as a sealing surface for sealing the cylinder of a pump housing during axial displacement of a plunger using a sealing element |
| CN2886123Y (en) * | 2006-02-16 | 2007-04-04 | 刘光跃 | Electromagnetic vibration pump |
| CN101427025A (en) * | 2006-04-18 | 2009-05-06 | 惠而浦股份有限公司 | Linear compressor |
| CN101275543A (en) * | 2007-03-27 | 2008-10-01 | 德昌电机股份有限公司 | Electromagnetic pump |
| CN201246292Y (en) * | 2007-08-13 | 2009-05-27 | 刘光跃 | Electromagnetic vibration pump |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103615366A (en) * | 2013-10-30 | 2014-03-05 | 江南大学 | Linear driving reciprocating type plunger pump |
| CN103615366B (en) * | 2013-10-30 | 2016-01-13 | 江南大学 | A kind of linear drives reciprocating plunger pump |
Also Published As
| Publication number | Publication date |
|---|---|
| US20120230847A1 (en) | 2012-09-13 |
| DE102010044775A1 (en) | 2011-03-10 |
| EP2475887A1 (en) | 2012-07-18 |
| WO2011029577A1 (en) | 2011-03-17 |
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Application publication date: 20120718 |