DE102010044775A1 - The vibration pump - Google Patents

Abstract

It is an oscillating armature pump with a pump housing, which comprises a cylinder for receiving a substantially linearly adjustable pump piston unit (10) proposed, which is economically cheaper to produce than the prior art. This is inventively achieved in that the pump piston unit (10) has at least one separate pumping element (11) for pumping the pumping fluid and a separate drive element (12) for driving the pumping element (11).

Description

The invention relates to a vibration pump with a pump housing, which comprises a cylinder for receiving a substantially linearly adjustable pump piston unit, according to the preamble of claim 1.

State of the art

Vibrating armature pumps are characterized by a piston swinging back and forth in a movement axis, which at least partially consists 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 mode of 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 A1 or DE 600 16 905 T2 described. These oscillating 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 can be made for example by squeezing, caulking, rolling, clamping, pressing, gluing, welding, shrinking or other types of production. In this case, undercuts are provided, for example, in one part, engage in the corresponding emphasis of the other part when mating.

The disadvantage here, however, is that the production of corresponding undercuts or connection process steps consuming and thus economically expensive.

Purpose and advantages of the invention

The object of the invention is in contrast to propose a vibrating armature pump with a pump housing comprising a cylinder for receiving a substantially linearly adjustable pumping piston unit, 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 advantageous embodiments and developments of the invention are possible.

Accordingly, an oscillating armature pump according to the invention is characterized in that the pumping piston unit has at least one separate pumping element for pumping the pumping fluid and a separate drive element for driving the pumping element. This means that, in operation according to the invention, two separate or loose elements forming the reciprocating pump piston unit. Accordingly, the two separate or loose elements of the pump piston unit are arranged side by side or one behind the other in operation without a (material-fit or frictional or non-detachable) connection between the two elements, ie. H. 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 connecting process steps or complex, constructive arrangements for connecting the two elements superfluous, so that it is omitted according to the invention, which saves corresponding costs. Accordingly, an oscillating armature pump according to the invention can be 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, z. B. on a squeezing according to EP 0 288 216 B1 or a pressing process according to DE 600 16 905 T2 be omitted, which means corresponding savings in 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 separate during operation are advantageously arranged loosely next to one another or one behind the other, ie in particular also during the reciprocating movement of the pump piston unit. For example, these are flat contact surfaces of the separate pumping element and / or the separate drive element of advantage.

Advantageously, the pumping element has a first stop for the drive element and the drive element has a second stop for the pumping element. 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 stops are designed as planar surfaces, 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 is provided for applying force to the pumping piston unit and / or the pumping element. For example, the first spring element is 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 pumping element can be realized.

Advantageously, this ensures that the first spring element that the two loose or separate parts are limited and held together or connected, in particular in the idle state and during the pumping or the pumping movement.

In an advantageous variant of the invention, at least one second spring element is provided for applying force to the pump piston unit and / or the drive element and / or the first spring element, wherein the spring force of the second spring element is advantageously directed counter to the spring force of the first spring element. Advantageously, the second spring element is tensioned or compressed by means of the drive or the drive unit.

Advantageously, the second spring element pushes or pumps the fluid, d. H. 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, d. H. the separate pumping element and the separate drive element, are formed. In this case, the spring force of the second spring element acts in an advantageous manner as a restoring force for returning the pump piston unit, being pumped at the same time advantageously in resetting.

Preferably, the drive element consists essentially of a ferromagnetic material. This makes it possible for at least one electromagnetic drive coil or the like to transfer the pumping force or the pumping energy to the pumping element of the pumping piston unit in an advantageous manner or to act on it. 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. When using stainless steel as the material for the drive element is of particular advantage that this material also in liquid media such as water in general does not rust or not oxidized. As a result, the life of the vibrating armature pump according to the invention is formed advantageously long.

On the other hand, a magnetic or magnetizable material such as (rusting) steels could certainly be used, the z. B. be formed with a surface coverage correspondingly resistant to corrosion. However, it has been found that appropriate occupancies or coatings etc. are worn away by the reciprocation or oscillation of the pumping piston unit, which leads to disadvantageous 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 have 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. On the one hand, these plastics are resistant to chemicals and / or inexpensive and / or have an advantageous sliding property.

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

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

2 a schematic longitudinal section through an oscillating armature piston unit according to the invention, which is arranged between two spring elements.

