EP2475887A1

EP2475887A1 - Vibrating armature pump

Info

Publication number: EP2475887A1
Application number: EP10757026A
Authority: EP
Inventors: Rudolf Lonski
Original assignee: Vermietungsgemeinschaft Harald Schrott & Sysko AG GbR
Current assignee: Vermietungsgemeinschaft Harald Schrott & Sysko AG GbR
Priority date: 2009-09-09
Filing date: 2010-09-08
Publication date: 2012-07-18
Also published as: WO2011029577A1; DE102010044775A1; CN102597517A; US20120230847A1

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

"Oscillating pump"

The invention relates to a vibrating armature pump with a

Pump housing, which has a cylinder for receiving a in

Substantially linearly adjustable pump piston unit comprises, according to the preamble of claim 1.

State of the art

Vibrating anchorage pumps are characterized by one in one

Movement axis oscillating piston back and forth, which consists at least partially of magnetic or magnetizable material and is driven by an electromagnetic coil.

When immersed in a cylinder, the piston of an oscillating armature pump displaces a fluid located therein, in particular water. When it leaves the cylinder, it is filled with fluid or water again via a piston so that cyclic pumping operations can take place during the oscillation of the pumping process.

For this operation, it is necessary to make the interior of the cylinder fluid dense. This seal must be ensured in each position of the piston, which is why usually a sliding surface is formed as a sealing surface, which also perceives this sealing function in the axial movement of the piston.

Such oscillating armature pumps are for example in the

Publications EP 0 288 216 B1, DE 10 2005 048 765 AI or

CONFIRMATION COPY DE 600 16 905 T2. These vibrating armature pumps disclose composite pistons with a part of a

ferromagnetic, metallic material and a part of a non-metallic and non-ferromagnetic material, wherein the parts are positively and non-positively connected to each other for operation. The connection of the two parts, for example, by squeezing, caulking, rolling,

Clamping, pressing, gluing, welding, shrinking or other types of production are made. Here are, for example, in one part undercuts

provided lock in the corresponding emphasis of the other part when mating.

The disadvantage here, however, is that the production

corresponding undercuts or

Connection process steps consuming and thus cost-intensive.

Purpose and advantages of the invention

The object of the invention is in contrast, a

Oscillating pump with a pump housing, which has a cylinder for receiving a substantially linearly adjustable

Pump piston unit comprises, to propose, which is economically cheaper to produce than the prior art.

This object is achieved on the basis of an oscillating armature pump of the aforementioned type, by the characterizing features of claim 1. The measures mentioned in the dependent claims are advantageous embodiments and

Further developments of the invention possible.

Accordingly, an inventive invention

Schwingankerpumpe characterized in that the pumping piston unit at least one separate pumping element for pumping the

Pump fluid and a separate drive element for driving the pumping element has. This means that in operation according to the invention, two separate or loose elements that are form reciprocating pump piston unit.

Accordingly, the two separate or loose elements of the pump piston unit in operation side by side or

arranged one behind the other without a connection (material or frictional) between the two elements, ie. between the pumping element and the drive element.

With the help of the two separate in operation elements or of the pumping element and the drive element are

Connection process steps or complex, constructive

Arrangements for connecting the two elements superfluous, so that they are omitted according to the invention, which saves corresponding costs. Accordingly, a

Vibrating anchor pump according to the invention are produced particularly economically favorable.

It has surprisingly been found that a connection of the two elements or the separate pumping element and the separate drive element for the proper operation of the vibrating armature pump is not absolutely necessary. Thus, e.g. be dispensed with a squeezing according to EP 0 288 216 Bl or a pressing process according to DE 600 16 905 T2, which means corresponding savings in the production. Above all, economic advantages over this prior art are also achieved in that is dispensed with corresponding recesses or undercuts or the like.

According to the invention, the pump element which is separate during operation and the drive element which is separate during operation are advantageously located loosely next to one another or one behind the other

arranged, i. especially during the outward and

Moving the pump piston unit. For example, planar contact surfaces of the separate pumping element and / or the separate drive element are advantageous for this purpose.

Advantageously, the pumping element has a first stop for the drive element and the drive element has a second stop Stop for the pumping element on. This ensures that a defined contact or a defined contact surface, namely the corresponding stops, are present, whereby a dimensionally accurate pump piston unit can be realized.

For example, the attacks are planer surfaces

formed so that comparatively large forces, especially from the drive element for driving the pumping element between the two in operation separate or loose elements

can be transmitted. Furthermore, effective forces can be transmitted from the pumping element to the separate drive element, for example advantageous restoring forces or the like.

Preferably, at least one first spring element for

Applying force to the pumping piston unit and / or the

Pump element provided. For example, the first one is

Spring element designed such that the drive movement is somewhat slowed down. The drive movement can preferably be generated by at least one electric drive, in particular by an electromagnetic coil. As a result, an advantageous or defined pumping movement or

Drive movement for driving the separate or loose

Pump element realized.

Advantageously, the first spring element ensures that the two loose or separate parts are limited and

are held together or connected, in particular in

Hibernation and during the pumping or the

Pumping movement.

In an advantageous variant of the invention, at least one second spring element for applying force is

Pump piston unit and / or the drive element and / or the first spring element provided, wherein the spring force of the second spring element is directed in an advantageous manner, the spring force of the first spring element. In

Advantageously, the second spring element by means of the drive or the drive unit is tensioned or

pressed together . Advantageously, the second spring element presses or pumps the fluid, ie the spring stroke of the second spring element substantially corresponds to the pumping stroke of the oscillating armature pump according to the invention. Hereby, the second spring element as a return spring for returning the pump piston unit or the two separate in operation elements, ie the separate

Pumping element and the separate drive element, are formed. Here, the spring force of the second acts

Spring element in an advantageous manner as a restoring force for returning the pump piston unit, which is pumped at the same time in an advantageous manner.

Preferably, the drive element consists essentially of a ferromagnetic material. This makes it possible that at least one electromagnetic drive coil or the like, the pumping power and the pumping energy to the

Pumping element of the pump piston unit transmits in an advantageous manner or this is acted upon. It has been shown that a drive of the oscillating armature pump, which can be moved linearly back and forth, or its pumping piston unit, can be produced and operated in a particularly economically favorable manner by means of an electromagnetic coil.

Preferably, the drive element consists essentially of magnetic or magnetizable material, in particular magnetic or magnetizable metal, preferably magnetic or magnetizable stainless steel. In the

Use of stainless steel as the material for the drive element is of particular advantage that this material also does not rust or does not oxidize in liquid media such as water in general. This will be the

Life of the vibrating armature pump according to the invention in

advantageously formed long.

On the other hand, a magnetic or

magnetizable material such as (rusting) steels are used, which are formed, for example, with a surface coverage corresponding corrosion resistant. However, it has been shown that appropriate occupancies or coatings etc. are worn by the reciprocating or swinging of the pumping piston unit, which leads to adverse wear and can expose the rusting material. Rocker armature pumps according to the invention should be able to perform about 40 million strokes or more without adverse effect. This can be achieved in an advantageous manner, especially with a stainless steel as the material for the drive element.

In a particular embodiment of the invention, the pumping element consists essentially of a plastic, wherein above all thermoplastics and / or thermosets, in particular mixtures of the two come into question. It has been shown that corresponding plastics are particularly good

Sliding properties and are also cheap. Especially the sealing function of the pumping element is particularly well realized with an advantageous plastic. For example, as the thermoplastic, polyacetate, PEEK, Vespel or the like and / or thermoset BMC or the like can be used. These plastics are on the one hand resistant to chemicals and / or inexpensive and / or have an advantageous

Slip feature on.

Alternatively, a stainless steel may be used as the material for the pumping element. This material is characterized in the use of the pumping element mainly by the fact that it is resistant to abrasion and corrosion and

dry run resistant and / or temperature resistant.

embodiment

An embodiment of the invention is illustrated in the drawing and will be explained in more detail with reference to FIGS.

Show in detail

Fig. 1 is a schematic longitudinal section through an oscillating armature pump according to the invention and

Fig. 2 is a schematic longitudinal section through an inventive

Schwingankerkolbeneinheit which is arranged between two spring elements.

The oscillating armature pump 1 according to FIG. 1 comprises a

two-part pump housing 2, which is fixed to a yoke 3 of an electromagnetic coil 4.

The pump housing 2 comprises a tubular anchor receptacle 6, which is inserted into the interior of the coil 4 and a

Cylinder part 7, which rests on a flange 8 on the yoke 3.

A pump piston unit or a pump piston 10 is inserted into the pump housing 2 and comprises a pumping element or piston part 11 and a drive element or magnetic part 12. The piston part 11 is tubular with an axial passage and immersed in a cylinder 13, which in the Cylinder part 7 is formed.

The pump piston 10 and thus also the piston part 11

perform cyclical axial displacements during operation

Direction of the double arrow A, i. it oscillates periodically in the axial direction back and forth.