The vibration tank pump 1 according to the 1 includes a two-piece pump housing 2 at a yoke 3 an electromagnetic coil 4 is attached.

The pump housing 2 includes a tubular anchor receptacle 6 that go into the interior of the coil 4 is plugged in and a cylinder part 7 that has a flange 8th at the yoke 3 is applied.

A pump piston unit or a pump piston 10 is in the pump housing 2 inserted and includes 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 one in the cylinder part 7 is trained.

The pump piston 10 and thus also the piston part 11 perform cyclic axial displacements in operation in the direction of the double arrow A, ie it oscillates periodically in the axial direction back and forth.

At the magnet part 12 opposite side is the cylinder 13 through a crossbar 16 closed, which has a central passage opening 17 having. The piston side is supported on the cross bar 16 a compression spring 18 starting with a sealing body 19 on the outlet of the tubular piston part 11 suppressed.

On the piston 11 opposite side of the crosspiece 16 is the cylinder part 7 elongated tubular and forms at its outer end the pressure-side connecting piece 20 the vibration tank pump 1 , A support ring 21 is in the connecting piece 20 inserted and forms a stop for another compression spring 22 that is a sealing body 23 to the crossbar 16 presses while the through hole 17 closes.

The pump piston 10 is starting from the piston part 11 towards the magnet part 12 provided with a two-stage cross-sectional widening. At the piston part 11 with a small cross-section thus closes an intermediate part 24 with medium cross section and the magnetic part 12 with a large cross section. In the middle part 24 is a cross hole 25 attached to the axial passages 26 . 27 of the piston part 11 on the one hand and magnetic part 12 on the other hand.

A first compression spring 28 encloses the intermediate part 24 and relies on the gradation of the piston part 11 with large cross-section on one side. Here is a jetty 14 provided, which advantageously has a radial centering of the piston part 11 regarding the magnetic part 12 guaranteed. The two parts 11 . 12 also have a contact 5 or in each case an axial contact surface on which the two parts 11 . 12 touch.

On the opposite side is the compression spring 28 on a stop disc 29 supported between the anchor seat 6 and the cylinder part 7 of the pump housing 2 is used.

On the piston part 11 opposite side has the magnetic part 12 a recess 32 on, leaving a jetty 15 is formed. A second compression spring 31 rests on the recess 32 from, with the compression spring 31 through the footbridge 15 is held radially or centered.

On the opposite side of the compression spring 31 this is due to a gradation 33 the anchor seat 6 at. The anchor seat 6 includes a stop 30 and is out of the coil 4 extends out and forms at its end a connector grommet 34 for connecting a supply line.

The vibration tank pump 1 works as follows.

By applying the coil 4 with alternating current or advantageously with a pulsating or intermittent voltage without sign change, such. B. with only one (positive or negative) half-waves (ie, the other half-waves are possibly by means of a diode or the like "hidden") comprehensive AC voltage, the pump piston 10 oscillated in the axial direction A. He oscillates periodically to one by the springs 28 . 31 and optionally also the compression spring 18 defined neutral position.

According to the invention, the two separate parts 11 . 12 in operation only loosely together, without a fixed or permanent connection exists. Only the two springs 28 . 31 ensure the reliable juxtaposition of the two pump piston parts 11 . 12 without additional connection measures.

Upon penetration of the piston part 11 in the cylinder 13 will that be in the cylinder 13 displaced fluid displaced. This closes the sealing body 19 the exit opening of the axial passage 26 in the piston part 11 from. That in the cylinder 13 As a result, fluid located seeks its way through the passage opening 17 of the crossbar 16 in the connecting piece 20 , wherein the sealing body 23 against the pressure of the compression spring 22 from the passage opening 17 is pushed away by the pressurized fluid.

When swinging back the pump piston 10 in the opposite direction, the piston part pulls 11 out of the cylinder 13 back. That in the cylinder 13 Residual fluid is thereby relaxed and placed in the subsequent sequence under negative pressure. As a result, the passage opening 17 by means of the compression spring 22 and the sealing body 23 locked. The compression spring 22 and the sealing body 23 form a check valve, through which the return flow of the once in the area of the connecting piece 20 reached fluid is prevented.