At the side opposite the magnet part 12, the cylinder 13 is closed by a transverse web 16 which has a central passage opening 17. Towards the piston side, a compression spring 18 is supported on the transverse web 16, which presses a sealing body 19 onto the outlet of the tubular body

Piston part 11 presses.

On the opposite side of the piston 11 of the cross bar 16, the cylinder part 7 is tubularly extended and forms at its outer end the pressure-side connecting piece 20 of the vibrating anchor pump 1. A support ring 21 is in the Inserted connecting piece 20 and forms a stop for a further compression spring 22, which presses a sealing body 23 to the crossbar 16 and thereby the passage opening 17th

closes.

The pump piston 10 is starting from the piston part 11 in

Direction to the magnet part 12 with a two-stage

Cross-sectional extension provided. The piston part 11 with a small cross-section thus closes an intermediate part 24 with an average cross section and the magnetic part 12 with a large one

Cross section. In the intermediate part 24 has a transverse bore 25 is attached to the axial passages 26, 27 of the

Piston part 11 on the one hand and magnetic part 12 on the other hand in conjunction.

A first compression spring 28 surrounds the intermediate part 24 and is supported on the gradation of the piston part 11 with a large cross section on one side. Here, a web 14 is provided, which advantageously a radial

Centering of the piston member 11 with respect to the magnetic part 12 ensured. The two parts 11, 12 also have a contact 5 and respectively an axial contact surface on which the two parts 11, 12 touch.

On the opposite side, the compression spring 28 is supported on a stop plate 29 which between the

Anchor receptacle 6 and the cylinder part 7 of the pump housing 2 is inserted.

On the side opposite the piston part 11, the magnetic part 12 has a recess 32, so that a web 15 is formed. A second compression spring 31 is supported on the recess 32, wherein the compression spring 31 is radially held or centered by the web 15.

On the opposite side of the compression spring 31, this is applied to a gradation 33 of the anchor seat 6. The

Anchor receptacle 6 comprises a stop 30 and is extended out of the coil 4 and forms at its end a Connector sleeve 34 for connecting a supply line.

The vibration tank pump 1 operates as follows.

By applying the coil 4 with alternating current or advantageously with a pulsating or

intermittent voltage without sign change, such as with only one (positive or negative) half-waves (i.e., the other half-waves are possibly "hidden" by means of a diode or the like)

AC voltage, the pump piston 10 is set in vibration in the axial direction A. It oscillates periodically by a defined by the compression springs 28, 31 and possibly also the compression spring 18 neutral position.

According to the invention, the two separate parts 11, 12 are in operation only loosely together without a fixed or

permanent connection exists. Only the two springs 28, 31 ensure reliable Anexnanderliegen the two pump piston parts 11, 12 without additional

Related activities.

Upon penetration of the piston member 11 in the cylinder 13, the fluid contained in the cylinder 13 is displaced. Here, the sealing body 19 closes off the outlet opening of the axial passage 26 in the piston part 11. The cylinder 13

As a result, fluid located seeks its way through the passage opening 17 of the cross bar 16 in the

Connecting piece 20, wherein the sealing body 23 is pressed against the pressure of the compression spring 22 from the through hole 17 by the pressurized fluid.

When swinging back the pump piston 10 in the opposite direction, the piston member 11 withdraws from the cylinder 13 back. The residual fluid contained in the cylinder 13 is thereby expanded and placed in the further consequence under negative pressure. As a result, the passage opening 17 is closed by means of the compression spring 22 and the sealing body 23. The compression spring 22 and the sealing body 23 form a check valve, through which the Reflux of once reached in the region of the connecting piece 20 fluid is prevented.

During the retraction of the piston part 11, a negative pressure forms in the cylinder 13, which causes the sealing body 19 to lift off the outlet of the axial passage 26, so that fluid flows through the passage 26 into the cylinder 13. The liquid or gaseous Fuid passes via the inlet nozzle 34 into the interior of the anchor receptacle 6 and through de axial passage 27 of the agnetteils 12 to the axial passage 26 of the piston member 11th

After the cylinder 13 in the backward movement of

Piston part 11 was filled, which is in the cylinder 13th

fluid in the forward movement of the piston member 11 in turn displaced from the cylinder 13 through the passage opening 17.

In the illustrated embodiment, the magnetic member 12 is located with its large cross-section close to the inner wall of the armature receptacle 6. However, the oscillatory motion of the pump piston 10 requires the cyclic filling and emptying of the interior of the armature receptacle 6 on both sides of the magnetic member 12. Since in this embodiment of the magnetic member 12 only a very small gap between the magnet part 12 and inner wall of the armature receptacle 6 is present, is located in this

Embodiment, the transverse bore 25 in the intermediate region 24, so that unimpeded fluid flow from one side of the

Magnet part 12 is ensured on the other and vice versa

However, the function of the transverse bore 25 can also be otherwise, for example, by longitudinal holes or notches in

Magnet part 12 can be realized. The present

However, the embodiment offers the advantage of a large magnetic mass in the area of action of the coil 4.

Due to the two-sided spring mounting of the pump piston 10 by means of the compression springs 28, 31 occurs at start-up at each dead center in the axial movement, a spring-return of the Movement, so that no hard stop takes place. This results in a very quiet running of the pump. In addition, this arrangement is a mechanically oscillatory system, so that less energy is required by the coil 4 to the mechanical components of the

Oscillating rocker pump to keep in vibration.

By supporting the compression springs 31, 28 at the respective gradations of the pump piston 10, the compression springs 28, 31 in conjunction with the extension 32 and the intermediate part 24 with a central cross section at the same time centering for the

Pump piston 10.

In a multi-part design of the pump piston 10, there is still the possibility of different choice of material between the magnetic part 12 and piston part 11. The choice of material in the piston part 11 can thus with regard to

Sealing function can be selected, with the magnetic

Properties a subordinate or no role at all

play. For this part of the pump piston 10 can therefore be magnetic or non-magnetic as needed

Materials are used.

Of particular advantage is that in the magnetic part 12 in

Immediately effective range of the coil 4 a sufficiently large mass of magnetic material is arranged. At the material of the magnetic member 12 no significant properties in terms of tightness of the pump are made, so that at this point, for example, a

Material selection can be made in terms of efficiency or performance of the pump.

In addition, the two- or multi-part design of the pump piston 10 in the region of the magnetic member 12 which

Possibility of a simple production, for example by cutting the magnetic part 12 of a piece of pipe with

corresponding diameter and axial passage 27 from

suitable magnetic or magnetizable material. Accordingly, the pump according to the invention is a piston pump 1 with electromagnetic drive 4. For the operation of the pump 1 is advantageously not shown in detail

Half-wave rectification of particular advantage. An advantageous rectifier, in particular a diode or the like, is

preferably already integrated in the pump 1, so that in an advantageous manner to the coil terminals a geng. Conventional alternating voltage can be applied. In an advantageous alternating voltage with a frequency of e.g. f = 50 Hz 50 half-waves per second are generated by means of the rectifier.

An advantageous voltage half-wave causes in the pump 1, in particular the following operations: a) magnetic effect on the pump piston 10:

The current flowing through the coil 4 during the application of a voltage half-wave generates a magnetic field in the coil 4 which acts as an electromagnetic force on the piston 10 (large

Diameter) and against the piston spring 31 acts.

In order to achieve the greatest possible magnetic force effect, the coil 4 is preferably surrounded by an iron circle.

This iron circle is interrupted in the region of the piston side, against which the piston spring 31 acts, advantageously by an air gap of a few millimeters in length. The two pieces of iron which form the air gap may e.g. be named as Polhülsen and the remaining iron circle as Kastenjochblech.

As soon as the current begins to flow and the magnetic

Effect of the coil field is greater than the force with which the piston 10 is held in the rest position, the piston 10 moves in the direction of the air gap. In an advantageous embodiment, this piston stroke in the direction of the piston spring, for example, about 6 to 7 mm. As soon as the current (half wave) and thus the magnetic force action on the piston 10 drops or the piston 10 has largely bridged the air gap and the piston spring 31 is maximally tensioned. After the magnetic force effect of the coil 4 has largely dropped, the piston 10 moves due to the

Force action of the piston spring 31 again in the direction of

Piston rest position. The kinetic energy of the piston 10 is so great that the piston 10 continues to move beyond the rest position and is now braked in an advantageous manner by the damping spring 28. For example, this damped stroke is about 3 to 4 mm. The damping spring 28 then moves the piston 10 back in the direction of Kolbenruhelage and oscillates in the rest position as a function of friction and

Fluid damping again. b) pumping e.g. without counter pressure

The piston 10 has a large and a small diameter. The large diameter is used by means of a

Magnetic field to cause a force in the direction of the air gap. The small diameter serves as a hydraulic

Pressure piston 11.