During the retraction of the piston part 11 forms in the cylinder 13 a negative pressure, which causes the sealing body 19 from the exit of the axial passage 26 lifts off, allowing fluid through the passage 26 in the cylinder 13 nachströmt. The liquid or gaseous Fuid passes over the inlet nozzle 34 inside the anchorage 6 as well as through the axial passage 27 of the magnetic part 12 for axial passage 26 of the piston part 11 ,

After the cylinder 13 in the backward movement of the piston part 11 is filled, that is in the cylinder 13 located fluid in the forward movement of the piston member 11 turn out of the cylinder 13 through the passage opening 17 repressed.

In the illustrated embodiment, the magnetic part is located 12 with its large cross section close to the inner wall of the anchor seat 6 , The oscillation movement of the pump piston 10 However, requires the cyclic filling and emptying of the interior of the anchor receptacle 6 on both sides of the magnet part 12 , As in this embodiment of the magnetic part 12 only a very small gap between the magnetic part 12 and inner wall of the anchor receptacle 6 is present, is located in this embodiment, the transverse bore 25 in the intermediate area 24 , allowing unimpeded fluid flow from one side of the magnet part 12 is guaranteed to the other and vice versa.

The function of the cross hole 25 However, it can also be otherwise, for example by longitudinal bores or notches in the magnet part 12 be realized. However, the present embodiment offers the advantage of a large magnetic mass in the range of effect of the coil 4 ,

Due to the double-sided spring mounting of the pump piston 10 by means of the compression springs 28 . 31 During springing to each dead center in the axial movement, a spring-loaded reversal of the movement takes place 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 from the coil 4 is required to keep the mechanical components of the oscillating armature pump in vibration.

By supporting the compression springs 31 . 28 at the respective gradations of the pump piston 10 form the compression springs 28 . 31 in connection with the extension 32 or the intermediate part 24 Center 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 material selection between magnetic part 12 and piston part 11 , The material selection at the piston part 11 can thus be selected with regard to the sealing function, wherein the magnetic properties play a minor or no role. For this part of the pump piston 10 Accordingly, magnetic or non-magnetic materials can be used as needed.

Of particular advantage is that in the magnetic part 12 in the immediate area of effect of the coil 4 a sufficiently large mass of magnetic material is arranged. To the material of the magnetic part 12 no appreciable properties in terms of tightness of the pump are made, so that at this point, for example, a choice of materials in terms of efficiency or performance of the pump can be made.

In addition, the two- or multi-part design of the pump piston offers 10 in the area of the magnetic part 12 the possibility of a simple production, for example by cutting to length of the magnetic part 12 from a pipe section with a corresponding diameter and axial passage 27 Made of suitable magnetic or magnetizable material.

Consequently, the pump according to the invention is a piston pump 1 with electromagnetic drive 4 , For the operation of the pump 1 is advantageously a non-illustrated half-wave rectification of particular advantage. An advantageous rectifier, in particular a diode or the like, is preferably already in the pump 1 integrated, so that in general an advantageous AC voltage can be applied to the coil terminals. In an advantageous AC voltage with a frequency of z. B. f = 50 Hz are using the rectifier per second 50 Voltage half waves generated.

An advantageous voltage half-wave causes in the pump 1 especially the following processes:

a) magnetic effect on the pump piston 10 :

The when applying a voltage half-wave through the coil 4 flowing electricity is generated in the coil 4 a magnetic field acting 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 is 4 preferably surrounded by an iron circle. This iron circle is in the area of the piston side, against which the piston spring 31 acts, advantageously interrupted by an air gap with a few millimeters in length. The two iron parts which can form the air gap z. B. can be named as Polhülsen and the remaining iron circle as Kastenjochblech.

As soon as the current begins to flow and the magnetic field of the coil field becomes greater than the force with which the piston is energized 10 is held in the rest position, the piston moves 10 in the direction of the air gap. In an advantageous embodiment, this piston stroke in the direction of the piston spring z. B. about 6 to 7 mm. Once the current (half-wave) and thus the magnetic force on the piston 10 drops or the piston 10 The air gap has largely bridged is also the piston spring 31 maximum tension.