The hydraulic pressure piston 11 protrudes in the rest position about 8 mm into a compression chamber. This hydraulic

Plunger 11 is advantageously hollow in the middle 26 or drilled. This bore 26 is in turn with a

Valve 19 and a compression spring 18 (long) closed.

Moves the piston 10 due to the electromagnetic force, so that is behind the piston 10 (side of

Piston spring) located water in an advantageous manner by the large piston bore 27 and then pressed through the small piston bore 26. In this process, opens the, the small piston bore 26 closing valve 19 and the compression chamber is filled with water.

As soon as the piston stroke has reached its maximum and the piston 10 begins to move in the opposite direction again due to the force of the piston spring 31, the valve located on the piston 10 closes 19, so that in the

Compression chamber immersed pressure piston 11 with his Increasing volume displaces the water located there. Due to this displacement operation, the valve located at the pump outlet 23 opens and the water exits from the pump 1.

Because the piston 10 due to its kinetic energy is e.g. because of the damping spring 28 can move beyond the rest position even this will also displace water into the compression chamber plunger volume.

As soon as the damping spring 28 moves the piston 10 again in the direction of the rest position, the valve 23 closes at the outlet (short spring 22) and the valve 19 on the piston 10 (long spring 18) opens, so that the compression chamber is filled with water again and the Process is repeated as long as

Voltage half-waves abut the coil 4. c) pumping at a back pressure of e.g. p = 12 bar:

Once at the pump outlet side, the flow

is reduced, for example, with a throttle, a corresponding back pressure builds up at the pump outlet. This

Counterpressure causes the piston 10 is displaced from its rest position at p = 0 bar.

The displacement of the piston 10 is determined by the surface of the pressure piston 11, the pressure acting on the pressure piston surface and the counteracting force of the piston spring 31. The greater the back pressure, the more the piston 10 is moved from its rest position at p = 0 bar. This reduces the air gap and the bias of the piston spring 31 (force of the spring 31 in the rest position) is larger. Because the air gap has become smaller and at the same time the spring force is larger, when applying the electrical half wave of the

Piston stroke no longer e.g. 6 mm to 7 mm as at p = 0 bar, but much smaller.

The smaller piston stroke has the consequence that less water is displaced in the pressure chamber. Will the throttle completely

closed, the piston 10 continues with each pump stroke moved from the rest position until the electromagnetic force no longer allows tensioning of the piston spring 31 and the piston 10 finally comes to the voice.

LIST OF REFERENCE NUMBERS

1 vibration tank pump

2 pump housings

3 yoke

4 coil

5 contact

6 anchorage

7 cylinder part

8 flange

9 ring shoulder

10 pump pistons

11 piston part

12 agnetteil

13 cylinders

14 footbridge

15 footbridge

16 crossbar

17 passage opening

18 compression spring

19 sealing body

20 connecting pieces

21 support ring

22 compression spring

23 sealing bodies

24 intermediate part

25 cross bore

26 axial passage

27 axial passage

28 compression spring

29 Stop disc

30 stop

31 compression spring

32 recess

33 gradation

34 connection grommet

Claims

claims

An oscillating armature pump comprising a pump housing (2) including a cylinder (13) for receiving a substantially linear one

adjustable pump piston unit (10), characterized

in that the pump piston unit (10) has at least one separate pump element (11) for pumping the pump fluid and a separate drive element (12) for driving the pump

Pump element (11).

2. vibration pump according to claim 1, characterized in that the pumping element (11) has a first stop (5) for the drive element (12) and the drive element (12) a

Having second stop (5) for the pumping element (11).

3. vibrating armature pump according to one of the preceding claims, characterized in that at least a first

Spring element (28) for applying force to the

Pump piston unit (10) and / or the pumping element (11) is provided.

4. vibrating tank pump according to one of the preceding claims, characterized in that at least a second

Spring element (31) for applying force to the

Pump piston unit (10) and / or the drive element (12) is provided, wherein the spring force of the second

Spring element (31) of the spring force of the first spring element (28) is directed opposite.

5. vibration pump according to one of the preceding claims, characterized in that at least the drive element (12) consists essentially of a ferromagnetic material.

6. vibration pump according to one of the preceding claims, characterized in that at least the drive element (12) consists essentially of stainless steel.

7. vibration pump according to one of the preceding claims, characterized in that at least the pumping element (11) consists essentially of a plastic.

8. vibration pump according to one of the preceding claims, characterized in that at least one coil (4) for adjusting the drive element (12) is provided.

9. vibration pump according to one of the preceding claims, characterized in that a pulsating or

intermittent voltage is provided.