After the magnetic force of the coil 4 has largely fallen off, the piston moves 10 due to the force effect of the piston spring 31 again in the direction of the Kolbenruhelage. The kinetic energy of the piston 10 is so big that the piston 10 beyond the rest position further moves and now in an advantageous manner by the damping spring 28 is slowed down. For example, this damped stroke is about 3 to 4 mm. The damping spring 28 moves the piston 10 Then back to the direction of the piston rest position and swing back into the rest position as a function of friction and fluid damping.

b) pumping z. B. without back pressure

The piston 10 has a large and a small diameter. The large diameter is used to cause a force in the direction of the air gap by means of a magnetic field. 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 pressure piston 11 is advantageously hollow in the middle 26 or bored. This hole 26 is in turn with a valve 19 and a compression spring 18 closed (long).

Moves the piston 10 because of the electromagnetic force, it will be behind the piston 10 (Side of the piston spring) located water in an advantageous manner by the large piston bore 27 and then through the small piston bore 26 pressed. In this process, that opens, the small piston bore 26 closing valve 19 and the compression chamber is filled with water.

Once the piston stroke has reached its maximum and the piston 10 due to the force of the piston spring 31 again begins to move in the opposite direction, that closes on the piston 10 located valve 19 so that the plunger dipping into the compression chamber 11 with its increasing volume displaces the water located there. Due to this displacement process, the valve located at the pump outlet opens 23 and the water comes out of the pump 1 out.

Because the piston 10 due to its kinetic energy z. B. because of the damping spring 28 can move beyond the rest position even further, this piston plunging into the compression chamber will additionally displace water.

Once the damping spring 28 the piston 10 moved back towards the rest position, the valve closes 23 at the exit (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 on the coil 4 issue.

c) pumping at a back pressure of z. Eg p = 12 bar:

As soon as the flow on the pump outlet side is reduced, for example with a throttle, a corresponding back pressure builds up at the pump outlet. This back pressure causes the piston 10 is shifted from its rest position at p = 0 bar.

The displacement of the piston 10 is determined by the area 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 becomes 10 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) gets bigger. Because the air gap has become smaller and at the same time the spring force is greater, the piston stroke is no longer z when applying the electrical half-wave. B. 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. If the throttle is completely closed, then the piston 10 at each pump stroke further from the rest position moves until the electromagnetic force no tensioning of the piston spring 31 allows more and the piston 10 finally comes to the vote.

LIST OF REFERENCE NUMBERS

1

The vibration pump

2

pump housing

3

yoke

4

Kitchen sink

5

Contact

6

anchor recording

7

cylinder part

8th

flange

9

annular shoulder

10

pump pistons

11

piston part

12

magnetic part

13

cylinder

14

web

15

web

16

crosspiece

17

Through opening

18

compression spring

19

sealing body

20

spigot

21

support ring

22

compression spring

23

sealing body

24

intermediate part

25

cross hole

26

axial passage

27

axial passage

28

compression spring

29

stop disc

30

attack

31

compression spring

32

recess

33

gradation

34

connection nozzle

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 0288216 B1 [0005, 0011]
• DE 102005048765 A1 [0005]
• DE 60016905 T2 [0005, 0011]

Claims (9)

Oscillating pump with a pump housing ( 2 ), which has a cylinder ( 13 ) for receiving a substantially linearly adjustable pump piston unit ( 10 ), characterized in that the pump piston unit ( 10 ) at least one separate pumping element ( 11 ) for pumping the pumping fluid and a separate drive element ( 12 ) for driving the pumping element ( 11 ) having. Oscillating tank pump according to claim 1, characterized in that the pumping element ( 11 ) a first stop ( 5 ) for the drive element ( 12 ) and the drive element ( 12 ) a second stop ( 5 ) for the pumping element ( 11 ) having. Vibrating anchor pump according to one of the preceding claims, characterized in that at least one first spring element ( 28 ) for applying force to the pump piston unit ( 10 ) and / or the pumping element ( 11 ) is provided. Oscillating pump according to one of the preceding claims, characterized in that at least one 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. Vibrating anchor pump according to one of the preceding claims, characterized in that at least the drive element ( 12 ) consists essentially of a ferromagnetic material. Vibrating anchor pump according to one of the preceding claims, characterized in that at least the drive element ( 12 ) consists essentially of stainless steel. Vibrating anchor pump according to one of the preceding claims, characterized in that at least the pumping element ( 11 ) consists essentially of a plastic. Oscillating pump according to one of the preceding claims, characterized in that at least one coil ( 4 ) for adjusting the drive element ( 12 ) is provided. Oscillating tank pump according to one of the preceding claims, characterized in that a pulsating or intermittent voltage is provided.

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